Distributed high-efficiency energy-saving phase change heat storage system

Abstract

This invention relates to the field of phase change thermal energy storage, and more particularly to a distributed, high-efficiency, energy-saving phase change thermal energy storage system, comprising: a phase change thermal energy storage unit, which includes a heat collection chamber, a heat pump disposed on the outer wall of the heat collection chamber, a plurality of manifolds connected to the heat collection chamber, a liquid level sensor disposed on the side wall of one of the manifolds, and an electric heating plate disposed on the inner wall of the thermal energy storage unit; a heat exchange unit, which includes a heat exchanger connected to the heat collection chamber via a first delivery pipe, and a second delivery pump connected to the heat exchanger; a cooling unit, which includes a cooling plate disposed at the bottom of the cooling chamber, and a cylinder disposed inside the cooling chamber; and a transport unit, which includes a transport box disposed below the mold, a pressure sensor disposed at the bottom of the inner wall of the transport box, a transport pipe connected to the heat collection chamber, and a negative pressure fan disposed inside the heat collection chamber.

Description

Technical Field

[0001] This invention relates to the field of phase change thermal energy storage, and more particularly to a distributed, high-efficiency, and energy-saving phase change thermal energy storage system. Background Technology

[0002] Existing thermal energy storage systems often suffer from severe energy loss and low energy storage efficiency. Phase change thermal energy storage technology, on the other hand, offers advantages such as high energy density, strong stability, no permanent energy decay, and high reliability. However, current research on phase change thermal energy storage is still in its early stages, with issues including slow thermal conductivity of phase change materials, uneven distribution of heat exchange tubes embedded within the phase change material, and significant temperature changes in the phase change material before or after the phase change, leading to substantial loss rates.

[0003] Chinese patent CN107388337B provides a distributed, high-efficiency, energy-saving phase change thermal energy storage system, including a thermal storage loop and an output loop composed of a phase change thermal energy storage body, a heat exchanger, and an electric heater. The thermal storage loop includes a new energy heating mode and an electric heating mode. In the new energy heating mode, the phase change thermal energy storage body and the heat exchanger are connected to form a thermal storage cycle. In the electric heating mode, the phase change thermal energy storage body and the electric heater are connected to form a thermal storage cycle. The system is flexible in layout, occupies little space, has a large heat storage capacity, and allows for rapid and convenient heat storage / use. However, there is a problem that the phase change material undergoes multiple phase changes in the same space, resulting in some crystals at the bottom of the thermal storage device that cannot liquefy, leading to insufficient utilization of the phase change material and low thermal storage efficiency. Summary of the Invention

[0004] To address this issue, the present invention provides a distributed, high-efficiency, and energy-saving phase change thermal storage system, which can solve the problem that due to the phase change material undergoing multiple phase changes in the same space, some crystals at the bottom of the thermal storage device cannot be liquefied, resulting in insufficient utilization of the phase change material and low thermal storage efficiency.

[0005] To achieve the above objectives, the present invention provides a distributed, high-efficiency, energy-saving phase change thermal energy storage system, comprising:

[0006] A phase change thermal energy storage unit includes a heat collection chamber, a heat pump disposed on the outer wall of the heat collection chamber for providing heat to the phase change material, several manifolds connected to the heat collection chamber for storing liquid phase change material, a liquid level sensor disposed on the side wall of one of the manifolds for real-time acquisition of the maximum liquid level height in each manifold and the rate of change of liquid level height in each manifold, a thermal energy storage chamber connected to each manifold, and several electric heating plates disposed on the inner wall of the thermal energy storage chamber for heat compensation of the phase change material.

[0007] A heat exchange unit includes a heat exchanger connected to the heat collection chamber via a first delivery pipe, a second delivery pump connected to the heat exchanger for controlling the solid-liquid mixture of the phase change material that has completed heat exchange to leave the heat exchanger, and a second delivery pipe connected to the second delivery pump for transporting the solid-liquid mixture of the phase change material.

[0008] The cooling unit includes a cooling chamber connected to the second conveying pipe, a cooling plate disposed at the bottom of the cooling chamber for absorbing heat from the phase change material, and a cylinder disposed inside the cooling chamber for driving a plurality of compression rods connected to the cylinder to compress the phase change material so that the phase change material enters the mold.

[0009] The transport unit includes a transport box located below the mold, a pressure sensor located at the bottom of the inner wall of the transport box for acquiring the gravity of the phase change material, a conveying device located below the transport box for driving the transport box, a transport pipe connected to the heat collection chamber for transporting the phase change material in the transport box to the heat collection chamber, and a negative pressure fan located in the heat collection chamber for providing suction to the transport pipe.

[0010] The central control unit includes:

[0011] A heat storage regulation module, which is connected to the phase change heat storage unit, is used to determine whether to start the heat pump and obtain the heat output of the heat pump based on the maximum liquid level height in each of the manifolds obtained in real time by the liquid level sensor, and to obtain the operating power of each of the heating plates based on the rate of change of the liquid level height in each of the manifolds.

[0012] A circulation adjustment module, which is connected to the heat storage adjustment module, the heat exchange unit and the cooling unit respectively, is used to obtain the real-time pump pressure of the second delivery pump according to the operating power of each of the electric heating plates, obtain the cooling capacity of the cooling chip according to the real-time pump pressure of the second delivery pump, and obtain the operating cycle of the cylinder according to the cooling capacity of the cooling chip.

[0013] A transport control module, which is connected to the cycle adjustment module and the transport unit respectively, is used to obtain the solid design gravity inside the transport box according to the operating cycle of the cylinder.

[0014] Furthermore, the heat storage regulating module determines to start the heat pump under the first liquid level condition, and determines not to start the heat pump under the second liquid level condition;

[0015] Wherein, the first liquid level height condition is that the maximum liquid level height in each of the manifolds, as obtained in real time by the liquid level sensor, is less than 1 / 3 of the height of the manifold; and the second liquid level height condition is that the maximum liquid level height in each of the manifolds, as obtained in real time by the liquid level sensor, is greater than or equal to 1 / 3 of the height of the manifold.

[0016] Furthermore, the heat storage regulation module, under the first liquid level height condition, obtains the heating capacity of the heat pump based on the maximum liquid level height in each of the manifolds obtained in real time by the liquid level sensor, wherein,

[0017] The heat storage regulation module obtains the heat pump's heating capacity as the first heating capacity under the third liquid level condition;

[0018] The heat storage regulation module obtains the heat pump's heating capacity as the second heating capacity under the fourth liquid level condition;

[0019] The third liquid level condition is that the maximum liquid level in each of the manifolds, as obtained in real time by the liquid level sensor, is less than 1 / 10 of the manifold height, and the fourth liquid level condition is that the maximum liquid level in each of the manifolds, as obtained in real time by the liquid level sensor, is greater than or equal to 1 / 10 of the manifold height.

[0020] The heat output of the heat pump, obtained under the third and fourth liquid level conditions, is determined by the maximum liquid level height in each of the manifolds, which is obtained in real time by the liquid level sensor.

[0021] Furthermore, the heat storage regulation module obtains the operating power of each heating plate as the first operating power under the first liquid level change condition; the heat storage regulation module obtains the operating power of each heating plate as the second operating power under the second liquid level change condition; and the heat storage regulation module determines not to start each heating plate under the third liquid level change condition.

[0022] Wherein, the first liquid level change condition is that the liquid level height change rate in each of the manifolds is less than the first standard liquid level height change rate; the second liquid level change condition is that the liquid level height change rate in each manifold is greater than or equal to the first standard liquid level height change rate and less than or equal to the second standard liquid level height change rate; and the third liquid level change condition is that the liquid level height change rate in each manifold is greater than the second standard liquid level height change rate.

[0023] The first operating power obtained under the first liquid level change condition is determined by the liquid level height change rate in each of the manifolds and the first standard liquid level height change rate. The second operating power obtained under the second liquid level change condition is determined by the liquid level height change rate in each manifold, the first standard liquid level height change rate, and the second standard liquid level height change rate.

[0024] Furthermore, the phase change thermal storage system also includes a first delivery pump connected to the first delivery pipe for providing kinetic energy to the phase change material where the pressure difference is insufficient. The thermal storage regulation module obtains a first standard rate of change of liquid level height and a second standard rate of change of liquid level height based on the real-time pump pressure of the first delivery pump.

[0025] The first standard rate of change of liquid level height is determined either by the difference between the standard pump pressure of the first delivery pump and the real-time pump pressure of the first delivery pump, or by the ratio of the standard pump pressure of the first delivery pump to the real-time pump pressure of the first delivery pump. The second standard rate of change of liquid level height is determined by the first standard rate of change of liquid level height.

[0026] Furthermore, the circulation adjustment module obtains the real-time pump pressure of the first delivery pump based on the maximum liquid level height in each manifold, wherein,

[0027] The real-time pump pressure of the first delivery pump can be determined by the difference between the height of each manifold and the maximum liquid level in each manifold, or it can be equal to the standard pump pressure of the first delivery pump.

[0028] Specifically, when the minimum liquid level in each of the manifolds is higher than the liquid level in the first delivery pipe, the first delivery pump does not operate.

[0029] Furthermore, the circulation adjustment module obtains the real-time pump pressure of the second delivery pump based on the real-time pump pressure of the first delivery pump, wherein,

[0030] The real-time pump pressure of the second delivery pump can be determined either by the logarithm of the standard pump pressure of the first delivery pump with the real-time pump pressure of the first delivery pump as the base, or by the ratio of the real-time pump pressure of the first delivery pump to the standard pump pressure of the first delivery pump.

[0031] When the first delivery pump is not running, the real-time pump pressure of the second delivery pump is equal to 0.5 times the standard pump pressure of the first delivery pump.

[0032] Furthermore, the circulation adjustment module obtains the cooling capacity of the cooling chip under the first pump pressure condition as the first cooling capacity; the circulation adjustment module obtains the cooling capacity of the cooling chip under the second pump pressure condition as the second cooling capacity.

[0033] Wherein, the first pump pressure condition is that the real-time pump pressure of the second delivery pump is less than or equal to 1.2 times the standard pump pressure of the second delivery pump, and the second pump pressure condition is that the real-time pump pressure of the second delivery pump is greater than 1.2 times the standard pump pressure of the second delivery pump.

[0034] The cooling capacity of the cooling chip obtained under the first pump pressure condition and the second pump pressure condition is determined by the real-time pump pressure of the second delivery pump.

[0035] Furthermore, the cycle adjustment module obtains the cylinder's operating cycle as a first operating cycle under the first cooling determination condition; the cycle adjustment module obtains the cylinder's operating cycle as a second operating cycle under the second cooling determination condition.

[0036] The first cooling determination condition is that the cooling capacity of the cooling chip is less than or equal to the average of the standard cooling capacity and the designed cooling capacity of the cooling chip, and the second cooling determination condition is that the cooling capacity of the cooling chip is greater than the average of the standard cooling capacity and the designed cooling capacity of the cooling chip.

[0037] The operating cycle of the cylinder, obtained under the first and second cooling determination conditions, is determined by the cooling capacity of the cooling element.

[0038] Furthermore, the transportation control module obtains the solid design gravity inside the transportation box as the first design gravity under the first operating cycle condition; the transportation control module obtains the solid design gravity inside the transportation box as the second design gravity under the second operating cycle condition.

[0039] When the pressure sensor detects that the weight of the solid inside the transport box reaches the designed weight of the solid, the conveying device is started in a first operating mode. The first operating mode is that the conveying device drives the transport box in a counterclockwise direction. The first operating cycle condition is that the operating cycle of the cylinder is less than or equal to a preset operating cycle. The second operating cycle condition is that the operating cycle of the cylinder is greater than the preset operating cycle.

[0040] The solid design gravity inside the transport box, obtained under the first and second operating cycle conditions, is determined by the operating cycle of the cylinder.

[0041] Compared with the prior art, the beneficial effects of the present invention are as follows: The present invention is equipped with a phase change thermal storage unit, which can determine the current available heat supply by using the real-time liquid level height in the manifold obtained by the liquid level sensor, and determine the external heat energy demand by using the rate of change of the liquid level height in the manifold obtained by the liquid level sensor. This allows for heat compensation for liquid phase change materials stored for a long time, ensuring that they can quickly reach the phase change point and exchange a large amount of heat energy with the working liquid when they arrive at the heat exchanger. The present invention is equipped with a heat exchange unit, which allows the solid-liquid mixture of the phase change material to leave the heat exchanger promptly after completing the heat exchange with the working liquid, so that the liquid phase change material can promptly enter the heat exchanger to continue exchanging heat with the working liquid, ensuring that the amount of phase change material in the heat exchanger, storage chamber, and collector chamber remains in a relatively dynamic balance. The present invention is equipped with a cooling unit, which allows the phase change material to be converted into a solid material that is easy to transport, improving the utilization rate of the phase change material. The present invention is equipped with a transportation unit, which can automatically transfer the solid phase change material to the phase change thermal storage unit, realizing the self-circulation of phase change material distribution in the thermal storage system.

[0042] In particular, this invention determines whether to activate the heat pump based on the maximum liquid level height in each manifold obtained by the liquid level sensor. When the liquid level height in each manifold is low, the heat pump is activated to heat the solid phase change material in the heat collection chamber, causing the phase change material to convert into a liquid state and enter the manifold. When the liquid level height in each manifold is high, the solid phase change material is temporarily stored in the heat collection chamber to avoid excessive liquid phase change material in the heat storage chamber. Since the external heat energy demand is low, the liquid phase change material in the heat storage chamber will remain for too long, causing the heat energy to be naturally lost to the air. By controlling the liquid level height in each manifold, excessive compensation heat energy generated by the heating plate can be avoided, thereby achieving energy saving and environmental protection.

[0043] In particular, the present invention obtains the heating capacity of the heat pump based on the maximum liquid level height in each of the manifolds obtained by the liquid level sensor. When the maximum liquid level height in each manifold is extremely low, it can be determined that the amount of phase change material in the heat storage chamber is low. Selecting a larger heating capacity can ensure that the liquid phase change material in the heat collection chamber is replenished in a timely manner, avoiding the situation where the heat supply to the outside suddenly increases and the amount of phase change material in the heat collection chamber is insufficient, resulting in the heat exchange effect not meeting the requirements.

[0044] In particular, the present invention obtains the operating power of each heating plate based on the rate of change of liquid level in each manifold. When the rate of change of liquid level in each manifold is low, it can be determined that the phase change material in the heat collector chamber has a long residence time in the heat collector chamber and its natural heat loss is large. Therefore, a larger operating power of the heating plate is selected to compensate for the heat of the phase change material in the heat collector chamber. Conversely, when the phase change material in the heat collector chamber has a short residence time, the heat loss of the material itself has a negligible impact on the heat exchange in the heat exchanger. Therefore, a smaller operating power is selected.

[0045] In particular, the present invention adjusts the real-time pump pressure of the second delivery pump based on the real-time pump pressure of the first delivery pump. When the real-time pump pressure of the first delivery pump is large, it can be determined that the average storage time of the phase change material in the current heat collector chamber is large and the circulation amount of the phase change material in the system is small. By adjusting the pump pressure of the delivery pump to accelerate the circulation of the phase change material in the system, the heat compensation of the electric heating plate on the phase change material can be reduced, and the volatilization of the phase change material at high temperature can be reduced, which is energy-saving and environmentally friendly.

[0046] In particular, the present invention obtains the cooling capacity of the cooling chip based on the real-time pump pressure of the second delivery pump. When the real-time pump pressure of the second delivery pump is large, selecting a higher cooling capacity can ensure that the phase change material in the cooling chamber is completely converted into a solid during cylinder operation, avoiding the phase change material entering the mold being a solid-liquid mixture. When the real-time pump pressure of the second delivery pump is small, selecting a lower cooling capacity can avoid the phase change material temperature being too low, resulting in more heat required for phase change in the heat collection chamber, thus avoiding unnecessary energy waste.

[0047] In particular, the present invention obtains the cylinder operating cycle based on the cooling capacity of the cooling chip. When the cooling capacity of the cooling chip is small, selecting a smaller operating cycle can ensure that the temperature of the solid phase change material exiting from the mold opening is not too low. When the cooling capacity of the cooling chip is large, it can be determined that the amount of phase change material entering the cooling chamber per unit time is large. Selecting a larger operating cycle can ensure that the phase change material exiting from the mold opening is a completely solid material.

[0048] In particular, the present invention obtains the solid design gravity in the transport box that drives the transmission device based on the cylinder's operating cycle. When the cylinder's operating cycle is large, selecting a smaller solid design gravity can ensure that the phase change material can be replenished in the heat collection chamber in a timely manner. When the cylinder's operating cycle is small, selecting a larger solid design gravity can avoid repeated operation of the conveying device, main fixed pulley, and auxiliary fixed pulley. Energy saving and emission reduction are achieved by increasing the amount of phase change material transported per unit number of times. Attached Figure Description

[0049] Figure 1 This is a schematic diagram of a distributed, high-efficiency, energy-saving phase change thermal energy storage system according to an embodiment of the invention.

[0050] Figure 2 This is a diagram illustrating the architecture of a distributed, high-efficiency, energy-saving phase change thermal energy storage system as an embodiment of the invention. Detailed Implementation

[0051] To make the objectives and advantages of the present invention clearer, the present invention will be further described below with reference to embodiments; it should be understood that the specific embodiments described herein are merely for explaining the present invention and are not intended to limit the present invention.

[0052] Preferred embodiments of the present invention will now be described with reference to the accompanying drawings. Those skilled in the art should understand that these embodiments are merely illustrative of the technical principles of the present invention and are not intended to limit the scope of protection of the present invention.

[0053] It should be noted that in the description of this invention, the terms "upper", "lower", "left", "right", "inner", "outer", etc., which indicate directions or positional relationships, are based on the directions or positional relationships shown in the accompanying drawings. This is only for the convenience of description and is not intended to indicate or imply that the device or element must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation of this invention.

[0054] Furthermore, it should be noted that, in the description of this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0055] Please see Figure 1 As shown, it is a schematic diagram of a distributed high-efficiency energy-saving phase change thermal energy storage system according to an embodiment of the present invention, including:

[0056] A phase change thermal energy storage unit includes a heat collection chamber 1 for absorbing heat from a phase change material and converting it from a solid to a liquid state; a heat pump 2 disposed on the outer wall of the heat collection chamber for providing heat to the phase change material; several manifolds 3 connected to the heat collection chamber for storing the liquid phase change material; a liquid level sensor 4 disposed on the side wall of one of the manifolds for obtaining the maximum liquid level height in each manifold and the rate of change of the liquid level height in each manifold; a thermal energy storage chamber 5 connected to each manifold for storing the liquid phase change material; and several heating plates 6 disposed on the inner wall of the thermal energy storage chamber for heat compensation of the phase change material.

[0057] The heat exchange unit includes a first delivery pipe 8 connected to the heat collection chamber for transporting phase change material, a control valve 7 disposed in the first delivery pipe for controlling the flow rate of phase change material, a first delivery pump 9 connected to the first delivery pipe for providing kinetic energy to phase change material with insufficient pressure difference, a heat exchanger 10 connected to the first delivery pump for exchanging heat between phase change material and working liquid, a second delivery pump 11 connected to the heat exchanger for controlling the solid-liquid mixture of phase change material after heat exchange to leave the heat exchanger, and a second delivery pipe 12 connected to the second delivery pump for transporting the solid-liquid mixture of phase change material.

[0058] The cooling unit includes a cooling chamber 13 connected to the second conveying pipe for releasing heat from the phase change material to convert it into a solid state, a cooling plate 14 disposed at the bottom of the cooling chamber for absorbing heat from the phase change material, a cylinder 15 disposed inside the cooling chamber, a plurality of compression rods 16 connected to the cylinder for extruding the solid phase change material, a mold 17 connected to the cooling chamber for forming the solid phase change material, and a cutting device 18 disposed above the mold opening for cutting the phase change material into blocks.

[0059] The transport unit includes a transport box 19 located below the mold for receiving phase change material, a pressure sensor 20 located at the bottom of the inner wall of the transport box for obtaining the gravity of the phase change material, an iron block 21 located on the outer wall surface of the transport box away from the mold, a conveying device 22 located below the transport box for driving the transport box, a vertical pole 25 located at the end of the conveying device, a sleeve 22 sleeved on the vertical pole, an electromagnet 24 fixedly connected to the outer surface of the sleeve, a main fixed pulley 26 located at the bottom end of the vertical pole, a secondary fixed pulley 27 located at the top end of the vertical pole, cables 28 wound around the main fixed pulley and the secondary fixed pulley for pulling the transport box up, a transport pipe 29 located on the top side of the vertical pole and connected to the heat collection chamber for transporting the phase change material in the transport box to the heat collection chamber, and a negative pressure fan 30 located in the heat collection chamber for providing suction to the transport pipe.

[0060] Specifically, this embodiment does not limit the type of heat pump. This embodiment preferably uses an air source heat pump as a device to provide heat to the solid phase change material in the heat collection chamber.

[0061] Please see Figure 2 As shown, this is an architectural diagram of a distributed, high-efficiency, energy-saving phase change thermal energy storage system according to an embodiment of the present invention. The distributed, high-efficiency, energy-saving phase change thermal energy storage system further includes a central control unit, which includes:

[0062] A heat storage regulation module, which is connected to the phase change heat storage unit, is used to determine whether to start the heat pump and obtain the heat output of the heat pump based on the maximum liquid level height in each of the manifolds obtained in real time by the liquid level sensor, and to obtain the operating power of each of the heating plates based on the rate of change of the liquid level height in each of the manifolds.

[0063] A circulation adjustment module, which is connected to the heat storage adjustment module, the heat exchange unit and the cooling unit respectively, is used to obtain the real-time pump pressure of the second delivery pump according to the operating power of each of the electric heating plates, obtain the cooling capacity of the cooling chip according to the real-time pump pressure of the second delivery pump, and obtain the operating cycle of the cylinder according to the cooling capacity of the cooling chip.

[0064] The transport control module, which is connected to the circulation adjustment module and the transport unit respectively, is used to obtain the solid design gravity inside the transport box according to the operating cycle of the cylinder, obtain the dwell time of the transport box after reaching the preset lifting height according to the solid design gravity inside the transport box, and obtain the impeller speed of the negative pressure fan according to the dwell time of the transport box after reaching the preset lifting height.

[0065] Please continue reading. Figure 1As shown, when heat pump 2 is in operation, it provides heat to the solid phase change material in the collector chamber 1, causing the phase change material to change from solid to liquid and enter each manifold 3. The liquid level sensor 4 monitors the liquid level in each manifold in real time. When the liquid level in each manifold is greater than or equal to 1 / 3 of the manifold height, the heat storage regulation module controls the heat pump to stop working. The liquid phase change material enters the heat storage chamber 5 from each manifold. The heat storage regulation module obtains the operating power of the heating plate 6 based on the rate of change of the liquid level in each manifold obtained by the liquid level sensor to compensate for the insufficient heat storage of the phase change material due to natural heat release. The control valve 7 controls the phase change material to enter the heat exchanger 10 from the first delivery pipe 8. When the liquid level in each manifold... When the liquid level is below that of the first delivery pipe, the first delivery pump 9 operates to allow the phase change material in the first delivery pipe to overcome gravity and enter the heat exchanger. When the working liquid and the phase change material complete heat exchange in the heat exchanger, the phase change material in the heat exchanger is a solid-liquid mixture. The second delivery pump 11 controls the solid-liquid mixture to enter the cooling chamber 13 through the second delivery pipe 12. The cooling plate 14 operates to accelerate the conversion of the solid-liquid mixture into a solid state. When the cylinder 15 reaches the start of the operating cycle, it starts to operate so that each compression rod 16 pushes the solid phase change material into the mold 17 for molding and pushes the molded phase change material out of the mold. The cutting device 18 cuts the phase change material pushed out from the mold opening at a fixed speed so that the phase change material falls into solid blocks and is transported to the cooling chamber. When the pressure sensor 20 detects that the weight of the phase change material inside the transport box 19 reaches a preset value, the conveying device 22 operates in the first mode to transport the transport box to the bottom of the upright 25. The electromagnet 24 generates an attractive force on the iron block 21, and the main fixed pulley 26 rotates counterclockwise to drive the auxiliary fixed pulley 27 to rotate, thereby recovering the cable 28. This causes the sleeve 23 to lift the transport box to a preset height via the electromagnet. When the transport box reaches the preset height, the main and auxiliary fixed pulleys stop operating, and the negative pressure fan 30 operates to allow the phase change material inside the transport box to enter the heat collection chamber from the transport pipe 29. When the dwell time of the transport box reaches the preset dwell time, the main fixed pulley rotates clockwise to drive the auxiliary fixed pulley to rotate, thereby extending the cable and lowering the transport box to the bottom of the upright 25. When the rod reaches the bottom, the electromagnet stops operating, and the conveying device operates in the second mode to transport the transport box back to the area below the mold opening. The cutting device consists of a blade and a motor. The rotating wheel inside the motor drives the blade to rotate, thus cutting the phase change material. The conveying device consists of a motor, reducer, rollers, support, idler rollers, conveyor belt, counterweight, etc., which will not be described in detail. As long as it can transport the transport box in two directions, it is sufficient. The first operating mode of the conveying device is that the conveyor belt rotates counterclockwise, and the second operating mode is that the conveyor belt rotates clockwise. When the cylinder starts running, the second conveying pump stops transporting the phase change material to the cooling chamber. When the conveying device starts running in the second operating mode, the second conveying pump resumes transporting the phase change material to the cooling chamber.

[0066] Specifically, this embodiment does not limit the specific phase change material, but paraffin is preferred as the phase change material for heat storage and heat exchange.

[0067] Specifically, this invention includes a phase change thermal storage unit that can determine the available heat supply by using the real-time liquid level height in the manifold obtained by a liquid level sensor, and determine the external heat energy demand by using the rate of change of the liquid level height in the manifold obtained by the liquid level sensor. This allows for heat compensation of liquid phase change materials stored for extended periods, ensuring they quickly reach the phase change point and exchange a large amount of heat energy with the working liquid upon arrival at the heat exchanger. The invention also includes a heat exchange unit that allows the solid-liquid mixture of the phase change material to leave the heat exchanger promptly after heat exchange with the working liquid, allowing the liquid phase change material to re-enter the heat exchanger to continue exchanging heat with the working liquid, thus maintaining a relative dynamic balance in the amount of phase change material in the heat exchanger, storage chamber, and collector chamber. Furthermore, the invention includes a cooling unit that converts the phase change material into a transportable solid, improving its utilization rate. Finally, the invention includes a transportation unit that automatically transfers the solid phase change material to the phase change thermal storage unit, achieving a self-circulating distribution of phase change material in the thermal storage system.

[0068] The heat storage regulation module determines whether to start the heat pump based on the maximum liquid level height in each of the manifolds obtained in real time by the liquid level sensor.

[0069] The heat storage regulation module determines to start the heat pump under the first liquid level condition;

[0070] The heat storage regulation module determines that the heat pump will not be started under the second liquid level condition;

[0071] Wherein, the first liquid level height condition is that the maximum liquid level height in each of the manifolds, as obtained in real time by the liquid level sensor, is less than 1 / 3 of the height of the manifold; and the second liquid level height condition is that the maximum liquid level height in each of the manifolds, as obtained in real time by the liquid level sensor, is greater than or equal to 1 / 3 of the height of the manifold.

[0072] Specifically, this invention determines whether to activate the heat pump based on the maximum liquid level height in each manifold obtained by the liquid level sensor. When the liquid level height in each manifold is low, the heat pump is activated to heat the solid phase change material in the heat collection chamber, causing the phase change material to convert into a liquid state and enter the manifold. When the liquid level height in each manifold is high, the solid phase change material is temporarily stored in the heat collection chamber to avoid excessive liquid phase change material in the heat storage chamber. Since the external heat energy demand is low, the liquid phase change material in the heat storage chamber will remain for too long, causing the heat energy to be naturally lost to the air. By controlling the liquid level height in each manifold, excessive compensation heat energy generated by the heating plate can be avoided, thereby achieving energy saving and environmental protection.

[0073] The heat storage regulation module obtains the heating capacity of the heat pump based on the maximum liquid level in each of the manifolds, as measured in real time by the liquid level sensor, under the first liquid level height condition.

[0074] The heat storage regulation module obtains the heat pump's heating capacity as the first heating capacity under the third liquid level condition;

[0075] The heat storage regulation module obtains the heat pump's heating capacity as the second heating capacity under the fourth liquid level condition;

[0076] The third liquid level condition is that the maximum liquid level in each of the manifolds, as obtained in real time by the liquid level sensor, is less than 1 / 10 of the manifold height, and the fourth liquid level condition is that the maximum liquid level in each of the manifolds, as obtained in real time by the liquid level sensor, is greater than or equal to 1 / 10 of the manifold height.

[0077] Wherein, the first heating capacity Q1 = Q0 × (1 + (Hh) / H)² is set, and the second heating capacity Q2 = (1 + h² / H²) × Q0, where h is the maximum liquid level height in each of the manifolds obtained in real time by the liquid level sensor, H is the height of each of the manifolds, and Q0 is the standard heating capacity of the heat pump.

[0078] Specifically, in this embodiment, the standard heating capacity of the heat pump is Q0=35kW, and the height of the manifold is H=110cm.

[0079] Specifically, the present invention obtains the heating capacity of the heat pump based on the maximum liquid level height in each of the manifolds obtained by the liquid level sensor. When the maximum liquid level height in each manifold is extremely low, it can be determined that the amount of phase change material in the heat storage chamber is low. Selecting a larger heating capacity can ensure that the liquid phase change material in the heat collection chamber can be replenished in a timely manner, avoiding the situation where the heat supply to the outside suddenly increases and the amount of phase change material in the heat collection chamber is insufficient, resulting in the heat exchange effect not meeting the requirements.

[0080] The heat storage regulation module obtains the operating power of each heating plate based on the rate of change of the liquid level in each of the manifolds, wherein,

[0081] The heat storage regulation module obtains the operating power of each of the heating plates as the first operating power under the first liquid level change condition;

[0082] The heat storage regulation module obtains the operating power of each of the heating plates as the second operating power under the second liquid level change condition;

[0083] The heat storage regulation module determines that it will not activate any of the heating plates under the third liquid level change condition;

[0084] Wherein, the first liquid level change condition is that the liquid level height change rate in each of the manifolds is less than the first standard liquid level height change rate; the second liquid level change condition is that the liquid level height change rate in each manifold is greater than or equal to the first standard liquid level height change rate and less than or equal to the second standard liquid level height change rate; and the third liquid level change condition is that the liquid level height change rate in each manifold is greater than the second standard liquid level height change rate.

[0085] Wherein, the first operating power P1 is set to P0 × (1 + Δh1 / (Δh + Δh1)), and the second operating power P2 is set to P0 × (Δh - Δh1) × (Δh2 - Δh) / (Δh1 × Δh2). In the formula, Δh is the rate of change of liquid level in each of the manifolds. The heat storage regulation module presets the first standard rate of change of liquid level as Δh1 and the second standard rate of change of liquid level as Δh2. P0 is the standard operating power of each of the heating plates.

[0086] The thermal storage regulation module obtains the first standard rate of change of liquid level height and the second standard rate of change of liquid level height based on the real-time pump pressure of the first delivery pump, wherein,

[0087] The thermal storage regulation module obtains the first standard rate of change of liquid level height Δh1 = (1 + (N0 - N) / N0) × Δh0 and the second standard rate of change of liquid level height Δh2 = 2.5 × Δh1 under the first pressure condition;

[0088] The thermal storage regulation module obtains the first standard change rate of liquid level height Δh1=(N / N0)×Δh0 and the second standard change rate of liquid level height Δh2=2×Δh1 under the second pressure condition;

[0089] In the formula, N is the real-time pump pressure of the first delivery pump, and N0 is the standard pump pressure of the first delivery pump;

[0090] Wherein, the first pressure condition is that the real-time pump pressure of the first delivery pump is less than the standard pump pressure of the first delivery pump, and the second pressure condition is that the real-time pump pressure of the first delivery pump is greater than or equal to the standard pump pressure of the second delivery pump.

[0091] The circulation adjustment module obtains the real-time pump pressure of the first delivery pump based on the maximum liquid level height in each manifold, wherein...

[0092] The circulation adjustment module obtains the real-time pump pressure of the first delivery pump as the first pressure under the first liquid level height condition;

[0093] The circulation adjustment module obtains the real-time pump pressure of the first delivery pump as the second pressure under the second liquid level height condition;

[0094] The first pressure is set as N1 = N0 × (1 + (H0 - h) / H0), and the second pressure is set as N2 = N0. When the liquid level in each manifold is higher than the minimum liquid level in the first delivery pipe, the first delivery pump does not operate.

[0095] Specifically, in this embodiment, the standard operating power of each heating plate is 170W, and the standard pump pressure of the first delivery pump is 2.7 bar; in this embodiment, the liquid level height change rate is a vector, with the liquid level height decreasing in the positive direction and the liquid level height increasing in the negative direction.

[0096] Specifically, this invention obtains the operating power of each heating plate based on the rate of change of liquid level in each manifold. When the rate of change of liquid level in each manifold is low, it can be determined that the phase change material in the heat collector chamber has a longer residence time in the heat collector chamber, and its natural heat loss is greater. Therefore, a larger operating power of the heating plate is selected to compensate for the heat loss of the phase change material in the heat collector chamber. Conversely, when the phase change material in the heat collector chamber has a shorter residence time in the heat collector chamber, the impact of its own heat loss on the heat exchange in the heat exchanger can be ignored, so a smaller operating power is selected.

[0097] The circulation adjustment module obtains the real-time pump pressure of the second delivery pump based on the real-time pump pressure of the first delivery pump, wherein,

[0098] The circulation adjustment module obtains the real-time pump pressure of the second delivery pump as the first pump pressure under the first pressure condition;

[0099] The circulation adjustment module obtains the real-time pump pressure of the second delivery pump as the second pump pressure under the first pressure condition;

[0100] Wherein, the first pump pressure F1 is set as N0 × log Ni N0, set the second pump pressure F2 = N0 × (Ni / N0) 0.5 In the formula, i = 1, 2;

[0101] When the first delivery pump is not running, the real-time pump pressure of the second delivery pump is equal to 0.5 times the standard pump pressure of the first delivery pump.

[0102] Specifically, the present invention adjusts the real-time pump pressure of the second delivery pump based on the real-time pump pressure of the first delivery pump. When the real-time pump pressure of the first delivery pump is large, it can be determined that the average storage time of the phase change material in the current heat collector chamber is large and the circulation amount of the phase change material in the system is small. By adjusting the pump pressure of the delivery pump to accelerate the circulation of the phase change material in the system, the heat compensation of the heating plate on the phase change material can be reduced, and the volatilization of the phase change material at high temperature can be reduced, which is energy-saving and environmentally friendly.

[0103] The circulation adjustment module obtains the cooling capacity of the cooling chip based on the real-time pump pressure of the second delivery pump, wherein,

[0104] The circulation adjustment module obtains the cooling capacity of the cooling chip as the first cooling capacity under the first pump pressure condition;

[0105] The circulation adjustment module obtains the cooling capacity of the cooling chip under the second pump pressure condition as the second cooling capacity;

[0106] Wherein, the first pump pressure condition is that the real-time pump pressure of the second delivery pump is less than or equal to 1.2 times the standard pump pressure of the second delivery pump, and the second pump pressure condition is that the real-time pump pressure of the second delivery pump is greater than 1.2 times the standard pump pressure of the second delivery pump.

[0107] Wherein, the first cooling capacity is set as W1=W0×Fu / F0, W2=min{W0×(Fu / F0)²,Wa}, where u=1,2, W0 is the standard cooling capacity of the cooling chip, and Wa is the designed cooling capacity of the cooling chip.

[0108] Specifically, in this embodiment, the standard cooling capacity of the refrigeration chip is 8kW, and the designed cooling capacity of the refrigeration chip is 15kW.

[0109] Specifically, the present invention obtains the cooling capacity of the cooling chip based on the real-time pump pressure of the second delivery pump. When the real-time pump pressure of the second delivery pump is large, selecting a higher cooling capacity can ensure that the phase change material in the cooling chamber is completely converted into a solid during cylinder operation, avoiding the phase change material entering the mold being a solid-liquid mixture. When the real-time pump pressure of the second delivery pump is small, selecting a lower cooling capacity can avoid the phase change material temperature being too low, resulting in more heat required for phase change in the heat collection chamber, thus avoiding unnecessary energy waste.

[0110] The cycle adjustment module obtains the operating cycle of the cylinder based on the cooling capacity of the cooling element, wherein,

[0111] The cycle adjustment module obtains the cylinder's operating cycle as the first operating cycle under the first refrigeration determination condition;

[0112] The cycle adjustment module obtains the cylinder's operating cycle as the second operating cycle under the second refrigeration determination condition;

[0113] The first cooling determination condition is that the cooling capacity of the cooling chip is less than or equal to the average of the standard cooling capacity and the designed cooling capacity of the cooling chip, and the second cooling determination condition is that the cooling capacity of the cooling chip is greater than the average of the standard cooling capacity and the designed cooling capacity of the cooling chip.

[0114] Wherein, the first operating cycle T1 is set as T0 × [1 + Wv / (0.5 × (W0 + Wa))], and the second operating cycle T2 is set as T0 + T0 × [1.5 + 0.5 × (W0 + Wa) / Wv]; where v = 1, 2, T0 is the standard operating cycle of the cylinder, [1 + Wv / (0.5 × (W0 + Wa))] represents rounding down 1 + Wv / (0.5 × (W0 + Wa)), and [1.5 + 0.5 × (W0 + Wa) / Wv] represents rounding down 1.5 + 0.5 × (W0 + Wa) / Wv].

[0115] Specifically, in this embodiment, T0 = 12min, and one operating cycle represents the interval between the start of the cylinder's previous operation and the start of its next operation.

[0116] Specifically, the present invention obtains the cylinder's operating cycle based on the cooling capacity of the cooling chip. When the cooling capacity of the cooling chip is small, selecting a smaller operating cycle can ensure that the temperature of the solid phase change material exiting from the mold opening is not too low. When the cooling capacity of the cooling chip is large, it can be determined that the amount of phase change material entering the cooling chamber per unit time is large, and selecting a larger operating cycle can ensure that the phase change material exiting from the mold opening is a completely solid material.

[0117] The transport control module obtains the solid design gravity inside the transport box based on the cylinder's operating cycle to start the conveying device in a first operating mode, wherein...

[0118] The transportation control module obtains the solid design gravity inside the transportation box as the first design gravity under the first operating cycle condition.

[0119] The transportation control module obtains the solid design gravity inside the transportation box as the second design gravity under the second operating cycle condition.

[0120] When the pressure sensor detects that the weight of the solid inside the transport box reaches the designed weight of the solid, the conveying device is started in a first operating mode. The first operating mode is that the conveying device drives the transport box in a counterclockwise direction. The first operating cycle condition is that the operating cycle of the cylinder is less than or equal to a preset operating cycle. The second operating cycle condition is that the operating cycle of the cylinder is greater than the preset operating cycle.

[0121] Here, the first design gravity is set as G1 = G0 × (T0' / Tc). 0.5 The second design gravity is set as G2 = G0 × T0' / Tc, where c = 1, 2, T0' is the preset operating cycle, and G0 is the preset standard value of solid gravity.

[0122] Specifically, in this embodiment, G0 is set to 3kg and T0' is set to 1.35×T0.

[0123] Specifically, this invention obtains the solid design gravity in the transport box that drives the transmission device based on the cylinder's operating cycle. When the cylinder's operating cycle is long, selecting a smaller solid design gravity ensures that the phase change material can be replenished in the heat collection chamber in a timely manner. When the cylinder's operating cycle is short, selecting a larger solid design gravity avoids the repeated operation of the conveying device, main fixed pulley, and auxiliary fixed pulley. Energy saving and emission reduction are achieved by increasing the amount of phase change material transported per unit number of cycles.

[0124] The transport control module obtains the dwell time of the transport container after reaching the preset lifting height based on the design gravity of the solid objects inside the transport container.

[0125] The transportation control module obtains the dwell time of the transportation box after it reaches the preset lifting height under the first gravity condition as the first dwell time.

[0126] The transportation control module obtains the dwell time of the transportation box after it reaches the preset lifting height under the second gravity condition as the second dwell time.

[0127] Wherein, the first gravity condition is that the designed weight of the solid inside the transport box is less than or equal to the preset standard value of the solid weight, and the second gravity condition is that the designed weight of the solid inside the transport box is greater than the preset standard value of the solid weight;

[0128] Wherein, the first dwell time t1 = tmin + Δt × Gq / ΔG is set, and the second dwell time t2 = tmin + log G0 Gq×△t×Gq / △G, where q=1, 2, △t is the preset unit time, △G is the preset unit gravity, and tmin is the preset minimum dwell time.

[0129] Specifically, in this embodiment, tmin=4min, Δt=0.5min, ΔG=0.2N, and the preset lifting height in this embodiment is the position where the distance between the top of the transport box and the bottom of the transport pipe is 10cm.

[0130] The transport control module obtains the impeller speed of the negative pressure fan based on the dwell time of the transport box after reaching the preset lifting height.

[0131] The transportation control module determines the impeller speed of the negative pressure fan as the first speed under the first-time judgment condition;

[0132] The transport control module obtains the impeller speed of the negative pressure fan as the second speed under the second time determination condition;

[0133] The first time determination condition is that the dwell time of the transport box when it reaches the preset lifting height is less than or equal to the preset standard dwell time, and the second time determination condition is that the dwell time of the transport box when it reaches the preset lifting height is greater than the preset standard dwell time.

[0134] Wherein, the first rotational speed is set to ω1=ω0×t0×tz / tmin², and the second rotational speed is set to ω2=ω0, where z=1,2, ω0 is the standard rotational speed of the negative pressure fan, and t0 is the preset standard dwell time.

[0135] Specifically, in this embodiment, t0 = 7.5 min, ω0 = 110 r / min.

[0136] The technical solution of the present invention has been described above with reference to the preferred embodiments shown in the accompanying drawings. However, it will be readily understood by those skilled in the art that the scope of protection of the present invention is obviously not limited to these specific embodiments. Without departing from the principles of the present invention, those skilled in the art can make equivalent changes or substitutions to the relevant technical features, and the technical solutions after these changes or substitutions will all fall within the scope of protection of the present invention.

[0137] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A distributed high-efficiency energy-saving phase change heat storage system, characterized in that, include, A phase change thermal energy storage unit includes a heat collection chamber, a heat pump disposed on the outer wall of the heat collection chamber for providing heat to the phase change material, several manifolds connected to the heat collection chamber for storing liquid phase change material, a liquid level sensor disposed on the side wall of one of the manifolds for real-time acquisition of the maximum liquid level height in each manifold and the rate of change of liquid level height in each manifold, a thermal energy storage chamber connected to each manifold, and several electric heating plates disposed on the inner wall of the thermal energy storage chamber for heat compensation of the phase change material. A heat exchange unit includes a heat exchanger connected to the heat collection chamber via a first delivery pipe, a second delivery pump connected to the heat exchanger for controlling the solid-liquid mixture of the phase change material that has completed heat exchange to leave the heat exchanger, and a second delivery pipe connected to the second delivery pump for transporting the solid-liquid mixture of the phase change material. The cooling unit includes a cooling chamber connected to the second conveying pipe, a cooling plate disposed at the bottom of the cooling chamber for absorbing heat from the phase change material, and a cylinder disposed inside the cooling chamber for driving a plurality of compression rods connected to the cylinder to compress the phase change material so that the phase change material enters the mold. The transport unit includes a transport box located below the mold, a pressure sensor located at the bottom of the inner wall of the transport box for acquiring the gravity of the phase change material, a conveying device located below the transport box for driving the transport box, a transport pipe connected to the heat collection chamber for transporting the phase change material in the transport box to the heat collection chamber, and a negative pressure fan located in the heat collection chamber for providing suction to the transport pipe. The central control unit includes: A heat storage regulation module, which is connected to the phase change heat storage unit, is used to determine whether to start the heat pump and obtain the heat output of the heat pump based on the maximum liquid level height in each of the manifolds obtained in real time by the liquid level sensor, and to obtain the operating power of each of the heating plates based on the rate of change of the liquid level height in each of the manifolds. A circulation adjustment module, which is connected to the heat storage adjustment module, the heat exchange unit and the cooling unit respectively, is used to obtain the real-time pump pressure of the second delivery pump according to the operating power of each of the electric heating plates, obtain the cooling capacity of the cooling chip according to the real-time pump pressure of the second delivery pump, and obtain the operating cycle of the cylinder according to the cooling capacity of the cooling chip. The transport control module, which is connected to the cycle adjustment module and the transport unit respectively, is used to obtain the solid design gravity inside the transport box according to the operating cycle of the cylinder.

2. The distributed high efficient energy saving phase change thermal storage system of claim 1, wherein, The heat storage regulating module determines to start the heat pump under the first liquid level condition; the heat storage regulating module determines not to start the heat pump under the second liquid level condition. Wherein, the first liquid level height condition is that the maximum liquid level height in each of the manifolds, as obtained in real time by the liquid level sensor, is less than 1 / 3 of the height of the manifold; and the second liquid level height condition is that the maximum liquid level height in each of the manifolds, as obtained in real time by the liquid level sensor, is greater than or equal to 1 / 3 of the height of the manifold.

3. The distributed high efficient energy saving phase change thermal storage system of claim 2, wherein, The heat storage regulation module obtains the heating capacity of the heat pump based on the maximum liquid level in each of the manifolds, as measured in real time by the liquid level sensor, under the first liquid level height condition. The heat storage regulation module obtains the heat pump's heating capacity as the first heating capacity under the third liquid level condition; The heat storage regulation module obtains the heat pump's heating capacity as the second heating capacity under the fourth liquid level condition; The third liquid level condition is that the maximum liquid level in each of the manifolds, as obtained in real time by the liquid level sensor, is less than 1 / 10 of the manifold height, and the fourth liquid level condition is that the maximum liquid level in each of the manifolds, as obtained in real time by the liquid level sensor, is greater than or equal to 1 / 10 of the manifold height. The heat output of the heat pump, obtained under the third and fourth liquid level conditions, is determined by the maximum liquid level height in each of the manifolds, which is obtained in real time by the liquid level sensor.

4. The distributed high-efficiency energy-saving phase change thermal energy storage system according to claim 3, characterized in that, The heat storage regulation module obtains the operating power of each heating plate as the first operating power under the first liquid level change condition; the heat storage regulation module obtains the operating power of each heating plate as the second operating power under the second liquid level change condition; the heat storage regulation module determines not to start each heating plate under the third liquid level change condition. Wherein, the first liquid level change condition is that the liquid level height change rate in each of the manifolds is less than the first standard liquid level height change rate; the second liquid level change condition is that the liquid level height change rate in each manifold is greater than or equal to the first standard liquid level height change rate and less than or equal to the second standard liquid level height change rate; and the third liquid level change condition is that the liquid level height change rate in each manifold is greater than the second standard liquid level height change rate. The first operating power obtained under the first liquid level change condition is determined by the liquid level height change rate in each of the manifolds and the first standard liquid level height change rate. The second operating power obtained under the second liquid level change condition is determined by the liquid level height change rate in each manifold, the first standard liquid level height change rate, and the second standard liquid level height change rate.

5. The distributed high efficient energy saving phase change thermal storage system of claim 4, wherein, The phase change thermal storage system further includes a first delivery pump connected to the first delivery pipe for providing kinetic energy to the phase change material where the pressure difference is insufficient. The thermal storage regulation module obtains a first standard rate of change of liquid level height and a second standard rate of change of liquid level height based on the real-time pump pressure of the first delivery pump. The first standard rate of change of liquid level height is determined either by the difference between the standard pump pressure of the first delivery pump and the real-time pump pressure of the first delivery pump, or by the ratio of the standard pump pressure of the first delivery pump to the real-time pump pressure of the first delivery pump. The second standard rate of change of liquid level height is determined by the first standard rate of change of liquid level height.

6. The distributed high efficient energy saving phase change thermal storage system of claim 5, wherein, The circulation adjustment module obtains the real-time pump pressure of the first delivery pump based on the maximum liquid level height in each manifold, wherein... The real-time pump pressure of the first delivery pump can be determined by the difference between the height of each manifold and the maximum liquid level in each manifold, or it can be equal to the standard pump pressure of the first delivery pump. Specifically, when the minimum liquid level in each of the manifolds is higher than the liquid level in the first delivery pipe, the first delivery pump does not operate.

7. The distributed high-efficiency energy-saving phase change thermal energy storage system according to claim 6, characterized in that, The circulation adjustment module obtains the real-time pump pressure of the second delivery pump based on the real-time pump pressure of the first delivery pump, wherein, The real-time pump pressure of the second delivery pump can be determined either by the logarithm of the standard pump pressure of the first delivery pump with the real-time pump pressure of the first delivery pump as the base, or by the ratio of the real-time pump pressure of the first delivery pump to the standard pump pressure of the first delivery pump. When the first delivery pump is not running, the real-time pump pressure of the second delivery pump is equal to 0.5 times the standard pump pressure of the first delivery pump.

8. The distributed high efficient energy saving phase change thermal storage system of claim 7, wherein, The circulation adjustment module obtains the cooling capacity of the cooling chip under the first pump pressure condition as the first cooling capacity; the circulation adjustment module obtains the cooling capacity of the cooling chip under the second pump pressure condition as the second cooling capacity. Wherein, the first pump pressure condition is that the real-time pump pressure of the second delivery pump is less than or equal to 1.2 times the standard pump pressure of the second delivery pump, and the second pump pressure condition is that the real-time pump pressure of the second delivery pump is greater than 1.2 times the standard pump pressure of the second delivery pump. The cooling capacity of the cooling chip obtained under the first pump pressure condition and the second pump pressure condition is determined by the real-time pump pressure of the second delivery pump.

9. The distributed high efficient energy saving phase change thermal storage system of claim 8, wherein, The cycle adjustment module obtains the cylinder's operating cycle as a first operating cycle under the first cooling determination condition; the cycle adjustment module obtains the cylinder's operating cycle as a second operating cycle under the second cooling determination condition. The first cooling determination condition is that the cooling capacity of the cooling chip is less than or equal to the average of the standard cooling capacity and the designed cooling capacity of the cooling chip, and the second cooling determination condition is that the cooling capacity of the cooling chip is greater than the average of the standard cooling capacity and the designed cooling capacity of the cooling chip. The operating cycle of the cylinder, obtained under the first and second cooling determination conditions, is determined by the cooling capacity of the cooling element.

10. The distributed high efficient energy saving phase change thermal storage system of claim 9, wherein, The transportation control module obtains the solid design gravity inside the transportation box as the first design gravity under the first operating cycle condition. The transportation control module obtains the solid design gravity inside the transportation box as the second design gravity under the second operating cycle condition. When the pressure sensor detects that the weight of the solid inside the transport box reaches the designed weight of the solid, the conveying device is started in a first operating mode. The first operating mode is that the conveying device drives the transport box in a counterclockwise direction. The first operating cycle condition is that the operating cycle of the cylinder is less than or equal to a preset operating cycle. The second operating cycle condition is that the operating cycle of the cylinder is greater than the preset operating cycle. The solid design gravity inside the transport box, obtained under the first and second operating cycle conditions, is determined by the operating cycle of the cylinder.

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