CN219492688U - Compressor with adjustable guide vanes and energy storage thermal management system - Google Patents

Abstract

The utility model discloses an energy storage thermal management system, which adopts a centrifugal compressor to carry out refrigeration cycle, and a guide vane with an adjustable opening is arranged at the inlet of the centrifugal compressor, and the surge margin of the centrifugal compressor can be obviously increased and the energy efficiency of the full working condition of the energy storage thermal management system can be obviously improved by carrying out joint adjustment on the opening of the guide vane and the rotating speed of the centrifugal compressor.

Description

Compressor with adjustable guide vanes and energy storage thermal management system

Technical Field

The utility model relates to the technical field of heat management, in particular to a compressor with adjustable guide vanes and an energy storage heat management system.

Background

Thermal management refers to the management and control of the temperature of the overall system, discrete components, or its environment, with the purpose of maintaining proper operation or improving performance or longevity of the components. Currently, thermal management is generally required in fields such as electrochemical energy storage, and thermal management has a significant impact on the performance, lifetime, and safety of energy storage systems. Because the heat exchange capability of the liquid cooling heat management system is strong, the temperature difference of the electric core can be within 3 ℃, and therefore, compared with an air cooling system, the liquid cooling can obviously prolong the service life of the energy storage system. In view of this, liquid cooling systems are currently used in the energy storage field.

The refrigeration capacity required by the energy storage liquid cooling system is usually 100kW or less, and the refrigeration cycle with small refrigeration capacity adopts a traditional vortex or rotor compressor. In some heat management systems, in order to omit an oil return pipeline, the reliability of the compressor and the system is improved, and a centrifugal compressor is adopted to replace a scroll compressor. An air bearing is arranged in the centrifugal compressor, and the rotating shaft is not contacted with the bearing during working, but is suspended by a gas film to suspend a motor rotor, so that the service life of the bearing can be prolonged by at least 1 time; meanwhile, the size and the weight of the centrifugal compressor based on the high-speed permanent magnet synchronous motor are respectively about 50 percent and about 90 percent smaller than those of the vortex compressor.

However, the centrifugal compressor usually has surge protection, that is, at a certain exhaust pressure, the minimum flow rate only by adjusting the rotation speed is limited by a surge line, which means that at a certain ambient temperature, the minimum refrigerating capacity of the centrifugal compressor is constrained, and the improvement of the partial load energy efficiency of the energy storage power station is not facilitated.

Disclosure of Invention

Aiming at part or all of the problems in the prior art, a first aspect of the utility model provides a compressor with adjustable guide vanes, wherein the opening degree of the guide vanes is adjustable at the air inlet of the compressor.

Further, the vane includes:

the blades are uniformly distributed around the circumference of the rotating shaft of the compressor; and

the actuating shaft is arranged along the central axis of the vane and is perpendicular to the rotating shaft of the compressor, and under the control of the driving mechanism, the actuating shaft drives the vane to rotate so as to adjust the opening of the guide vane, and then the flow entering the compressor is adjusted.

Further, the centrifugal compressor comprises multiple stages, and guide vanes are arranged at the air inlets of each stage.

Further, the opening of the next-stage guide vane is obtained by interpolation according to the opening of the previous-stage guide vane.

Further, the driving mechanism is a driving motor.

Based on the compressor as described above, a second aspect of the present utility model provides an energy storage thermal management system, comprising:

a refrigeration cycle module for a refrigerant cycle, comprising:

a compressor as described above for compressing a refrigerant to form a first state refrigerant;

a condenser having an inlet connected to a discharge port of the compressor for cooling the refrigerant in the first state to form a refrigerant in a second state having a temperature lower than the first state but a pressure equal to the first state; and

a throttling device connected to the outlet of the condenser to throttle the refrigerant in the second state to expand to a third state, the third state having a pressure lower than the second state but a temperature equal to the second state;

an intermediate heat exchanger comprising:

the refrigerant pipeline comprises a first inlet and a first outlet, the first inlet is communicated with the outlet of the throttling device, and the first outlet is communicated with the air inlet of the compressor; and

a coolant pipe line arranged around the refrigerant pipe line, so that the coolant and the refrigerant can exchange heat, and the coolant pipe line is communicated with the pipe line of the coolant circulation module and comprises a second inlet and a second outlet; and

the cooling fluid circulation module is used for cooling the energy storage device through cooling fluid circulation and comprises a water pump, and the water pump is used for providing power for the cooling fluid circulation.

Further, the coolant circulation module further includes a PTC heater to supply heat to the energy storage device.

Further, the energy storage heat management system further comprises a fan arranged at the condenser and used for introducing normal-temperature air into the condenser to realize heat exchange.

Further, the energy storage heat management system further comprises a temperature sensor and a pressure sensor.

Further, the temperature sensor and the pressure sensor are arranged at the first outlet of the intermediate heat exchanger and/or the exhaust port of the compressor.

According to the energy storage thermal management system and the control method thereof, the guide vane with the adjustable opening is arranged at the inlet of the centrifugal compressor, the surge margin of the centrifugal compressor can be obviously increased by carrying out joint adjustment on the opening of the guide vane and the rotating speed of the centrifugal compressor, and the energy storage thermal management system can work under smaller refrigerating capacity at a certain environmental temperature, so that the energy efficiency of the full working condition of the energy storage thermal management system is obviously improved.

Drawings

To further clarify the above and other advantages and features of embodiments of the present utility model, a more particular description of embodiments of the utility model will be rendered by reference to the appended drawings. It is appreciated that these drawings depict only typical embodiments of the utility model and are therefore not to be considered limiting of its scope. In the drawings, for clarity, the same or corresponding parts will be designated by the same or similar reference numerals.

FIG. 1 shows a schematic diagram of a thermal management system for storing energy according to an embodiment of the present utility model;

FIG. 2 illustrates a schematic structural view of a vane of an embodiment of the present utility model;

FIG. 3 illustrates a centrifugal compressor unloading line schematic of an embodiment of the utility model;

FIG. 4 is a flow chart of a control method of an energy storage thermal management system according to an embodiment of the utility model;

FIG. 5 is a diagram illustrating the shape factor SF versus surge line shape for one embodiment of the present utility model;

FIG. 6 shows a schematic view of surge lines at different rotational speeds according to an embodiment of the present utility model; and

FIG. 7 illustrates a schematic diagram of the opening relationship of a two-stage vane according to one embodiment of the utility model.

Detailed Description

In the following description, the present utility model is described with reference to various embodiments. One skilled in the relevant art will recognize, however, that the embodiments may be practiced without one or more of the specific details, or with other alternative and/or additional methods, materials, or components. In other instances, well-known structures, materials, or operations are not shown or described in detail to avoid obscuring aspects of the utility model. Similarly, for purposes of explanation, specific numbers, materials and configurations are set forth in order to provide a thorough understanding of the embodiments of the utility model. However, the utility model is not limited to these specific details. Furthermore, it should be understood that the embodiments shown in the drawings are illustrative representations and are not necessarily drawn to scale.

Reference throughout this specification to "one embodiment" or "the embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment is included in at least one embodiment of the present utility model. The appearances of the phrase "in one embodiment" in various places in the specification are not necessarily all referring to the same embodiment.

In an embodiment of the utility model, the term "surge line" refers to a line connecting surge points of different vane openings. A point on the "variable frequency surge line" means that the compressor can no longer be unloaded by a reduced speed. A point "Guan Daoshe surge line" refers to the point that is the minimum cold that the compressor can achieve at the corresponding pressure ratio.

Because the centrifugal compressor has surge protection, namely, under certain exhaust pressure, the minimum flow only by regulating the rotating speed can be limited by a surge line, which means that the minimum refrigerating capacity of the compressor is restrained under certain ambient temperature, and the improvement of partial load energy efficiency of the energy storage power station is not facilitated. According to the energy storage thermal management system and the control method thereof, provided by the utility model, the guide vane with the adjustable opening degree is arranged at the inlet of the centrifugal compressor, and the surge margin of the centrifugal compressor can be obviously increased by carrying out joint adjustment on the opening degree of the guide vane and the rotating speed of the centrifugal compressor.

The embodiments of the present utility model will be further described with reference to the drawings.

Fig. 1 shows a schematic structure of an energy storage thermal management system according to an embodiment of the present utility model. As shown in fig. 1, an energy storage thermal management system includes a refrigeration cycle module 001, an intermediate heat exchanger 002, and a coolant circulation module 003. The refrigeration cycle module 001 is used for circulation of a refrigerant, heat is taken away through phase change of the refrigerant, and then cooling can be performed on cooling liquid, the cooling liquid circulation module 003 is used for circulation of the cooling liquid to cool or supply heat to the energy storage device, and the refrigeration cycle module 001 and the cooling liquid circulation module 003 are coupled through the intermediate heat exchanger 002.

As shown in fig. 1, the core component of the refrigeration module 001 is a centrifugal compressor 011, preferably an air-floating centrifugal compressor. An air inlet of the centrifugal compressor 011 is communicated with an intermediate heat exchanger 002, and a high-temperature low-pressure refrigerant after heat exchange with a cooling liquid in the intermediate heat exchanger enters the centrifugal compressor 011 to be compressed, so that a first-state refrigerant is formed.

In order to increase the surge margin of the centrifugal compressor, in one embodiment of the utility model, a guide vane is provided at the air inlet of the centrifugal compressor 011, wherein the opening of the guide vane is adjustable. FIG. 2 illustrates a schematic structural view of a vane of an embodiment of the present utility model. As shown in fig. 2, in one embodiment of the utility model, the vane comprises a plurality of blades 201, which are evenly distributed circumferentially around the rotational axis of the centrifugal compressor. By controlling the rotation of the blades about an axis, the opening of the vanes may be controlled, thereby regulating the flow into the centrifugal compressor, in one embodiment of the utility model the axis of the blades is perpendicular to the rotational axis of the centrifugal compressor. As shown in fig. 2, in one embodiment of the present utility model, an actuating shaft 202 is disposed at the central axis of each vane, and the actuating shaft 202 is perpendicular to the rotation axis of the centrifugal compressor, and under the control of a driving mechanism such as a driving motor, the actuating shaft drives the vane to rotate to adjust the opening of the guide vane, thereby adjusting the flow entering the centrifugal compressor, and realizing the increase or decrease of the refrigerating capacity. In one embodiment of the utility model, when the centrifugal compressor is multi-stage, guide vanes may be provided at each stage of air intake, i.e. multi-stage guide vanes may be included in the refrigeration module.

As shown in fig. 1, the refrigeration cycle module 001 further includes a condenser 012 and a throttle device 013. Wherein the inlet of the condenser 012 is connected to the exhaust port of the centrifugal compressor 011 for cooling the refrigerant in the first state to obtain a refrigerant in a second state, the temperature of the refrigerant in the second state being lower than that of the refrigerant in the first state but the pressure is substantially unchanged. In one embodiment of the present utility model, in order to improve the refrigerating efficiency, a fan 014 is further disposed at the fins of the condenser 012, and the fan 014 introduces the normal temperature air into the fins of the condenser 012, so that the heat of the high temperature refrigerant inside the condenser 012 exchanges heat with the air, thereby achieving the purpose of condensation. The throttle device 013 is connected to the outlet of the condenser 012 to throttle the refrigerant in the second state, and the throttled refrigerant rapidly expands to form a third state, in which the pressure of the refrigerant is lower than that of the refrigerant in the second state but the temperature is substantially unchanged. The refrigerant in the third state enters the intermediate heat exchanger to exchange heat with the coolant. In an embodiment of the present utility model, the throttling device refers to a device or element for reducing the pressure of gas for evaporation purposes, and may be, for example: expansion valves, capillaries, orifice tubes, etc.

In order to calculate the refrigeration requirement of the system and thus control the working state of each device or module, and to protect the system from running, in one embodiment of the present utility model, a temperature sensor T and a pressure sensor P are also provided in the refrigeration module 001. As shown, the temperature sensor T and the pressure sensor P may be provided at the first outlet of the intermediate heat exchanger and/or at the exhaust port of the centrifugal compressor, for example.

The intermediate heat exchanger comprises two inlets and two outlets, thereby forming a refrigerant pipeline and a cooling liquid pipeline. The inlet and outlet of the refrigerant pipeline are denoted as a first inlet and a first outlet, the first inlet is communicated with the throttling device 013, and the first outlet is communicated with the air inlet of the centrifugal compressor 011. The inlet and outlet of the cooling liquid pipeline are marked as a second inlet and a second outlet, the cooling liquid pipeline is respectively communicated with the inlet and outlet of the pipeline in the cooling liquid circulation module, and the cooling liquid pipeline is arranged around the refrigerant pipeline, so that cooling liquid and refrigerant can exchange heat. In one embodiment of the utility model, an evaporator is employed as the intermediate heat exchanger.

As shown, in one embodiment of the utility model, the cooling module 003 includes a water pump 031 and a PTC heater 032. Wherein the water pump 031 is used to power the coolant circulation. The water pump 031 is connected to the second inlet of the intermediate heat exchanger through a water pipe, and sends the cooling liquid into the intermediate heat exchanger. After transferring heat to the refrigerant, the cooling liquid reaches the energy storage device through the pipeline, and heat generated by the battery core of the energy storage device, such as an energy storage battery, is transferred to the cooling liquid, and the warmed cooling liquid returns to the water pump again to circulate. The PTC heater 032 is then used to supply heat to an energy storage device, such as a battery cell. In one embodiment of the present utility model, in order to enhance heat exchange efficiency, in the intermediate heat exchanger, a coolant inflow direction and a refrigerant inflow direction are opposite, for example, the intermediate heat exchanger first inlet and second outlet may be provided at a first side of the intermediate heat exchanger, and the second inlet and first outlet may be provided at a second side of the intermediate heat exchanger opposite to the first side.

The energy storage heat management system in the embodiment of the utility model adopts the air-cooled condenser, when the refrigeration requirement of the energy storage power station is reduced and the refrigeration capacity is required to be correspondingly reduced, as the environment temperature is kept unchanged, the unloading line of the centrifugal compressor is shown as a figure 3, namely the pressure ratio of the centrifugal compressor is kept unchanged, and only the flow is reduced. As shown in fig. 3, the centrifugal compressor works at point P1 with the flow pressure ratio and the rotation speed percentage (m 1, pr, N1) at rated refrigeration capacity, and the centrifugal compressor is unloaded along the unloading line when the refrigeration capacity is reduced, first reaches point P2 (m 2, pr, N2), and the guide vane remains fully opened in the process from point P1 to point P2, but the rotation speed is reduced from point N1 to point N2, and the point P2 is already located on the variable frequency surge line and cannot be further unloaded by reducing the rotation speed. In one embodiment of the utility model, m2 is equal to about 70% of m1, i.e. the cooling capacity can be reduced to about 70% of the nominal value by frequency conversion alone. In order to further reduce the cold, the opening of the guide vane is required to be turned down from the point P2, and finally the point P3 (m 3, pr and N2) is reached, and in the process, the rotating speed is kept unchanged by N2, and only the opening of the guide vane is turned down. In one embodiment of the utility model, m3 is equal to about 40% of m1, i.e. adjusting the vane opening only can reduce the rated cooling capacity to about 40%. The point P3 is located on the vane closing surge line, i.e., the point P3 is the minimum cold energy point that the centrifugal compressor can achieve at the pressure ratio pr.

Based on this, fig. 4 shows a flow chart of a control method of the energy storage thermal management system according to an embodiment of the utility model. As shown in fig. 4, the control method includes:

first, in step 401, a surge line is fitted. Fitting to obtain surge lines of the centrifugal compressor at different rotating speeds. Before a real-time cold control strategy, the map of the centrifugal compressor needs to be calibrated through a test, each rotating speed line has surge points with different guide vane opening degrees, and in order to improve efficiency, only limited data points are usually measured. Based on the prioritized data points, in one embodiment of the utility model, the following functional relationship is used to fit the surge line:

Pr＝Prmin-(Prmax-Prmin)/(e^a-1)+(Prmax-Prmin)/(e^a-1)*e^b；

wherein, the liquid crystal display device comprises a liquid crystal display device,

pr is the pressure ratio, prmin is the minimum pressure ratio, prmax is the maximum pressure ratio, prmin=Prmin_d (Spd_a/Spd_d)/(SF_spd_c) Prmin/Prmax), prmax=Prmax_d (Spd_a/Spd_d)/(SF_spd c), where Spd_d is the design speed, spd_a is the actual speed, prmin_d is the design speed minimum pressure ratio, prmax_d is the design speed maximum pressure ratio, SF_spd is the speed linear factor, which in one embodiment of the utility model takes a value of 2, and c=Spd_d/Spd_a when Spd_a > Spd_d, c=Spd_a/Spd_d when Spd_a < Spd_d, FIG. 6 shows a schematic diagram of different speeds, 100%, 90% speeds according to one embodiment of the utility model;

a=sf (IGVmax-IGVmin), where IGVmax is the maximum opening of the guide vane, IGVmin is the minimum opening of the guide vane, SF is a shape factor, and is used to control the shape of the surge line, the smaller the absolute value of the shape factor is, the more conservative the surge line is, fig. 5 is a schematic diagram showing the relationship between the shape factor SF and the shape of the surge line according to an embodiment of the present utility model, as shown in fig. 5, sf= -0.01 is more conservative, sf= -0.02 is moderate, sf= -0.04 is more aggressive; and

b=sf (IGV-IGVmin), wherein IGV is the current opening of the guide vane;

next, at step 402, the system is initialized. And fitting to obtain a surge line, and then adjusting the cold quantity. The system controls the guide vane to be in a full-open state in an initial state, namely when the system is just started;

next, in step 403, the current cooling capacity is monitored in real time and it is determined whether the target cooling capacity is reached. And after the energy storage heat management system starts to work, monitoring and judging whether the current cold quantity reaches the target cold quantity in real time. In one embodiment of the utility model, the current cold quantity is judged by monitoring the condensation temperature and the return water temperature of the cooling water in real time. Specifically, the method comprises the following steps:

measuring the condensation temperature and the backwater temperature in real time;

calculating the difference between the condensing temperature and the ambient temperature, and comparing the difference with a first preset value:

if the difference value is smaller than the first preset value, the target cooling capacity is not reached; if the difference value is larger than or equal to the first preset value, calculating the backwater temperature and the backwater temperature

The difference of the target values is compared with a second preset value:

if the difference value between the backwater temperature and the target value is larger than a second preset value, the target cold quantity is not reached; and

if the difference value between the backwater temperature and the target value is smaller than or equal to a second preset value, when the current temperature maintaining time is recorded, if the current temperature maintaining time is larger than or equal to the preset time, the target cold quantity is reached, and otherwise, the target cold quantity is not reached.

In one embodiment of the utility model, the first preset value is 7 ℃, the second preset value is 1.5 ℃, and the preset time period is 15min, when the condensation temperature minus the ambient temperature is more than or equal to 7 ℃, if the deviation between the measured value and the target value of the backwater temperature is within 1.5 ℃ and the temperature is kept for 15min, the target cold energy is considered to be reached. If the cooling capacity is required to be reduced according to the monitoring result, the step 441 is performed, and if the cooling capacity is required to be increased, the step 451 is performed;

in step 441, the rotational speed is reduced. When the cooling capacity needs to be reduced, the rotating speed is reduced according to a first preset step length, and meanwhile, whether the current cooling capacity reaches the target cooling capacity or not is monitored in real time according to the method. In one embodiment of the present utility model, the first preset step is a step of 0.5% of the design rotational speed. In one embodiment of the present utility model, if the difference between the condensation temperature and the ambient temperature is lower than the first preset value, the throttling device may be turned down to increase the difference between the condensation temperature and the ambient temperature above the first preset value, and then the rotation speed is reduced to be associated with the throttling device until the target cooling capacity is reached. During the rotation speed reduction, the frequency conversion surge line is reached as the rotation speed is gradually reduced, and the process proceeds to step 442. In one embodiment of the utility model, surge is considered to touch the surge line when the number of surges occurring within a specified period of time is greater than a first preset value, wherein whether surge occurs is determined based on the current percentage fluctuation. In one embodiment of the utility model, a surge is considered to occur when the current percentage fluctuates by 10% or more, such as: the 1 st current percentage was 50%, the 2 nd current percentage was 65%, and the current percentage fluctuation was 15% without any operation, and a surge was considered to occur. In yet another embodiment of the utility model, two surges within 4 minutes are considered to reach the surge line;

at step 442, the vane opening and rotational speed are co-tuned. When the surge line is reached, if the cold quantity still needs to be continuously reduced, the opening degree of the guide vane needs to be reduced according to a second preset step length. In one embodiment of the present utility model, the second preset step is 1% of the opening. When the guide vane is turned down, the pressure ratio is reduced, when the difference between the condensing temperature and the ambient temperature is lower than a first preset value and the target cooling capacity is not reached yet, the rotating speed is further increased to enable the condensing temperature to return to the ambient temperature more than +7 ℃, and then the guide vane and the rotating speed are adjusted in a combined mode, so that the difference between the condensing temperature and the ambient temperature is maintained to be more than the first preset value and the target cooling capacity is reached. As the coldness continues to decrease, the closing vane surge line is touched, at which point the minimum coldness has been reached. In order to protect the centrifugal compressor, in one embodiment of the utility model, in the process of reducing the cold quantity, if the number of times of surging in a designated time period is larger than a second preset value, the compressor is triggered to stop for protection, for example, 4 times of surging in 8min, and the centrifugal compressor is controlled to stop;

in step 451, the vane opening is increased. When the cooling capacity needs to be increased, the opening of the guide vane is increased according to a third preset step length, and meanwhile whether the current cooling capacity reaches the target cooling capacity or not is monitored in real time according to the method. In one embodiment of the present utility model, the third preset step is 1% of the opening. If the target cooling capacity is not reached when the guide vane is fully opened, entering step 452;

at step 452, the rotational speed is increased. If the target cold quantity is not reached when the guide vane is fully opened, the rotating speed is increased according to the fourth preset step length until the target cold quantity is reached. In one embodiment of the present utility model, the fourth preset step is a step of 0.5% of the design rotational speed.

As previously mentioned, in other embodiments of the utility model, the centrifugal compressor, if multi-stage, may have vanes disposed at the inlet of each stage. Taking a two-stage centrifugal compressor as an example, when guide vanes are arranged at two-stage air inlets, the surge lines of the two-stage guide vanes are required to be calibrated respectively, the two-stage centrifugal compressor is fitted in a parameterized manner according to the method, two-stage linkage is required when the opening of the guide vanes is regulated, the opening of the second-stage guide vanes is a function of the opening of the first stage, and the sectional interpolation is carried out according to the opening relation shown in fig. 7.

According to the energy storage thermal management system and the control method thereof, the guide vane with the adjustable opening is arranged at the inlet of the centrifugal compressor, the surge margin of the centrifugal compressor can be obviously increased by carrying out joint adjustment on the opening of the guide vane and the rotating speed of the centrifugal compressor, and the energy storage thermal management system can work under smaller refrigerating capacity at a certain environmental temperature, so that the energy efficiency of the full working condition of the energy storage thermal management system is obviously improved.

While various embodiments of the present utility model have been described above, it should be understood that they have been presented by way of example only, and not limitation. It will be apparent to those skilled in the relevant art that various combinations, modifications, and variations can be made therein without departing from the spirit and scope of the utility model. Thus, the breadth and scope of the present utility model as disclosed herein should not be limited by any of the above-described exemplary embodiments, but should be defined only in accordance with the following claims and their equivalents.

Claims (9)

1. A compressor with adjustable guide vanes, characterized in that the air inlet of the compressor is provided with guide vanes with adjustable opening, wherein the guide vanes comprise:

the blades are uniformly distributed around the circumference of the rotating shaft of the compressor; and

the actuating shaft is arranged along the central axis of the vane and is perpendicular to the rotating shaft of the compressor, and under the control of the driving mechanism, the actuating shaft drives the vane to rotate so as to adjust the opening of the guide vane, and then the flow entering the compressor is adjusted.

2. The compressor of claim 1, wherein the compressor comprises multiple stages, and vanes are provided at an inlet of each stage.

3. The compressor as recited in claim 2 wherein the opening of the subsequent stage vane is interpolated from the opening of the previous stage vane.

4. The compressor of claim 1, wherein the drive mechanism is a drive motor.

5. An energy storage thermal management system, comprising:

a refrigeration cycle module comprising:

the compressor of any one of claims 1 to 4, configured to compress refrigerant to form a first state refrigerant;

a condenser having an inlet connected to a discharge port of the compressor and configured to cool the refrigerant in the first state to form a refrigerant in a second state, the second state having a temperature lower than the first state but a pressure equal to the first state; and

a throttling device connected to the outlet of the condenser to throttle the refrigerant in the second state to expand to a third state, the third state having a pressure lower than the second state but a temperature equal to the second state;

an intermediate heat exchanger comprising:

the refrigerant pipeline comprises a first inlet and a first outlet, the first inlet is communicated with the outlet of the throttling device, and the first outlet is communicated with the air inlet of the compressor; a cooling liquid pipeline which is arranged around the refrigerant pipeline, so that cooling liquid and the refrigerant can exchange heat, and is communicated with the pipeline of the cooling liquid circulation module, and comprises a second inlet and a second outlet; and

a coolant circulation module configured to circulate a coolant to cool the energy storage device includes a water pump configured to power the coolant circulation.

6. The energy storage thermal management system of claim 5, wherein the coolant circulation module further comprises a PTC heater to provide heat to the energy storage device.

7. The energy storage thermal management system of claim 5, further comprising a fan disposed at the condenser configured to direct ambient air into the condenser to effect heat exchange.

8. The energy storage thermal management system of claim 5, further comprising a temperature sensor and a pressure sensor.

9. The energy storage thermal management system of claim 8, wherein the temperature sensor and pressure sensor are disposed at a first outlet of the intermediate heat exchanger and/or at a discharge outlet of the compressor.