Thermal management system and method of controlling the same

Abstract

The present disclosure provides a thermal management system, comprising: a refrigerant line for circulation of a refrigerant, wherein the refrigerant flows through a compressor, a condenser, an expansion valve, and a heat exchanger. The thermal management system further comprises a controller configured to determine a flow rate of refrigerant discharged from the compressor based on a target temperature in the heat exchanger, and to control an opening degree of the expansion valve based on the determined flow rate of refrigerant discharged from the compressor.

Description

Technical Field

[0001] This disclosure relates to a thermal management system and a control method thereof for controlling the opening of an expansion valve based on the flow rate of refrigerant discharged from the compressor. background

[0002] In recent years, thermal management systems have become a key element in the automotive industry for achieving various objectives, such as improving fuel efficiency, protecting batteries and engines, and providing a comfortable interior environment for passengers. In particular, with the continued expansion of the electric vehicle market (such as pure electric vehicles and hybrid vehicles), the importance of technologies that maximize energy efficiency and achieve optimal thermal management for automobiles is increasingly evident.

[0003] One of the core elements of this type of thermal management system is the refrigerant cycle, and the effective control of the expansion valve and compressor during the refrigerant cycle is a crucial factor determining system performance. In the refrigerant cycle, the compressor compresses the refrigerant to a high-temperature, high-pressure state, while the expansion valve controls the refrigerant flow to transition from the high-temperature, high-pressure state to a low-temperature, low-pressure state. The compressor and expansion valve constitute the high-pressure side and low-pressure side of the system, respectively.

[0004] The control of these two devices directly affects the cooling and heating performance of the system. In particular, the control of the expansion valve plays an important role in optimizing the stability and performance of the entire system.

[0005] The above description of the background technology is intended only to enhance the understanding of the background of this disclosure and should not be construed as an admission that it corresponds to prior art known to those skilled in the art. Summary of the Invention

[0006] Therefore, in view of the above problems, this disclosure aims to provide a thermal management system and a control method thereof, which can optimally control the opening of the expansion valve so that the refrigerant discharged from the compressor can flow through the expansion valve without changing its flow rate.

[0007] The purpose of this disclosure is not limited to the purposes mentioned above, and other purposes not mentioned should be clearly understood by those skilled in the art through the following description.

[0008] According to one aspect of this disclosure, the above and other objectives can be achieved by providing a thermal management system comprising: a refrigerant line for refrigerant circulation, wherein refrigerant flows through a compressor, a condenser, an expansion valve, and a heat exchanger; and a controller configured to determine the refrigerant flow rate discharged from the compressor based on a target temperature in the heat exchanger, and to control the opening degree of the expansion valve based on the refrigerant flow rate.

[0009] According to another aspect of this disclosure, a method for controlling a thermal management system is provided, the system comprising: a refrigerant line through which refrigerant circulates through a compressor, a condenser, an expansion valve, and a heat exchanger, the method comprising: determining a refrigerant flow rate discharged from the compressor based on a target temperature in the heat exchanger, and controlling the opening degree of the expansion valve based on the determined refrigerant flow rate. Attached Figure Description

[0010] The above and other objects, features and advantages of this disclosure will become clearer from the following detailed description taken in conjunction with the accompanying drawings.

[0011] Figure 1-3 This is a schematic diagram illustrating an example of a thermal management circuit implementing a thermal management system applicable to embodiments of the present disclosure.

[0012] Figure 4 This is a schematic diagram illustrating a controller according to an embodiment of the present disclosure.

[0013] Figure 5 This is a schematic diagram illustrating an expansion valve opening control method according to an embodiment of the present disclosure.

[0014] Figure 6 This is a schematic diagram illustrating a control method for a thermal management system according to an embodiment of the present disclosure. Detailed Implementation

[0015] The descriptions of the specific structures and functions of the embodiments disclosed in this specification or application are merely illustrative of embodiments of this disclosure, which can be implemented in various forms, and should not be construed as being limited to the embodiments described in this specification or application.

[0016] Because embodiments according to this disclosure can be modified in various ways and have various forms, specific embodiments will be shown in the accompanying drawings and described in detail in this specification or application. However, this is not intended to limit embodiments according to the concepts of this disclosure to a particular form, but should be understood to include all modifications, equivalents, and alternatives, encompassing the spirit and scope of this disclosure.

[0017] Unless otherwise stated, all terms (including technical or scientific terms) shall have the same meaning as commonly understood by one of ordinary skill in the art to which this disclosure pertains. Common terms, such as those defined in dictionaries, shall be interpreted as having the same meaning as the term in the relevant technical context. Unless otherwise defined in this disclosure, such terms shall not be interpreted in an idealized or overly formal manner.

[0018] The embodiments disclosed in this specification will now be described in detail with reference to the accompanying drawings. The same or similar reference numerals denote the same or similar components, and redundant descriptions thereof will be omitted.

[0019] In the following description of the embodiments, the term "preset" means that the value of a parameter is preset when the parameter is used in a method or algorithm. According to the embodiments, the value of the parameter can be set at the beginning of the method or algorithm or during the execution of the method or algorithm.

[0020] The terms “module”, “unit”, or “part” used to refer to components are for the purpose of understanding the components herein and should not be considered to have specific meanings or functions. As used herein, the terms “unit”, “module”, or “part” refer to a single unit that performs at least one function or operation, which may be implemented by hardware, software, or a combination thereof. The operation or function of the methods described in conjunction with the forms disclosed herein may be directly embodied in hardware or software modules executed by a processor, or in a combination thereof. When a component, unit, part, controller, device, element, apparatus, etc., of this disclosure is described as having a purpose or performing an operation, function, etc., it shall be considered herein to be “configured” to satisfy that purpose or perform that operation or function. Individual components, units, parts, controllers, devices, elements, apparatuses, etc., may be embodied individually or included in a processor and memory (e.g., a non-transitory computer-readable medium) as part of that apparatus.

[0021] In the following description of the embodiments disclosed in this specification, detailed descriptions of known functions and configurations incorporated herein are omitted where such descriptions might obscure the subject matter of this disclosure. Furthermore, the accompanying drawings are provided only for ease of understanding of the embodiments disclosed herein and do not limit the technical concepts disclosed herein, but include all modifications, equivalents, and alternatives within the spirit and scope of this disclosure.

[0022] Although the terms "first" and / or "second" are used to describe various components, such components are not limited by these terms. These terms are used to distinguish one component from another.

[0023] When a component is "attached to" or "connected to" another component, it should be understood that although the component may be directly attached to or connected to another component, there may be a third component between the two components. When a component is "directly attached to" or "directly connected to" another component, it should be understood that there are no elements between the two components.

[0024] Unless the context clearly indicates otherwise, elements described in the singular are intended to include multiple elements.

[0025] In this specification, it is further understood that the terms "comprising" or "including" specifically refer to the presence of the said features, graphics, steps, operations, components, parts or combinations thereof, but do not exclude the presence or addition of one or more other features, graphics, steps, operations, components, parts or combinations thereof.

[0026] Before describing the control method of the thermal management system according to embodiments of the present disclosure, the following references are made. Figure 1-3 Describe an example of implementing the thermal management circuit that constitutes this thermal management system.

[0027] Figure 1-3 This is a schematic diagram illustrating an example of a thermal management circuit implementing a thermal management system applicable to embodiments of the present disclosure.

[0028] refer to Figure 1 The thermal management system includes a refrigerant line RL, and can perform cooling / heating within the vehicle and thermal management of vehicle components through the refrigerant line RL.

[0029] More specifically, in addition to the refrigerant line RL, the thermal management system may also include a coolant line CL for heat exchange with vehicle components 110a and 110b. The refrigerant circulating in the refrigerant line RL and the coolant circulating in the coolant line CL can exchange heat with each other.

[0030] More specifically, vehicle components 110a and 110b that perform thermal management can be connected to the coolant line CL, and the temperature of vehicle components 110a and 110b can be managed to an appropriate range or target temperature through heat exchange between vehicle components 110a and 110b and the coolant line CL.

[0031] Vehicle components 110a and 110b may include a drive system 110a (e.g., a motor and an inverter) and a battery 110b. However, in embodiments of this disclosure, vehicle components 110a and 110b are not necessarily limited to the above examples and may include various components requiring heat dissipation. For example, vehicle components that perform thermal management and are connected to the coolant line CL may include various types of controllers (not shown), such as an autopilot controller, a motor controller, a vehicle controller, and a controller involved in performing integrated thermal management according to embodiments of this disclosure.

[0032] Although Figure 1A coolant line CL is shown for thermal management of the drive system 110a and the battery 110b. However, such a coolant line CL can be replaced by a coolant line for thermal management of other vehicle components 110a and 110b (e.g., a controller), or it can coexist with coolant lines for thermal management of other components during implementation. Furthermore, various embodiments may include various situations, such as providing only a single coolant line for thermal management of a single component, and multiple components connected in series to a single coolant line.

[0033] Coolant pumps 121, 122, and 123 can be provided for circulating coolant in coolant lines CL1 and CL2, and coolant pumps 121, 122, and 123 can consume electricity to deliver coolant to vehicle components 110a and 110b. Such coolant pumps 121, 122, and 123 can be implemented as electric water pumps (EWPs), for example, by using an electric motor to circulate coolant.

[0034] Coolant introduced into vehicle assemblies 110a and 110b via coolant pumps 121, 122 and 123 can absorb the heat generated by vehicle assemblies 110a and 110b through heat exchange as it flows through them, thereby cooling vehicle assemblies 110a and 110b.

[0035] As the coolant flows through vehicle components 110a and 110b, the coolant that has absorbed heat can flow to radiators 130a and 130b. During its flow through radiators 130a and 130b, the heat absorbed from vehicle components 110a and 110b is released into the surrounding environment, and then flows back to vehicle components 110a and 110b. In this case, radiators 130a and 130b can be classified as a low-temperature radiator 130a and a high-temperature radiator 130b.

[0036] A compressor 151, a condenser 152, expansion valves 153a, 153b and 153c, and a heat exchanger are installed on the refrigerant line RL, through which the refrigerant circulates in the refrigerant line RL.

[0037] More specifically, the refrigerant line RL may be equipped with heat exchangers, such as a water-cooled condenser 154a, an air-cooled condenser 154b, a cooler 159, and an evaporator 156, and heat exchange between the refrigerant and the surrounding environment occurs in such heat exchangers.

[0038] Compressor 151 consumes electricity to discharge refrigerant in a high-temperature, high-pressure state. The high-temperature, high-pressure refrigerant passing through compressor 151 expands in expansion valves 153a, 153b, and 153c, transforming into a low-temperature, low-pressure state. It then exchanges heat with the surrounding environment through a heat exchanger in a low-temperature, low-pressure state, thereby lowering the ambient temperature. In one embodiment, expansion valves 153a and 153b can be implemented as electronic expansion valves, and expansion valve 153c can be implemented as a thermal expansion valve.

[0039] For example, when heat exchange occurs via the water-cooled condenser 154a, the heat from the coolant lines CL1 and CL2 connected to vehicle components 110a and 110b can be absorbed by the heat pump function of the refrigerant line RL. More specifically, refer to Figure 2 The high-temperature, high-pressure refrigerant flowing through compressor 151 is converted to a low-temperature, low-pressure state as it flows through condenser 152 and expansion valve 153a. This low-temperature, low-pressure refrigerant then exchanges heat with coolant lines CL1 and CL2 in water-cooled condenser 154a. After the heat exchange, the refrigerant flows through receiver 157 and back to compressor 151. By repeating this process, thermal management of vehicle components 110a and 110b can be achieved through the heat pump function.

[0040] Furthermore, the battery 110b connected to the cooler 159 can be cooled during heat exchange via the cooler 159. More specifically, refer to... Figure 3 The high-temperature, high-pressure refrigerant flowing through compressor 151 is converted to a low-temperature, low-pressure state when it flows through expansion valve 153b, and this low-temperature, low-pressure refrigerant exchanges heat with coolant line CL2 in cooler 159. After heat exchange, the refrigerant flows through receiver 157 and back to compressor 151. By repeating this process, battery 110b can eventually be cooled.

[0041] In addition, the thermal management system may also be equipped with: a cooling fan 171 and damper 172 for controlling the inflow of external air, a liquid receiver dryer RD for removing moisture from the refrigerant flowing through the water-cooled condenser 154a, a liquid receiver tank RT with a coolant storage space, valves v1, v2, v3 and v4 for controlling the flow rate of refrigerant or coolant, an indoor heater 161 for cooling / heating, an evaporator 156, a blower 173, a temporary door 174, an air inlet valve 175, and an internal heater 162 for raising the battery temperature, etc. Furthermore, a high-pressure side sensor S capable of detecting at least one of temperature and pressure may be installed on the outlet side of the compressor 151.

[0042] Based on the thermal management circuit of the above thermal management system, various types of thermal management can be performed. In particular, when the thermal management system is applied to a vehicle, various thermal management schemes can be obtained based on the vehicle's internal conditions, external conditions, and the status of vehicle components 110a and 110b.

[0043] Figure 1 The description mainly shows the components related to the thermal management circuit applicable to embodiments of this disclosure. The actual thermal management system can be implemented by including more or fewer components.

[0044] The following describes the operations performed by the controller that controls the components of the aforementioned thermal management system.

[0045] Figure 4 A schematic diagram of a controller according to an embodiment of the present disclosure is shown.

[0046] refer to Figure 4 The controller 200 can adjust the temperature according to the target temperature T. tar Control the opening φ of expansion valves 153a and 153b exv The operating load N of compressor 151 comp The duty cycle of cooling fan 171 fan and the operating volume N of the coolant pump ewp The controller may include: a communication device for communicating with other controllers or sensors to control the controller's functions; a memory for storing operating system or logic instructions and input / output information; and one or more processors for performing the judgments, calculations, decisions, etc., required to control these functions.

[0047] More specifically, the refrigerant flow determination unit 210 can be based on the target temperature T. tar To determine the refrigerant flow rate discharged from compressor 151 (Refrigerant flow rate discharged from the compressor) It can also determine the airflow through the cooling fan 171. and the coolant flow rate through coolant pumps 121, 122 and 123 In this case, the refrigerant flow determination unit 210 can determine the refrigerant flow rate discharged by the compressor. And accordingly, the airflow through the cooling fan 171 can be determined. and the coolant flow rate through coolant pumps 121, 122 and 123

[0048] For example, the refrigerant flow determination unit 210 can determine the refrigerant flow rate, that is, the refrigerant flow rate discharged by the compressor. It satisfies the target temperature in the heat exchanger and minimizes the power consumption of compressor 151 within a preset prediction range. The prediction range refers to a time range; using the above method, the optimal refrigerant flow rate that minimizes power consumption within a certain time period starting from the current time can be obtained.

[0049] In this case, based on the determined refrigerant flow rate discharged from the compressor. The airflow rate through cooling fan 171 can be determined. and the coolant flow rate through coolant pumps 121, 122 and 123

[0050] On the other hand, the refrigerant flow determination unit 210 can determine the refrigerant flow rate, that is, the refrigerant flow rate discharged by the compressor. It meets the target temperature in the heat exchanger and minimizes the total power consumption of the compressor 151, cooling fan 171, and coolant pumps 121, 122, and 123 within a preset prediction range.

[0051] The target temperature in the heat exchanger is, when... Figure 2 As shown, when heat exchange occurs through expansion valve 153a and water-cooled condenser 154a, the target temperature in water-cooled condenser 154a can be determined by the temperature of vehicle component 110a, coolant temperature, etc., which are thermal management targets. Furthermore, when... Figure 3 When heat exchange occurs through expansion valve 153b and cooler 159, the target temperature in the heat exchanger is the target temperature in cooler 159, and it can be determined by the temperature of vehicle component 110b, coolant temperature, etc., which are thermal management targets.

[0052] Control unit 220 can base its operation on a determined refrigerant flow rate discharged from the compressor. airflow and coolant flow To control expansion valves 153a and 153b, and further control the operation of compressor 151, cooling fan 171 and coolant pumps 121, 122 and 123.

[0053] Control unit 220 can control the opening degree φ of expansion valves 153a and 153b. exv The operating outputs of compressor 151, cooling fan 171, and coolant pumps 121, 122, and 123 are sent to the corresponding control targets.

[0054] The opening φ of expansion valves 153a and 153b exv This can represent the opening degree of expansion valves 153a and 153b between fully open and fully closed states, and can also represent the situation where heat exchange occurs through expansion valve 153a and water-cooled condenser 154a (e.g.) Figure 2 The opening degree of expansion valve 153a (as shown) can also indicate the situation where heat exchange occurs between expansion valve 153b and cooler 159 (e.g.) Figure 3 (As shown) The opening degree of expansion valve 153b.

[0055] The operating speeds of compressor 151, cooling fan 171, and coolant pumps 121, 122, and 123 can be respectively based on the rotational speed N of the motor driving compressor 151. comp The driving load duty of the motor driving the cooling fan 171 fan and the rotational speed N of the motors driving coolant pumps 121, 122 and 123. ewp Output in the form of .

[0056] Control unit 220 is based on the refrigerant flow rate discharged from the compressor. To control the opening φ of expansion valve 153a or 153b exv In this case, the opening φ of the expansion valve 153a or 153b is controlled. exv In this case, the temperature and pressure on the heat exchanger side, such as the water-cooled condenser 154a or cooler 159, can be disregarded. In other words, in one embodiment, the control unit 220 can operate solely based on the refrigerant flow rate discharged from the compressor. To control the opening φ of expansion valve 153a or 153b exv This eliminates the need to consider the temperature and pressure on the heat exchanger side. Therefore, in one embodiment, it is not necessary to control the opening φ of the expansion valve 153a or 153b based on the temperature and pressure on the heat exchanger side. exv Therefore, the low-pressure side sensor used to detect the temperature and pressure on the heat exchanger side can be omitted.

[0057] More specifically, the control unit 220 can control the opening degree φ of the expansion valve 153a or 153b. exv So that the flow rate of refrigerant flowing through expansion valve 153a or 153b is equal to the flow rate of refrigerant discharged from the compressor. Correspondingly, the opening degree φ of expansion valve 153a or 153b can be adjusted. exv Control is the flow rate of refrigerant allowed to flow through the expansion valve and the flow rate of refrigerant discharged from the compressor. The minimum opening degree that matches (i.e., the lowest value of the opening degree). However, the flow rate of refrigerant flowing through expansion valve 153a or 153b is different from the flow rate of refrigerant discharged from the compressor. Corresponding situations may include: the flow rate of refrigerant flowing through the expansion valve and the flow rate of refrigerant discharged from the compressor. The difference between them is within the preset tolerance range, and the flow rate of refrigerant flowing through the expansion valve and the flow rate of refrigerant discharged from the compressor are considered. The corresponding situation.

[0058] The control unit 220 can refer to the following table based on the refrigerant flow rate discharged from the compressor. To control the opening φ of expansion valve 153a or 153b exv The table shows the refrigerant flow rate discharged by the compressor. The input value is its corresponding opening φ. exv This is the output value. See below for reference. Figure 5 Describe it.

[0059] Figure 5 This is a schematic diagram illustrating an expansion valve opening control method according to an embodiment of the present disclosure.

[0060] Figure 5 Shows the refrigerant flow rate discharged from the compressor. The opening φ of expansion valve 153a or 153b exv The relationship between these parameters applies to controlling the opening φ of expansion valves 153a or 153b. exv The table shows the refrigerant flow rate discharged from the compressor. The values ​​of each value are related to the opening φ of expansion valve 153a or 153b. exv The values ​​are matched. In this case, the refrigerant flow rate discharged from the compressor can be set. The specific value corresponds to the opening φ of expansion valve 153a or 153b. exv So that the refrigerant flow rate through expansion valve 153a or 153b is equal to the refrigerant flow rate discharged from the compressor. Matching. For example, the opening φ of expansion valve 153a or 153b can be set using the following formula. exv .

[0061]

[0062] In this formula, A is the refrigerant inflow area when expansion valve 153a or 153b is fully open, and ρ in P is the density of the refrigerant flowing into expansion valve 153a or 153b. in and P out These represent the refrigerant pressures on the inlet and outlet sides of expansion valves 153a and 153b, respectively.

[0063] According to this opening control, the refrigerant discharged by the compressor 151 can flow through the expansion valve 153a or 153b without changing its flow rate, thereby preventing problems such as energy consumption and high pressure caused by the mismatch between the refrigerant flow rate through the expansion valve 153a or 153b and the refrigerant flow rate discharged by the compressor 151.

[0064] Refer again Figure 4The controller 200 may also include a low-pressure side temperature / pressure determination unit 230. The low-pressure side temperature / pressure determination unit 230 may be based on the opening φ of the expansion valve 153a or 153b. exv To determine at least one of the refrigerant pressure or temperature on the outlet side of expansion valves 153a or 153b. In other words, in one embodiment, the temperature and pressure of the low-pressure refrigerant can be obtained by using a low-pressure side temperature / pressure determination unit 230 instead of a low-pressure side sensor.

[0065] More specifically, the low-pressure side temperature / pressure determination unit 230 can be based on the opening φ of the expansion valve 153a or 153b. exv To determine the refrigerant pressure change at expansion valve 153a or 153b, and based on the determined refrigerant pressure change and the refrigerant pressure P at the compressor 151 outlet side detected by the high-pressure side sensor S. high The refrigerant pressure at the outlet side of expansion valve 153a or 153b is determined by the high-pressure side pressure. For example, the low-pressure side temperature / pressure determination unit 230 can use the following formula to determine the refrigerant pressure at the outlet side of expansion valve 153a or 153b.

[0066] P out,exv =P in,exv +△P exv

[0067] In this formula, P out,exv P is the refrigerant pressure on the outlet side of expansion valve 153a or 153b. in,exv The pressure is the refrigerant pressure at the inlet side of expansion valve 153a or 153b, while the pressure P at the outlet side of compressor 151 is obtained through high-pressure side sensor S. high Can be used as P in,exv ΔP exv This indicates the refrigerant pressure change at expansion valve 153a or 153b, and its value depends on the opening φ of expansion valve 153a or 153b. exv Determined. For example, by referring to a table, which pre-stores the opening φ according to expansion valve 153a or 153b. exv Given a specific value for the refrigerant pressure change, the refrigerant pressure change can be obtained.

[0068] Furthermore, the low-pressure side temperature / pressure determination unit 230 can determine the refrigerant pressure P at the compressor 151 outlet side detected by the high-pressure side sensor S. high and temperature T highThe temperature of the refrigerant at the outlet side of expansion valve 153a or 153b is determined by the pressure of the refrigerant at the outlet side of expansion valve 153a or 153b. For example, the low-pressure side temperature / pressure determination unit 230 can use the following formula to determine the temperature of the refrigerant at the outlet side of expansion valve 153a or 153b.

[0069]

[0070] In this formula, T s This indicates the temperature on the outlet side of expansion valve 153a or 153b, T. d This indicates the temperature at the outlet side of compressor 151. η isen γ is the isentropic process efficiency of compressor 151, which can be obtained through the mapping relationship between the operating quantity of compressor 151 and the refrigerant pressure. γ is a constant, which can be the ratio of isobaric specific heat to isocapacitive specific heat in isentropic processes, and a set value, such as 1.088, can be used in multi-directional processes.

[0071] Furthermore, the pressure and temperature at the outlet side of expansion valve 153a or 153b can represent the pressure and temperature at the outlet side of expansion valve 153a when heat exchange occurs through expansion valve 153a and water-cooled condenser 154a (e.g., Figure 2 (as shown); it can also represent the pressure and temperature at the outlet side of the expansion valve 153b when heat exchange occurs through the expansion valve 153b and the cooler 159 (as shown). Figure 3 (As shown).

[0072] Since the low-pressure side temperature / pressure determination unit 230 determines the temperature and pressure at the outlet side of the expansion valve 153a or 153b in this manner, a separate sensor on the low-pressure side can be omitted, thereby simplifying the configuration of the refrigerant line RL and reducing the cost of installing sensors.

[0073] The following will refer to Figure 6 A control method for a thermal management system according to an embodiment of the present disclosure is described.

[0074] Figure 6 This is a schematic diagram illustrating a control method for a thermal management system according to an embodiment of the present disclosure.

[0075] refer to Figure 6 The controller 200 determines whether the refrigerant cycle is in operation (S610). In the refrigerant cycle, the refrigerant circulates through the compressor 151, condenser 152, expansion valves 153a and 153b and heat exchanger in the refrigerant line RL.

[0076] If the refrigerant cycle is not in operation ("No" in S610), there is no need to adjust the opening φ of expansion valves 153a and 153b. exvTherefore, no further control is required. If the refrigerant cycle is in operation ("Yes" in S610), the refrigerant flow rate discharged from the compressor is determined through optimal control of the refrigerant cycle. (S620).

[0077] Subsequently, the controller 200 determines the refrigerant flow rate discharged from the compressor. To control the opening φ of expansion valves 153a and 153b exv (S630), in this case, the opening φ of expansion valves 153a and 153b exv It can be controlled so that the refrigerant flow through the expansion valve is equal to the refrigerant flow discharged from the compressor. Correspondingly.

[0078] According to the various embodiments of this disclosure described above, the refrigerant flow through the expansion valve is controlled by the opening degree corresponding to the refrigerant flow rate output by the compressor, so that the refrigerant output by the compressor can flow through the expansion valve without changing its flow rate, thereby preventing abnormal pressure or heat exchanger performance degradation.

[0079] The effects that can be obtained by this disclosure are not limited to those mentioned above. Those skilled in the art to which this disclosure pertains should be able to clearly understand other effects not mentioned through the description.

[0080] Although the present disclosure has been described and illustrated with reference to the specific embodiments described above, those skilled in the art should understand that the present disclosure can be modified and altered in various ways without departing from the technical spirit of the present disclosure as defined by the claims.

Claims

1. A thermal management system, comprising: A refrigerant pipeline is configured for circulating refrigerant, wherein the refrigerant is configured to flow through a compressor, a condenser, an expansion valve, and a heat exchanger; and The controller is configured as follows: The refrigerant flow rate discharged from the compressor is determined based on the target temperature in the heat exchanger; and The opening degree of the expansion valve is controlled based on the determined refrigerant flow rate.

2. The thermal management system according to claim 1, wherein, The controller is also configured to control the opening of the expansion valve based on the refrigerant flow rate rather than on the temperature and pressure on the heat exchanger side.

3. The thermal management system according to claim 1, wherein, The controller is also configured to control the opening of the expansion valve so that the refrigerant flow through the expansion valve corresponds to a determined refrigerant flow.

4. The thermal management system according to claim 3, wherein, The controller is also configured to control the opening of the expansion valve to a minimum opening that matches the refrigerant flow through the expansion valve with the refrigerant flow discharged from the compressor.

5. The thermal management system according to claim 3, wherein, The controller is also configured to control the opening degree of the expansion valve via a reference table, the table taking the refrigerant flow rate as input and the opening degree of the expansion valve corresponding to the input value as output.

6. The thermal management system according to claim 1, wherein, The controller is also configured to determine the refrigerant pressure on the outlet side of the expansion valve based on the opening degree of the expansion valve.

7. The thermal management system according to claim 6 further includes a high-pressure side sensor disposed on the compressor outlet side, configured to detect the pressure of the refrigerant on the compressor outlet side. in, The controller is also configured to determine the refrigerant pressure change at the expansion valve based on the opening degree of the expansion valve, and to determine the refrigerant pressure at the expansion valve outlet based on the determined refrigerant pressure change and the refrigerant pressure at the compressor outlet detected by the high-pressure side sensor.

8. The thermal management system according to claim 7, wherein, The high-pressure side sensor also detects the temperature of the refrigerant at the compressor outlet, and the controller determines the temperature of the refrigerant at the expansion valve outlet based on the pressure and temperature of the refrigerant at the compressor outlet detected by the high-pressure side sensor and the determined pressure of the refrigerant at the expansion valve outlet.

9. The thermal management system according to claim 1, wherein, The controller is also configured to determine the refrigerant flow rate such that the refrigerant flow rate meets the target temperature in the heat exchanger and minimizes the power consumption of the compressor within a preset prediction range.

10. The thermal management system according to claim 9, further comprising: At least one coolant line having a coolant pump for circulating coolant, the coolant exchanging heat with the refrigerant through the heat exchanger; as well as A cooling fan is used to introduce air into the thermal management target where heat is exchanged with the coolant. The controller is further configured to determine the refrigerant flow rate such that the refrigerant flow rate meets the target temperature in the heat exchanger and minimizes the total power consumption of the compressor, the coolant pump, and the cooling fan within a preset prediction range.

11. A method for controlling a thermal management system, the method comprising the following steps: The refrigerant flow rate discharged from the compressor is determined based on the target temperature in the heat exchanger; as well as The opening degree of the expansion valve is controlled based on the determined refrigerant flow rate.

12. The method according to claim 11, wherein, The control steps include controlling the opening of the expansion valve based on the refrigerant flow rate rather than on the temperature and pressure on the heat exchanger side.

13. The method according to claim 11, wherein, The control steps include controlling the opening of the expansion valve so that the refrigerant flow rate through the expansion valve corresponds to the determined refrigerant flow rate.

14. The method according to claim 13, wherein, The control steps include controlling the opening of the expansion valve to a minimum opening that matches the refrigerant flow rate through the expansion valve with the refrigerant flow rate discharged from the compressor.

15. The method according to claim 13, wherein, The control steps include: controlling the opening degree of the expansion valve by referring to a table, wherein the table takes the refrigerant flow rate discharged by the compressor as the input value and the opening degree of the expansion valve corresponding to the input value as the output value.

16. The method of claim 11, further comprising the step of: The pressure of the refrigerant on the outlet side of the expansion valve is determined based on the opening degree of the expansion valve.

17. The method according to claim 16, wherein, The step of determining the pressure includes: determining the refrigerant pressure change at the expansion valve based on the opening degree of the expansion valve, and determining the refrigerant pressure at the outlet side of the expansion valve based on the determined refrigerant pressure change and the refrigerant pressure at the compressor outlet side detected by a high-pressure side sensor installed at the compressor outlet side.

18. The method of claim 17, further comprising the step of: The temperature of the refrigerant at the outlet side of the expansion valve is determined based on the pressure and temperature of the refrigerant at the compressor outlet side detected by the high-pressure side sensor and the determined pressure of the refrigerant at the outlet side of the expansion valve.

19. The method according to claim 11, wherein, The determining step includes: determining the refrigerant flow rate discharged by the compressor, such that the refrigerant flow rate meets the target temperature in the heat exchanger and minimizes the power consumption of the compressor within a preset prediction range.

20. The method according to claim 19, wherein, The determining step includes: determining the refrigerant flow rate discharged by the compressor such that the refrigerant flow rate meets the target temperature in the heat exchanger, and minimizing the total power consumption of the compressor, coolant pump, and cooling fan within a preset prediction range, wherein the coolant pump is installed on the coolant pipeline for coolant circulation, the coolant exchanges heat with the refrigerant through the heat exchanger, and the cooling fan is used to introduce air into the thermal management target that exchanges heat with the coolant.

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