CN118306170A

CN118306170A - Control method of thermal management system and related device

Info

Publication number: CN118306170A
Application number: CN202410276768.5A
Authority: CN
Inventors: 王玥; 胡浩茫
Original assignee: Huawei Technologies Co Ltd
Current assignee: Huawei Technologies Co Ltd
Priority date: 2024-03-08
Filing date: 2024-03-08
Publication date: 2024-07-09

Abstract

A control method and a related device for a thermal management system are provided. In this scheme, this thermal management system includes controller and first refrigerant return circuit, and this first refrigerant return circuit includes compressor and bypass route, and the export of this compressor communicates with the entry of this bypass route, and the export of this bypass route communicates with the entry of this compressor. The controller is used for controlling the following operations to be performed: starting the compressor to work at a first rotation speed so that at least part of refrigerant output from the compressor is input into the compressor again through the bypass path; the rotational speed of the compressor is increased to a second rotational speed in case the inlet pressure of the compressor reaches a first pressure value and/or the inlet temperature of the compressor reaches a first temperature value. By adopting the scheme of the application, the normal use of the air conditioning system in a low-temperature environment can be realized.

Description

Control method of thermal management system and related device

Technical Field

The application relates to the technical field of thermal management, in particular to a control method and a related device of a thermal management system.

Background

The vehicle is widely used as a convenient travel tool. Air conditioning systems are an important component in vehicles to regulate the temperature within the cabin and provide a comfortable riding environment for passengers. However, for example, in an environment of-20 degrees celsius or less, the compressor cannot be operated normally due to the excessively low temperature and pressure of the cooling medium at the inlet of the compressor, so that the air conditioning system cannot be used normally. In view of this, further research is needed in the aspect of thermal management of electric vehicles at present.

Disclosure of Invention

The application provides a control method and a related device of a thermal management system, which are used for realizing normal use of an air conditioning system in a low-temperature environment.

In a first aspect, the present application provides a method for controlling a thermal management system, the method being applied to a controller of the thermal management system; the heat management system includes a first refrigerant circuit including a compressor and a bypass path, an outlet of the compressor communicating with an inlet of the bypass path, and an outlet of the bypass path communicating with an inlet of the compressor.

The method comprises the following steps that the controller controls the following operations to be executed: starting the compressor to operate at a first rotational speed so that at least part of the refrigerant output from the compressor is re-input into the compressor through the bypass path; and increasing the rotational speed of the compressor to a second rotational speed when the inlet pressure of the compressor reaches a first pressure value and/or the inlet temperature of the compressor reaches a first temperature value.

In a specific implementation, the compressor cannot operate stably for a long time due to the fact that the inlet temperature and the pressure are too low in a low-temperature environment, but a short period of operation can be started. Based on the above, in the above scheme, during the transient operation, the compressor is started to operate at a lower rotation speed, and the high-pressure high-temperature refrigerant output by the compressor is sent back to the inlet of the compressor through the bypass path, so as to increase the temperature and pressure of the refrigerant at the inlet of the compressor, and promote the compressor to continue to operate at a low temperature. Then, when the inlet pressure or temperature of the compressor reaches a preset value, the rotating speed of the compressor is increased, the output power of the compressor is increased, and the compressor is further driven to continuously and stably run, so that the normal operation of the compressor at low temperature is realized, and the normal use of an air conditioning system in a low-temperature environment is realized.

In one possible embodiment, the thermal management system includes a second refrigerant circuit and a first coolant circuit, where the second refrigerant circuit includes refrigerant channels of the compressor, the condenser, and a refrigerant channel of the cooler; the first coolant circuit includes a first water pump and a coolant flow passage of the cooler. The method further comprises the following operation execution controlled by the controller: in the case where the temperature difference between the temperature of the coolant in the first coolant circuit and the inlet temperature of the compressor is greater than a first threshold value, the first water pump is started to drive the circulation of the coolant in the first coolant circuit.

In the above scheme, the cooling liquid in the first cooling liquid loop can be driven to circulate, and then the cooling medium in the second cooling medium loop can be heated through heat exchange of the cooler, so that the inlet temperature of the compressor can be further increased. That is, in the present solution, the existing cooling liquid is used as a heat source to save the cost of additional heating.

In one possible embodiment, the first refrigerant circuit further includes a first valve device, an inlet of the first valve device communicates with an inlet of the bypass path, and an outlet of the first valve device communicates with an outlet of the bypass path. In the process of increasing the rotation speed of the compressor to the second rotation speed, the method further comprises the following operation execution controlled by the controller: reducing the opening degree of the first valve device when the suction superheat degree of the compressor is larger than a second temperature value; when the suction superheat degree of the compressor is smaller than a third temperature value, the opening degree of the first valve device is increased.

In the above scheme, the opening of the first valve device can be adjusted to adjust the flow of the refrigerant flowing back to the inlet of the compressor by the bypass path, and then the temperature of the inlet of the compressor is adjusted to maintain the balance of the suction superheat degree of the compressor, so that the damage to the compressor caused by liquid impact is prevented.

In one possible embodiment, the thermal management system includes a second refrigerant loop or a third refrigerant loop; the second refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and a refrigerant flow passage of the cooler; the third refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and an evaporator; the aforementioned thermal management system further comprises a second valve device; the second valve device is arranged at the refrigerant flow passage inlet of the cooler or at the evaporator inlet. In the process of increasing the rotation speed of the compressor to the second rotation speed, the method further comprises the following operation execution controlled by the controller: increasing the opening degree of the second valve device when the suction superheat degree of the compressor is greater than a second temperature value; and reducing the opening degree of the second valve device when the suction superheat degree of the compressor is smaller than a third temperature value.

In the above scheme, the opening of the second valve device can be adjusted to adjust the flow of the refrigerant flowing back to the inlet of the compressor in the second refrigerant loop or the third refrigerant loop, so as to adjust the temperature of the inlet of the compressor to maintain the balance of the suction superheat degree of the compressor, and prevent the damage to the compressor caused by liquid impact.

In a possible embodiment, the thermal management system further comprises a gas-liquid separator and a condenser, the gas-liquid separator being disposed at an inlet of the compressor; the refrigerant flow passage inlet of the condenser is communicated with the outlet of the compressor and the inlet of the bypass path; the first refrigerant circuit further includes a first valve device, an inlet of the first valve device communicates with an inlet of the bypass path, and an outlet of the first valve device communicates with an outlet of the bypass path. In the process of increasing the rotation speed of the compressor to the second rotation speed, the method further comprises the following operation execution controlled by the controller: reducing the opening of the first valve device when the degree of supercooling of the outlet of the condenser refrigerant flow passage is greater than a fourth temperature value; and increasing the opening degree of the first valve device when the supercooling degree of the refrigerant flow passage outlet of the condenser is smaller than a fifth temperature value.

In the above scheme, the opening of the first valve device can be adjusted to adjust the flow rate of the refrigerant flowing back to the inlet of the compressor from the bypass path, so as to adjust the flow rate of the refrigerant entering the condenser to maintain the outlet supercooling degree of the refrigerant flow passage of the condenser, thereby adjusting the performance and stability of the system operation.

In a possible embodiment, the thermal management system further comprises a gas-liquid separator, the gas-liquid separator being disposed at an inlet of the compressor; the heat management system comprises a second refrigerant loop or a third refrigerant loop; the second refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and a refrigerant flow passage of the cooler; the third refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and an evaporator; the aforementioned thermal management system further comprises a second valve device; the second valve device is arranged at the refrigerant flow passage inlet of the cooler or at the evaporator inlet. In the process of increasing the rotation speed of the compressor to the second rotation speed, the method further comprises the following operation execution controlled by the controller: increasing the opening of the second valve device when the degree of supercooling of the condenser refrigerant flow passage outlet is greater than a fourth temperature value; and reducing the opening degree of the second valve device when the supercooling degree of the refrigerant flow passage outlet of the condenser is smaller than a fifth temperature value.

In the above scheme, the opening of the second valve device is adjusted to adjust the flow rate of the refrigerant flowing into the condenser in the second refrigerant loop or the third refrigerant loop, so as to adjust the supercooling degree balance of the outlet of the refrigerant flow channel of the condenser, and further adjust the performance and stability of the thermal management system.

In a possible embodiment, the thermal management system further includes a second coolant loop including a coolant flow passage of the condenser, a warm air core, and a second water pump. The method further comprises the following operation execution controlled by the controller: and when the outlet pressure of the compressor reaches a second pressure value and/or the output power of the compressor reaches a first power value, the second water pump is started and operates at a first duty ratio.

In the scheme, the second cooling liquid loop is started to operate when the compressor can stably operate and can provide certain heat, so that the cooling liquid of the loop can exchange heat from the condenser to obtain the heat.

In a possible embodiment, the thermal management system further comprises a blower for delivering hot air generated based on the warm air core; the method further comprises the following operation execution controlled by the controller: and the duty ratio of the second water pump is increased to a second duty ratio according to the rotating speed of the compressor and the air quantity of the blower.

In the scheme, the circulation speed of the second cooling liquid loop is increased by increasing the duty ratio of the second water pump so as to further obtain heat from the heat exchange of the first condenser, and the temperature of the cooling liquid in the second cooling liquid loop is rapidly increased.

In one possible embodiment, the first refrigerant circuit further includes a first valve device, an inlet of the first valve device communicates with an inlet of the bypass path, and an outlet of the first valve device communicates with an outlet of the bypass path. In the process of increasing the duty ratio of the second water pump to the second duty ratio according to the rotation speed of the compressor and the air quantity of the blower, the controller is further configured to control the following operations to be performed: reducing the opening degree of the first valve device when the outlet pressure of the compressor is smaller than a third pressure value and the inlet pressure of the compressor is smaller than an upper limit value of the inlet pressure of the compressor; and increasing the opening degree of the first valve device when the outlet pressure of the compressor is greater than the fourth pressure value and the inlet pressure of the compressor is less than the lower limit value of the inlet pressure of the compressor.

In the above scheme, the opening of the first valve device is adjusted, so that the inlet and outlet pressure of the compressor can meet the preset pressure range, and the output power of the compressor can meet the requirement.

In one possible embodiment, the thermal management system includes a second refrigerant loop or a third refrigerant loop; the second refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and a refrigerant flow passage of the cooler; the third refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and an evaporator; the aforementioned thermal management system further comprises a second valve device; the second valve device is arranged at the refrigerant flow passage inlet of the cooler or at the evaporator inlet.

In the process of increasing the duty ratio of the second water pump to the second duty ratio according to the rotation speed of the compressor and the air quantity of the blower, the controller is further configured to control the following operations to be performed: reducing the opening degree of the second valve device when the outlet pressure of the compressor is smaller than a third pressure value and the inlet pressure of the compressor is smaller than an upper limit value of the inlet pressure of the compressor; and increasing the opening degree of the second valve device when the outlet pressure of the compressor is greater than the fourth pressure value and the inlet pressure of the compressor is less than the lower limit value of the inlet pressure of the compressor.

In the above scheme, the opening of the second valve device is adjusted, so that the inlet and outlet pressure of the compressor can meet the preset pressure range, and the output power of the compressor can meet the requirement.

In a possible embodiment, the thermal management system further comprises a blower for delivering hot air generated based on the warm air core. The method further comprises the following operation execution controlled by the controller: and when the temperature of the cooling liquid in the second cooling liquid circuit reaches a sixth temperature value, the blower is started.

In the scheme, the blower is started to blow when the cooling liquid of the warm air loop rises to a certain temperature, so that cold air is prevented from being blown out to a user, and the user experience is improved.

In a possible embodiment, the aforementioned thermal management system further comprises a third valve device; an inlet of the third valve device communicates with an outlet of the compressor and an inlet of the bypass path. After the second water pump is started, the controller is also included to control the following operations to be executed: the opening degree of the third valve device is increased according to the outlet pressure and the temperature of the compressor.

In the scheme, the opening of the third valve device before the second water pump is started is smaller, so that the air pressure and the temperature of the inlet of the compressor can be quickly improved. After the second water pump is turned on, it is indicated that heating can be performed by the warm air circuit, and therefore the opening degree of the third valve device can be increased to increase the flow rate of the compressor to the condenser, so as to increase the heat exchanged to the warm air circuit.

In a possible embodiment, the thermal management system further comprises a blower for delivering hot air generated based on the warm air core; before the compressor is started, the method further comprises the following operation execution controlled by the controller: the blower is turned on.

In the scheme, the air blower is started before the compressor is started, noise generated during the operation of the air blower can be reduced, noise in the passenger cabin is reduced, and user experience is improved.

In one possible embodiment, the thermal management system is a thermal management system in a vehicle, and before the increasing the rotation speed of the compressor to the second rotation speed, the thermal management system further includes: determining an output power of the compressor based on an outside environment temperature, an inside environment temperature, and a model size of the vehicle; the second rotational speed is determined based on the output power.

In the scheme, the output power of the compressor is determined based on the ambient temperature and the vehicle size, and the rotating speed of the compressor is further determined, so that the heating requirement of the vehicle can be met under the condition of reducing unnecessary power output.

In a second aspect, the present application provides a thermal management system comprising a controller and a first refrigerant circuit, the first refrigerant circuit comprising a compressor and a bypass path, an outlet of the compressor being in communication with an inlet of the bypass path, an outlet of the bypass path being in communication with an inlet of the compressor. The controller is used for controlling the following operations to be executed: starting the compressor to operate at a first rotational speed so that at least part of the refrigerant output from the compressor is re-input into the compressor through the bypass path; and increasing the rotational speed of the compressor to a second rotational speed when the inlet pressure of the compressor reaches a first pressure value and/or the inlet temperature of the compressor reaches a first temperature value.

In one possible embodiment, the thermal management system includes a second refrigerant circuit and a first coolant circuit, where the second refrigerant circuit includes refrigerant channels of the compressor, the condenser, and a refrigerant channel of the cooler; the first coolant circuit includes a first water pump and a coolant flow passage of the cooler. The aforementioned controller is further configured to control execution of: in the case where the temperature difference between the temperature of the coolant in the first coolant circuit and the inlet temperature of the compressor is greater than a first threshold value, the first water pump is started to drive the circulation of the coolant in the first coolant circuit.

In one possible embodiment, the first refrigerant circuit further includes a first valve device, an inlet of the first valve device communicates with an inlet of the bypass path, and an outlet of the first valve device communicates with an outlet of the bypass path. The controller is further configured to control the following operations to be performed during the process of increasing the rotation speed of the compressor to the second rotation speed: reducing the opening degree of the first valve device when the suction superheat degree of the compressor is larger than a second temperature value; when the suction superheat degree of the compressor is smaller than a third temperature value, the opening degree of the first valve device is increased.

In one possible embodiment, the thermal management system includes a second refrigerant loop or a third refrigerant loop; the second refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and a refrigerant flow passage of the cooler; the third refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and an evaporator; the aforementioned thermal management system further comprises a second valve device; the second valve device is arranged at the refrigerant flow passage inlet of the cooler or at the evaporator inlet. The controller is further configured to control the following operations to be performed during the process of increasing the rotation speed of the compressor to the second rotation speed: increasing the opening degree of the second valve device when the suction superheat degree of the compressor is greater than a second temperature value; and reducing the opening degree of the second valve device when the suction superheat degree of the compressor is smaller than a third temperature value.

In a possible embodiment, the thermal management system further comprises a gas-liquid separator and a condenser, the gas-liquid separator being disposed at an inlet of the compressor; the refrigerant flow passage inlet of the condenser is communicated with the outlet of the compressor and the inlet of the bypass path; the first refrigerant circuit further includes a first valve device, an inlet of the first valve device communicates with an inlet of the bypass path, and an outlet of the first valve device communicates with an outlet of the bypass path. The controller is further configured to control the following operations to be performed during the process of increasing the rotation speed of the compressor to the second rotation speed: reducing the opening of the first valve device when the degree of supercooling of the outlet of the condenser refrigerant flow passage is greater than a fourth temperature value; and increasing the opening degree of the first valve device when the supercooling degree of the refrigerant flow passage outlet of the condenser is smaller than a fifth temperature value.

In a possible embodiment, the thermal management system further comprises a gas-liquid separator, the gas-liquid separator being disposed at an inlet of the compressor; the heat management system comprises a second refrigerant loop or a third refrigerant loop; the second refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and a refrigerant flow passage of the cooler; the third refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and an evaporator; the aforementioned thermal management system further comprises a second valve device; the second valve device is arranged at the refrigerant flow passage inlet of the cooler or at the evaporator inlet. The controller is further configured to control the following operations to be performed during the process of increasing the rotation speed of the compressor to the second rotation speed: increasing the opening of the second valve device when the degree of supercooling of the condenser refrigerant flow passage outlet is greater than a fourth temperature value; and reducing the opening degree of the second valve device when the supercooling degree of the refrigerant flow passage outlet of the condenser is smaller than a fifth temperature value.

In a possible embodiment, the thermal management system further includes a second coolant loop including a coolant flow passage of the condenser, a warm air core, and a second water pump. The aforementioned controller is further configured to control execution of: and when the outlet pressure of the compressor reaches a second pressure value and/or the output power of the compressor reaches a first power value, the second water pump is started and operates at a first duty ratio.

In a possible embodiment, the thermal management system further comprises a blower for delivering hot air generated based on the warm air core. The method further comprises the steps of: and the duty ratio of the second water pump is increased to a second duty ratio according to the rotating speed of the compressor and the air quantity of the blower.

In one possible embodiment, the first refrigerant circuit further includes a first valve device, an inlet of the first valve device communicates with an inlet of the bypass path, and an outlet of the first valve device communicates with an outlet of the bypass path. The controller is further configured to control the following operations to be performed during the process of increasing the duty ratio of the second water pump to the second duty ratio according to the rotation speed of the compressor and the air volume of the blower: reducing the opening degree of the first valve device when the outlet pressure of the compressor is smaller than a third pressure value and the inlet pressure of the compressor is smaller than an upper limit value of the inlet pressure of the compressor; and increasing the opening degree of the first valve device when the outlet pressure of the compressor is greater than the fourth pressure value and the inlet pressure of the compressor is less than the lower limit value of the inlet pressure of the compressor.

In one possible embodiment, the thermal management system includes a second refrigerant loop or a third refrigerant loop; the second refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and a refrigerant flow passage of the cooler; the third refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and an evaporator; the aforementioned thermal management system further comprises a second valve device; the second valve device is arranged at the refrigerant flow passage inlet of the cooler or at the evaporator inlet. The controller is further configured to control the following operations to be performed during the process of increasing the duty ratio of the second water pump to the second duty ratio according to the rotation speed of the compressor and the air volume of the blower: reducing the opening degree of the second valve device when the outlet pressure of the compressor is smaller than a third pressure value and the inlet pressure of the compressor is smaller than an upper limit value of the inlet pressure of the compressor; and increasing the opening degree of the second valve device when the outlet pressure of the compressor is greater than the fourth pressure value and the inlet pressure of the compressor is less than the lower limit value of the inlet pressure of the compressor.

In a possible embodiment, the thermal management system further comprises a blower for delivering hot air generated based on the warm air core. The method further comprises the steps of: and when the temperature of the cooling liquid in the second cooling liquid circuit reaches a sixth temperature value, the blower is started.

In a possible embodiment, the aforementioned thermal management system further comprises a third valve device; an inlet of the third valve device communicates with an outlet of the compressor and an inlet of the bypass path. After the second water pump is started, the controller is further configured to control the following operations to be performed: the opening degree of the third valve device is increased according to the outlet pressure and the temperature of the compressor.

In a possible embodiment, the thermal management system further comprises a blower for delivering hot air generated based on the warm air core; the controller is further configured to control the following operations to be performed before the compressor is started: the blower is turned on.

In a third aspect, the present application provides a controller comprising a processor and a memory, wherein the memory is for storing a computer program or computer instructions, the processor being for executing the computer program or computer instructions stored in the memory, such that the controller performs the method of any of the first aspects above.

In a fourth aspect, the present application provides a vehicle comprising a thermal management system as described in any one of the second aspects above. Or the vehicle comprises a controller as described in the third aspect above.

In a fifth aspect, the present application provides a computer readable storage medium having stored thereon a computer program or computer instructions for execution by a processor to implement the method of any one of the first aspects.

In a sixth aspect, the present application is a computer program product, which, when executed by a processor, implements a method according to any of the first aspects.

The solutions provided in the second aspect to the sixth aspect are used to implement or cooperate to implement the method provided in the first aspect correspondingly, so that the same or corresponding beneficial effects as those of the method corresponding to the first aspect can be achieved, and no further description is given here.

Drawings

FIG. 1 is a schematic diagram of a portion of a thermal management system according to an embodiment of the present application;

FIG. 2 is a schematic flow chart of a method according to an embodiment of the present application;

FIGS. 3 to 11 are schematic views illustrating a part of a thermal management system according to an embodiment of the present application;

fig. 12 is a schematic structural diagram of a controller according to an embodiment of the present application.

Detailed Description

In the embodiments of the present application, "a plurality" means two or more. In the embodiment of the present application, "and/or" is used to describe the association relationship of the association object, and represents three relationships that may exist independently, for example, a and/or B may represent: a alone, B alone, or both a and B. Description modes such as "at least one (or at least one) of a1, a2, … …, and an" adopted in the embodiments of the present application include a case where any one of a1, a2, … …, and an exists alone, and also include a case where any combination of any plurality of a1, a2, … …, and an exists alone; for example, the description of "at least one of a, b, and c" includes the case of a alone, b alone, c alone, a and b in combination, a and c in combination, b and c in combination, or abc in combination.

The terms "first," "second," and the like in this disclosure are used for distinguishing between similar elements or items having substantially the same function and function, and it should be understood that there is no logical or chronological dependency between the terms "first," "second," and "n," and that there is no limitation on the amount and order of execution. It will be further understood that, although the following description uses the terms first, second, etc. to describe various elements, these elements should not be limited by the terms. These terms are only used to distinguish one element from another element.

In various embodiments of the application, where terminology and/or descriptions of the various embodiments are consistent and may be referred to each other, unless specifically indicated as such and where logical conflict, features of different embodiments may be combined to form new embodiments in accordance with their inherent logical relationships.

Illustratively, the connection described in the embodiments of the present application refers to communication of the coolant channels or refrigerant channels, or communication achieved by adjusting the associated valve devices, etc.

In order to realize normal use of the air conditioning system in a low-temperature environment, a heater is adopted in the prior art to preheat the cooling liquid or the refrigerant, so that the compressor can work normally in the low-temperature environment. However, the heater has higher cost, and the extra consumption of electric energy is also needed, so that the endurance mileage is reduced. In order to realize normal use of the air conditioning system in a low-temperature environment at low cost, through deep analysis, it is found that the compressor can be started to operate briefly even in the low-temperature environment. However, the temperature and pressure at the inlet of the compressor are too low due to the excessively low ambient temperature, so that the requirement of stable operation of the compressor cannot be met (for example, the inlet pressure of the compressor is required to reach 1 atmosphere, the inlet temperature is higher than-20 ℃), etc. Thus, the compressor is stopped after a short period of operation (e.g., 1 to 5 minutes), so that the compressor cannot be operated normally. Based on the above, the embodiment of the application provides a control method of a thermal management system. The control method of the thermal management system can utilize the short running time of the compressor to send the high-temperature and high-pressure refrigerant output by the compressor back to the inlet of the compressor so as to improve the temperature and the pressure of the refrigerant at the inlet of the compressor, and further promote the compressor to continue running so as to realize the normal operation of the compressor at low temperature.

The embodiment of the application is suitable for vehicles and also suitable for other thermal management scenes of cooling (heat dissipation) and/or heating requirements. The application is mainly described by taking an application scene of a vehicle as an example. The embodiment of the application can be applied to traditional fuel vehicles and electric vehicles. The electric automobile is a vehicle suitable for driving by an electric driver. The electric vehicle may be a pure electric vehicle (pure ELECTRIC VEHICLE/battery ELECTRIC VEHICLE, pure EV/battery EV), a hybrid vehicle (hybrid ELECTRIC VEHICLE, HEV), a Range Extended ELECTRIC VEHICLE (REEV), a plug-in hybrid ELECTRIC VEHICLE (PHEV), a new energy vehicle (NEW ENERGY VEHICLE, NEV), or the like.

Before describing the control method of the thermal management system provided by the embodiment of the present application, a part of the thermal management circuit (including a refrigerant circuit and/or a cooling liquid circuit) included in the thermal management system in the embodiment of the present application is described in an exemplary manner. For ease of understanding, reference may be made to fig. 1 for exemplary purposes. As shown in fig. 1, the thermal management system according to the embodiment of the present application may include a refrigerant circuit L1. The refrigerant circuit L1 may include a compressor 101 and a bypass path 102. Illustratively, the outlet of the compressor 101 communicates with the inlet of the bypass path 102. The outlet of the bypass path 102 communicates with the inlet of the compressor 101.

In a specific implementation, the thermal management system of an embodiment of the present application may further include a controller (not shown). The controller may control the opening or closing of the devices in the thermal management system, the opening of the valve arrangement, etc. For example, the controller may send a control instruction to the device or the valve apparatus to cause the device or the valve apparatus to perform a corresponding operation according to the control instruction. Thus, various cooling modes, heating modes or heat dissipation modes can be realized. The embodiments of the present application are not described in detail.

The opening degree of the valve device described above refers to, for example, the caliber of the opening of the valve in the valve device. Specifically, the larger the opening, the larger the caliber indicating that the valve is opened, and the larger the flow rate which can pass through the valve. Conversely, the smaller the opening, the smaller the aperture that the valve opens, and the smaller the flow that can pass through the valve.

Based on the above-described thermal management system, the embodiment of the application provides a control method of the thermal management system. For example, see fig. 2, the method includes, but is not limited to, the following steps.

S201, the controller controls the compressor 101 to start and operate at the first rotational speed, so that at least part of the refrigerant output from the compressor 101 is re-input into the compressor 101 through the bypass path 102.

In a specific implementation, the inlet pressure to the compressor is too low (e.g., below 1 atmosphere, etc.) due to the ambient temperature being too low. And thus the compressor is not operated normally, so that the thermal management system is not operated normally. In this case, the compressor may be started and operated for a short period of time although it cannot be operated normally for a long period of time. Based on this, the controller may first control the compressor to start and operate the compressor at a lower rotational speed (i.e., the first rotational speed described above). So that at least part of the refrigerant outputted from the compressor 101 is re-inputted to the compressor 101 through the bypass path 102. Since the high-temperature and high-pressure refrigerant is outputted from the compressor 101, the high-temperature and high-pressure refrigerant flows back to the compressor 101 through the bypass path 102, and the temperature and pressure of the refrigerant at the inlet of the compressor 101 can be increased. Thereby causing the compressor to continue to operate.

The first rotation speed may be a preset initial rotation speed of the compressor, for example. In one possible implementation, the initial rotational speed is set to take into account environmental constraints in a scenario where the temperature and/or pressure are low, and the compressor can be started and operated for a period of time at the initial rotational speed even if the environmental conditions do not meet the requirements for stable operation of the compressor. The embodiment of the application does not limit the specific value and the acquisition mode of the first rotating speed.

Illustratively, the bypass path 102 may be a pipe or may be a flow channel integrated on a substrate, etc., which is not limited in this embodiment of the present application.

S202, when the inlet pressure of the compressor 101 reaches the first pressure value and/or the inlet temperature of the compressor 101 reaches the first temperature value, the controller controls the compressor 101 to increase the rotation speed to the second rotation speed.

In a specific implementation, after the high-temperature and high-pressure refrigerant output by the compressor 101 is led back to the inlet of the compressor 101 through the bypass path 102, the pressure and the temperature at the inlet of the compressor 101 are gradually increased. In the case where the inlet pressure of the compressor 101 reaches the first pressure value, or where the inlet temperature of the compressor 101 reaches the first temperature value, or where both are satisfied, the controller may send a control instruction to the compressor 101 to increase the rotation speed of the compressor 101 to the second rotation speed. So that the output power of the compressor 101 is improved, and the compressor is further promoted to continuously and stably run, and the normal operation of the compressor 101 at low temperature is realized.

The first pressure value or the first temperature value may be preset, which is not limited by the embodiment of the present application.

Illustratively, in one possible implementation, the correspondence between the inlet pressure of the compressor 101 and the inlet temperature of the compressor 101 is as follows: inlet temperature = saturation temperature for inlet pressure + suction superheat. Specifically, the saturation temperature corresponding to the inlet pressure may be obtained through table lookup under the condition of knowing the inlet pressure, which is not described herein. The description of the suction superheat is referred to in the following description and will not be described in detail here. Based on this, the inlet pressure is determined and the inlet temperature is determined with the suction superheat remaining stable. Then, the correspondence relationship is also present between the above-described first pressure value and the first temperature value, for example.

In one possible implementation, the thermal management system may be a thermal management system in a vehicle. The value of the second rotation speed may be determined based on the required output power of the compressor 101. The required output power may be determined according to the vehicle exterior environment temperature, the vehicle interior temperature, and the model size of the vehicle. For example, a map of the three of the vehicle exterior environment temperature, the vehicle interior temperature, and the model size of the vehicle with the required output power may be configured in advance. The required output power can be determined by looking up a table. For example, in a specific implementation, a temperature sensor may be provided on the vehicle to detect an outside environment temperature and an inside environment temperature. The controller can acquire the temperature outside the vehicle and the temperature inside the vehicle detected by the temperature sensor. The model size of the vehicle is also preconfigured and may be obtained by the controller. Then, the controller performs a look-up table based on the acquired vehicle exterior environment temperature, vehicle interior temperature and model size of the vehicle, thereby obtaining the required output power.

In addition, a map of the required output power and the rotational speed of the compressor 101 may be configured in advance. The second rotating speed corresponding to the required output power can be determined through table lookup. Alternatively, the required output power and/or the second rotational speed may be calculated in a corresponding manner instead of setting the map tables in advance. The embodiments of the present application are not limited in this regard.

In another possible implementation manner, if the thermal management system is not limited to the thermal management system in the vehicle, but may be a thermal management system in another device or environment, the second rotation speed may be directly preset, without any look-up table or calculation. Of course, the second rotational speed is greater than the first rotational speed.

It will be appreciated that the above description of the second rotational speed is merely exemplary and is not intended to limit embodiments of the present application. The embodiment of the application does not limit the specific value and the acquisition mode of the second rotating speed.

In another possible implementation manner, after the controller controls the compressor 101 to increase the rotation speed to the second rotation speed, the controller may further control the compressor 101 to increase the rotation speed to the third rotation speed. To meet higher output power requirements. The third rotational speed is greater than the second rotational speed. It will be appreciated that the controller may make one or more adjustments to the compressor speed based on the desired compressor output power, and embodiments of the present application are not limited in this regard.

In one possible implementation, as shown in fig. 3. The thermal management system further includes a refrigerant circuit L2 and a cooling liquid circuit L3. The refrigerant circuit L2 includes refrigerant channels of the compressor 101, the condenser 103, and a refrigerant channel of the cooler 104. The coolant circuit L3 includes a water pump 106 and a coolant flow passage of the cooler 104.

As shown in fig. 3, d ₁₁ represents an inlet of the refrigerant flow path of the condenser 103, and d ₁₂ represents an outlet of the refrigerant flow path of the condenser 103. In addition, the condenser 103 further includes a coolant flow passage. d ₁₃ denotes an inlet of the coolant flow passage of the condenser 103, and d ₁₄ denotes an outlet of the coolant flow passage of the condenser 103. d ₂₁ denotes an inlet of the refrigerant flow passage of the cooler 104, d ₂₂ denotes an outlet of the refrigerant flow passage of the cooler 104, d ₂₃ denotes an inlet of the coolant flow passage of the cooler 104, and d ₂₄ denotes an outlet of the coolant flow passage of the cooler 104. The connection relationship between each device in the refrigerant circuit L2 and the cooling liquid circuit L3 may be exemplarily shown in fig. 3, which is not described herein.

Illustratively, as shown in FIG. 3, the thermal management system may further include a valve arrangement 105. A valve device 105 may be provided at the inlet of the cooler 104. Specifically, the inlet of the valve means 105 is connected to the outlet d ₁₂ of the condenser 103. The outlet of the valve device 105 is connected to the inlet d ₂₁ of the refrigerant flow path of the cooler 104. The valve device 105 may, for example, adjust the opening. The valve device 105 may be, for example, an expansion valve. Alternatively, the valve device 105 may be a valve having a switching function, and may be, for example, a Shut Off Valve (SOV) or the like. It is to be understood that the description herein of the types of valve devices 105 is merely exemplary and is not to be construed as limiting embodiments of the present application. The valve device 105 may cool and decompress the high-temperature and high-pressure liquid refrigerant from the condenser 103, and output the low-temperature and low-pressure refrigerant to the cooler 104. The valve device 105 also has a function of adjusting the flow rate.

Illustratively, as shown in FIG. 3, a target device 107 may also be included in the coolant loop L3. The target device 107 may include, for example, one or more of the following: an electric drive, a battery and a heat sink. The electric driver is a device for driving the vehicle to run. The electric drive may include, for example, a power distribution unit (power distribution unit, PDU), a micro-control unit (microcontroller unit, MCU), a modular power assembly (modular drivetrain concept, MDC), an electronically controlled drive unit (ELECTRIC DRIVE unit, EDU), or a motor, among others. The coolant circuit L3 may be, for example, a heat dissipation circuit of the target device 107.

In a specific implementation, if the inlet pressure and inlet temperature of the compressor 101 are too low, for example, lower than the temperature of the cooling liquid in the cooling liquid circuit L3, before or after the start of the compressor 101. The circulation of the cooling liquid loop L3 can be started to exchange heat with the refrigerant in the refrigerant loop L2, so as to increase the temperature of the refrigerant in the refrigerant loop L2. Thereby elevating the inlet pressure and inlet temperature of the compressor 101.

Illustratively, in a specific implementation, there is a temperature sensor that monitors the temperature of the cooling fluid in the cooling fluid circuit L3 described above. The monitored temperature is then compared to the compressor inlet temperature. In case the temperature difference between the temperature of the cooling liquid in the cooling liquid circuit L3 and the inlet temperature of the compressor 101 is greater than a first threshold value, the above-mentioned water pump 106 is started to drive the circulation of the cooling liquid in the cooling liquid circuit L3. Thereby realizing heat exchange with the refrigerant in the refrigerant loop L2. Illustratively, the value of the first threshold may be, for example, greater than or equal to zero, which is not limited by embodiments of the present application.

In a possible implementation, in fig. 3, before starting the compressor 101, the controller may control the opening of the valve device 105 to be adjusted to the initial opening. So that after the compressor 101 is started, the refrigerant in the refrigerant circuit L2 can be turned on to circulate and return the refrigerant to the inlet of the compressor 101 at a certain initial flow rate. It is understood that the initial opening degree may be a preset opening degree or an opening degree calculated according to a certain algorithm. The embodiment of the application does not limit the specific value and the acquisition mode of the initial opening.

In one possible implementation, one may exemplarily refer to fig. 4. In fig. 4, the refrigerant circuit L1 may further include a valve device 108. An inlet of the valve device 108 communicates with an inlet of the bypass path 102, and an outlet of the valve device 108 communicates with an outlet of the bypass path 102. The valve device 108 may, for example, adjust the opening. The valve device 108 may be, for example, an expansion valve or the like. Alternatively, the valve device 108 may be a valve having a switching function, and may be, for example, a Shut Off Valve (SOV) or the like. It will be appreciated that the description herein of the nature of the valve arrangement 108 is merely exemplary and is not to be construed as limiting embodiments of the application. A valve device 108 is provided in the bypass path 102, and the flow rate and/or the pressure of the refrigerant fed back to the inlet of the compressor 101 can be controlled by adjusting the valve device 108.

Illustratively, in one possible implementation, in fig. 4, the controller may control the opening of the valve arrangement 108 to be adjusted to the initial opening prior to starting the compressor 101. So that after the compressor 101 is started, the refrigerant in the refrigerant loop L1 can be started to circulate, and the high-temperature and high-pressure refrigerant output by the compressor 101 is led back to the inlet of the compressor 101 according to a certain initial flow. It is understood that the initial opening degree may be a preset opening degree or an opening degree calculated according to a certain algorithm. The embodiment of the application does not limit the specific value and the acquisition mode of the initial opening.

In one possible implementation, an exemplary reference may be made to fig. 5. The thermal management system may further include a refrigerant circuit L4. The refrigerant circuit L4 may include a compressor 101, a refrigerant flow passage of the condenser 103, an evaporator 109, and a valve device 110. The valve device 110 is arranged at the inlet of the evaporator 109. The connection relationship between each device in the refrigerant circuit L4 may be illustrated in fig. 5, and will not be described herein.

For example, the valve device 110 may adjust the opening degree. The valve device 110 may be, for example, an expansion valve or the like. Alternatively, the valve device 110 may be a valve having a switching function, for example, a shut-off valve or the like. It is to be understood that the description herein of the types of valve devices 110 is merely exemplary and is not to be construed as limiting embodiments of the present application. The valve device 110 may be used to cool and decompress the high-temperature and high-pressure liquid refrigerant from the condenser 103, and obtain a low-temperature and low-pressure refrigerant to be input into the evaporator 109. In addition, the valve device 110 can also regulate the flow.

Illustratively, in one possible implementation, in fig. 5, the controller may control the opening of the valve device 110 to be adjusted to the initial opening before starting the compressor 101. So that after the compressor 101 is started, the refrigerant in the refrigerant circuit L4 can be turned on to circulate and return the refrigerant to the inlet of the compressor 101 at a certain initial flow rate. It is understood that the initial opening degree may be a preset opening degree or an opening degree calculated according to a certain algorithm. The embodiment of the application does not limit the specific value and the acquisition mode of the initial opening.

Illustratively, in a possible implementation, in the case where the valve device 108 is included in the refrigerant circuit L1, for example, in the case shown in fig. 4 or 5 described above, the suction superheat balance of the compressor 101 may be maintained by adjusting the opening degree of the valve device 108. The suction superheat of the compressor 101 is a difference between the saturation temperature of the suction gas and the temperature of the suction gas of the compressor 101. Too much or too little suction superheat affects the performance and stability of the compressor 101, for example, problems such as liquid hammer or excessive discharge temperature may occur. Therefore, the suction superheat is generally controlled within a certain range. Illustratively, the compressor suction superheat = compressor suction temperature (i.e., inlet temperature) -suction pressure (i.e., inlet pressure) corresponds to the saturation temperature.

For example, in the above-described process of increasing the rotation speed of the compressor 101 to the second rotation speed, the opening degree of the valve device 108 may be adjusted to adjust the suction superheat degree of the compressor 101. For example, it is preferable to maintain the suction superheat of the compressor 101 within a range smaller than the second temperature value and larger than the third temperature value. The second temperature value and the third temperature value may be preset, or may be determined according to actual operation requirements of the compressor 101, for example, and the embodiment of the present application is not limited thereto. Then, in the process of increasing the rotation speed of the compressor 101 to the second rotation speed, the controller may acquire the suction superheat of the compressor 101. For example, after the temperature and pressure at the inlet of the compressor 101 are measured by the temperature sensor and the pressure sensor, the saturation temperature corresponding to the pressure is obtained by looking up a table. Then, the suction superheat of the compressor 101 is calculated based on the above-described formula for calculating the suction superheat of the compressor. And compares the calculated suction superheat of the compressor 101 with the second and third temperature values.

For example, in the case where the suction superheat of the compressor 101 is greater than the second temperature value, the controller may control the opening degree of the valve device 108 to be reduced. To reduce the high temperature and high pressure refrigerant flowing back to the inlet of the compressor 101, thereby reducing the temperature rising speed of the inlet of the compressor 101. In the case where the suction superheat of the compressor 101 is smaller than the third temperature value, the controller may control the opening degree of the valve device 108 to be increased. To increase the temperature-rising speed of the inlet of the compressor 101 by increasing the high-temperature and high-pressure refrigerant flowing back to the inlet of the compressor 101. Specifically, the opening of the valve device 108 is adjusted to adjust the flow rate of the refrigerant flowing back to the inlet of the compressor 101 from the bypass path 102, and then the temperature of the inlet of the compressor 101 is adjusted to maintain the suction superheat balance of the compressor 101, so as to prevent damage to the compressor 101 caused by liquid impact.

Illustratively, in one possible implementation, in the case where the valve device 105 is included in the refrigerant circuit L2, for example, in the case shown in fig. 3, 4, or 5 described above, the suction superheat balance of the compressor 101 may be maintained by adjusting the opening degree of the valve device 105. Illustratively, in the above-described process of increasing the rotational speed of the compressor 101 to the second rotational speed, the opening degree of the valve device 105 may be adjusted to adjust the suction superheat of the compressor 101. In the same manner, for example, it is preferable to maintain the suction superheat of the compressor 101 within a range smaller than the second temperature value and larger than the third temperature value. Then, the controller may control the opening degree of the valve device 105 to be increased if the calculated suction superheat degree of the compressor 101 is greater than the second temperature value after comparing the calculated suction superheat degree of the compressor 101 with the second temperature value and the third temperature value. To increase the low temperature and pressure refrigerant flowing back to the inlet of the compressor 101, thereby reducing the temperature of the refrigerant at the inlet of the compressor 101. If the suction superheat of the compressor 101 is smaller than the third temperature value, the controller may control the opening degree of the valve device 105 to be reduced. To reduce the low temperature and pressure refrigerant flowing back to the inlet of the compressor 101, thereby increasing the temperature of the refrigerant at the inlet of the compressor 101. Specifically, the opening degree of the valve device 105 is adjusted to adjust the flow rate of the refrigerant flowing back to the inlet of the compressor 101 in the refrigerant circuit L2, so as to adjust the temperature of the inlet of the compressor 101 to maintain the suction superheat balance of the compressor 101, so as to prevent damage to the compressor 101 caused by liquid impact.

For example, in one possible implementation, in the case where the refrigerant circuit L4 is included, for example, in the case shown in fig. 5, the suction superheat balance of the compressor 101 may be maintained by adjusting the opening degree of the valve device 110. For example, in the above-described process of increasing the rotation speed of the compressor 101 to the second rotation speed, the opening degree of the valve device 110 may be adjusted to adjust the suction superheat degree of the compressor 101. In the same manner, for example, it is preferable to maintain the suction superheat of the compressor 101 within a range smaller than the second temperature value and larger than the third temperature value. Then, the controller compares the calculated suction superheat of the compressor 101 with the second temperature value and the third temperature value, and if the suction superheat of the compressor 101 is greater than the second temperature value, the controller may control the opening degree of the valve device 110 to be increased. To increase the low temperature and pressure refrigerant flowing back to the inlet of the compressor 101, thereby reducing the temperature of the refrigerant at the inlet of the compressor 101. If the suction superheat of the compressor 101 is smaller than the third temperature value, the controller may control the opening degree of the valve device 110 to be reduced. To reduce the low temperature and pressure refrigerant flowing back to the inlet of the compressor 101, thereby increasing the temperature of the refrigerant at the inlet of the compressor 101. Specifically, the opening degree of the valve device 110 is adjusted to adjust the flow rate of the refrigerant flowing back to the inlet of the compressor 101 in the refrigerant circuit L4, so as to adjust the temperature of the inlet of the compressor 101 to maintain the suction superheat balance of the compressor 101, so as to prevent the damage to the compressor 101 caused by the occurrence of liquid impact.

In a possible implementation, if the thermal management system further includes a gas-liquid separator, the gas-liquid separator is disposed at an inlet of the compressor 101. For ease of understanding, reference may be made to fig. 6, and fig. 6 is an illustration in combination with fig. 5, and fig. 3 and fig. 4 are the same and are not repeated. In fig. 6, the outlet of the gas-liquid separator is connected to the inlet of the compressor 101. The outlet of the gas-liquid separator is connected to the outlet of the valve device 108, the outlet d ₂₂ of the refrigerant flow path of the cooler 104, and the outlet of the evaporator 109. In this case, in the process of increasing the rotation speed of the compressor 101 to the second rotation speed, the opening degree of one or more of the valve device 108, the valve device 105, and the valve device 110 may be adjusted based on the supercooling degree to maintain the supercooling degree balance of the condenser 103.

Illustratively, the outlet supercooling degree of the condenser 103 refers to a difference between a refrigerant saturation temperature corresponding to an outlet pressure of the refrigerant flow channel of the condenser 103 and a refrigerant temperature of the refrigerant flow channel outlet of the condenser 103. Too much or too little supercooling can affect the performance and stability of the thermal management system. Therefore, the supercooling degree is generally controlled within a certain range. Illustratively, the subcooling = saturation temperature corresponding to the condenser 103 refrigerant flow path outlet pressure-the condenser 103 refrigerant flow path outlet refrigerant temperature. If the condenser refrigerant flow path outlet has no pressure sensor, the condenser refrigerant flow path outlet pressure in the above equation can be approximately replaced by the compressor 101 discharge pressure.

For example, it is preferable that the degree of supercooling of the refrigerant flow passage outlet of the condenser 103 is maintained within a range smaller than the fourth temperature value and larger than the fifth temperature value. The fourth temperature value and the fifth temperature value may be preset, or may be determined according to actual operating requirements of the thermal management system, for example, and embodiments of the present application are not limited in this respect. Then, in the process of increasing the rotation speed of the compressor 101 to the second rotation speed, the controller may obtain the supercooling degree of the refrigerant flow passage outlet of the condenser 103 in real time. And compares the degree of supercooling of the refrigerant flow passage outlet of the condenser 103 with the fourth temperature value and the fifth temperature value.

In one possible implementation, the controller may control the opening of the valve arrangement 108 to decrease in the event that the degree of subcooling of the refrigerant flow path outlet of the condenser 103 is greater than a fourth temperature value. To reduce the high temperature and pressure refrigerant flowing back to the inlet of the compressor 101, thereby reducing the supercooling degree of the refrigerant flow passage outlet of the condenser 103. In the case where the degree of supercooling of the refrigerant flow passage outlet of the condenser 103 is smaller than the fifth temperature value, the controller may control the opening degree of the valve device 108 to be increased. To increase the high temperature and pressure refrigerant flowing back to the inlet of the compressor 101, thereby increasing the supercooling degree of the refrigerant flow passage outlet of the condenser 103. Specifically, the opening of the valve device 108 is adjusted to adjust the flow rate of the refrigerant flowing back to the inlet of the compressor 101 from the bypass path 102, and then the flow rate of the refrigerant flowing into the condenser 103 is adjusted to maintain the outlet supercooling degree of the refrigerant flow channel of the condenser 103, so as to adjust the performance and stability of the system operation.

In another possible implementation, the controller may control the opening of the valve device 105 to increase if the degree of supercooling of the refrigerant flow passage of the condenser 103 is greater than the fourth temperature value. To increase the refrigerant flowing into the condenser 103 and thereby reduce the supercooling of the refrigerant flow passage outlet of the condenser 103. If the outlet subcooling of the refrigerant flow path of the condenser 103 is less than the fifth temperature value, the controller may control the opening of the valve device 105 to decrease. To reduce the refrigerant flowing into the condenser 103 and thereby increase the supercooling degree of the outlet of the condenser 103. Specifically, the opening of the valve device 105 is adjusted to adjust the flow rate of the refrigerant flowing into the condenser 103 in the refrigerant loop L2, so as to adjust the supercooling balance of the refrigerant channel outlet of the condenser 103, thereby adjusting the performance and stability of the thermal management system.

In another possible implementation, the controller may control the opening degree of the valve device 110 to increase if the outlet subcooling degree of the condenser 103 is greater than the fourth temperature value. To increase the refrigerant flowing into the condenser 103 and thereby reduce the outlet subcooling of the refrigerant flow path of the condenser 103. If the outlet supercooling degree of the refrigerant flow passage of the condenser 103 is smaller than the fifth temperature value, the controller may control the opening degree of the valve device 110 to be reduced. To reduce the refrigerant flowing into the condenser 103 and thereby increase the outlet supercooling of the refrigerant flow path of the condenser 103. Specifically, the opening degree of the valve device 110 is adjusted to adjust the flow rate of the refrigerant passing through the condenser 103 in the refrigerant loop L4, and further adjust the supercooling degree of the outlet of the condenser 103, so as to adjust the performance and stability of the thermal management system.

In a possible implementation, the thermal management system may further include a coolant loop L5. For ease of understanding, an exemplary reference may be made to fig. 7. Fig. 7 is an example of combining the above fig. 5, and fig. 3 and fig. 4 are the same, and are not repeated. As shown in fig. 7, the coolant circuit L5 includes a coolant flow passage of the condenser 103, a warm air core 111, and a water pump 112. Illustratively, in a specific implementation, the water pump 112 is normally off during the above-described process. Until the compressor 101 is turned on, the controller may control the water pump 112 to be turned on and control the water pump 112 to operate at the first duty ratio when the outlet pressure of the compressor 101 reaches the second pressure value, or the output power of the compressor 101 reaches the first power value, or both. After the water pump 112 is turned on, the coolant in the coolant circuit L5 is driven to circulate, and the temperature of the coolant is increased by heat exchange with the condenser 103.

Illustratively, the duty cycle of the water pump refers to the proportion of the high level that is occupied in one signal period. For example, the water pump accumulates a time period of high level and b time period of low level in a continuous process of actual operation, and the water pump circulates in this way. Then the duty cycle of the pump is a/(a+b). Illustratively, the water pump duty cycle is generally expressed in percent.

Illustratively, the second pressure value and the first power value may be preconfigured or further determined according to the working requirement of the compressor 101, which is not limited by the embodiment of the present application. Similarly, the first duty ratio may be preset, or determined according to an actual working requirement, which is not limited by the embodiment of the present application.

In the above-described scheme, the fact that the outlet pressure of the compressor 101 reaches the second pressure value or that the output power of the compressor 101 reaches the first power value indicates that the compressor 101 can be stably operated and a certain amount of heat can be provided. Based on this, the operating coolant loop L5 is opened so that the coolant of the loop can exchange heat from the condenser 103 to obtain heat. Providing for subsequent heating.

In one possible implementation, the first duty cycle is an initial duty cycle of the operation of the water pump 112, and as the compressor 101 operates more and more steadily, the duty cycle of the water pump 112 may be increased to a second duty cycle. Specifically, the duty ratio of the water pump 112 may be adjusted according to the rotational speed of the compressor 101. Illustratively, in one possible implementation, a map of the rotational speed of the compressor 101 and the duty cycle of the water pump 112 may be preconfigured. When the rotation speed of the compressor 101 reaches the preset rotation speed, the duty ratio corresponding to the preset rotation speed, that is, the second duty ratio, may be obtained by looking up a table. The controller then controls the water pump 112 to operate at the second duty cycle.

In a possible implementation manner, in the process of increasing the duty cycle of the water pump 112 to the second duty cycle, it is also ensured that the inlet and outlet pressure of the compressor 101 is maintained within a certain preset range, so as to meet the requirement of the output power of the compressor 101. Illustratively, in a specific implementation, the compressor 101 has an inlet pressure upper limit and an inlet pressure lower limit. The compressor 101 can be operated normally only in this range of inlet pressure. The controller may maintain the inlet and outlet pressure balance of the compressor 101 by adjusting the opening of one or more of the valve means 108, 105, and 110. For ease of understanding, valve arrangement 108 is exemplified.

Illustratively, the controller may obtain the outlet pressure and the inlet pressure of the compressor 101 during the increasing of the duty cycle of the water pump 112 to the second duty cycle. In the case where the outlet pressure of the compressor 101 is smaller than the third pressure value and the inlet pressure of the compressor 101 is smaller than the upper limit value of the inlet pressure of the compressor 101, the opening degree of the valve device 108 is controlled to be reduced. So that the outlet pressure of the compressor 101 is gradually increased to meet the output power requirement. In the case where the outlet pressure of the compressor 101 is greater than the fourth pressure value and the inlet pressure of the compressor 101 is less than the inlet pressure lower limit value of the compressor 101, the opening degree of the valve device 108 is controlled to be increased. So that the inlet pressure of the compressor 101 is gradually increased to meet the output power requirement.

Illustratively, the fourth pressure value is greater than or equal to the third pressure value. The values of the third pressure value and the fourth pressure value may be preset, or may be determined according to practical application requirements, which is not limited in the embodiment of the present application.

Similarly, in another possible implementation, the controller may obtain the outlet pressure and the inlet pressure of the compressor 101 during the step of increasing the duty cycle of the water pump 112 to the second duty cycle. In the case where the outlet pressure of the compressor 101 is smaller than the third pressure value and the inlet pressure of the compressor 101 is smaller than the upper limit value of the inlet pressure of the compressor 101, the opening degree of the valve device 105 is controlled to be reduced. So that the outlet pressure of the compressor 101 is gradually increased to meet the output power requirement. In the case where the outlet pressure of the compressor 101 is greater than the fourth pressure value and the inlet pressure of the compressor 101 is less than the inlet pressure lower limit value of the compressor 101, the opening degree of the valve device 105 is controlled to be increased. So that the inlet pressure of the compressor 101 is gradually increased to meet the output power requirement.

Similarly, in another possible implementation, the controller may obtain the outlet pressure and the inlet pressure of the compressor 101 during the step of increasing the duty cycle of the water pump 112 to the second duty cycle. In the case where the outlet pressure of the compressor 101 is smaller than the third pressure value and the inlet pressure of the compressor 101 is smaller than the upper limit value of the inlet pressure of the compressor 101, the opening degree of the valve device 110 is controlled to be reduced. So that the outlet pressure of the compressor 101 is gradually increased to meet the output power requirement. In the case where the outlet pressure of the compressor 101 is greater than the fourth pressure value and the inlet pressure of the compressor 101 is less than the inlet pressure lower limit value of the compressor 101, the opening degree of the valve device 110 is controlled to be increased. So that the inlet pressure of the compressor 101 is gradually increased to meet the output power requirement.

In one possible implementation, a blower (not shown) is also included in the thermal management system. The blower may be used to deliver hot air generated based on the above-described warm air core 111. Illustratively, in a specific implementation, the blower is normally off during the above-described process. The controller may control the blower to be turned on when the coolant temperature of the coolant circuit L5 reaches a sixth temperature value after the circulation of the coolant circuit L5 is turned on to perform heat exchange. So as to be convenient for conveying hot air to heat users. The sixth temperature value may be preset, or may be actually determined according to an actual application requirement or an instruction of a user, which is not limited by the embodiment of the present application.

In another possible implementation, an exemplary reference may be made to fig. 8. Fig. 8 is an illustration in conjunction with fig. 7, and is the same as fig. 3 to 6, and is not repeated. Also included in the thermal management system is a valve arrangement 113. The inlet of the valve device 113 communicates with the outlet of the compressor 101 and the inlet of the bypass path 102. The outlet of the valve device 113 is also in communication with the inlet of the refrigerant passage of the condenser 103. The valve device 113 may adjust the opening degree, for example. The valve device 113 may be, for example, an expansion valve. The pressure of the refrigerant fed back to the inlet of the compressor 101 can be raised by decreasing the opening of the valve device 113, so that the pressure of the inlet of the compressor 101 can be raised rapidly. The valve device 113 also has a function of adjusting the flow rate.

Illustratively, in one possible implementation, in fig. 8, the controller may control the opening of the valve device 113 to be adjusted to the initial opening before starting the compressor 101. After the compressor 101 is started, the refrigerant loop L2 or the refrigerant loop L4 may be opened to circulate, and the refrigerant output by the compressor 101 may be led back to the inlet of the compressor 101 according to a certain initial flow. It is understood that the initial opening degree may be a preset opening degree or an opening degree calculated according to a certain algorithm. The embodiment of the application does not limit the specific value and the acquisition mode of the initial opening.

In a possible implementation, if the thermal management system includes the valve device 113, the coolant loop L5, and the blower, see, for example, the thermal management system shown in fig. 8. The controller may then control the blower to be turned on prior to starting the compressor 101. The noise of the compressor is masked by the sound generated when the blower operates. Or in another possible implementation, even if the valve device 113 is included, the controller may control the blower to be turned on again in case the coolant temperature of the coolant loop L5 reaches the above-mentioned sixth temperature value. The specific manner of selecting which way to turn on the blower may be determined according to actual needs, and embodiments of the present application are not limited in this respect.

In one possible implementation, the blower is turned on by a controller before the controller controls the compressor 101 to start. The second duty ratio may be determined based on the rotational speed of the compressor 101 and the air volume of the blower. For example, in one possible implementation, a map of the rotational speed of the compressor 101, the air volume of the blower, and the duty ratio of the water pump 112 may be configured in advance. When the rotation speed of the compressor 101 reaches a preset rotation speed, the air volume of the blower is acquired for table lookup. Thereby, the second duty ratio which is the duty ratio corresponding to the preset rotating speed and the air quantity can be obtained. The controller then controls the water pump 112 to operate at the second duty cycle.

In a possible implementation, if the thermal management system includes the valve device 113 and the coolant loop L5. Then, after the circulation heat exchange of the coolant circuit L5 is started, the controller may control to increase the opening degree of the valve device 113. Specifically, the opening degree of the valve device 113 may be increased according to the outlet pressure and the outlet temperature of the compressor 101. For example, a map may be set in advance between the outlet pressure, the outlet temperature of the compressor 101, and the opening degree of the valve device 113. When the outlet pressure and the outlet temperature of the compressor 101 reach preset values, the opening degree corresponding to the valve device 113 is obtained through table lookup. Or the opening degree corresponding to the valve device 113 may be calculated based on the outlet pressure and the outlet temperature of the compressor 101 according to a preset calculation formula. The embodiments of the present application are not limited in this regard. Then, the controller controls the opening of the valve device 113 to increase based on the obtained opening size corresponding to the valve device 113.

In the above-mentioned scheme, the valve device 113 has a small opening degree before the water pump 112 is turned on, which helps to quickly raise the pressure and temperature of the inlet of the compressor 101. After the water pump 112 is turned on, it is indicated that heating can be performed by the warm air circuit (i.e., the above-described coolant circuit L5), and thus the opening degree of the valve device 113 can be increased. To increase the flow of compressor 101 to condenser 103 to increase the heat transfer to the warm air circuit.

In another possible implementation, see fig. 9 for an example, the condenser 103 is replaced by an air-cooled condenser as described above. In addition, in fig. 9, the thermal management system may also include a condenser 114 and a valve arrangement 115. The condenser 114 may be, for example, an air-cooled condenser, and the condenser 114 may be used to provide heating (e.g., to provide heat to a passenger compartment of a vehicle, etc.). Illustratively, in this implementation, after the compressor 101 is turned on, and when the outlet pressure of the compressor 101 reaches the second pressure value, or the output power of the compressor 101 reaches the first power value, or both, the controller controls the operation of turning on the water pump 112 instead of controlling to increase the opening of the valve device 115 and turn on the condenser 114. The high temperature and high pressure refrigerant output by the compressor 101 may then be input to the condenser 114 for heat exchange for heating the air in the passenger compartment to heat the passenger compartment. The refrigerant output from the condenser 114 after heat exchange may flow back to the compressor 101 through the evaporator 109 and/or the cooler 104.

Because the existing warm air core body heats the passenger cabin in a way that the high-temperature refrigerant output by the compressor transfers heat to the cooling liquid, and then the high-temperature cooling liquid flows to the warm air core body to heat air, secondary heating is needed, and the heat exchange efficiency is reduced. In the scheme, the air cooling type condenser is used for directly heating air to heat the member cabin, so that the heat exchange efficiency is higher, and the heat utilization rate is higher.

It will be appreciated that the above description is mainly given by taking the example of starting the thermal management system to heat the user in a low-temperature environment. In particular implementations, the thermal management system may also be used to heat a power battery in a vehicle, etc., after being activated in a low temperature environment. Or the thermal management system may also be used for cooling or dissipating heat from the target device, etc. The embodiments of the present application will not be described in detail.

Further, it is understood that the inclusion of components in each of the refrigerant circuits or coolant circuits described above is merely exemplary. In particular implementations, these loops may include more or fewer devices, which may be increased or decreased depending on the actual application requirements. The embodiments of the present application are not limited in this regard. For ease of understanding, reference may be made to fig. 10 or 11 for exemplary purposes.

As shown in fig. 10, the above-described thermal management system may further include a nine-way valve 116, a battery 117, an electric actuator 118, a radiator 119, a water pump 120, a water pump 121, a check valve 122, a three-way valve 123, and a water kettle 124. Wherein nine ports are included in nine-way valve 116, as shown in fig. 10, with 1 through 9 denoting the nine ports. Three-way valve 123 includes three ports, wherein the three ports are denoted as d ₅₁、d₅₂ and d ₅₃. The connection relationship among the nine-way valve 116, the battery 117, the electric driver 118, the radiator 119, the water pump 120, the water pump 121, the one-way valve 122, the three-way valve 123 and the water kettle 124 in the thermal management system is shown in fig. 10, and is not repeated. In particular implementations, the controller may control the communication and closing of the various interfaces of the nine-way valve 116. By controlling the communication of the ports in the nine-way valve 116, various cooling, heating, or cooling modes may be implemented. For example, the coolant circuit L3 may be implemented by controlling the communication of the ports in the nine-way valve 116. The embodiments of the present application are not described in detail.

As further shown in fig. 11, the thermal management system may further include a five-way valve 126, a four-way valve 125, a battery 117, an electric drive 118, a radiator 119, a water pump 120, a water pump 121, a three-way valve 127, a water kettle 124, and a water kettle 128. Wherein the five-way valve 126 includes five ports. The four-way valve 125 includes four ports. The three-way valve 127 includes three ports. The connection relationship among the five-way valve 126, the four-way valve 125, the battery 117, the electric driver 118, the radiator 119, the water pump 120, the water pump 121, the three-way valve 127, the water kettle 124 and the water kettle 128 in the thermal management system is shown in fig. 11, and is not described in detail. In a specific implementation, the controller may control the communication and closing of the interfaces of the five-way valve 126 and the four-way valve 125. By controlling the communication condition of the interfaces in the five-way valve 126 and the four-way valve 125, various cooling modes, heating modes, or heat dissipation modes can be realized. For example, the above-described coolant circuit L3 may be realized by controlling the communication of the ports in the five-way valve 126 and the four-way valve 125. The embodiments of the present application are not described in detail.

It should be understood that the foregoing descriptions of fig. 10 and 11 are merely examples, and are not meant to limit the embodiments of the present application. In particular implementations, there are other thermal management systems that include the various circuits described above and methods of applying the same.

In summary, the compressor can be started to operate briefly under a low-temperature environment. Based on the above, in the above scheme, during the transient operation, the compressor is started to operate at a lower rotation speed, and the high-pressure high-temperature refrigerant output by the compressor is sent back to the inlet of the compressor through the bypass path, so as to increase the temperature and pressure of the refrigerant at the inlet of the compressor, and promote the compressor to continue to operate at a low temperature. Then, when the inlet pressure or temperature of the compressor reaches a preset value, the rotating speed of the compressor is increased, the output power of the compressor is increased, and the compressor is further driven to continuously and stably run, so that the normal operation of the compressor at low temperature is realized, and the normal use of an air conditioning system in a low-temperature environment is realized.

In a possible implementation manner, the embodiment of the application further provides a controller. Fig. 12 is a schematic diagram of a possible hardware structure of a controller according to the present application, where the controller may be a controller in the method according to the foregoing embodiment. The controller 1200 shown in fig. 12 may include: a processor 1201, a memory 1202 and a communication interface 1203. The processor 1201, the communication interface 1203, and the memory 1202 may be connected to each other or to each other via a bus 1204.

By way of example, memory 1202 for storing computer programs and data for controller 1200, memory 1202 may include, but is not limited to, random access memory (random access memory, RAM), read-only memory (ROM), erasable programmable read-only memory (erasable programmable read only memory, EPROM), or portable read-only memory (compact disc read-only memory, CD-ROM), etc.

Software or program code required for the function of all or part of the units of the controller in the above described method embodiments is stored in the memory 1202.

In a possible implementation manner, if software or program code required for a function of a part of the units is stored in the memory 1202, the processor 1201 may implement a part of the functions in addition to calling the program code in the memory 1202, and may cooperate with other components (such as the communication interface 1203) to perform other functions (such as a function of receiving or sending data or instructions) described in a method embodiment.

The number of the communication interfaces 1203 may be plural, for supporting the controller 1200 to communicate, such as to receive or transmit data or signals or instructions, etc.

By way of example, the processor 1201 may be a central processor unit, a general purpose processor, a digital signal processor, an application specific integrated circuit, a field programmable gate array or other programmable logic device, a transistor logic device, a hardware component, or any combination thereof. A processor may also be a combination that performs a computational function, such as a combination comprising one or more microprocessors, a combination of a digital signal processor and a microprocessor, and so forth. The processor 1201 may be configured to read the program stored in the memory 1202 and perform the operations performed by the controller in the method described above with respect to fig. 2 and its possible embodiments.

The specific operation and beneficial effects of each unit in the controller 1200 shown in fig. 12 may be referred to the corresponding description in the above method embodiments, and will not be repeated here.

The embodiment of the application also provides a vehicle, which comprises the controller according to any one of the above embodiments or the thermal management system according to any one of the above possible embodiments.

Embodiments of the present application also provide a computer-readable storage medium storing a computer program that is executed by a processor to implement operations performed by the controller of any of the above-described various embodiments and possible embodiments thereof.

Embodiments of the present application also provide a computer program product, which when read and executed by a computer, performs the operations performed by the controller of any of the various embodiments and possible embodiments thereof.

It should be understood that, in the embodiments of the present application, the sequence number of each process does not mean the sequence of execution, and the execution sequence of each process should be determined by its functions and internal logic, and should not constitute any limitation on the implementation process of the embodiments of the present application.

It will be further understood that the terms "comprises" and/or "comprising," when used in this specification, specify the presence of stated features, integers, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and/or groups thereof.

It should be further appreciated that reference throughout this specification to "one embodiment," "an embodiment," "one possible implementation" means that a particular feature, structure, or characteristic described in connection with the embodiment or implementation is included in at least one embodiment of the present application. Thus, the appearances of the phrases "in one embodiment" or "in an embodiment," "one possible implementation" in various places throughout this specification are not necessarily all referring to the same embodiment. Furthermore, the particular features, structures, or characteristics may be combined in any suitable manner in one or more embodiments.

Finally, it should be noted that: the above embodiments are only for illustrating the technical solution of the present application, and not for limiting the same; although the application has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some or all of the technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit of the application.

Claims

1. A control method of a thermal management system, wherein the method is applied to a controller of the thermal management system; the thermal management system comprises a first refrigerant loop, wherein the first refrigerant loop comprises a compressor and a bypass path, an outlet of the compressor is communicated with an inlet of the bypass path, and an outlet of the bypass path is communicated with an inlet of the compressor; the method comprises the following operation execution controlled by the controller:

Starting the compressor to operate at a first rotational speed so that at least part of the refrigerant output from the compressor is re-input into the compressor through the bypass path;

And increasing the rotation speed of the compressor to a second rotation speed under the condition that the inlet pressure of the compressor reaches a first pressure value and/or the inlet temperature of the compressor reaches a first temperature value.

2. The method of claim 1, wherein the thermal management system comprises a second refrigerant circuit and a first coolant circuit, the second refrigerant circuit comprising refrigerant channels of the compressor, condenser, and cooler; the first cooling liquid loop comprises a first water pump and a cooling liquid flow channel of the cooler; the method also includes the controller controlling the following operations to be performed:

In the event that the temperature difference between the temperature of the coolant in the first coolant circuit and the inlet temperature of the compressor is greater than a first threshold, the first water pump is started to drive circulation of the coolant in the first coolant circuit.

3. The method of claim 1 or 2, wherein the first refrigerant circuit further comprises a first valve device, an inlet of the first valve device being in communication with an inlet of the bypass path, an outlet of the first valve device being in communication with an outlet of the bypass path;

during the process of increasing the rotation speed of the compressor to the second rotation speed, the method further comprises the following operation execution controlled by the controller:

reducing the opening of the first valve means in the event that the suction superheat of the compressor is greater than a second temperature value;

And increasing the opening degree of the first valve device when the suction superheat degree of the compressor is smaller than a third temperature value.

4. The method of any of claims 1-3, wherein the thermal management system comprises a second refrigerant circuit or a third refrigerant circuit; the second refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and a refrigerant flow passage of the cooler; the third refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and an evaporator; the thermal management system further comprises a second valve device; the second valve device is arranged at the refrigerant flow passage inlet of the cooler or at the evaporator inlet;

increasing the opening of the second valve device when the suction superheat of the compressor is greater than a second temperature value;

And reducing the opening degree of the second valve device when the suction superheat degree of the compressor is smaller than a third temperature value.

5. The method of any of claims 1-4, wherein the thermal management system further comprises a gas-liquid separator and a condenser, the gas-liquid separator disposed at an inlet of the compressor; the refrigerant flow passage inlet of the condenser is communicated with the outlet of the compressor and the inlet of the bypass path; the first refrigerant circuit further comprises a first valve device, an inlet of the first valve device is communicated with an inlet of the bypass path, and an outlet of the first valve device is communicated with an outlet of the bypass path;

reducing the opening of the first valve device when the supercooling degree of the refrigerant flow passage outlet of the condenser is larger than a fourth temperature value;

and increasing the opening degree of the first valve device under the condition that the supercooling degree of the refrigerant flow passage outlet of the condenser is smaller than a fifth temperature value.

6. The method of any of claims 1-5, wherein the thermal management system further comprises a gas-liquid separator disposed at an inlet of the compressor; the thermal management system comprises a second refrigerant loop or a third refrigerant loop; the second refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and a refrigerant flow passage of the cooler; the third refrigerant loop comprises the compressor, a refrigerant flow passage of the condenser and an evaporator; the thermal management system further comprises a second valve device; the second valve device is arranged at the refrigerant flow passage inlet of the cooler or at the evaporator inlet;

Increasing the opening of the second valve device when the supercooling degree of the refrigerant flow passage outlet of the condenser is greater than a fourth temperature value;

and reducing the opening degree of the second valve device under the condition that the supercooling degree of the refrigerant flow passage outlet of the condenser is smaller than a fifth temperature value.

7. The method of any of claims 1-6, wherein the thermal management system further comprises a second coolant loop comprising a coolant flow passage of the condenser, a warm air core, and a second water pump; the method also includes the controller controlling the following operations to be performed:

And when the outlet pressure of the compressor reaches a second pressure value and/or the output power of the compressor reaches a first power value, starting the second water pump and operating at a first duty ratio.

8. The method of claim 7, wherein the first refrigerant circuit further comprises a first valve device, an inlet of the first valve device being in communication with an inlet of the bypass path, an outlet of the first valve device being in communication with an outlet of the bypass path; in the process of increasing the duty ratio of the second water pump to the second duty ratio according to the rotation speed of the compressor and the air quantity of the blower, the method further comprises the following operation execution controlled by the controller:

Reducing the opening of the first valve means in the case where the outlet pressure of the compressor is less than a third pressure value and the inlet pressure of the compressor is less than the upper limit value of the inlet pressure of the compressor;

The opening degree of the first valve device is increased in a case where the outlet pressure of the compressor is greater than the fourth pressure value and the inlet pressure of the compressor is less than the compressor inlet pressure lower limit value.

9. The method of claim 8, wherein the thermal management system comprises a second refrigerant circuit or a third refrigerant circuit; the second refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and a refrigerant flow passage of the cooler; the third refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and an evaporator; the thermal management system further comprises a second valve device; the second valve device is arranged at the refrigerant flow passage inlet of the cooler or at the evaporator inlet;

In the process of increasing the duty ratio of the second water pump to the second duty ratio according to the rotation speed of the compressor and the air quantity of the blower, the method further comprises the following operation execution controlled by the controller:

reducing the opening of the second valve means in the case where the outlet pressure of the compressor is less than a third pressure value and the inlet pressure of the compressor is less than the upper limit value of the inlet pressure of the compressor;

In the case where the outlet pressure of the compressor is greater than the fourth pressure value and the inlet pressure of the compressor is less than the compressor inlet pressure lower limit value, the opening degree of the second valve device is increased.

10. The method of any of claims 7-9, wherein the thermal management system further comprises a third valve device; an inlet of the third valve device communicates with an outlet of the compressor and an inlet of the bypass path;

after the second water pump is started, the controller is further included to control the following operation to be executed:

the opening degree of the third valve device is increased according to the outlet pressure and temperature of the compressor.

11. The method of claim 10, wherein the thermal management system further comprises a blower for delivering hot air generated based on the warm air core; the method further includes, prior to the starting the compressor, the controller controlling the execution of: the blower is turned on.

12. A thermal management system comprising a controller and a first refrigerant circuit, the first refrigerant circuit comprising a compressor and a bypass path, an outlet of the compressor in communication with an inlet of the bypass path, an outlet of the bypass path in communication with an inlet of the compressor; the controller is used for controlling the following operations to be performed:

13. The thermal management system of claim 12, wherein the thermal management system comprises a second refrigerant circuit and a first coolant circuit, the second refrigerant circuit comprising refrigerant channels of the compressor, condenser, and cooler; the first cooling liquid loop comprises a first water pump and a cooling liquid flow channel of the cooler; the controller is also used for controlling the following operations to be performed:

14. The thermal management system of claim 12 or 13, wherein the first refrigerant circuit further comprises a first valve device, an inlet of the first valve device being in communication with an inlet of the bypass path, an outlet of the first valve device being in communication with an outlet of the bypass path;

During the process of increasing the rotation speed of the compressor to the second rotation speed, the controller is further configured to control the following operations to be performed:

15. The thermal management system of any of claims 12-14, wherein the thermal management system comprises a second refrigerant circuit or a third refrigerant circuit; the second refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and a refrigerant flow passage of the cooler; the third refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and an evaporator; the thermal management system further comprises a second valve device; the second valve device is arranged at the refrigerant flow passage inlet of the cooler or at the evaporator inlet;

16. The thermal management system of any of claims 12-15, further comprising a gas-liquid separator and a condenser, the gas-liquid separator disposed at an inlet of the compressor; the refrigerant flow passage inlet of the condenser is communicated with the outlet of the compressor and the inlet of the bypass path; the first refrigerant circuit further comprises a first valve device, an inlet of the first valve device is communicated with an inlet of the bypass path, and an outlet of the first valve device is communicated with an outlet of the bypass path;

17. The thermal management system of any of claims 12-16, further comprising a gas-liquid separator disposed at an inlet of the compressor; the thermal management system comprises a second refrigerant loop or a third refrigerant loop; the second refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and a refrigerant flow passage of the cooler; the third refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and an evaporator; the thermal management system further comprises a second valve device; the second valve device is arranged at the refrigerant flow passage inlet of the cooler or at the evaporator inlet;

18. The thermal management system of any of claims 12-17, further comprising a second coolant loop comprising a coolant flow passage of the condenser, a warm air core, and a second water pump; the controller is also used for controlling the following operations to be performed:

19. The thermal management system of claim 18, wherein the first refrigerant circuit further comprises a first valve device, an inlet of the first valve device being in communication with an inlet of the bypass path, an outlet of the first valve device being in communication with an outlet of the bypass path; during the process of increasing the duty ratio of the second water pump to the second duty ratio according to the rotation speed of the compressor and the air quantity of the blower, the controller is further configured to control the following operations to be performed:

20. The thermal management system of claim 19, wherein the thermal management system comprises a second refrigerant loop or a third refrigerant loop; the second refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and a refrigerant flow passage of the cooler; the third refrigerant loop comprises a refrigerant flow passage of the compressor and the condenser and an evaporator; the thermal management system further comprises a second valve device; the second valve device is arranged at the refrigerant flow passage inlet of the cooler or at the evaporator inlet;

During the process of increasing the duty ratio of the second water pump to the second duty ratio according to the rotation speed of the compressor and the air quantity of the blower, the controller is further configured to control the following operations to be performed:

21. The thermal management system of any of claims 18-20, further comprising a third valve device; an inlet of the third valve device communicates with an outlet of the compressor and an inlet of the bypass path;

After the second water pump is started, the controller is further used for controlling the following operations to be performed:

22. The thermal management system of claim 21, further comprising a blower for delivering hot air generated based on the warm air core; the controller is further configured to control the following operations to be performed before the compressor is started: the blower is turned on.

23. A controller comprising a processor and a memory, wherein the memory is for storing a computer program or computer instructions, and the processor is for executing the computer program or computer instructions stored in the memory, such that the controller performs the method of any of claims 1-11.

24. A vehicle comprising the thermal management system of any one of claims 12-22; or the vehicle comprises a controller as claimed in claim 23.