WO2024124552A1

WO2024124552A1 - Transportation device and temperature control system thereof

Info

Publication number: WO2024124552A1
Application number: PCT/CN2022/139690
Authority: WO
Inventors: 赵宇
Original assignee: 宁德时代(上海)智能科技有限公司; 宁德时代新能源科技股份有限公司
Priority date: 2022-12-16
Filing date: 2022-12-16
Publication date: 2024-06-20

Abstract

Disclosed in the present application are a transportation device and a temperature control system thereof. The temperature control system comprises a refrigerant circuit. The refrigerant circuit comprises a compressor, a condensing heat exchanger, a first air conditioning heat exchanger, a second air conditioning heat exchanger, and a refrigerant switching assembly. In a first air conditioning refrigeration mode, the refrigerant switching assembly introduces a refrigerant output by the condensing heat exchanger into one of the first air conditioning heat exchanger and the second air conditioning heat exchanger in a pressure reduction manner, so that one of the first air conditioning heat exchanger and the second air conditioning heat exchanger performs evaporation on an air conditioning flow to absorb heat, or in a second air conditioning refrigeration mode, the refrigerant switching assembly sequentially introduces the refrigerant output by the condensing heat exchanger into the first air conditioning heat exchanger and the second air conditioning heat exchanger in a pressure reduction manner, respectively, so that the first air conditioning heat exchanger and the second air conditioning heat exchanger sequentially perform evaporation on the air conditioning flow to absorb heat. In this way, the temperature control system provided by the present application has two different air conditioning refrigeration modes, and can be allowed to be switched according to actual working conditions.

Description

Traffic equipment and its temperature control system

[Technical field]

The present application relates to the field of thermal management technology, and in particular to a transportation device and a temperature control system thereof.

【Background technique】

The air conditioning system of transportation equipment is generally used to meet the air conditioning needs of the cockpit and provide a comfortable driving environment for the driver. In addition, with the development of battery technology, batteries are gradually replacing traditional fossil energy in the transportation field. In new energy transportation equipment that uses batteries as energy, the air conditioning system may also need to meet the thermal management requirements of batteries, motors or other components, resulting in increased energy consumption of the air conditioning system. Therefore, how to reduce the energy consumption of the air conditioning system is an important factor in increasing the mileage of transportation equipment and reducing travel costs.

Since transportation equipment needs to operate under complex and changeable working conditions, both air conditioning and thermal management requirements are variable. However, the working mode of the air conditioning system of current transportation equipment is relatively single, which makes it difficult to cope with the flexibility of complex working conditions.

[Summary of the invention]

The present application mainly provides a transportation equipment and a temperature control system thereof to solve the problem that the working mode of the air-conditioning system of the transportation equipment is relatively single.

In order to solve the above technical problems, a technical solution adopted in this application is: to provide a temperature control system. The temperature control system includes a refrigerant circuit for circulating refrigerant, the refrigerant circuit includes a compressor, a condensing heat exchanger, a first air-conditioning heat exchanger, a second air-conditioning heat exchanger and a refrigerant switching component. The temperature control system has an air-conditioning refrigeration mode for refrigerating an air-conditioning airflow. The air-conditioning refrigeration mode includes a first air-conditioning refrigeration mode and a second air-conditioning refrigeration mode. The refrigerant switching component introduces the refrigerant compressed by the compressor into the condensing heat exchanger for condensation and heat release in the first air-conditioning refrigeration mode and the second air-conditioning refrigeration mode. In the first air-conditioning refrigeration mode, the refrigerant switching component introduces the refrigerant output by the condensing heat exchanger into one of the first air-conditioning heat exchanger and the second air-conditioning heat exchanger in a pressure-reducing manner, so that the one of the first air-conditioning heat exchanger and the second air-conditioning heat exchanger evaporates and absorbs heat from the air-conditioning airflow, or in the second air-conditioning refrigeration mode, the refrigerant switching component introduces the refrigerant output by the condensing heat exchanger into the first air-conditioning heat exchanger and the second air-conditioning heat exchanger in a pressure-reducing manner in sequence, so that the first air-conditioning heat exchanger and the second air-conditioning heat exchanger evaporate and absorb heat from the air-conditioning airflow in sequence.

Through the above-mentioned method, the present application provides two air-conditioning refrigeration modes, allowing traffic equipment to select between the two air-conditioning refrigeration modes according to actual working conditions. Specifically, in the first air-conditioning refrigeration mode, one of the first air-conditioning heat exchanger and the second air-conditioning heat exchanger completes the single-stage refrigeration of the air-conditioning airflow, and its control method is relatively simple. In the second air-conditioning refrigeration mode, the first air-conditioning heat exchanger and the second air-conditioning heat exchanger are used to complete the two-stage refrigeration of the air-conditioning airflow, that is, one of the first air-conditioning heat exchanger and the second air-conditioning heat exchanger is used to pre-cool the air-conditioning airflow, and then the other air-conditioning heat exchanger is used to perform secondary refrigeration on the pre-cooled air-conditioning airflow, and its energy efficiency ratio is relatively high, and a relatively good refrigeration effect can be achieved.

In some embodiments, the temperature control system also includes a control module, which controls the refrigerant switching component to switch to the first air-conditioning refrigeration mode in response to the air-conditioning refrigeration load in the air-conditioning refrigeration mode being less than or equal to a preset air-conditioning refrigeration load threshold, or controls the refrigerant switching component to switch to the second air-conditioning refrigeration mode in response to the air-conditioning refrigeration load being greater than the air-conditioning refrigeration load threshold.

Through the above method, when the air conditioning refrigeration load is low, the relatively simple first air conditioning refrigeration mode is selected to achieve efficient and concise control; and when the air conditioning refrigeration load is high, the second air conditioning refrigeration mode is selected to improve the system energy efficiency ratio.

In some embodiments, the refrigerant circuit further includes a first thermal management heat exchanger and a second thermal management heat exchanger, the temperature control system further includes a thermal management circuit for circulating a heat transfer agent, the thermal management circuit is used to perform thermal management on a specified component of the transportation equipment, the temperature control system has a thermal management refrigeration mode for refrigerating the specified component, the thermal management refrigeration mode includes a first thermal management refrigeration mode and a second thermal management refrigeration mode, the refrigerant switching component introduces the refrigerant compressed by the compressor into the condensing heat exchanger for condensation and heat release in the first thermal management refrigeration mode and the second thermal management refrigeration mode, In the cold mode, the refrigerant switching component introduces the refrigerant output from the condensing heat exchanger into one of the first thermal management heat exchanger and the second thermal management heat exchanger in a pressure-reducing manner, thereby causing the first thermal management heat exchanger and the second thermal management heat exchanger to evaporate and absorb heat from the heat conductor, or in the second thermal management cooling mode, the refrigerant switching component introduces the refrigerant output from the condensing heat exchanger into the first thermal management heat exchanger and the second thermal management heat exchanger in sequence in a pressure-reducing manner, thereby causing the first thermal management heat exchanger and the second thermal management heat exchanger to evaporate and absorb heat from the heat conductor in sequence.

Through the above-mentioned method, the present application provides two thermal management refrigeration modes, allowing traffic equipment to select between the two thermal management refrigeration modes according to actual working conditions. Specifically, in the first thermal management refrigeration mode, one of the first thermal management heat exchanger and the second thermal management heat exchanger is used to complete single-stage refrigeration of the heat conductor, and its control method is simpler. In the second thermal management refrigeration mode, both the first thermal management heat exchanger and the second thermal management heat exchanger are used to complete two-stage refrigeration of the heat conductor, that is, one of the first thermal management heat exchanger and the second thermal management heat exchanger is used to pre-cool the heat conductor first, and then the other is used to perform secondary refrigeration on the pre-cooled heat conductor, and its energy efficiency ratio is relatively high, and a relatively good refrigeration effect can be achieved.

In some embodiments, the temperature control system includes a control module, which controls the refrigerant switching component to switch to the first thermal management refrigeration mode in response to the thermal management refrigeration load in the thermal management refrigeration mode being less than or equal to a preset thermal management refrigeration load threshold, or controls the refrigerant switching component to switch to the second thermal management refrigeration mode in response to the thermal management refrigeration load being greater than the thermal management refrigeration load threshold.

Through the above method, when the thermal management cooling load is low, the relatively simple first thermal management cooling mode is selected to achieve efficient and concise control; and when the thermal management cooling load is high, the second thermal management cooling mode is selected to improve the system energy efficiency ratio.

In some embodiments, the temperature control system includes a control module, which is configured to selectively enable the air-conditioning refrigeration mode and the thermal management refrigeration mode at the same time or to enable one of the air-conditioning refrigeration mode and the thermal management refrigeration mode alone, and to switch between the first air-conditioning refrigeration mode and the second air-conditioning refrigeration mode independently of the thermal management refrigeration mode, and/or to switch between the first thermal management refrigeration mode and the second thermal management refrigeration mode independently of the air-conditioning refrigeration mode.

Through the above method, a combination of multiple cooling modes can be achieved, so that a more suitable cooling mode can be provided based on the demand of cooling load, thereby improving the energy efficiency ratio of the system.

In some embodiments, the thermal management circuit includes a third air-conditioning heat exchanger for exchanging heat with the condensing heat exchanger through the heat conductor, and the temperature control system has an air-conditioning heating mode for heating the air-conditioning airflow, and the air-conditioning heating mode includes a first air-conditioning heating mode and a second air-conditioning heating mode. The refrigerant switching component introduces the refrigerant compressed by the compressor into the condensing heat exchanger for condensation and heat release in the first air-conditioning heating mode and the second air-conditioning heating mode. In the first air-conditioning heating mode, the refrigerant switching component disconnects the flow path from the condensing heat exchanger to the first and second air-conditioning heat exchangers to heat the air-conditioning airflow using the third air-conditioning heat exchanger, or in the second air-conditioning heating mode, the refrigerant switching component introduces the refrigerant output from the condensing heat exchanger into at least one of the first and second air-conditioning heat exchangers, so that the at least one of the first and second air-conditioning heat exchangers and the third air-conditioning heat exchanger can heat the air-conditioning airflow in turn.

Through the above method, the present application provides two air conditioning heating modes, allowing traffic equipment to select between the two air conditioning heating modes according to actual working conditions. Specifically, in the first air conditioning heating mode, the third air conditioning heat exchanger is used to complete the single-stage heating of the air conditioning airflow, and its control method is relatively simple. In the second air conditioning heating mode, the third air conditioning heat exchanger and the first air conditioning heat exchanger and/or the second air conditioning heat exchanger are used to perform two-stage or more stage heating of the air conditioning airflow, and its energy efficiency ratio is relatively high, which can achieve a relatively good heating effect.

In some embodiments, the temperature control system also includes a control module, which controls the refrigerant switching component to switch to the first air-conditioning heating mode in response to the air-conditioning heating load in the air-conditioning heating mode being less than or equal to a preset air-conditioning heating load threshold, or controls the refrigerant switching component to switch to the second air-conditioning heating mode in response to the air-conditioning heating load being greater than the air-conditioning heating load threshold.

Through the above method, when the air conditioning heating load is low, the first air conditioning heating mode is selected to achieve efficient and simple control; and when the air conditioning heating load is high, the second air conditioning heating mode is selected to improve the system energy efficiency ratio.

In some embodiments, the air-conditioning heating mode includes a third air-conditioning heating mode. In the third air-conditioning heating mode, the refrigerant switching component introduces the refrigerant compressed by the compressor into at least one of the first air-conditioning heat exchanger and the second air-conditioning heat exchanger without passing through the condensing heat exchanger, thereby condensing and releasing heat from the air-conditioning airflow.

Through the above manner, on the basis of the first air-conditioning heating mode and the second air-conditioning heating mode in the form of an indirect heat pump, a third air-conditioning heating mode in the form of a direct heat pump is further provided, thereby providing more mode options.

In some embodiments, the thermal management circuit is also configured to cool the condensing heat exchanger through the heat conductor, and the temperature control system also includes a control module, which controls the refrigerant switching component to switch to the third air conditioning heating mode in response to the temperature of the heat conductor supplied to the condensing heat exchanger in the first air conditioning heating mode or the second air conditioning heating mode being greater than or equal to a preset temperature threshold.

In the above manner, by limiting the temperature threshold and switching to the third air conditioning heating mode when the heat transfer agent temperature exceeds the temperature threshold, the problem of limited system high pressure and limited compressor speed caused by the excessively high return temperature of the heat transfer agent at the condensing heat exchanger of the indirect heat pump can be alleviated.

In some embodiments, the designated component includes a first designated component, the thermal management circuit includes a first sub-thermal management circuit, a second sub-thermal management circuit, a third sub-thermal management circuit, a fourth sub-thermal management circuit and a thermal conductive agent switching component, the first sub-thermal management circuit is used to connect the condensing heat exchanger, the second sub-thermal management circuit includes an ambient heat exchanger, the third sub-thermal management circuit is connected to the first thermal management heat exchanger, the fourth sub-thermal management circuit is connected to the second thermal management heat exchanger, and one of the third sub-thermal management circuit and the fourth sub-thermal management circuit includes a first heat exchange area for heat exchange with the first designated component; in the air conditioning heating mode, the refrigerant switching component introduces the refrigerant into the first thermal management heat exchanger or the second thermal management heat exchanger connected to the third sub-thermal management circuit and the other of the four sub-thermal management circuits, and evaporates and absorbs heat; the thermal conductive agent switching component circulates the thermal conductive agent between the first sub-thermal management circuit and the second sub-thermal management circuit in the air conditioning cooling mode, and the thermal conductive agent switching component circulates the thermal conductive agent between the other of the third sub-thermal management circuit and the fourth sub-thermal management circuit and the second sub-thermal management circuit in the air conditioning heating mode.

In the above manner, by reusing the environmental heat exchanger in the air conditioning cooling mode and the air conditioning heating mode, the cost of the temperature control system can be effectively reduced, and the structure of the temperature control system can be more compact and simple.

In some embodiments, the thermal conductor switching component disables the circulation of the thermal conductor within the third sub-thermal management loop and the fourth sub-thermal management loop when not in the thermal management cooling mode, or forms a self-circulation of the thermal conductor within one of the third sub-thermal management loop and the fourth sub-thermal management loop, and circulates the thermal conductor between the third sub-thermal management loop and the fourth sub-thermal management loop in the thermal management cooling mode.

Through the above method, the energy efficiency ratio of the system can also be improved by reducing the circulation of the heat conductor in the sub-thermal management loop to reduce the energy consumption of the temperature control system.

In some embodiments, when not in the thermal management cooling mode, the temperature control system also includes a control module, which selectively controls the thermal conductor switching component to disable the circulation of the thermal conductor in the third sub-thermal management loop and the fourth sub-thermal management loop in response to the heat dissipation demand of the first designated component, or to form self-circulation of the thermal conductor in one of the third sub-thermal management loop and the fourth sub-thermal management loop.

Through the above method, based on the heat dissipation demand of the first designated component, the heat transfer agent in the sub-thermal management loop that exchanges heat with the first designated component is controlled to circulate selectively, which can meet the heat dissipation demand of the first designated component and help reduce energy consumption.

In some embodiments, one of the third sub-thermal management loop and the fourth sub-thermal management loop also includes a second heat exchange zone for heat exchange with a heater, and the thermal conductor switching component is also capable of circulating the thermal conductor between the third sub-thermal management loop and the fourth sub-thermal management loop in the air-conditioning heating mode, and guiding the thermal conductor to flow through the second heat exchange zone without passing through the first thermal management heat exchanger or the second thermal management heat exchanger and the first heat exchange zone to which the third sub-thermal management loop and the fourth sub-thermal management loop are connected.

In the above manner, the heater is used as an auxiliary heat source to supplement heat to the refrigerant circuit when the external ambient temperature is low and it is difficult to use the ambient heat exchanger to absorb heat from the environment, so as to reliably ensure the air conditioning heating effect of the temperature control system.

In some embodiments, the thermal conductor switching component can also guide the thermal conductor to flow through the first heat exchange area and the second heat exchange area without flowing through the first thermal management heat exchanger or the second thermal management heat exchanger to which one of the third sub-thermal management loop and the fourth sub-thermal management loop is connected.

Through the above method, by using the heater as an auxiliary heat source, the heat of the refrigerant circuit can be supplemented while heating the first designated component, thereby performing temperature management on the first designated component to ensure the air conditioning heating effect of the temperature control system and avoid the adverse effects of low temperature on the performance of the first designated component.

In some embodiments, the thermal conductor switching component includes a first thermal conductor valve and a second thermal conductor valve, the first thermal conductor valve being used to separately bypass the first thermal management heat exchanger or the second thermal management heat exchanger connected to one of the third sub-thermal management loop and the fourth sub-thermal management loop, and the second thermal conductor valve being used to simultaneously bypass the first heat exchange zone and the first thermal management heat exchanger or the second thermal management heat exchanger connected to one of the third sub-thermal management loop and the fourth sub-thermal management loop.

In the above manner, by controlling the first heat transfer agent valve and the second heat transfer agent valve, the heater can selectively supply heat to the refrigerant circuit alone, or the heater can simultaneously supply heat to the first designated component and the refrigerant circuit, so that the structure of the thermal management circuit is simple, low-cost and easy to implement.

In some embodiments, the designated component also includes a second designated component, the thermal management circuit also includes a fifth sub-thermal management circuit, the fifth sub-thermal management circuit includes a third heat exchange zone for heat exchange with the second designated component, and the thermal conductor switching component is also capable of circulating the thermal conductor between one of the third sub-thermal management circuit and the fourth sub-thermal management circuit and the fifth sub-thermal management circuit in the air conditioning heating mode.

Through the above method, the second designated component is used as an auxiliary heat source, the thermal management circuit absorbs heat from the second designated component and supplies heat to the refrigerant circuit or heats the first designated component through the first thermal management heat exchanger, thereby recovering and utilizing the waste heat of the second designated component, saving energy, and effectively improving the energy efficiency ratio of the temperature control system.

In some embodiments, the first designated component is a battery module of the transportation device, and the second designated component is a motor module of the transportation device.

Through the above method, since the motor module in the transportation equipment generates a lot of heat when working, it can be used as an auxiliary heat source to heat the temperature control system. In the low temperature environment, the energy conversion efficiency of the battery module is low. Therefore, the waste heat generated by the motor module can be used to supply the refrigerant circuit and the battery module, thereby improving energy utilization and energy efficiency.

In some embodiments, the thermal conductor switching component selectively circulates the thermal conductor between the first sub-thermal management circuit and the second sub-thermal management circuit in the air-conditioning refrigeration mode and/or the thermal management refrigeration mode, or circulates the thermal conductor between the first sub-thermal management circuit, the second sub-thermal management circuit and the fifth sub-thermal management circuit.

In the above manner, the heat dissipation requirement of the refrigerant circuit or the refrigerant circuit and the second designated component is selectively met by utilizing the environmental heat exchanger in the second thermal management sub-circuit to dissipate heat to the external environment.

In some embodiments, the third air-conditioning heat exchanger is located in the first sub-thermal management loop, and the temperature control system also includes an airflow switching component, and the temperature control system is configured to control the airflow switching component to guide the air-conditioning airflow through the third air-conditioning heat exchanger in the air-conditioning heating mode, and to guide the air-conditioning airflow not through the third air-conditioning heat exchanger in the air-conditioning cooling mode.

In the above manner, by setting the airflow switching component, it is possible to flexibly control whether the air-conditioning airflow performs heat exchange with the third air-conditioning heat exchanger, thereby reliably distinguishing the air-conditioning heating mode from the air-conditioning cooling mode and avoiding interference between the two modes.

In some embodiments, the thermal conductor switching component forms a self-circulation of the thermal conductor in the first sub-thermal management loop in the first air-conditioning heating mode and the second air-conditioning heating mode.

Through the above method, the heat absorbed by the first sub-thermal management loop from the third air-conditioning heat exchanger is fully utilized to heat the air-conditioning airflow, avoiding additional heat loss caused by the heat transfer agent entering other sub-thermal management loops, thereby effectively improving the system energy efficiency ratio in the heating mode.

In some embodiments, in the thermal management cooling mode, the refrigerant switching component guides the refrigerant through the first thermal management heat exchanger and the second thermal management heat exchanger in sequence, and in the second air conditioning heating mode, the refrigerant switching component guides the refrigerant through only one of the first air conditioning heat exchanger and the second air conditioning heat exchanger.

In the above manner, the first thermal management heat exchanger and the second thermal management heat exchanger are connected in series to reduce the complexity of the refrigerant circuit, making the refrigerant circuit more concise. In the second air-conditioning heating mode, the refrigerant is set to pass through only one of the first air-conditioning heat exchanger and the second air-conditioning heat exchanger, so that the number of components through which the refrigerant flows is small, which can avoid the refrigerant temperature dropping too low or the pressure dropping too low due to the refrigerant flow path being too long, resulting in poor heating effect of the air conditioning airflow.

In some embodiments, the outlet of the compressor is connected to the inlet of the condensing heat exchanger, and the refrigerant switching assembly includes a first refrigerant valve, a second refrigerant valve, a third refrigerant valve, a fourth refrigerant valve, a fifth refrigerant valve and a sixth refrigerant valve. The first refrigerant valve is connected between the outlet of the condensing heat exchanger and the inlet of the first air-conditioning heat exchanger. One end of the second refrigerant valve is connected between the outlet of the compressor and the inlet of the condensing heat exchanger. The other end of the second refrigerant valve is connected to the inlet of the first air-conditioning heat exchanger. One end of the third refrigerant valve is connected between the first refrigerant valve and the outlet of the condensing heat exchanger. The other end of the third refrigerant valve is connected to the inlet of the second air-conditioning heat exchanger and the inlet of the first thermal management heat exchanger through the fourth refrigerant valve and the fifth refrigerant valve, respectively. The sixth refrigerant valve is connected between the outlet of the first thermal management heat exchanger and the inlet of the second thermal management heat exchanger. The outlet of the first thermal management heat exchanger and the outlet of the second thermal management heat exchanger are connected to the inlet of the compressor. The sixth refrigerant valve is configured to selectively form or not form a pressure reduction on the refrigerant.

By the above method, the valve group and its position included in the refrigerant switching assembly are limited to simplify the structure of the refrigerant circuit, so that the refrigerant circuit can circulate the refrigerant more efficiently and controllably, thereby reducing energy dissipation during its circulation process and improving the energy efficiency ratio.

In order to solve the above technical problems, another technical solution adopted by the present application is to provide a transportation device, which includes the temperature control system as described above.

Through the above method, the temperature control system is applied to transportation equipment, and the various working modes provided by the temperature control system are utilized to provide transportation equipment with heating and cooling solutions for changing working conditions, so as to fully and energy-efficiently meet the temperature control needs of transportation equipment.

【Brief Description of the Drawings】

In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the drawings required for use in the embodiments or the prior art descriptions are briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative work, among which:

FIG1 is a schematic structural diagram of an embodiment of a temperature control system provided by the present application;

FIG2 is a schematic diagram of the structure of a refrigerant circuit in the temperature control system shown in FIG1 ;

FIG3 is a schematic diagram of the structure of a thermal management circuit in the temperature control system shown in FIG1 ;

FIG4 is a circuit diagram of a refrigerant circuit in a first air-conditioning cooling mode;

FIG5 is a circuit diagram of a refrigerant circuit in a second air-conditioning cooling mode;

6 is a circuit diagram of a refrigerant circuit in the first air-conditioning cooling mode and the first thermal management cooling mode at the same time or in the second air-conditioning heating mode and the first thermal management cooling mode at the same time;

7 is a circuit schematic diagram of a refrigerant circuit in both the second air-conditioning refrigeration mode and the first thermal management refrigeration mode;

8 is a circuit diagram of a refrigerant circuit in a first air conditioning refrigeration mode and a second thermal management refrigeration mode at the same time;

9 is a circuit schematic diagram of a refrigerant circuit in a second air-conditioning cooling mode and a second thermal management cooling mode at the same time;

10 is a circuit diagram of a refrigerant circuit in a first thermal management cooling mode or in both a first air-conditioning heating mode and a first thermal management cooling mode;

FIG11 is a circuit diagram of a refrigerant circuit in a second thermal management refrigeration mode;

12 is a circuit diagram of a refrigerant circuit in both the second air conditioning heating mode and the first thermal management cooling mode;

13 is a circuit diagram of a refrigerant circuit in both the third air-conditioning heating mode and the first thermal management cooling mode;

FIG14 is a schematic diagram of a first circuit of a thermal management circuit in an air conditioning cooling mode;

FIG15 is a second circuit diagram of the thermal management circuit in the air conditioning cooling mode;

16 is a schematic diagram of a first circuit of a thermal management circuit in a thermal management cooling mode or in both an air conditioning cooling mode and a thermal management cooling mode;

17 is a second circuit diagram of the thermal management circuit in the thermal management cooling mode or in the air conditioning cooling mode and the thermal management cooling mode at the same time;

FIG18 is a schematic diagram of a first circuit of a thermal management circuit in a first air conditioning and heating mode or a second air conditioning and heating mode;

FIG19 is a second circuit schematic diagram of the thermal management circuit in the first air conditioning heating mode or the second air conditioning heating mode;

FIG20 is a third circuit schematic diagram of the thermal management circuit in the first air conditioning heating mode or the second air conditioning heating mode;

FIG21 is a fourth circuit schematic diagram of the thermal management circuit in the first air conditioning heating mode or the second air conditioning heating mode;

FIG22 is a schematic diagram of a first circuit of a thermal management circuit in a third air-conditioning heating mode;

FIG23 is a second circuit schematic diagram of the thermal management circuit in the third air-conditioning heating mode;

FIG24 is a third circuit schematic diagram of the thermal management circuit in the third air-conditioning heating mode;

FIG. 25 is a fourth circuit schematic diagram of the thermal management circuit in the third air-conditioning heating mode.

【Detailed ways】

The following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the technical solutions in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of this application.

The terms "first", "second", and "third" in the embodiments of the present application are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the number of indicated technical features. Thus, the features defined as "first", "second", and "third" can expressly or implicitly include at least one of the features. In the description of the present application, the meaning of "multiple" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined. In addition, the terms "including" and "having" and any of their variations are intended to cover non-exclusive inclusions. For example, a process, method, system, product, or device comprising a series of steps or units is not limited to the listed steps or units, but optionally also includes steps or units that are not listed, or optionally also includes other steps or units inherent to these processes, methods, products, or devices.

Reference to "embodiments" herein means that a particular feature, structure, or characteristic described in conjunction with the embodiments may be included in at least one embodiment of the present application. The appearance of the phrase in various locations in the specification does not necessarily refer to the same embodiment, nor is it an independent or alternative embodiment that is mutually exclusive with other embodiments. It is explicitly and implicitly understood by those skilled in the art that the embodiments described herein may be combined with other embodiments.

Since transportation equipment needs to operate under complex and changeable working conditions, both air conditioning requirements and thermal management requirements are variable. However, the current working mode of the air conditioning system of transportation equipment is relatively single, and it is difficult to cope with the flexibility of complex working conditions. Through long-term research and experimental comparison, the applicant provides the following temperature control system with multiple working modes.

The present application provides a temperature control system 100 for transportation equipment. Referring to Figures 1 to 3, Figure 1 is a structural schematic diagram of the temperature control system provided by the present application, Figure 2 is a structural schematic diagram of the refrigerant circuit in the temperature control system shown in Figure 1, and Figure 3 is a structural schematic diagram of the thermal management circuit in the temperature control system shown in Figure 1.

The transportation equipment can be various types of vehicles, and the temperature control system 100 is arranged therein for cooling and heating to maintain the cockpit, battery module, motor module or other electronic devices at a suitable temperature, thereby providing a comfortable driving environment for the user and keeping the heat-generating components in the transportation equipment at a suitable temperature, thereby maintaining reliable performance.

The temperature control system 100 includes a refrigerant circuit 10 for circulating refrigerant, the refrigerant circuit 10 includes a compressor 11, a condensing heat exchanger 12, a first air-conditioning heat exchanger 13, a second air-conditioning heat exchanger 14 and a refrigerant switching component 15, and the temperature control system 100 has an air-conditioning refrigeration mode for refrigerating the air-conditioning airflow, and the air-conditioning refrigeration mode includes a first air-conditioning refrigeration mode and a second air-conditioning refrigeration mode. As shown in Figures 4 and 5, the refrigerant switching component 15 introduces the refrigerant compressed by the compressor 11 into the condensing heat exchanger 12 for condensation and heat release in the first air-conditioning refrigeration mode and the second air-conditioning refrigeration mode. As further shown in Figure 4, in the first air-conditioning refrigeration mode, the refrigerant switching component 15 introduces the refrigerant output by the condensing heat exchanger 12 into one of the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14 in a depressurized manner, so that one of the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14 evaporates and absorbs heat from the air-conditioning airflow. As further shown in Figure 5, in the second air-conditioning refrigeration mode, the refrigerant switching component 15 introduces the refrigerant output by the condensing heat exchanger 12 into the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14 in turn in a pressure-reducing manner, so that the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14 evaporate and absorb heat from the air-conditioning airflow in turn.

Among them, the compressor 11 is a fluid machinery that boosts low-pressure fluid to high-pressure fluid, that is, the compressor 11 can compress the low-temperature and low-pressure refrigerant fluid and input the high-temperature and high-pressure refrigerant fluid into the condensing heat exchanger 12, so that the refrigerant can complete condensation and heat release in the condensing heat exchanger 12; the compressor 11 can specifically be a piston compressor or a centrifugal compressor, etc.

Refrigerant, also known as coolant or refrigerant, is a medium substance used in various heat engines to complete energy conversion, thereby realizing energy transfer. It usually undergoes a reversible phase change (such as gas-liquid phase change) during the energy conversion process, or it can remain in a gaseous state during the energy conversion process. It can be a hydrocarbon (such as propane, ethylene) or ammonia, etc.

The condensing heat exchanger 12, the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14 are all heat exchange devices that realize heat transfer between two or more fluids at different temperatures, so that heat is transferred from the fluid with a higher temperature to the fluid with a lower temperature; the refrigerant condenses and releases heat in the condensing heat exchanger 12, and evaporates and absorbs heat in the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14; and the refrigerant exchanges heat with the heat conductor in the condensing heat exchanger 12, and exchanges heat with the air-conditioning airflow in the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14.

The refrigerant switching assembly 15 may include multiple valve groups for switching the refrigerant path, for example, it includes multiple shut-off valves and multiple expansion valves, so that the opening or closing of each valve group can realize the flow path selection of the refrigerant. In other words, the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14 can be connected in series under the control of the refrigerant switching assembly 15 to realize the second air-conditioning refrigeration mode; the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14 can also be connected to the refrigerant circuit 10 under the control of the refrigerant switching assembly 15 to realize the first air-conditioning refrigeration mode.

The air conditioning cooling mode can be used to achieve cooling in the vehicle cabin, wherein the air conditioning air flow is cooled after absorbing heat through the first air conditioning heat exchanger 13 and/or the second air conditioning heat exchanger 14, and the temperature is reduced, and can be guided into the vehicle cabin to cool the ambient temperature in the cabin, so that the temperature in the cabin can be maintained within a temperature range suitable for the user's body temperature.

For example, in summer, the temperature in the vehicle cabin is high, and the temperature in the vehicle cabin can be lowered by turning on the air conditioning refrigeration mode, so that the user can drive more comfortably. Based on different air conditioning refrigeration loads or other working conditions, the first air conditioning refrigeration mode or the second air conditioning refrigeration mode can be selected for cooling, wherein the first air conditioning refrigeration mode uses one of the first air conditioning heat exchanger 13 and the second air conditioning heat exchanger 14 to evaporate and absorb heat from the air conditioning airflow, and the second air conditioning refrigeration mode uses the first air conditioning heat exchanger 13 and the second air conditioning heat exchanger 14 to evaporate and absorb heat from the air conditioning airflow in sequence, that is, the first air conditioning refrigeration mode uses a single-stage refrigeration method for the air conditioning airflow, and the second air conditioning refrigeration mode uses a two-stage refrigeration method of precooling the air conditioning airflow once and then cooling the precooled air conditioning airflow twice. The air conditioning airflow can effectively increase the amount of cold it can absorb by adding a precooling step, so that its cooling range is larger, and thus the energy efficiency ratio in the second air conditioning refrigeration mode is higher, and a stronger cooling effect can be achieved.

Relatively speaking, in the first air conditioning refrigeration mode, only one of the first air conditioning heat exchanger 13 and the second air conditioning heat exchanger 14 needs to be controlled to complete the cooling of the air conditioning airflow, and its control method is simpler; while in the second air conditioning refrigeration mode, pre-cooling is performed first and then secondary cooling is performed, and its energy efficiency ratio is higher, which can achieve a stronger cooling effect and thus meet a stronger cooling demand. In other words, by setting two air conditioning refrigeration modes, the present application can enable the transportation equipment to switch modes according to the cooling conditions required by itself during air conditioning cooling.

In one embodiment, the temperature control system 100 also includes a control module 70, which controls the refrigerant switching component 15 to switch to the first air-conditioning refrigeration mode in response to the air-conditioning refrigeration load in the air-conditioning refrigeration mode being less than or equal to a preset air-conditioning refrigeration load threshold, or controls the refrigerant switching component 15 to switch to the second air-conditioning refrigeration mode in response to the air-conditioning refrigeration load being greater than the air-conditioning refrigeration load threshold.

The control module 70 can be a CPU (Central Processing Unit), an MCU (Microcontroller Unit) or a circuit board with a control circuit, etc., which is connected to the refrigerant switching component 15 through a signal line, wherein the signal line between the control module 70 and the remaining components in the temperature control system 100 as shown in FIG. 1 is omitted.

The preset air conditioning refrigeration load threshold can be a specific value or a value range, which can be obtained through experiments or simulation verification of two air conditioning refrigeration modes combined with ambient temperature and a temperature suitable for the user's body feel. This application does not impose any specific restrictions on its specific value size or range.

After long-term research, the applicant found that when the air-conditioning refrigeration load is low, the energy efficiency ratios of the two air-conditioning refrigeration modes are not much different, and thus a simpler control method can be obtained by selecting the first air-conditioning refrigeration mode; when the air-conditioning refrigeration load is high, the second air-conditioning refrigeration mode is selected to improve the system energy efficiency ratio.

The temperature control system 100 automatically switches to the first air conditioning and cooling mode or the second air conditioning and cooling mode based on the above set conditions.

As shown in FIGS. 1 and 2 , in this embodiment, the refrigerant switching assembly 15 includes a first refrigerant valve 151, a third refrigerant valve 153 and a fourth refrigerant valve 154. The compressor 11, the condensing heat exchanger 12, the first refrigerant valve 151, the first air conditioning heat exchanger 13, the fourth refrigerant valve 154 and the second air conditioning heat exchanger 14 form a series loop, one end of the third refrigerant valve 153 is connected between the first refrigerant valve 151 and the outlet of the condensing heat exchanger 12, and the other end of the third refrigerant valve 153 is connected between the outlet of the first air conditioning heat exchanger 13 and the fourth refrigerant valve 154.

The first refrigerant valve 151 and the fourth refrigerant valve 154 may be expansion valves, and the third refrigerant valve 153 may be a stop valve or a switch valve.

Referring to FIG. 2 and FIG. 4 , FIG. 4 is a circuit diagram of the refrigerant circuit of the temperature control system in the first air conditioning refrigeration mode as shown in FIG. 2 . In the first air conditioning refrigeration mode, the first refrigerant valve 151 is closed and the third refrigerant valve 153 is opened, so that the first air conditioning heat exchanger 13 can be bypassed, so that the refrigerant output by the condensing heat exchanger 12 is introduced into the second air conditioning heat exchanger 14 through the fourth refrigerant valve 154, wherein the fourth refrigerant valve 154 reduces the pressure of the refrigerant passing through, and then the second air conditioning heat exchanger 14 evaporates and absorbs heat from the air conditioning airflow. In other embodiments, the refrigerant can also be introduced into the first air conditioning heat exchanger 13 by closing the third refrigerant valve 153 and the fourth refrigerant valve 154.

Referring to FIG. 2 and FIG. 5 , FIG. 5 is a circuit diagram of the refrigerant circuit of the temperature control system in the second air conditioning refrigeration mode as shown in FIG. 2 . In the second air conditioning refrigeration mode, the third refrigerant valve 153 is closed, and the refrigerant output by the condensing heat exchanger 12 is first introduced into the first air conditioning heat exchanger 13 through the first refrigerant valve 151, and then introduced into the second air conditioning heat exchanger 14 through the fourth refrigerant valve 154, wherein the first refrigerant valve 151 and the fourth refrigerant valve 154 successively reduce the pressure of the refrigerant passing through, so that the first air conditioning heat exchanger 13 and the second air conditioning heat exchanger 14 successively evaporate and absorb heat from the air conditioning airflow.

Furthermore, a gas-liquid separation device 18 is provided at the outlet of the condensing heat exchanger 12 , and a check valve 19 is provided at the outlet of the first air-conditioning heat exchanger 13 .

Optionally, a valve group may be provided to bypass the second air-conditioning heat exchanger 14 to determine whether to connect the second air-conditioning heat exchanger 14 to the circulation loop of the refrigerant loop 10; alternatively, the branch where the first air-conditioning heat exchanger 13 is located, the branch where the second air-conditioning heat exchanger 14 is located, and the bypass pipe branch are connected in parallel, and valve groups are provided on the three branches to realize the first air-conditioning refrigeration mode and the second air-conditioning refrigeration mode as described above.

Further, the refrigerant circuit 10 also includes a first thermal management heat exchanger 16 and a second thermal management heat exchanger 17, the temperature control system 100 also includes a thermal management circuit 20 for circulating a heat transfer agent, the thermal management circuit 20 is used to perform thermal management on a designated component 30 of the traffic equipment, and the temperature control system 100 has a thermal management refrigeration mode for refrigerating the designated component 30, and the thermal management refrigeration mode includes a first thermal management refrigeration mode and a second thermal management refrigeration mode. As shown in Figures 6-9, the refrigerant switching component 15 introduces the refrigerant compressed by the compressor 11 into the condensing heat exchanger 12 for condensation and heat release in the first thermal management refrigeration mode and the second thermal management refrigeration mode. As further shown in Figures 6-7, in the first thermal management refrigeration mode, the refrigerant switching component 15 introduces the refrigerant output from the condensing heat exchanger 12 into one of the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 in a depressurized manner, thereby causing one of the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 to evaporate and absorb heat from the heat transfer agent. Further, as shown in Figures 8-9, in the second thermal management refrigeration mode, the refrigerant switching component 15 introduces the refrigerant output by the condensing heat exchanger 12 into the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 in a pressure-reducing manner, so that the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 evaporate and absorb heat from the heat transfer agent in turn.

As shown in Figure 2, in this embodiment, the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 are connected in series in the refrigerant circuit 10, and the refrigerant switching component 15 also includes a fifth refrigerant valve 155 and a sixth refrigerant valve 156. The fifth refrigerant valve 155 is connected between the refrigerant inlet of the first thermal management heat exchanger 16 and the outlet of the first air-conditioning heat exchanger 13, and the sixth refrigerant valve 156 is connected to the pipeline between the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17, wherein the fifth refrigerant valve 155 and the sixth refrigerant valve 156 can be expansion valves, so that the expansion valve can be used to form a pressure reduction on the refrigerant, and when the expansion valve is at the maximum opening degree, it has no pressure reduction effect on the refrigerant flowing through.

Therefore, in the first thermal management cooling mode, one of the fifth refrigerant valve 155 and the sixth refrigerant valve 156 is at the maximum opening degree, so that the refrigerant output by the condensing heat exchanger 12 can be introduced into one of the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 in a reduced pressure manner.

In the second thermal management refrigeration mode, the fifth refrigerant valve 155 and the sixth refrigerant valve 156 are not at the maximum opening degree, and the refrigerant output by the condensing heat exchanger 12 can be introduced into the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 in sequence in a reduced pressure manner.

Referring to Figures 2, 6 and 7, Figure 6 is a circuit diagram of the refrigerant circuit in the first air-conditioning refrigeration mode and the first thermal management refrigeration mode at the same time, and Figure 7 is a circuit diagram of the refrigerant circuit in the second air-conditioning refrigeration mode and the first thermal management refrigeration mode at the same time. In Figures 6 and 7, the sixth refrigerant valve 156 is omitted, indicating that it is at the maximum opening degree and has no decompression effect on the refrigerant. In the first thermal management refrigeration mode, the fifth refrigerant valve 155 has a decompression effect on the refrigerant, and the refrigerant output by the condensing heat exchanger 12 is introduced into the first thermal management heat exchanger 16 in a decompression manner, while the sixth refrigerant valve 156 is at the maximum opening degree and has no decompression effect on the refrigerant flowing through, and the refrigerant flows through the second thermal management heat exchanger 17 without decompression.

Referring to Figures 2, 8 and 9, Figure 8 is a circuit diagram of the refrigerant circuit in the first air conditioning refrigeration mode and the second thermal management refrigeration mode at the same time, and Figure 9 is a circuit diagram of the refrigerant circuit in the second air conditioning refrigeration mode and the second thermal management refrigeration mode at the same time. In the second thermal management refrigeration mode, both the fifth refrigerant valve 155 and the sixth refrigerant valve 156 have a decompression effect on the refrigerant. The refrigerant output from the condensing heat exchanger 12 is first introduced into the first thermal management heat exchanger 16 in a decompression manner after passing through the fifth refrigerant valve 155, and then introduced into the second thermal management heat exchanger 17 in a decompression manner through the sixth refrigerant valve 156.

In other embodiments, a valve group and a bypass pipe can be provided to bypass one of the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 to realize the first thermal management refrigeration mode and the second thermal management refrigeration mode as described above. The specific structure of the bypass pipe can refer to the bypass structure of the third refrigerant valve 153 to the first air-conditioning heat exchanger 13, which will not be repeated here.

The thermal management loop 20 can be used for thermal management of cooling or heating of a designated component 30, wherein the thermal management loop 20 performs thermal management by thermal coupling with the designated component 30, for example, the thermal management loop 20 is wrapped around the designated component 30, or the thermal management loop 20 is at least attached to a contact surface of the designated component 30 to perform contact heat transfer, thereby achieving thermal management of the designated component 30.

The designated component 30 may be an electronic component such as a battery module, motor module or controller on transportation equipment, which is sometimes prone to excessive temperature rise during operation, for example, due to high ambient temperature, long working hours or insufficient heat dissipation under high power, and high temperature can easily lead to a decline in its performance. Therefore, thermal management can keep the designated component 30 at a suitable temperature during operation to obtain better performance.

Among them, the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 are also heat exchange devices that realize heat transfer between two or more fluids at different temperatures. The heat conductor is a liquid or gas that conducts heat. The refrigerant and the heat conductor exchange heat in the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17, wherein the refrigerant evaporates and absorbs heat, and its own temperature rises, while the heat conductor absorbs heat and its temperature decreases. Therefore, when the heat conductor flows through the designated component 30, it can take away the heat of the designated component 30 to achieve thermal management of the designated component 30.

The first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 can be selectively connected to the refrigerant circuit 10 by means of the refrigerant switching assembly 15, so that the refrigerant can be introduced into at least one of them, wherein the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 can be connected in series or in parallel, and the present application does not impose any specific restrictions on this.

The thermal management loop 20 can be controlled to pass through at least one of the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17, so that the heat transfer agent can complete the heat exchange with the refrigerant therein to achieve temperature reduction thermal management, that is, thermal management cooling mode. The thermal management loop 20 can also be controlled not to pass through the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 to achieve temperature increase thermal management.

The thermal management refrigeration mode is used to achieve cooling for the designated component 30 to perform cooling thermal management, wherein after the heat conductor exchanges heat with the refrigerant in the first thermal management heat exchanger 16 and/or the second thermal management heat exchanger 17, the temperature of the heat conductor decreases, and under the guidance of the thermal management circuit 20, the heat conductor can flow through the designated component 30, thereby cooling the designated component 30 to maintain the designated component 30 working at the set temperature, so that it has better working performance, thereby achieving thermal management of the designated component 30.

In the above embodiment, the first thermal management refrigeration mode uses one of the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 to evaporate and absorb heat from the heat conductor, and the second thermal management refrigeration mode uses the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 to evaporate and absorb heat from the heat conductor in sequence, that is, the first thermal management refrigeration mode performs single-stage refrigeration on the heat conductor, and the second thermal management refrigeration mode performs a pre-cooling on the heat conductor, and then performs a secondary refrigeration on the pre-cooled heat conductor. By adding a preheating step to the heat conductor, the amount of cold absorbed by it can be effectively increased, thereby making the cooling range of the heat conductor larger, and thus the energy efficiency ratio in the second thermal management refrigeration mode is higher, and a stronger refrigeration effect can be achieved.

Relatively speaking, in the first thermal management cooling mode, only one of the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 is needed to complete the cooling of the heat transfer agent, and its control method is simpler. In the second thermal management cooling mode, precooling is performed first and then secondary cooling is performed, which has a higher energy efficiency ratio and can achieve a stronger cooling effect. In other words, by setting two thermal management cooling modes, the present application allows the transportation equipment to switch modes according to the cooling conditions required by itself during thermal management.

In one embodiment, the control module 70 also controls the refrigerant switching component 15 to switch to the first thermal management refrigeration mode in response to the thermal management refrigeration load in the thermal management refrigeration mode being less than or equal to a preset thermal management refrigeration load threshold, or controls the refrigerant switching component 15 to switch to the second thermal management refrigeration mode in response to the thermal management refrigeration load being greater than the thermal management refrigeration load threshold.

The preset thermal management cooling load threshold can be a specific value or a range of values, which can be obtained through experiments using two thermal management cooling modes combined with the required operating temperature of the specified component 30. The present application does not impose any specific restrictions on its specific value size or range.

After long-term research, the applicant found that when the thermal management load is low, the energy efficiency ratios of the two thermal management refrigeration modes are not much different. Therefore, by selecting a relatively simple first thermal management refrigeration mode, efficient and concise control can be achieved; and when the thermal management refrigeration load is high, the second thermal management refrigeration mode is selected to improve the system energy efficiency ratio.

The temperature control system 100 automatically switches to the first thermal management cooling mode or the second thermal management cooling mode based on the above set conditions.

Continuing to refer to Figure 2, in this embodiment, the control module 70 is configured to selectively enable the air-conditioning refrigeration mode and the thermal management refrigeration mode at the same time or to enable one of the air-conditioning refrigeration mode and the thermal management refrigeration mode alone, and to switch between the first air-conditioning refrigeration mode and the second air-conditioning refrigeration mode independently of the thermal management refrigeration mode, and to switch between the first thermal management refrigeration mode and the second thermal management refrigeration mode independently of the air-conditioning refrigeration mode.

Specifically, the refrigerant switching component 15 can independently realize the regulation of the first air-conditioning heat exchanger 13, the second air-conditioning heat exchanger 14, the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17, and can selectively connect the first air-conditioning heat exchanger 13, the second air-conditioning heat exchanger 14, the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 to the refrigerant circuit 10, so as to switch the air-conditioning cooling mode and the thermal management cooling mode independently of each other.

Specifically, the above-mentioned specific switching modes can be understood in detail by referring to Figures 2, 4 to 11. As shown in Figure 2, each valve group in the refrigerant switching assembly 15 is in a corresponding open or closed state to form a refrigerant circuit schematic diagram as shown in Figures 4 to 11 respectively.

Among them, Figures 6 to 9 show that the temperature control system 100 can simultaneously enable the air-conditioning refrigeration mode and the thermal management refrigeration mode, Figures 3 and 4 show that the temperature control system 100 can enable the air-conditioning refrigeration mode alone, Figures 10 and 11 show that the temperature control system 100 can enable the thermal management refrigeration mode alone, and Figures 6 and 7 as well as Figures 8 and 9 respectively show that the temperature control system 100 can switch between the first air-conditioning refrigeration mode and the second air-conditioning refrigeration mode independently of the thermal management refrigeration mode, and can switch between the first thermal management refrigeration mode and the second thermal management refrigeration mode independently of the air-conditioning refrigeration mode.

Further, referring to FIG. 1 and FIG. 3 , the thermal management circuit 20 includes a third air conditioning heat exchanger 211 for performing heat exchange with the condensing heat exchanger 12 through a heat transfer agent, and the temperature control system 100 has an air conditioning heating mode for heating the air conditioning airflow, and the air conditioning heating mode includes a first air conditioning heating mode and a second air conditioning heating mode. As shown in FIGS. 6 , 10 and 12 , the refrigerant switching component 15 introduces the refrigerant compressed by the compressor 11 into the condensing heat exchanger 12 for condensation and heat release in the first air conditioning heating mode and the second air conditioning heating mode. As further shown in FIG. 10 , in the first air conditioning heating mode, the refrigerant switching component 15 disconnects the flow path from the condensing heat exchanger 12 to the first air conditioning heat exchanger 13 and the second air conditioning heat exchanger 14, so as to heat the air conditioning airflow using the third air conditioning heat exchanger 211. As further shown in Figures 6 and 12, in the second air-conditioning heating mode, the refrigerant output by the condensing heat exchanger 12 is introduced into at least one of the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14, so that at least one of the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14 and the third air-conditioning heat exchanger 211 can heat the air-conditioning airflow in turn.

The air conditioning airflow is generated by the blower device 50, and the thermal management circuit 20 can also be used to heat the air conditioning airflow to achieve heating in the vehicle cabin. The third air conditioning heat exchanger 211 is a heat exchange device that realizes heat transfer between two or more fluids at different temperatures. The heat transfer agent exchanges heat with the air conditioning airflow in the third air conditioning heat exchanger 211, and the heat transfer agent releases heat to heat the air conditioning airflow.

Specifically, the refrigerant condenses and releases heat in the condensing heat exchanger 12, and the heat conductor exchanges heat with the refrigerant in the condensing heat exchanger 12, that is, the heat conductor absorbs heat, and then the heat conductor flows to the third air-conditioning heat exchanger 211, and exchanges heat with the air-conditioning airflow in the third air-conditioning heat exchanger 211 to heat the air-conditioning airflow.

The air conditioning heating mode is used to heat the vehicle cabin. In the air conditioning heating mode, the air conditioning airflow passes through the third air conditioning heat exchanger 211 and is heated, or the air conditioning airflow passes through at least one of the first air conditioning heat exchanger 13 and the second air conditioning heat exchanger 14 and the third air conditioning heat exchanger 211 in sequence and is heated. The heated air conditioning airflow is guided into the vehicle cabin to raise the ambient temperature in the cabin so that the temperature in the cabin can be maintained within a temperature range suitable for the user's body temperature.

For example, in winter, the temperature in the vehicle cabin is low. By turning on the air conditioning heating mode, the temperature in the vehicle cabin can be raised to make the user more comfortable while driving.

In the above embodiment, the first air-conditioning heating mode uses a separate third air-conditioning heat exchanger 211 to perform single-stage heating of the air-conditioning airflow, and the second air-conditioning heating mode uses at least one of the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14 and the third air-conditioning heat exchanger 211 to sequentially heat the air-conditioning airflow in two or more stages, that is, in the second air-conditioning heating mode, one of the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14 is used to preheat the air-conditioning airflow first, and then the third air-conditioning heat exchanger 211 is used to perform secondary heating of the preheated air-conditioning airflow, or the other of the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14 and the third air-conditioning heat exchanger 211 are used to perform secondary heating and tertiary heating of the preheated air-conditioning airflow. The air-conditioning airflow can effectively increase the amount of heat absorbed by the air-conditioning airflow by adding a preheating step, thereby making the temperature rise of the air-conditioning airflow greater, and thus the energy efficiency ratio in the second air-conditioning cooling mode is higher, and a stronger heating effect can be achieved.

Relatively speaking, in the first air conditioning heating mode, only the third air conditioning heat exchanger 211 is needed to heat the air conditioning airflow, and its control method is simpler; while the energy efficiency ratio in the second air conditioning heating mode is higher, and a stronger heating effect can be achieved. In other words, by setting two air conditioning heating modes, the present application can enable the transportation equipment to switch modes according to the heating conditions required by itself during air conditioning heating.

In one embodiment, the control module 70 controls the refrigerant switching component 15 to switch to the first air-conditioning heating mode in response to the air-conditioning heating load in the air-conditioning heating mode being less than or equal to a preset air-conditioning heating load threshold, or controls the refrigerant switching component 15 to switch to the second air-conditioning heating mode in response to the air-conditioning heating load being greater than the air-conditioning heating load threshold.

The preset air conditioning heating load threshold can be a specific value or a value range, which can be obtained through experiments or simulation verification based on two air conditioning heating modes combined with ambient temperature and a body temperature suitable for the user. This application does not impose any specific restrictions on its specific value size or range.

Through the above method, when the air-conditioning heating load is low, the energy efficiency ratios of the two air-conditioning heating modes are not much different, and then by selecting the first air-conditioning heating mode, efficient and simple control can be achieved; when the air-conditioning heating load is high, the second air-conditioning heating mode is selected to improve the system energy efficiency ratio.

The temperature control system 100 can automatically switch to the first air conditioning and heating mode or the second air conditioning and heating mode based on the above-set conditions.

Further, as shown in Figure 13, the air-conditioning heating mode includes a third air-conditioning heating mode. In the third air-conditioning heating mode, the refrigerant switching component 15 introduces the refrigerant compressed by the compressor 11 into at least one of the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14 without passing through the condensing heat exchanger 12, thereby condensing and releasing heat from the air-conditioning airflow.

As shown in Figures 1 and 2, the refrigerant switching assembly 15 also includes a second refrigerant valve 152, one end of the second refrigerant valve 152 is connected between the outlet of the compressor 11 and the inlet of the condensing heat exchanger 12, and the other end of the second refrigerant valve 152 is connected to the inlet of the first air-conditioning heat exchanger 13. The second refrigerant valve 152 can be a shut-off valve or a switch valve.

Referring to Figures 2 and 13 in combination, in the third air-conditioning heating mode, the first refrigerant valve 151 and the third refrigerant valve 153 are closed, the second refrigerant valve 152 is opened, and the fourth refrigerant valve 154 can be opened or closed, so that the refrigerant compressed by the compressor 11 can be introduced into at least one of the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14 without passing through the condensing heat exchanger 12.

That is, in the third air-conditioning heating mode, the refrigerant switching component 15 changes the flow path of the refrigerant so that the refrigerant compressed by the compressor 11 bypasses the condensing heat exchanger 12 and is directly introduced into at least one of the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14, and condenses and releases heat to heat the air-conditioning airflow.

Relatively speaking, the first air conditioning heating mode and the second air conditioning heating mode belong to the indirect heat pump mode, that is, the heat of the condensing heat exchanger 12 is transferred to the air conditioning airflow by using the heat conductor as a transfer. The third air conditioning heating mode changes the flow path of the refrigerant through the refrigerant switching component 15, and introduces the refrigerant compressed by the compressor 11 into at least one of the first air conditioning heat exchanger 13 and the second air conditioning heat exchanger 14 without passing through the condensing heat exchanger 12, so as to directly condense and release heat on the air conditioning airflow by using the first air conditioning heat exchanger 13 and/or the second air conditioning heat exchanger 14, and directly pass through. That is, the third air conditioning heating mode belongs to the direct heat pump mode, which can be used as an effective supplement to the indirect heat pump.

In one embodiment, the thermal management circuit 20 is also configured to cool the condensing heat exchanger 12 through a heat conductor, and the control module 70 also controls the refrigerant switching component 15 to switch to the third air-conditioning heating mode in response to the temperature of the heat conductor supplied to the condensing heat exchanger 12 in the first air-conditioning heating mode or the second air-conditioning heating mode being greater than or equal to a preset temperature threshold.

Specifically, in some cases, the return temperature of the heat transfer agent supplied to the condensing heat exchanger 12 may be too high, which will cause the high pressure of the temperature control system 100 to be limited, and the speed of the compressor 11 to be low, so that even if the waste heat is sufficient, it is impossible to absorb more waste heat, and the system energy efficiency ratio is low. If the refrigerant does not pass through the condensing heat exchanger 12, it can effectively avoid the adverse conditions caused by the excessively high return temperature of the heat transfer agent of the condensing heat exchanger 12, thereby relieving the high pressure limitation of the temperature control system 100 and the speed limitation of the compressor 11, and improving the system energy efficiency ratio.

The preset temperature threshold may be a specific value or a range of values, which may be obtained through specific experiments or simulation verifications. The present application does not impose any specific limitation on the specific value size or range.

In the above manner, by limiting the temperature threshold and switching to the third air-conditioning mode when the heat transfer agent temperature exceeds the temperature threshold, the system high pressure limitation and the compressor speed limitation caused by the excessively high return temperature of the heat transfer agent at the condensing heat exchanger 12 can be avoided.

The temperature control system 100 can automatically switch to the third air conditioning and heating mode based on the above set conditions.

1 and 3, in this embodiment, the designated component 30 includes a first designated component 31, the thermal management circuit 20 includes a first sub-thermal management circuit 21, a second sub-thermal management circuit 22, a third sub-thermal management circuit 23, a fourth sub-thermal management circuit 24 and a heat transfer agent switching component 25, the first sub-thermal management circuit 21 is used to connect to the condensing heat exchanger 12, the second sub-thermal management circuit 22 includes an environmental heat exchanger 221, the third sub-thermal management circuit 23 is connected to the first thermal management heat exchanger 16, the fourth sub-thermal management circuit 24 is connected to the second thermal management heat exchanger 17, and one of the third sub-thermal management circuit 23 and the fourth sub-thermal management circuit 24 includes a first heat exchange area 241 for heat exchange with the first designated component 31. As shown in FIGS. 10, 12 and 13, in the air conditioning heating mode, the refrigerant switching component 15 introduces the refrigerant into the first thermal management heat exchanger 16 or the second thermal management heat exchanger 17 connected to the other of the third sub-thermal management circuit 23 and the fourth sub-thermal management circuit 24, and evaporates and absorbs heat. As shown in FIGS. 14-17 , the thermal conductive agent switching assembly 25 circulates the thermal conductive agent between the first sub-thermal management loop 21 and the second sub-thermal management loop 22 in the air conditioning cooling mode. As shown in FIGS. 14-23 , the thermal conductive agent switching assembly 25 circulates the thermal conductive agent between the other of the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24 and the second sub-thermal management loop 22 in the air conditioning heating mode.

The first designated component 31 is a heat generating component, which may be a battery module, a motor module or other electronic components, etc. The environmental heat exchanger 221 is also a heat exchange device for realizing heat transfer between two or more fluids at different temperatures, and will not be described in detail.

The first sub-thermal management loop 21 , the second sub-thermal management loop 22 , the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24 are all used for circulating the heat transfer agent and are all pipeline structures.

The first sub-heat management loop 21 is used to connect to the condensing heat exchanger 12 so that the heat transfer agent and the refrigerant exchange heat in the condensing heat exchanger 12, wherein the refrigerant condenses and releases heat, and the heat transfer agent absorbs heat.

The second sub-heat management loop 22 includes an environmental heat exchanger 221 . The heat transfer agent circulates in the second sub-heat management loop 22 and can release heat to the external environment through the environmental heat exchanger 221 to complete heat exchange with the external air.

The thermal conductor switching component 25 may include a variety of valve groups and pumps, etc., which can connect different sub-thermal management loops through the valve groups or make the sub-thermal management loops self-circulating. The pump is used to provide the power required for the circulation of the thermal conductor. Therefore, the thermal conductor switching component 25 can enable the thermal conductor to circulate in at least one of the first sub-thermal management loop 21, the second sub-thermal management loop 22, the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24.

The control module 70 is also connected to the thermal conductive agent switching assembly 25 via a signal line to control it to circulate the thermal conductive agent in the corresponding sub-thermal management loop.

Referring to Figures 1, 3 and 14 in combination, Figure 14 is a first circuit schematic diagram of the thermal management circuit in the air-conditioning refrigeration mode, and specifically may be a circuit schematic diagram of the thermal management circuit 20 when the temperature control system 100 alone enables the air-conditioning refrigeration mode, and the air-conditioning refrigeration mode may be the first air-conditioning refrigeration mode or the second air-conditioning refrigeration mode.

In the air-conditioning cooling mode, the heat conductor switching component 25 connects the first sub-thermal management loop 21 and the second sub-thermal management loop 22, and circulates the heat conductor between the first sub-thermal management loop 21 and the second sub-thermal management loop 22, so that the heat absorbed by the heat conductor at the condensing heat exchanger 12 can be released to the outside through the ambient heat exchanger 221, wherein the heat conductor releases heat in the ambient heat exchanger 221 and the outside air absorbs heat.

As shown in FIG. 1 and FIG. 3 , the third thermal management sub-loop 23 is connected to the first thermal management heat exchanger 16 so that the heat transfer agent and the refrigerant can exchange heat in the first thermal management heat exchanger 16 , wherein the refrigerant releases heat and the heat transfer agent absorbs heat.

The fourth sub-heat management loop 24 is connected to the second heat management heat exchanger 17 so that the heat transfer agent and the refrigerant can exchange heat in the second heat management heat exchanger 17 , wherein the refrigerant releases heat and the heat transfer agent absorbs heat.

In this embodiment, the fourth sub-thermal management loop 24 is provided with a first heat exchange area 241 for heat exchange with the first designated component 31. The first designated component 31 exchanges heat with the fourth sub-thermal management loop 24 through the first heat exchange area 241, so that the first designated component 31 can be thermally managed by heating up or cooling down. The part of the fourth sub-thermal management loop 24 that contacts the first designated component 31 is the first heat exchange area 241, for example, part of the pipeline of the fourth sub-thermal management loop 24 is wound around the first designated component 31 or contacts one side of the first designated component 31. In other embodiments, the first heat exchange area 241 can also be set in the third sub-thermal management loop 23.

Referring to Figures 1, 3, 18, 19, 22 and 23, Figure 18 is a first circuit schematic diagram of the thermal management circuit in the first air-conditioning heating mode or the second air-conditioning heating mode, Figure 19 is a second circuit schematic diagram of the thermal management circuit in the first air-conditioning heating mode or the second air-conditioning heating mode, Figure 22 is a first circuit schematic diagram of the thermal management circuit in the third air-conditioning heating mode, and Figure 23 is a second circuit schematic diagram of the thermal management circuit in the third air-conditioning heating mode.

As shown in Figures 18, 19, 22 and 23, in the air conditioning heating mode, the heat transfer agent switching component 25 connects the third sub-thermal management loop 23 and the second sub-thermal management loop 22, and circulates the heat transfer agent between the third sub-thermal management loop 23 and the second sub-thermal management loop 22, wherein the heat absorbed by the heat transfer agent at the first thermal management heat exchanger 16 can be supplemented from the outside through the environmental heat exchanger 221, wherein the heat transfer agent absorbs heat in the environmental heat exchanger 221 and the outside air releases heat. In other embodiments, if the first heat exchange area 241 can also be set in the third sub-thermal management loop 23, a similar setting method can be adopted for the fourth sub-thermal management loop 24.

The present application can effectively reduce the cost of the temperature control system 100 by reusing the environmental heat exchanger 221 in the air conditioning cooling mode and the air conditioning heating mode, and make the structure of the temperature control system 100 more compact and simple.

Furthermore, the thermal conductor switching component 25 also disables the circulation of the thermal conductor within the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24 when not in the thermal management cooling mode, or forms a self-circulation of the thermal conductor within one of the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24, and circulates the thermal conductor between the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24 in the thermal management cooling mode.

As shown in FIG. 1 , FIG. 3 , FIG. 14 and FIG. 15 , FIG. 15 is a second circuit schematic diagram of the thermal management circuit in the air-conditioning cooling mode.

In this embodiment, the first heat exchange area 241 is arranged in the fourth sub-thermal management loop 24. When the temperature control system 100 is not in the thermal management cooling mode, that is, when the temperature control system 100 enables the air conditioning cooling mode or the air conditioning heating mode alone, as shown in FIG3 and FIG14, the heat transfer agent switching component 25 disables the circulation of the heat transfer agent in the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24; or as shown in FIG3 and FIG15, a self-circulation of the heat transfer agent is formed in the fourth sub-thermal management loop 24. When the first heat exchange area 241 is arranged in the third sub-thermal management loop 23, a similar arrangement may also be adopted for the fourth sub-thermal management loop 24.

Through the above method, when the temperature control system 100 is not in the thermal management cooling mode, the circulation of the heat conductor in the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24 is disabled, or the self-circulation of the heat conductor in one of the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24 having the first heat exchange area 241 is limited, that is, by reducing the circulation of the heat conductor in the sub-thermal management loop to reduce the energy consumption of the temperature control system 100, the system energy efficiency ratio can also be improved.

As shown in Figures 1, 3, 16 and 17, Figure 16 is a first circuit schematic diagram of a thermal management circuit in a thermal management refrigeration mode or in both air conditioning refrigeration mode and thermal management refrigeration mode, and Figure 17 is a second circuit schematic diagram of a thermal management circuit in a thermal management refrigeration mode or in both air conditioning refrigeration mode and thermal management refrigeration mode.

As shown in Figures 16 and 17, in this embodiment, in the thermal management refrigeration mode, the heat conductor switching component 25 circulates the heat conductor between the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24, and the first thermal management heat exchanger 16 and/or the second thermal management heat exchanger 17 cools the heat conductor, which can effectively increase the cooling effect on the heat conductor, thereby enhancing the heat dissipation effect of the first designated component 31, so that the cooling capacity generated by the system can be further utilized, reducing waste and effectively improving the system energy efficiency ratio.

In one embodiment, when not in the thermal management cooling mode, the control module 70 selectively controls the thermal conductive agent switching component 25 to disable the circulation of the thermal conductive agent within the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24 in response to the heat dissipation demand of the first designated component 31, or forms self-circulation of the thermal conductive agent within one of the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24.

As shown in FIG14, when the first designated component 31 does not generate heat or can meet the heat dissipation requirements by self-heating, the heat transfer agent switching component 25 selectively disables the circulation of the heat transfer agent in the third sub-heat management loop 23 and the fourth sub-heat management loop 24; as shown in FIG15, when the heat generation of the first designated component 31 is relatively high, but it is not necessary to perform heat management on it through the refrigerant, the heat transfer agent in the fourth sub-heat management loop 24 where the first heat exchange area 241 is located can be set to self-circulate to meet the heat dissipation requirements of the first designated component 31, thereby reducing energy consumption. Similarly, when the first heat exchange area 241 is located in the third sub-heat management loop 23, similar settings can be adopted for the third sub-heat management loop 23.

Specifically, the heat dissipation method suitable for the first designated component 31 may be selected by detecting the temperature of the first designated component 31 .

In this embodiment, based on the radiator requirement of the first designated component 31, the self-circulation of the heat conductor in the third sub-thermal management loop 23 or the fourth sub-thermal management loop 24 where the first heat exchange area 241 is located is selectively set to meet the heat dissipation requirement of the first designated component 31 in a low-energy manner.

Referring to Figures 1, 3, 20 and 24, Figure 20 is a third circuit schematic diagram of the thermal management circuit in the first air-conditioning heating mode or the second air-conditioning heating mode, and Figure 24 is a third circuit schematic diagram of the thermal management circuit in the third air-conditioning heating mode.

The fourth sub-thermal management loop 24 also includes a second heat exchange zone 242 for heat exchange with the heater 40. The heat conductor switching component 25 is also capable of circulating the heat conductor between the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24 in the air-conditioning heating mode, and guiding the heat conductor to flow through the second heat exchange zone 242 without passing through the second thermal management heat exchanger 17 connected to the fourth sub-thermal management loop 24 and the first heat exchange zone 241.

The first heat exchange area 241 and the second heat exchange area 242 are arranged in the same sub-heat management loop. In this embodiment, the fourth sub-heat management loop 24 includes the first heat exchange area 241 and the second heat exchange area 242, wherein the heater 40 is an electrical appliance that uses electrical energy to achieve a heating effect, and part of the pipeline of the fourth sub-heat management loop 24 passes through the heater 40 or is wound around the heater 40 to form the second heat exchange area 242.

In this embodiment, the heat conductor switching component 25 can also circulate the heat conductor between the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24 in the air-conditioning heating mode, and guide the heat conductor to flow through the second heat exchange area 242 without flowing through the second thermal management heat exchanger 17 connected to the fourth sub-thermal management loop 24 and the first heat exchange area 241, so that the heater 40 can be used as an auxiliary heat source to supplement the refrigerant loop 10 with heat when the external ambient temperature is low and it is difficult to use the ambient heat exchanger 221 to absorb heat from the environment, that is, to supplement the refrigerant loop 10 with heat through the first thermal management heat exchanger 16 to reliably ensure the heating effect of the temperature control system 100.

Similarly, when the first heat exchange area 241 is disposed in the third sub-heat management loop 23, the second heat exchange area 242 is disposed in the third sub-heat management loop 23. At this time, the heat transfer agent switching component 25 guides the heat transfer agent to flow through the second heat exchange area 242 without flowing through the first thermal management heat exchanger 16 connected to the third sub-heat management loop 23 and the first heat exchange area 241.

21 and 25 , FIG. 21 is a fourth circuit diagram of the thermal management circuit in the first air conditioning heating mode or the second air conditioning heating mode, and FIG. 25 is a fourth circuit diagram of the thermal management circuit in the third air conditioning heating mode.

Furthermore, the heat transfer agent switching assembly 25 can also guide the heat transfer agent to flow through the first heat exchange area 241 and the second heat exchange area 242 without flowing through the second thermal management heat exchanger 17 connected to the fourth sub-heat management loop 24 .

That is, in this embodiment, the heat conductor switching component 25 can also conduct the heat conductor to flow through the first heat exchange area 241 and the second heat exchange area 242 without flowing through the second thermal management heat exchanger 17 connected to the fourth sub-thermal management loop 24, so that the heater 40, as an auxiliary heat source, can simultaneously heat the first designated component 31 to perform temperature-raising thermal management on the first designated component 31, and supplement heat to the refrigerant loop 10, thereby ensuring the heating effect of the temperature control system 100 and avoiding the adverse effects of low temperature on the performance of the first designated component 31.

Similarly, when the first heat exchange area 241 is arranged in the third sub-heat management loop 23, the heat transfer agent switching assembly 25 can also guide the heat transfer agent to flow through the first heat exchange area 241 and the second heat exchange area 242 without flowing through the first thermal management heat exchanger 16. For example, the first designated component 31 is a battery module. In winter, due to the low outdoor temperature, the energy conversion efficiency of the battery module is reduced. By preheating the battery module, the energy conversion efficiency of the battery module in a low temperature environment can be improved.

Specifically, as shown in Figure 3, in this embodiment, the heat transfer agent switching component 25 includes a first heat transfer agent valve 251 and a second heat transfer agent valve 252. The first heat transfer agent valve 251 is used to bypass the second thermal management heat exchanger 17 connected to the fourth sub-thermal management loop 24 alone, and the second heat transfer agent valve 252 is used to bypass the first heat exchange area 241 and the second thermal management heat exchanger 17 at the same time.

In this embodiment, in combination with Figures 3 and 21, the first heat transfer agent valve 251 and the second heat transfer agent valve 252 are both arranged in the fourth sub-thermal management loop 24, and the first heat transfer agent valve 251 is used to separately bypass the second thermal management heat exchanger 17 connected to the fourth sub-thermal management loop 24, so that the heater 40 can simultaneously heat the first designated component 31 and supplement heat to the refrigerant loop 10; in combination with Figures 3 and 20, the second heat transfer agent valve 252 is used to simultaneously bypass the first heat exchange area 241 and the second thermal management heat exchanger 17, so that the heater 40 can supplement heat to the refrigerant loop 10.

The first heat transfer agent valve 251 may be a three-way valve or a combination of two two-way valves; the second heat transfer agent valve 252 may be a two-way valve or a switch valve.

By limiting the heat transfer agent switching component 25 to include the first heat transfer agent valve 251 and the second heat transfer agent valve 252, and limiting the functions of the first heat transfer agent valve 251 and the second heat transfer agent valve 252, it is possible to selectively realize that the heater 40 alone supplies heat to the refrigerant circuit 10, or the heater 40 simultaneously supplies heat to the first designated component 31 and the refrigerant circuit 10, so that the structure of the thermal management circuit 20 is simple, low-cost, and easy to implement.

Similarly, when the first heat exchange area 241 is disposed in the third heat management sub-loop 23 , the above functions can also be implemented in a similar manner.

Further, as shown in Figures 1 and 3, the designated component 30 further includes a second designated component 32, and the thermal management circuit 20 further includes a fifth sub-thermal management circuit 26, and the fifth sub-thermal management circuit 26 includes a third heat exchange area 263 for performing heat exchange with the second designated component 32. As shown in Figures 19 and 23, the thermal conductive agent switching component 25 can also circulate the thermal conductive agent between the fourth sub-thermal management circuit 24 and the fifth sub-thermal management circuit 26 in the air conditioning heating mode.

The second designated component 32 is also a heat-generating component, which may be a battery module, a motor module or other electronic components.

In this embodiment, the first designated component 31 is a battery module of the transportation equipment, and the second designated component 32 is a motor module of the transportation equipment. When the vehicle is running, the battery module and the motor module are the main heat sources, and their performance is also easily affected by the ambient temperature and the amount of heat generated by themselves. Therefore, by performing thermal management on the designated component 30, it can be ensured that the designated component 30 is in an environment suitable for its performance.

The fifth sub-thermal management loop 26 is also used for circulating the heat transfer agent and has a pipeline structure, and can form a circulation path with at least one of the first sub-thermal management loop 21 , the second sub-thermal management loop 22 , the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24 .

The portion of the fifth sub-thermal management loop 26 that contacts the second designated component 32 is the third heat exchange zone 263 , for example, part of the pipeline of the fifth sub-thermal management loop 26 is wound around the second designated component 32 , or contacts one side of the first designated component 31 , or passes through the second designated component 32 .

As shown in Figures 19 and 23, in this embodiment, the heat conductor switching component 25 is further capable of circulating the heat conductor between the fourth sub-thermal management circuit 24 and the fifth sub-thermal management circuit 26 in the air-conditioning heating mode, so as to use the second designated component 32 as an auxiliary heat source, thereby auxiliary heating the first designated component 31, or providing the air-conditioning heating, that is, adding heat to the refrigerant circuit 10, so as to recover the waste heat of the second designated component 32, save energy, and effectively improve the energy efficiency ratio of the temperature control system 100.

Similarly, when the first heat exchange area 241 is disposed in the third heat management sub-loop 23 , the third heat management sub-loop 23 and the fifth heat management sub-loop 26 may be similarly switched to be connected.

14 to 17 , the thermal conductive agent switching component 25 selectively circulates the thermal conductive agent between the first sub-thermal management loop 21 and the second sub-thermal management loop 22 in the air-conditioning cooling mode and/or the thermal management cooling mode, or circulates the thermal conductive agent between the first sub-thermal management loop 21, the second sub-thermal management loop 22 and the fifth sub-thermal management loop 26.

In the air-conditioning cooling mode and/or the thermal management cooling mode, the heat absorbed from the condensing heat exchanger 12 in the refrigerant circuit 10 can be dissipated to the outside through the ambient heat exchanger 221 by utilizing the heat conductor circulating between the first sub-thermal management circuit 21 and the second sub-thermal management circuit 22; or the heat absorbed from the condensing heat exchanger 12 and the second designated component 32 can be dissipated to the outside through the ambient heat exchanger 221 by utilizing the heat conductor circulating between the first sub-thermal management circuit 21, the second sub-thermal management circuit 22 and the fifth sub-thermal management circuit 26.

Specifically, based on the heat dissipation requirements of the second designated component 32, the fifth sub-thermal management loop 26 can be connected to the loop circulation of the first sub-thermal management loop 21 and the second sub-thermal management loop 22, so that the heat dissipation channel can be used to dissipate heat for the second designated component 32 at the same time, thereby avoiding performance limitation caused by overheating of the second designated component 32. At the same time, increasing the heat dissipation of the second designated component 32 on this basis will not increase much additional cost, but can effectively improve the heat dissipation performance of the second designated component 32.

As shown in Figures 1 to 3, the third air-conditioning heat exchanger 211 is located in the first sub-thermal management loop 21, and the temperature control system 100 also includes an airflow switching component 60. The temperature control system 100 is configured to control the airflow switching component 60 to guide the air-conditioning airflow through the third air-conditioning heat exchanger 211 in the air-conditioning heating mode, and to guide the air-conditioning airflow not through the third air-conditioning heat exchanger 211 in the air-conditioning cooling mode.

In this embodiment, by limiting the third air-conditioning heat exchanger 211 to be located in the first sub-thermal management loop 21, the complexity of the refrigerant loop 10 can be reduced. After the first sub-thermal management loop 21 exchanges heat with the condensing heat exchanger 12, the third air-conditioning heat exchanger 211 can be used to heat the air-conditioning airflow in the heating mode, or to dissipate heat to the outside through the ambient heat exchanger 221 in the non-heating mode.

In other embodiments, the third air-conditioning heat exchanger 211 and the first sub-thermal management loop 21 may also be independent of each other without a direct connection relationship; for example, the condensing heat exchanger 12 includes a first sub-condensing heat exchanger and a second sub-condensing heat exchanger, the third air-conditioning heat exchanger 211 performs heat exchange with the first sub-condensing heat exchanger, and the first sub-thermal management loop 21 performs heat exchange with the second sub-condensing heat exchanger.

The airflow switching component 60 can be used to change the flow path of the air-conditioning airflow to guide the air-conditioning airflow through the third air-conditioning heat exchanger 211 in the air-conditioning heating mode, so that the third air-conditioning heat exchanger 211 can heat the air-conditioning airflow, or guide the air-conditioning airflow not to pass through the third air-conditioning heat exchanger 211 in the air-conditioning cooling mode, so as to avoid the third air-conditioning heat exchanger 211 interfering with the cooled air-conditioning airflow.

The airflow switching component 60 can be a valve group, etc., so as to use the valve group to switch the air conditioning airflow path. By setting the airflow switching component 60, it is possible to flexibly control whether the air conditioning airflow is heat exchanged with the third air conditioning heat exchanger 211, thereby reliably distinguishing the air conditioning heating mode and the air conditioning cooling mode to avoid interference between the two modes. In addition, the airflow switching component 60 can be a baffle that can perform angle switching, which is set on the path of the air conditioning airflow and changes the direction of the air conditioning airflow by angle switching.

As shown in FIGS. 18 to 21 , the heat transfer agent switching assembly 25 forms a self-circulation of the heat transfer agent in the first heat management sub-loop 21 in the first air-conditioning heating mode and the second air-conditioning heating mode.

No matter in the first air-conditioning heating mode or the second air-conditioning heating mode, the third air-conditioning heat exchanger 211 is used to heat the air-conditioning airflow. By controlling the heat transfer agent switching component 25, a self-circulation of the heat transfer agent is formed in the first sub-thermal management loop 21, so as to make full use of the heat absorbed at the condensing heat exchanger 12 to heat the air-conditioning airflow, thereby avoiding additional heat loss caused by the heat transfer agent entering other sub-thermal management loops, thereby effectively improving the system energy efficiency ratio in the heating mode.

As shown in Figures 16 and 17, in the thermal management cooling mode, the refrigerant switching assembly 15 guides the refrigerant to pass through the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 in sequence, that is, the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 are limited to be connected in series to reduce the complexity of the refrigerant circuit 10, making the refrigerant circuit 10 more concise. As shown in Figure 12, in the second air conditioning heating mode, the refrigerant switching assembly 15 guides the refrigerant to pass through only one of the first air conditioning heat exchanger 13 and the second air conditioning heat exchanger 14.

In this embodiment, in the second air-conditioning heating mode, the refrigerant switching component 15 guides the refrigerant to pass through only one of the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14, so that the number of components through which the refrigerant flows in sequence is small, which can avoid the poor effect of heating the air-conditioning airflow using one of the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14 due to the refrigerant flow path being too long, the refrigerant temperature dropping too low or the pressure dropping too low.

As shown in Figures 1 to 3, in this embodiment, the outlet of the compressor 11 is connected to the inlet of the condensing heat exchanger 12, and the refrigerant switching assembly 15 includes a first refrigerant valve 151, a second refrigerant valve 152, a third refrigerant valve 153, a fourth refrigerant valve 154, a fifth refrigerant valve 155 and a sixth refrigerant valve 156. The first refrigerant valve 151 is connected between the outlet of the condensing heat exchanger 12 and the inlet of the first air-conditioning heat exchanger 13, one end of the second refrigerant valve 152 is connected between the outlet of the compressor 11 and the inlet of the condensing heat exchanger 12, and the other end of the second refrigerant valve 152 is connected to the inlet of the first air-conditioning heat exchanger 13. One end of the refrigerant valve 153 is connected between the first refrigerant valve 151 and the outlet of the condensing heat exchanger 12, the other end of the third refrigerant valve 153 is connected to the inlet of the second air-conditioning heat exchanger 14 and the inlet of the first thermal management heat exchanger 16 via the fourth refrigerant valve 154 and the fifth refrigerant valve 155 respectively, the sixth refrigerant valve 156 is connected between the outlet of the first thermal management heat exchanger 16 and the inlet of the second thermal management heat exchanger 17, the outlet of the first thermal management heat exchanger 16 and the outlet of the second thermal management heat exchanger 17 are connected to the inlet of the compressor 11, and the sixth refrigerant valve 156 is configured to selectively form or not form a pressure reduction on the refrigerant.

Among them, the first refrigerant valve 151, the fourth refrigerant valve 154, the fifth refrigerant valve 155 and the sixth refrigerant valve 156 are all expansion valves, wherein the expansion valve usually has a pressure-reducing effect on the refrigerant, but when the expansion valve is at the maximum opening degree, it has no pressure-reducing effect on the refrigerant flowing through.

The second refrigerant valve 152 and the third refrigerant valve 153 are both stop valves. The second refrigerant valve 152 is used to bypass the condensing heat exchanger 12, and the third refrigerant valve 153 is used to bypass the first air conditioning heat exchanger.

By limiting the valve group and its position included in the refrigerant switching assembly 15 to simplify the structure of the refrigerant circuit 10, the refrigerant circuit 10 can circulate the refrigerant more efficiently and controllably, thereby reducing energy dissipation during its circulation process and improving energy efficiency.

Specifically, in this embodiment, the thermal conductive agent switching component 25 includes a first thermal conductive agent valve 251, a second thermal conductive agent valve 252, a multi-way valve 253, a first pump 254, a second pump 255 and a third pump 256. The multi-way valve 253 includes a, b, c, d, e, f, g, h, i and j interfaces, wherein the two ends of the first sub-thermal management loop 21 are respectively connected to the a and b interfaces, the two ends of the second sub-thermal management loop 22 are respectively connected to the e and f interfaces, the two ends of the third sub-thermal management loop 23 are respectively connected to the g and h interfaces, the two ends of the fourth sub-thermal management loop 24 are respectively connected to the i and j interfaces, the two ends of the fifth sub-thermal management loop 26 are respectively connected to the c and d interfaces, any two interfaces in the multi-way valve 253 can be interconnected, the first pump 254 is arranged in the first sub-thermal management loop 21, the second pump 255 is arranged in the third sub-thermal management loop 23, and the third pump 256 is arranged in the fourth sub-thermal management loop 24.

The third pump 256 is arranged between the j interface and the heat conductor inlet of the second thermal management heat exchanger 17, and the first heat conductor valve 251 is a three-way valve, whose first port is connected to the pump outlet of the third pump 256, whose second port is connected to the heat conductor inlet of the second thermal management heat exchanger 17, and whose third port is connected between the heat conductor outlet of the second thermal management heat exchanger 17 and the first heat exchange zone 241; the second heat conductor valve 252 is a two-way valve, whose first port is connected between the pump outlet of the third pump 256 and the first port of the first heat conductor valve 251, whose first port is connected between the first heat exchange zone 241 and the second heat exchange zone 242, and the outlet of the second heat exchange zone 242 is connected to the i interface.

Among them, the compressor 11, the refrigerant switching component 15, the thermal conductive agent switching component 25, the heater 40 and the blower 50 are all communicatively connected with the control module 70 of the temperature control system 100. The control module 70 controls the operation of the compressor 11, the refrigerant switching component 15, the thermal conductive agent switching component 25, the heater 40 and the blower 50 to realize the heating and cooling functions as mentioned above.

In practical applications, the above-mentioned various modes can be combined. Specifically, the air-conditioning refrigeration mode of the temperature control system 100 can be combined with the thermal management refrigeration mode, and can be divided into at least six types based on the demand for refrigeration load, including: a first air-conditioning refrigeration mode, a second air-conditioning refrigeration mode, a first air-conditioning refrigeration mode and a first thermal management refrigeration mode, a second air-conditioning refrigeration mode and a first thermal management refrigeration mode, a first air-conditioning refrigeration mode and a second thermal management refrigeration mode, and a second air-conditioning refrigeration mode and a second thermal management refrigeration mode.

1 , 4 and 14 , the temperature control system 100 adopts the first air conditioning cooling mode, and the heat transfer agent circulates between the first sub-thermal management circuit 21 and the second sub-thermal management circuit 22 in the thermal management circuit 20, wherein the connection mode of each port of the multi-way valve 253 is a connecting to f, and b connecting to e.

In the refrigerant circuit 10, the gaseous refrigerant is compressed by the compressor 11 and then enters the condensing heat exchanger 12 along the circulation pipeline. The refrigerant condenses and releases heat in the condensing heat exchanger 12 to heat the heat transfer agent. Then, it passes through the gas-liquid separation device 18 and passes through the third refrigerant valve 153 along the circulation pipeline. Then, it is reduced in pressure by the fourth refrigerant valve 154 and introduced into the second air-conditioning heat exchanger 14. The second air-conditioning heat exchanger 14 evaporates and absorbs heat from the air-conditioning airflow guided by the blowing device 50, and the temperature of the air-conditioning airflow is reduced. Finally, the refrigerant returns to the compressor 11 along the circulation pipeline; wherein the first refrigerant valve 151, the second refrigerant valve 152, the fifth refrigerant valve 155 and the sixth refrigerant valve 156 are all in a closed state.

In the thermal management loop 20, the heat conductor enters the condensing heat exchanger 12 through the first pump 254 and absorbs heat from the refrigerant flowing through the condensing heat exchanger 12, then enters the third air-conditioning heat exchanger 211 through the circulation pipeline, then enters from the a port of the multi-way valve 253 and flows out from the f port, then enters the ambient heat exchanger 221 along the circulation pipeline and releases heat to the air flowing through the ambient heat exchanger 221, then enters from the e port of the multi-way valve along the circulation pipeline, flows out from the b port and returns to the first pump 254, wherein the first pump 254 provides power to transport the heat conductor.

Referring to FIG. 1 , FIG. 4 and FIG. 15 , the thermal management circuit 20 can also be coupled with the thermal management requirements of the first designated component 31 and the second designated component 32 to meet the requirements of thermal management of traffic equipment. The thermal conductive agent switching component 25 forms a self-circulation of the thermal conductive agent in the fourth sub-thermal management circuit 24, and circulates the thermal conductive agent between the first sub-thermal management circuit 21, the second sub-thermal management circuit 22 and the fifth sub-thermal management circuit 26, wherein the connection mode of each port of the multi-way valve 253 is a connected to f, e connected to d, c connected to b, and j connected to i.

Among them, a self-circulation of the heat conductor is formed in the fourth sub-thermal management loop 24, the heater 40 is not working, and the heat conductor flows through the first heat exchange zone 241 to absorb heat from the first designated component 31; when the heat conductor circulates between the first sub-thermal management loop 21, the second sub-thermal management loop 22 and the fifth sub-thermal management loop 26, the heat conductor flows through the third heat exchange zone 263 to absorb heat from the second designated component 32, and releases heat to the air through the ambient heat exchanger 221.

Referring to Figures 1, 5 and 14, the temperature control system 100 adopts the second air-conditioning refrigeration mode, and the refrigerant compressed by the compressor 11 condenses and releases heat in the condensing heat exchanger 12 to heat the heat transfer agent, and then is introduced into the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14 in a pressure-reducing manner to evaporate and absorb heat from the air-conditioning airflow in turn; the heat transfer agent circulates between the first sub-thermal management circuit 21 and the second sub-thermal management circuit 22 in the thermal management circuit 20, and the connection mode of the ports of the multi-way valve 253 is a connecting f, and b connecting e.

Referring to Figures 1, 5 and 15, when the temperature control system 100 adopts the second air-conditioning cooling mode, the thermal management circuit 20 can also be coupled with the thermal management requirements of the first designated component 31 and the second designated component 32 to meet the thermal management requirements of the transportation equipment. The circulation process of the heat conductor in the thermal management circuit 20 is the same as above and will not be repeated.

Referring to Figures 1, 6 and 16, the temperature control system 100 adopts the first air-conditioning cooling mode and the first thermal management cooling mode. In the thermal management circuit 20, the heat conductor circulates between the third sub-thermal management circuit 23 and the fourth sub-thermal management circuit 24, and circulates between the first sub-thermal management circuit 21 and the second sub-thermal management circuit 22. The connection mode of each port of the multi-way valve 253 is a connected to f, b connected to e, i connected to h, and j connected to g.

As shown in Figure 6, the refrigerant compressed by the compressor 11 condenses and releases heat in the condensing heat exchanger 12 to heat the heat conductor, and then the refrigerant is divided into two paths. One path of refrigerant is introduced into the second air-conditioning heat exchanger 14 in a pressure-reducing manner, and the second air-conditioning heat exchanger 14 evaporates and absorbs heat from the air-conditioning airflow, and then the refrigerant returns to the compressor 11 along the circulation pipeline; the other path of refrigerant is introduced into the first thermal management heat exchanger 16 in a pressure-reducing manner and evaporates and absorbs heat from the heat conductor flowing through the first thermal management heat exchanger 16. The heat conductor is cooled, and then enters the second thermal management heat exchanger 17 along the circulation pipeline through the sixth refrigerant valve 156, and finally returns to the compressor 11, wherein the sixth refrigerant valve 156 is in the maximum open state and has no pressure-reducing effect on the heat conductor.

As shown in Figure 16, the heat conductor circulates between the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24, and the heater 40 does not work, so as to utilize the heat exchange between the heat conductor and the refrigerant in the first thermal management heat exchanger 16 to meet the heat dissipation demand of the first designated component 31; when the heat conductor circulates between the first sub-thermal management loop 21 and the second sub-thermal management loop 22, the heat conductor absorbs heat from the condensing heat exchanger 12 and dissipates heat to the air using the ambient heat exchanger 221.

Referring to Figures 1, 6 and 17, when the temperature control system 100 adopts the first air-conditioning cooling mode and the first thermal management cooling mode, the thermal management circuit 20 can also be coupled with the thermal management requirements of the second designated component 32 to meet the thermal management requirements of the transportation equipment, and the thermal conductive agent switching component 25 further circulates the thermal conductive agent between the first sub-thermal management circuit 21, the second sub-thermal management circuit 22 and the fifth sub-thermal management circuit 26, wherein the connection mode of each port of the multi-way valve 253 is a connected to f, e connected to d, c connected to b, i connected to h, and j connected to g.

With reference to Figures 1, 7 and 16, the temperature control system 100 adopts the second air-conditioning refrigeration mode and the first thermal management refrigeration mode. The refrigerant compressed by the compressor 11 condenses and releases heat in the condensing heat exchanger 12 to heat the heat conductor, and then is introduced into the first air-conditioning heat exchanger 13 in a pressure-reducing manner. After that, the refrigerant is divided into two paths. One path of refrigerant is introduced into the second air-conditioning heat exchanger 14 in a pressure-reducing manner, so that the first air-conditioning heat exchanger 13 and the second air-conditioning heat exchanger 14 evaporate and absorb heat from the air-conditioning airflow in turn, and then returns to the compressor 11; the other path of refrigerant is introduced into the first thermal management heat exchanger 16 in a pressure-reducing manner and evaporates and absorbs heat from the heat conductor flowing through the first thermal management heat exchanger 16, and then returns to the compressor 11 along the circulation pipeline through the second thermal management heat exchanger 17, wherein the sixth refrigerant valve 156 is in the maximum open state, and has no pressure-reducing effect on the refrigerant; the circulation process of the heat conductor in the thermal management loop 20 is the same as above and will not be repeated.

1 , 7 and 17 , the thermal management circuit 20 can also be coupled with the thermal management requirements of the second designated component 32 to meet the thermal management requirements of the transportation equipment, which will not be described in detail.

Referring to FIG. 1 , FIG. 8 and FIG. 16 , the temperature control system 100 adopts the first air conditioning refrigeration mode and the second thermal management refrigeration mode. The refrigerant compressed by the compressor 11 condenses and releases heat in the condensing heat exchanger 12 to heat the heat transfer agent. Then, the refrigerant is divided into two paths. One path of refrigerant is introduced into the second air conditioning heat exchanger 14 in a depressurized manner. The second air conditioning heat exchanger 14 evaporates and absorbs heat from the air conditioning airflow, and then returns to the compressor 11. The other path of refrigerant is introduced into the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 in a depressurized manner. The first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 evaporate and absorb heat from the heat transfer agent flowing through, and then return to the compressor 11. The sixth refrigerant valve 156 has a depressurizing effect on the refrigerant. In the thermal management circuit 20, the heat transfer agent is cooled at both the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17. The cycle process is the same as above and will not be repeated.

1 , 8 and 17 , the thermal management loop 20 can also be coupled with the thermal management requirements of the second designated component 32 to meet the thermal management requirements of the transportation equipment, which will not be described in detail.

Referring to FIG. 1 , FIG. 9 and FIG. 16 , the temperature control system 100 adopts the second air conditioning refrigeration mode and the second thermal management refrigeration mode. The refrigerant compressed by the compressor 11 condenses and releases heat in the condensing heat exchanger 12 to heat the heat transfer agent, and then is introduced into the first air conditioning heat exchanger 13 in a reduced pressure manner. After that, the refrigerant is divided into two paths. One path of refrigerant is introduced into the second air conditioning heat exchanger 14 in a reduced pressure manner, so that the first air conditioning heat exchanger 13 and the second air conditioning heat exchanger 14 evaporate and absorb heat from the air conditioning airflow in turn, and then return to the compressor 11; the other path of refrigerant is introduced into the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 in a reduced pressure manner, respectively, and the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 evaporate and absorb heat from the heat transfer agent flowing through in turn, and then return to the compressor 11. In the thermal management loop 20, the heat transfer agent is cooled at both the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17, and its cycle process is the same as above and will not be repeated.

1 , 9 and 17 , the thermal management loop 20 can also be coupled with the thermal management requirements of the second designated component 32 to meet the thermal management requirements of the transportation equipment, which will not be described in detail.

In addition, the temperature control system 100 may also include a separate first thermal management cooling mode and a second thermal management cooling mode. These two cooling modes are suitable for battery charging scenarios to avoid low energy conversion efficiency caused by overheating of the battery during fast charging.

Referring to Figures 1, 10 and 16, the temperature control system 100 adopts the first thermal management refrigeration mode alone, and the refrigerant compressed by the compressor 11 condenses and releases heat in the condensing heat exchanger 12 to heat the heat conductor, and then is introduced into the first thermal management heat exchanger 16 in a pressure-reducing manner and evaporates and absorbs heat from the heat conductor flowing through the first thermal management heat exchanger 16, and then returns to the compressor 11 along the circulation pipeline through the second thermal management heat exchanger 17, wherein the sixth refrigerant valve 156 is in the maximum open state and has no pressure-reducing effect on the refrigerant; in the thermal management loop 20, the circulation process of the heat conductor is the same as above, the heat conductor is cooled in the first thermal management heat exchanger 16, and heat is exchanged with the first designated component 31 in the first heat exchange area 241, wherein the first designated component 31 is a battery module, and the heater 40 does not work.

1 , 10 and 17 , the thermal management circuit 20 can also be coupled with the thermal management requirements of the second designated component 32 to meet the thermal management requirements of the transportation equipment, which will not be described in detail.

Referring to FIG. 1 , FIG. 11 and FIG. 16 , the temperature control system 100 adopts the second thermal management refrigeration mode alone. The refrigerant compressed by the compressor 11 condenses and releases heat in the condensing heat exchanger 12 to heat the heat transfer agent, and then is introduced into the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 in a reduced pressure manner. The first thermal management heat exchanger 16 and the second thermal management heat exchanger 17 evaporate and absorb heat from the heat transfer agent flowing through in turn, and then return to the compressor 11. In the thermal management loop 20, the circulation process of the heat transfer agent is the same as above. The heat transfer agent is cooled in both the first thermal management heat exchanger 16 and the second thermal management heat exchanger 17, and heat is exchanged with the first designated component 31 in the first heat exchange area 241, wherein the first designated component 31 is a battery module, and the heater 40 does not work.

1 , 11 and 17 , the thermal management loop 20 can also be coupled with the thermal management requirements of the second designated component 32 to meet the thermal management requirements of the transportation equipment, which will not be described in detail.

In addition, in addition to the first air conditioning heating mode, the second air conditioning heating mode and the third air conditioning heating mode, the air conditioning heating mode of the temperature control system 100 can also be combined with the thermal management cooling mode, and can be divided into at least four types based on the demand for heating load, including: the first air conditioning heating mode and the first thermal management cooling mode, the first air conditioning heating mode and the second thermal management cooling mode, the second air conditioning heating mode and the second thermal management cooling mode, and the third air conditioning heating mode and the second thermal management cooling mode. The heating mode is used in the case of low ambient temperature to meet the heating demand for transportation equipment.

1 , 10 and 18 , the temperature control system 100 adopts a first air conditioning heating mode and a first thermal management cooling mode, the heat conductor of the first sub-thermal management loop 21 in the thermal management loop 20 is self-circulating, and the heat conductor is circulated between the second sub-thermal management loop 22 and the third sub-thermal management loop 23, wherein the connection mode of each port of the multi-way valve 253 is that a connects to b, e connects to h, and g connects to f.

The refrigerant circulation loop in the refrigerant circuit 10 is the same as the refrigerant circulation loop in the first thermal management refrigeration mode used by the temperature control system 100, and will not be described in detail. In the thermal management circuit 20, the heat transfer agent circulating in the first sub-thermal management circuit 21 is heated by heat exchange with the refrigerant in the condensing heat exchanger 12, and the air conditioning airflow is heated by the third air conditioning heat exchanger 211. The heat transfer agent in the first sub-thermal management circuit 21 is self-circulating, which can make full use of the heat obtained from the condensing heat exchanger 12 and reduce heat dissipation; the heat transfer agent is circulated between the second sub-thermal management circuit 22 and the third sub-thermal management circuit 23 to absorb heat from the environment by using the environmental heat exchanger 221, and the heat is supplemented to the refrigerant circuit 10 through the first thermal management heat exchanger 16.

Referring to FIG. 1 , FIG. 10 and FIG. 19 , the thermal management circuit 20 can also be coupled with the thermal management requirements of the first designated component 31 and the second designated component 32 to meet the requirements of thermal management of the traffic equipment. The thermal management circuit 20 further circulates the heat transfer agent between the fourth sub-thermal management circuit 24 and the fifth sub-thermal management circuit 26 , wherein the connection mode of each port of the multi-way valve 253 is that a connects to b, e connects to h, g connects to f, c connects to j, and i connects to d.

The heat conductor circulates between the fourth sub-thermal management loop 24 and the fifth sub-thermal management loop 26, wherein the heater 40 is not working, and the heat of the second designated component 32 itself is used as an auxiliary heat source to heat the first designated component 31 to improve the working performance of the first designated component 31 in a low temperature environment.

1, 10 and 20, the heat conductor of the first sub-thermal management loop 21 in the thermal management loop 20 is self-circulating, and the heat conductor circulates between the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24, wherein the connection mode of each port of the multi-way valve 253 is a connected to b, g connected to j, and i connected to h.

The heat transfer agent is circulated between the third sub-thermal management loop 23 and the fourth sub-thermal management loop 24 to supplement heat to the refrigerant loop 10 using the heater 40 when the ambient temperature is too low to absorb heat from the external environment. The heater 40 heats the heat transfer agent through the second heat exchange area 242 and uses the first thermal management heat exchanger 16 to supplement heat to the refrigerant loop 10, wherein the first heat transfer agent valve 251 is closed and the second heat transfer agent valve 252 is opened to bypass the second thermal management heat exchanger 17 and the first designated component 31.

Referring to Figures 1, 10 and 21, the thermal management circuit 20 can also be coupled with the thermal management requirements of the first designated component 31, wherein the second thermal transfer agent valve 252 is closed, and the first thermal transfer agent valve 251 bypasses the second thermal management heat exchanger 17 to utilize the heater 40 to heat the first designated component 31, wherein the first designated component 31 is a battery module, which can avoid limiting the energy conversion efficiency of the battery module in a low temperature environment, and at the same time can also supplement heat to the refrigerant circuit 10.

Referring to FIG. 1 , FIG. 12 and FIG. 18 , the temperature control system 100 adopts the second air conditioning heating mode and the first thermal management cooling mode. The refrigerant compressed by the compressor 11 condenses and releases heat in the condensing heat exchanger 12 to heat the heat transfer agent, and then is introduced into the first air conditioning heat exchanger 13 and the first thermal management heat exchanger 16 in a depressurized manner, and then returns to the compressor 11 through the second thermal management heat exchanger 17. Among them, the first refrigerant valve 151 is in a relatively large open state, so that the temperature of the refrigerant is still higher than the air temperature after the pressure is reduced, so that the first air conditioning heat exchanger 13 can preheat the air conditioning airflow, that is, the first air conditioning heat exchanger 13 and the third air conditioning heat exchanger 211 heat the air conditioning airflow in sequence.

Referring to Figures 1, 12 and 19, the thermal management circuit 20 can also be coupled with the thermal management requirements of the first designated component 31 and the second designated component 32 to meet the thermal management requirements of transportation equipment, and further increase the circulation of heat conductor between the fourth sub-thermal management circuit 24 and the fifth sub-thermal management circuit 26, wherein the heater 40 is not working, and the heat of the second designated component 32 itself is used as an auxiliary heat source to heat the first designated component 31 to improve the working performance of the first designated component 31 in a low temperature environment, and to reduce the temperature of the second designated component 32 to avoid performance degradation of the second designated component 32 due to overheating.

1 , 12 and 20 , when the external environment temperature is low and heat cannot be obtained from the environment, the thermal management circuit 20 obtains heat from the heater 40 to supplement the refrigerant circuit 10 , which will not be described in detail.

Referring to Figures 1, 12 and 21, when the low temperature environment affects the performance of the first designated component 31 (such as a battery module) and the heat provided by the second designated component 32 cannot meet the heat required by the first designated component 31, the thermal management circuit 20 obtains the heat of the heater 40 to heat the first designated component 31 and supplements it into the refrigerant circuit 10, which will not be repeated.

Referring to FIG. 1 , FIG. 6 and FIG. 18 , the temperature control system 100 adopts the second air conditioning heating mode and the first thermal management cooling mode. The refrigerant compressed by the compressor 11 condenses and releases heat in the condensing heat exchanger 12 to heat the heat transfer agent. Then, the refrigerant is divided into two paths. One path of the refrigerant is introduced into the second air conditioning heat exchanger 14 in a depressurized manner and then returns to the compressor 11; the other path of the refrigerant is introduced into the first thermal management heat exchanger 16 in a depressurized manner and then returns to the compressor 11 through the second thermal management heat exchanger 17. Among them, the fourth refrigerant valve 154 is in a relatively large open state, so that the temperature of the refrigerant is still higher than the air temperature after the pressure is reduced, so that the second air conditioning heat exchanger 14 can be used to heat the air conditioning airflow, that is, the second air conditioning heat exchanger 14 and the third air conditioning heat exchanger 211 heat the air conditioning airflow in sequence. In other words, damage to any one of the first air conditioning heat exchanger 13 and the second air conditioning heat exchanger 14 or the branch where they are located does not affect the heating effect in this state.

1 , 6 and 19 , in this heating mode, the heat of the second designated component 32 itself can also be used as an auxiliary heat source to heat the first designated component 31 , which will not be described in detail.

1 , 6 and 20 , when the external environment temperature is low and heat cannot be obtained from the environment, the thermal management circuit 20 obtains heat from the heater 40 to supplement the heat into the refrigerant circuit 10 , which will not be described in detail.

Referring to Figures 1, 6 and 21, when the low temperature environment affects the performance of the first designated component 31 (such as a battery module) and the heat provided by the second designated component 32 cannot meet the heat required by the first designated component 31, the thermal management circuit 20 obtains the heat of the heater 40 to heat the first designated component 31 and supplements it into the refrigerant circuit 10, which will not be repeated.

Referring to FIG. 1 , FIG. 13 and FIG. 22 , the temperature control system 100 adopts the third air conditioning heating mode and the first thermal management cooling mode. The refrigerant compressed by the compressor 11 is directly introduced into the first air conditioning heat exchanger 13 without passing through the condensing heat exchanger 12. It condenses and releases heat in the first air conditioning heat exchanger 13 and heats the air conditioning airflow, which can avoid the unfavorable condition that the high pressure of the temperature control system 100 is limited and the speed of the compressor 11 is low due to the excessive return water temperature of the condensing heat exchanger 12. Among them, the heat transfer agent circulates only between the second sub-thermal management loop 20 and the third sub-thermal management loop 23 in the thermal management loop 20, so that the environmental heat exchanger 221 can be used to absorb heat from the environment and replenish it to the refrigerant loop 10 through the first thermal management heat exchanger 16.

Referring to FIG. 1 , FIG. 13 and FIG. 23 , in this heating mode, the heat of the second designated component 32 itself can also be used as an auxiliary heat source to heat the first designated component 31 , which will not be described in detail.

1 , 13 and 24 , when the external environment temperature is low and heat cannot be obtained from the environment, the thermal management circuit 20 obtains heat from the heater 40 to supplement the heat into the refrigerant circuit 10 , which will not be described in detail.

Referring to Figures 1, 13 and 25, when the low temperature environment affects the performance of the first designated component 31 (such as a battery module) and the heat provided by the second designated component 32 cannot meet the heat required by the first designated component 31, the thermal management circuit 20 obtains the heat of the heater 40 to heat the first designated component 31 and supplements it into the refrigerant circuit 10, which will not be repeated.

Based on this, the present application also provides a transportation equipment, which includes a temperature control system 100 as described above. The transportation equipment can be a gasoline vehicle or a new energy vehicle. The temperature control system 100 is arranged in the transportation equipment, which can provide cooling or heating for the cockpit, and perform thermal management of the battery module and/or motor module in the vehicle.

By applying the temperature control system to transportation equipment and utilizing the various air-conditioning cooling modes, thermal management cooling modes, air-conditioning heating modes and their combinations provided by the temperature control system, heating and cooling solutions are provided to transportation equipment in various application scenarios, so as to fully and energy-efficiently meet the cooling needs of transportation equipment.

The above description is only an embodiment of the present application and does not limit the patent scope of the present application. Any equivalent structure or equivalent process transformation made using the contents of the present application specification and drawings, or directly or indirectly applied in other related technical fields, are also included in the patent protection scope of the present application.

Claims

A temperature control system for transportation equipment, characterized in that the temperature control system includes a refrigerant circuit for circulating refrigerant, the refrigerant circuit includes a compressor, a condensing heat exchanger, a first air-conditioning heat exchanger, a second air-conditioning heat exchanger and a refrigerant switching component, the temperature control system has an air-conditioning refrigeration mode for refrigerating an air-conditioning airflow, the air-conditioning refrigeration mode includes a first air-conditioning refrigeration mode and a second air-conditioning refrigeration mode, the refrigerant switching component introduces the refrigerant compressed by the compressor into the condensing heat exchanger for condensation and heat release in the first air-conditioning refrigeration mode and the second air-conditioning refrigeration mode, in the first air-conditioning refrigeration mode, the refrigerant switching component introduces the refrigerant output by the condensing heat exchanger into one of the first air-conditioning heat exchanger and the second air-conditioning heat exchanger in a depressurized manner in the first air-conditioning refrigeration mode, thereby causing the one of the first air-conditioning heat exchanger and the second air-conditioning heat exchanger to evaporate and absorb heat from the air-conditioning airflow, or in the second air-conditioning refrigeration mode, the refrigerant switching component introduces the refrigerant output by the condensing heat exchanger into the first air-conditioning heat exchanger and the second air-conditioning heat exchanger in sequence in a depressurized manner, thereby causing the first air-conditioning heat exchanger and the second air-conditioning heat exchanger to evaporate and absorb heat from the air-conditioning airflow in sequence.
The temperature control system as described in claim 1 is characterized in that the temperature control system also includes a control module, which controls the refrigerant switching component to switch to the first air-conditioning refrigeration mode in response to the air-conditioning refrigeration load in the air-conditioning refrigeration mode being less than or equal to a preset air-conditioning refrigeration load threshold, or controls the refrigerant switching component to switch to the second air-conditioning refrigeration mode in response to the air-conditioning refrigeration load being greater than the air-conditioning refrigeration load threshold.
The temperature control system as described in claim 1 or 2 is characterized in that the refrigerant circuit also includes a first thermal management heat exchanger and a second thermal management heat exchanger, the temperature control system also includes a thermal management circuit for circulating a heat conductor, the thermal management circuit is used to perform thermal management on designated components of the transportation equipment, the temperature control system has a thermal management refrigeration mode for refrigerating the designated components, the thermal management refrigeration mode includes a first thermal management refrigeration mode and a second thermal management refrigeration mode, the refrigerant switching component introduces the refrigerant compressed by the compressor into the condensing heat exchanger for condensation and heat release in the first thermal management refrigeration mode and the second thermal management refrigeration mode. In the first thermal management refrigeration mode, the refrigerant switching component introduces the refrigerant output by the condensing heat exchanger into one of the first thermal management heat exchanger and the second thermal management heat exchanger in a pressure-reducing manner, so that the first thermal management heat exchanger and the second thermal management heat exchanger evaporate and absorb heat from the heat conductor, or in the second thermal management refrigeration mode, the refrigerant switching component introduces the refrigerant output by the condensing heat exchanger into the first thermal management heat exchanger and the second thermal management heat exchanger in a pressure-reducing manner in sequence, so that the first thermal management heat exchanger and the second thermal management heat exchanger evaporate and absorb heat from the heat conductor in sequence.
The temperature control system as described in claim 3 is characterized in that the temperature control system includes a control module, which controls the refrigerant switching component to switch to the first thermal management refrigeration mode in response to the thermal management refrigeration load in the thermal management refrigeration mode being less than or equal to a preset thermal management refrigeration load threshold, or controls the refrigerant switching component to switch to the second thermal management refrigeration mode in response to the thermal management refrigeration load being greater than the thermal management refrigeration load threshold.
The temperature control system as described in claim 3 or 4 is characterized in that the temperature control system includes a control module, and the control module is configured to selectively enable the air-conditioning refrigeration mode and the thermal management refrigeration mode at the same time or enable one of the air-conditioning refrigeration mode and the thermal management refrigeration mode alone, and can switch between the first air-conditioning refrigeration mode and the second air-conditioning refrigeration mode independently of the thermal management refrigeration mode, and/or switch between the first thermal management refrigeration mode and the second thermal management refrigeration mode independently of the air-conditioning refrigeration mode.
The temperature control system according to any one of claims 3 to 5 is characterized in that the thermal management circuit includes a third air-conditioning heat exchanger for performing heat exchange with the condensing heat exchanger through the heat conductor, the temperature control system has an air-conditioning heating mode for heating the air-conditioning airflow, the air-conditioning heating mode includes a first air-conditioning heating mode and a second air-conditioning heating mode, the refrigerant switching component introduces the refrigerant compressed by the compressor into the condensing heat exchanger for condensation and heat release in the first air-conditioning heating mode and the second air-conditioning heating mode, the refrigerant switching component disconnects the flow path from the condensing heat exchanger to the first air-conditioning heat exchanger and the second air-conditioning heat exchanger in the first air-conditioning heating mode, so as to use the third air-conditioning heat exchanger to heat the air-conditioning airflow, or in the second air-conditioning heating mode, the refrigerant switching component introduces the refrigerant output by the condensing heat exchanger into at least one of the first air-conditioning heat exchanger and the second air-conditioning heat exchanger, so that the at least one of the first air-conditioning heat exchanger and the second air-conditioning heat exchanger and the third air-conditioning heat exchanger can heat the air-conditioning airflow in turn.
The temperature control system as described in claim 6 is characterized in that the temperature control system also includes a control module, which controls the refrigerant switching component to switch to the first air-conditioning heating mode in response to the air-conditioning heating load in the air-conditioning heating mode being less than or equal to a preset air-conditioning heating load threshold, or controls the refrigerant switching component to switch to the second air-conditioning heating mode in response to the air-conditioning heating load being greater than the air-conditioning heating load threshold.
The temperature control system as described in claim 6 or 7 is characterized in that the air-conditioning heating mode includes a third air-conditioning heating mode, and the refrigerant switching component introduces the refrigerant compressed by the compressor into at least one of the first air-conditioning heat exchanger and the second air-conditioning heat exchanger without passing through the condensing heat exchanger in the third air-conditioning heating mode, thereby condensing and releasing heat from the air-conditioning airflow.
The temperature control system as described in claim 8 is characterized in that the thermal management circuit is also configured to cool the condensing heat exchanger through the heat conductor, and the temperature control system also includes a control module, which controls the refrigerant switching component to switch to the third air conditioning heating mode in response to the temperature of the heat conductor supplied to the condensing heat exchanger in the first air conditioning heating mode or the second air conditioning heating mode being greater than or equal to a preset temperature threshold.
The temperature control system according to any one of claims 6 to 8, characterized in that the designated component includes a first designated component, the thermal management circuit includes a first sub-thermal management circuit, a second sub-thermal management circuit, a third sub-thermal management circuit, a fourth sub-thermal management circuit and a thermal conductive agent switching component, the first sub-thermal management circuit is used to connect the condensing heat exchanger, the second sub-thermal management circuit includes an ambient heat exchanger, the third sub-thermal management circuit is connected to the first thermal management heat exchanger, the fourth sub-thermal management circuit is connected to the second thermal management heat exchanger, and one of the third sub-thermal management circuit and the fourth sub-thermal management circuit includes a first heat exchange area for performing heat exchange with the first designated component;

In the air-conditioning heating mode, the refrigerant switching component introduces the refrigerant into the first thermal management heat exchanger or the second thermal management heat exchanger connected to the third sub-thermal management circuit and the other one of the four sub-thermal management circuits, and performs evaporation and heat absorption; the thermal conductor switching component circulates the thermal conductor between the first sub-thermal management circuit and the second sub-thermal management circuit in the air-conditioning cooling mode, and the thermal conductor switching component circulates the thermal conductor between the third sub-thermal management circuit, the other one of the fourth sub-thermal management circuit and the second sub-thermal management circuit in the air-conditioning heating mode.
The temperature control system as described in claim 10 is characterized in that the thermal conductor switching component disables the circulation of the thermal conductor in the third sub-thermal management loop and the fourth sub-thermal management loop when not in the thermal management refrigeration mode, or forms a self-circulation of the thermal conductor in one of the third sub-thermal management loop and the fourth sub-thermal management loop, and circulates the thermal conductor between the third sub-thermal management loop and the fourth sub-thermal management loop in the thermal management refrigeration mode.
The temperature control system as described in claim 11 is characterized in that, when not in the thermal management refrigeration mode, the temperature control system also includes a control module, which selectively controls the thermal conductor switching component to disable the circulation of the thermal conductor in the third sub-thermal management loop and the fourth sub-thermal management loop in response to the heat dissipation demand of the first designated component, or to form a self-circulation of the thermal conductor in one of the third sub-thermal management loop and the fourth sub-thermal management loop.
The temperature control system as described in claim 11 or 12 is characterized in that the third sub-thermal management loop and the fourth sub-thermal management loop also include a second heat exchange zone for heat exchange with the heater, and the heat conductor switching component is also capable of circulating the heat conductor between the third sub-thermal management loop and the fourth sub-thermal management loop in the air-conditioning heating mode, and guiding the heat conductor to flow through the second heat exchange zone without flowing through the first thermal management heat exchanger or the second thermal management heat exchanger and the first heat exchange zone to which the third sub-thermal management loop and the fourth sub-thermal management loop are connected.
The temperature control system as described in claim 13 is characterized in that the heat conductor switching component can also guide the heat conductor to flow through the first heat exchange zone and the second heat exchange zone without flowing through the first thermal management heat exchanger or the second thermal management heat exchanger connected to one of the third sub-thermal management loop and the fourth sub-thermal management loop.
The temperature control system as described in claim 14 is characterized in that the heat transfer agent switching component includes a first heat transfer agent valve and a second heat transfer agent valve, the first heat transfer agent valve is used to separately bypass the first thermal management heat exchanger or the second thermal management heat exchanger connected to the third sub-thermal management loop and the fourth sub-thermal management loop, and the second heat transfer agent valve is used to simultaneously bypass the first heat exchange zone and the first thermal management heat exchanger or the second thermal management heat exchanger connected to the third sub-thermal management loop and the fourth sub-thermal management loop.
The temperature control system according to any one of claims 11 to 14 is characterized in that the designated component also includes a second designated component, the thermal management circuit also includes a fifth sub-thermal management circuit, the fifth sub-thermal management circuit includes a third heat exchange zone for heat exchange with the second designated component, and the thermal conductor switching component is also capable of circulating the thermal conductor between the third sub-thermal management circuit and the fourth sub-thermal management circuit and the fifth sub-thermal management circuit in the air-conditioning heating mode.
The temperature control system as described in claim 16 is characterized in that the first designated component is a battery module of the transportation equipment, and the second designated component is a motor module of the transportation equipment.
The temperature control system as described in claim 16 is characterized in that the thermal conductor switching component selectively circulates the thermal conductor between the first sub-thermal management circuit and the second sub-thermal management circuit in the air-conditioning refrigeration mode and/or the thermal management refrigeration mode, or circulates the thermal conductor between the first sub-thermal management circuit, the second sub-thermal management circuit and the fifth sub-thermal management circuit.
The temperature control system according to any one of claims 10-18 is characterized in that the third air-conditioning heat exchanger is located in the first sub-thermal management loop, and the temperature control system also includes an airflow switching component, and the temperature control system is configured to control the airflow switching component to guide the air-conditioning airflow through the third air-conditioning heat exchanger in the air-conditioning heating mode, and to guide the air-conditioning airflow not through the third air-conditioning heat exchanger in the air-conditioning cooling mode.
The temperature control system as described in claim 19 is characterized in that the thermal conductor switching component forms a self-circulation of the thermal conductor in the first sub-thermal management loop in the first air-conditioning heating mode and the second air-conditioning heating mode.
The temperature control system as described in claim 6 is characterized in that, in the thermal management cooling mode, the refrigerant switching component guides the refrigerant to pass through the first thermal management heat exchanger and the second thermal management heat exchanger in sequence, and in the second air-conditioning heating mode, the refrigerant switching component guides the refrigerant to pass through only one of the first air-conditioning heat exchanger and the second air-conditioning heat exchanger.
The temperature control system according to claim 21 is characterized in that the outlet of the compressor is connected to the inlet of the condensing heat exchanger, and the refrigerant switching assembly includes a first refrigerant valve, a second refrigerant valve, a third refrigerant valve, a fourth refrigerant valve, a fifth refrigerant valve and a sixth refrigerant valve, the first refrigerant valve is connected between the outlet of the condensing heat exchanger and the inlet of the first air-conditioning heat exchanger, one end of the second refrigerant valve is connected between the outlet of the compressor and the inlet of the condensing heat exchanger, and the other end of the second refrigerant valve is connected to the inlet of the first air-conditioning heat exchanger, one end of the third refrigerant valve is connected between the first refrigerant valve and the outlet of the condensing heat exchanger, and the other end of the third refrigerant valve is connected to the inlet of the second air-conditioning heat exchanger and the inlet of the first thermal management heat exchanger through the fourth refrigerant valve and the fifth refrigerant valve, respectively, the sixth refrigerant valve is connected between the outlet of the first thermal management heat exchanger and the inlet of the second thermal management heat exchanger, the outlet of the first thermal management heat exchanger and the outlet of the second thermal management heat exchanger are connected to the inlet of the compressor, and the sixth refrigerant valve is configured to selectively form or not form a pressure reduction on the refrigerant.
A transportation equipment, characterized in that the transportation equipment includes a temperature control system as described in any one of claims 1-22.