Thermal Management System and Control Method for Mining Machinery

Abstract

A thermal management system for mining machinery and its control method are disclosed. The thermal management system includes: a compression condensation flow path, comprising a parallel compressor assembly and a condenser assembly connected in series with the parallel compressor assembly; a refrigerant pump flow path, comprising a refrigerant pump; a power battery heat exchange flow path, comprising a power battery heat exchange component and a first control valve group connected in series with the power battery heat exchange component; an evaporator flow path, comprising an evaporator assembly and a second control valve group connected in series with the evaporator assembly; a first multi-way valve configured to control the on / off relationship between each first end; a second multi-way valve configured to control the on / off relationship between each second end; and a thermal management controller, signal-connected to the parallel compressor assembly, condenser assembly, refrigerant pump, first control valve group, evaporator assembly, second control valve group, first multi-way valve, and second multi-way valve, configured to form corresponding refrigerant circulation loops according to different operating conditions.

Description

Technical Field

[0001] This disclosure relates to the field of mining operations, and in particular to a thermal management system for mining machinery and its control method. Background Technology

[0002] As global mineral resource development expands into open-pit mines, mining operations face increasingly severe challenges from high-temperature heat hazards. In open-pit mining environments, mining machinery operates continuously under high loads and around the clock. The heat generated by the equipment, combined with the high temperature of the surrounding rock, causes a sharp rise in the working environment temperature, seriously threatening equipment reliability, production efficiency, and personnel safety.

[0003] In some related technologies, electric mining machinery uses a single-compressor compression refrigeration cycle system to dissipate heat from the cab and power battery. Summary of the Invention

[0004] Research has revealed that the cooling capacity of thermal management systems for mining machinery in related technologies is severely insufficient in the extreme high-temperature environments of mining areas. This fails to meet the continuous heat dissipation requirements of heavy-duty equipment, easily leading to frequent overheating shutdowns. Traditional indirect cooling systems suffer from heat exchange losses and have response delays as high as 3-5 minutes, making them ill-suited to handle transient thermal shocks in mining machinery. Furthermore, in high-temperature environments, the exhaust temperature in single-compressor mode easily exceeds safety thresholds, causing lubricating oil carbonization and valve plate deformation.

[0005] In view of this, the present disclosure provides a thermal management system and control method for mining machinery, which can effectively meet the thermal management needs during the operation of mining machinery.

[0006] In one aspect of this disclosure, a thermal management system for mining machinery is provided, comprising:

[0007] The compression condensation flow path includes a parallel compressor assembly and a condenser assembly connected in series with the parallel compressor assembly;

[0008] Refrigerant pump flow path, including the refrigerant pump;

[0009] The power battery heat exchange flow path includes a power battery heat exchange component for heat exchange of the power battery of the mining machinery and a first control valve group connected in series with the power battery heat exchange component.

[0010] The evaporator flow path includes an evaporator assembly for cooling the crew compartment of the mining machinery and a second control valve group connected in series with the evaporator assembly;

[0011] A first multi-way valve is connected to the first end of the compression condensation flow path, the first end of the refrigerant pump flow path, the first end of the power battery heat exchange flow path, and the first end of the evaporator flow path, and is configured to control the on / off relationship between each of the first ends;

[0012] A second multi-way valve, connected to the second end of the compression condensation flow path, the second end of the refrigerant pump flow path, the second end of the power battery heat exchange flow path, and the second end of the evaporator flow path, is configured to control the on / off relationship between each of the second ends; and

[0013] The thermal management controller is signal-connected to the parallel compressor assembly, the condenser assembly, the refrigerant pump, the first control valve group, the evaporator assembly, the second control valve group, the first multi-way valve, and the second multi-way valve, and is configured to form a corresponding refrigerant circulation loop according to different operating conditions.

[0014] In some embodiments, the thermal management controller is configured to:

[0015] In the first operating condition where the ambient temperature is in the first range and the power battery needs to be cooled, the refrigerant pump flow path and the power battery heat exchange flow path are connected through the first multi-way valve and the second multi-way valve to form a cooling circuit, and the refrigerant pump is started to drive the refrigerant in the cooling circuit.

[0016] In some embodiments, the thermal management controller is configured to:

[0017] When the ambient temperature is within the first range and the temperature of the power battery exceeds the upper limit threshold of the preset temperature range, it is determined that the power battery needs to be cooled.

[0018] After the refrigerant pump is started, when the refrigerant temperature inside the power battery heat exchanger is lower than the lower limit threshold of the preset temperature range, the speed of the refrigerant pump is gradually reduced.

[0019] In some embodiments, the condenser assembly includes a condenser and a condenser fan, the condenser fan being signal-connected to the thermal management controller; the thermal management controller is configured to:

[0020] Under the first operating condition, the rotation speed of the condenser fan is adjusted according to the target temperature of the power battery heat exchange component.

[0021] In some embodiments, the parallel compressor assembly includes at least two compression paths connected in parallel and at least two compressors located in the at least two compression paths respectively; wherein the thermal management controller is configured to:

[0022] In the second operating condition where the ambient temperature is in the second range and the power battery needs to be cooled, the compression condensation flow path and the power battery heat exchange flow path are connected through the first multi-way valve and the second multi-way valve to form a compression refrigeration circuit, and some of the compressors of the at least two compressors are started to drive the refrigerant in the compression refrigeration circuit, wherein the minimum value of the second range is greater than or equal to the maximum value of the first range.

[0023] In some embodiments, the first control valve group includes a first solenoid valve and a first electronic expansion valve connected in parallel; the thermal management controller is configured to:

[0024] Under the first operating condition, the first solenoid valve is opened;

[0025] In the second operating condition, the first solenoid valve is closed, and the opening of the first electronic expansion valve is adjusted according to the target superheat of the power battery heat exchange component.

[0026] In some embodiments, the thermal management controller is configured to:

[0027] In the second operating condition, the rotational speed of the partial compressor is adjusted according to the target evaporation temperature of the power battery heat exchanger.

[0028] In some embodiments, the thermal management controller is configured to:

[0029] In the third operating condition where the ambient temperature is in the first range and the crew compartment of the mining machinery needs to be cooled, the refrigerant pump flow path and the evaporator flow path are connected through the first multi-way valve and the second multi-way valve to form a cooling circuit, and the refrigerant pump is started to drive the refrigerant in the cooling circuit.

[0030] In some embodiments, the evaporator assembly includes an evaporator; the thermal management controller is configured to:

[0031] In the third operating condition, the speed of the refrigerant pump is adjusted according to the target evaporation temperature of the evaporator.

[0032] In some embodiments, the evaporator assembly further includes an evaporating fan signal-connected to the thermal management controller; the thermal management controller is configured to:

[0033] In the third operating condition, the speed of the evaporation fan is adjusted according to the target evaporation temperature of the evaporator.

[0034] In some embodiments, the parallel compressor assembly includes at least two compression paths connected in parallel and at least two compressors located in the at least two compression paths respectively; the thermal management controller is configured to:

[0035] In the fourth operating condition where the ambient temperature is in the second range and the crew compartment of the mining machinery needs to be cooled, the compression condensation flow path and the evaporator flow path are connected through the first multi-way valve and the second multi-way valve to form a compression refrigeration circuit, and some of the compressors of the at least two compressors are started to drive the refrigerant in the compression refrigeration circuit, wherein the minimum value of the second range is greater than or equal to the maximum value of the first range.

[0036] In some embodiments, the evaporator assembly includes an evaporator, and the second control valve group includes a second solenoid valve and a second electronic expansion valve connected in parallel; the thermal management controller is configured to:

[0037] In the third operating condition, the second solenoid valve is opened;

[0038] In the fourth operating condition, the second solenoid valve is closed, and the opening of the second electronic expansion valve is adjusted according to the target superheat of the evaporator.

[0039] In some embodiments, the thermal management controller is configured to:

[0040] In the fourth operating condition, the rotational speed of the partial compressor is adjusted according to the target evaporation temperature of the evaporator.

[0041] In some embodiments, the mining machinery thermal management system further includes:

[0042] The converter flow path includes a converter heat exchanger for heat exchange of the DC-DC converter in the mining machinery and a third control valve group connected in series with the converter heat exchanger, wherein the DC-DC converter is used to realize the DC voltage conversion between the power battery and the low-voltage electrical system of the mining machinery.

[0043] The parallel compressor assembly includes at least two parallel compression flow paths and at least two compressors located in the at least two compression flow paths respectively; the thermal management controller is configured to:

[0044] In the fifth operating condition where cooling of the DC-DC converter is required, the compression condensation flow path and the converter flow path are connected through the first multi-way valve and the second multi-way valve to form a compression refrigeration circuit, and some of the compressors of the at least two compressors are started to drive the refrigerant in the compression refrigeration circuit.

[0045] In some embodiments, the third control valve group includes a third solenoid valve and a third electronic expansion valve connected in parallel; the thermal management controller is configured to:

[0046] In the fifth operating condition, the third solenoid valve is closed, and the opening of the third electronic expansion valve is adjusted according to the target superheat of the converter heat exchanger.

[0047] In some embodiments, the thermal management controller is configured to:

[0048] In the fifth operating condition, the rotational speed of the partial compressor is adjusted according to the target evaporation temperature of the heat exchanger of the converter.

[0049] In some embodiments, the parallel compressor assembly includes at least two compression paths connected in parallel and at least two compressors located in the at least two compression paths respectively; the thermal management controller is configured to:

[0050] In the sixth operating condition, where the ambient temperature is in the first range and the power battery and the passenger compartment need to be cooled, the refrigerant pump flow path and the evaporator flow path are connected through the first multi-way valve and the second multi-way valve to form a cooling circuit, and the refrigerant pump is started to drive the refrigerant in the cooling circuit. In addition, the compression condensation flow path and the power battery heat exchange flow path are connected through the first multi-way valve and the second multi-way valve to form a compression refrigeration circuit, and some of the compressors of the at least two compressors are started to drive the refrigerant in the compression refrigeration circuit.

[0051] In some embodiments, the evaporator assembly includes an evaporator and an evaporating fan; the first control valve group includes a first solenoid valve and a first electronic expansion valve connected in parallel; the second control valve group includes a second solenoid valve and a second electronic expansion valve connected in parallel; the evaporating fan is signal-connected to the thermal management controller; the thermal management controller is configured to:

[0052] In the sixth operating condition, the first solenoid valve is closed, the opening of the first electronic expansion valve is adjusted according to the target superheat of the power battery heat exchanger, the speed of the partial compressor is adjusted according to the target evaporation temperature of the power battery heat exchanger, the second solenoid valve is opened, and the speed of the refrigerant pump and / or the gear of the evaporator fan are adjusted according to the target evaporation temperature of the evaporator.

[0053] In some embodiments, the thermal management controller is configured to:

[0054] In the seventh operating condition, where the ambient temperature is in the second range and cooling of the power battery and the passenger compartment is required, the compression condensation flow path is connected to the power battery heat exchange flow path and the evaporator flow path through the first multi-way valve and the second multi-way valve to form a compression refrigeration circuit containing two branch flow paths: the power battery heat exchange flow path and the evaporator flow path. All compressors in the at least two compressors are then started to drive the refrigerant in the compression refrigeration circuit, wherein the minimum value of the second range is greater than or equal to the maximum value of the first range.

[0055] In some embodiments, the evaporator assembly includes an evaporator, the first control valve group includes a first solenoid valve and a first electronic expansion valve connected in parallel, and the second control valve group includes a second solenoid valve and a second electronic expansion valve connected in parallel; the thermal management controller is configured to:

[0056] In the seventh operating condition, the first solenoid valve and the second solenoid valve are closed, and the opening degree of the first electronic expansion valve and the second electronic expansion valve are adjusted according to the target superheat of the power battery heat exchanger and the evaporator, respectively. In addition, the speed of all compressors is adjusted according to the target evaporation temperature of the evaporator and the power battery heat exchanger.

[0057] In some embodiments, the mining machinery thermal management system further includes:

[0058] The converter flow path includes a converter heat exchanger for heat exchange of the DC-DC converter in the mining machinery and a third control valve group connected in series with the converter heat exchanger, wherein the DC-DC converter is used to realize the DC voltage conversion between the power battery and the low-voltage electrical system of the mining machinery.

[0059] The thermal management controller is configured as follows:

[0060] In the eighth operating condition, where the ambient temperature is in the second range and cooling of the power battery, the passenger compartment, and the DC-DC converter is required, the compression condensation flow path is connected to the power battery heat exchange flow path, the evaporator flow path, and the converter flow path through the first multi-way valve and the second multi-way valve to form a compression refrigeration circuit containing three branch flow paths: the power battery heat exchange flow path, the evaporator flow path, and the converter flow path. All compressors in the at least two compressors are then started to drive the refrigerant in the compression refrigeration circuit, wherein the minimum value of the second range is greater than or equal to the maximum value of the first range.

[0061] In some embodiments, the evaporator assembly includes an evaporator, the first control valve group includes a first solenoid valve and a first electronic expansion valve connected in parallel, the second control valve group includes a second solenoid valve and a second electronic expansion valve connected in parallel, and the third control valve group includes a third solenoid valve and a third electronic expansion valve connected in parallel; the thermal management controller is configured to:

[0062] In the eighth operating condition, the first solenoid valve, the second solenoid valve, and the third solenoid valve are closed, and the opening degrees of the first electronic expansion valve, the second electronic expansion valve, and the third electronic expansion valve are adjusted according to the target superheat of the power battery heat exchanger, the evaporator, and the converter heat exchanger, respectively. The speed of all compressors is adjusted according to the target evaporation temperature of the evaporator, the power battery heat exchanger, and the converter heat exchanger.

[0063] In some embodiments, the condenser assembly includes a condenser and a condenser fan, the condenser fan being signal-connected to the thermal management controller; the thermal management controller is configured to:

[0064] The speed of the condenser fan is adjusted according to the discharge pressure of the compressor that has been started.

[0065] In one aspect of this disclosure, a control method for the aforementioned thermal management system for mining machinery is provided, comprising:

[0066] Determine the current operating conditions;

[0067] By controlling at least a portion of the parallel compressor assembly, the condenser assembly, the refrigerant pump, the first control valve group, the evaporator assembly, the second control valve group, the first multi-way valve, and the second multi-way valve through the thermal management controller, a refrigerant circulation loop corresponding to the current operating condition is formed.

[0068] According to the embodiments of this disclosure, a compression condensation flow path including a parallel compressor assembly and a refrigerant pump flow path including a refrigerant pump are provided. With the cooperation of a first multi-way valve and a second multi-way valve, the thermal management controller can establish different refrigerant circulation loops according to the requirements of different operating conditions, so as to effectively cope with the needs of mining machinery operation such as cooling capacity, environmental adaptability and reliability in the complex environment of the mining area, and ensure the continuity of mining operations. Attached Figure Description

[0069] The accompanying drawings, which form part of this specification, illustrate embodiments of this disclosure and, together with the specification, serve to explain the principles of this disclosure.

[0070] This disclosure will become clearer with reference to the accompanying drawings and the following detailed description, wherein:

[0071] Figure 1 These are schematic diagrams illustrating the principles of some embodiments of the mining machinery thermal management system disclosed herein;

[0072] Figure 2 This is a schematic diagram of the control relationship under the first working condition according to an embodiment of the mining machinery thermal management system of this disclosure;

[0073] Figure 3 This is a schematic diagram of the control relationship under the second working condition according to an embodiment of the mining machinery thermal management system of this disclosure;

[0074] Figure 4 This is a schematic diagram of the control relationship under the third working condition according to an embodiment of the mining machinery thermal management system of this disclosure;

[0075] Figure 5 This is a schematic diagram of the control relationship under the fourth working condition according to the embodiment of the mining machinery thermal management system of this disclosure;

[0076] Figure 6 This is a schematic diagram of the control relationship under the fifth working condition according to the embodiment of the mining machinery thermal management system of this disclosure;

[0077] Figure 7 This is a schematic diagram of the control relationship under the sixth working condition according to the embodiment of the mining machinery thermal management system of this disclosure;

[0078] Figure 8 This is a schematic diagram of the control relationship under the seventh working condition according to the embodiment of the mining machinery thermal management system of this disclosure;

[0079] Figure 9 This is a schematic diagram of the control relationship under the eighth working condition according to the embodiment of the mining machinery thermal management system of this disclosure;

[0080] Figure 10 This is a flowchart illustrating some embodiments of the control method according to the present disclosure.

[0081] It should be understood that the dimensions of the various parts shown in the accompanying drawings are not drawn to actual scale. Furthermore, the same or similar reference numerals denote the same or similar components.

[0082] Explanation of reference numerals in the attached figures:

[0083] 11, 12 - Compressor; 111, 121 - First check valve; 112, 122 - Oil separator; 113, 123 - Oil return capillary tube; 13 - Condenser; 14 - Condenser fan; 15 - First three-way valve; 16 - Second three-way valve; 17 - Fourth solenoid valve; 18 - Gas-liquid separator;

[0084] 21-Refrigerant pump; 22-Liquid receiver; 23-Fifth solenoid valve; 24-Second check valve;

[0085] 31, 32 - Power battery heat exchange components; 33, 34 - First solenoid valve; 35, 36 - First electronic expansion valve; 37 - Third three-way valve; 38 - Fourth three-way valve;

[0086] 41-Evaporator; 42-Evaporator fan; 43-Second solenoid valve; 44-Second electronic expansion valve;

[0087] 51-Converter heat exchanger; 52-Third solenoid valve; 53-Third electronic expansion valve;

[0088] 61-First multi-way valve; 62-Second multi-way valve; 63-Thermal management controller; 64-Battery thermal management controller; 65-DC-CDC thermal management controller;

[0089] b1, b2 - Power battery; dd-DC converter;

[0090] f1 - Compression condensation flow path; f11, f12 - Compression flow path; f2 - Refrigerant pump flow path; f3 - Power battery heat exchange flow path; f4 - Evaporator flow path; f5 - Converter flow path. Detailed Implementation

[0091] Various exemplary embodiments of the present disclosure will now be described in detail with reference to the accompanying drawings. The descriptions of the exemplary embodiments are merely illustrative and are in no way intended to limit the present disclosure or its application or use. The present disclosure may be implemented in many different forms and is not limited to the embodiments described herein. These embodiments are provided so that the present disclosure will be thorough and complete, and will fully express the scope of the disclosure to those skilled in the art. It should be noted that, unless specifically stated otherwise, the relative arrangement of components and steps, the composition of materials, numerical expressions, and values ​​set forth in these embodiments should be interpreted as exemplary only and not as limiting.

[0092] When using terms like "includes" or "contains," to describe an element as "including" or "containing" one or more elements, it should be understood that the elements listed after the word are components of the element preceding the word, but this does not preclude the possibility that the element preceding the word may also contain other elements. Furthermore, this statement specifically covers situations where the element preceding the word is entirely composed of or specifically realized by all the elements listed after the word.

[0093] The terms "first," "second," and similar terms used in this disclosure do not indicate any order, quantity, or importance, but are merely used to distinguish different parts. Terms such as "upper," "lower," "left," and "right" are used only to indicate relative positional relationships, and these relative positional relationships may change accordingly when the absolute position of the described object changes.

[0094] In this disclosure, when a specific device is described as being located between a first device and a second device, an intermediary device may or may not be present between the specific device and the first or second device. When a specific device is described as being connected to other devices, the specific device may be directly connected to the other devices without an intermediary device, or it may be not directly connected to the other devices but have an intermediary device.

[0095] All terms used in this disclosure (including technical or scientific terms) have the same meaning as understood by one of ordinary skill in the art to which this disclosure pertains, unless otherwise specifically defined. It should also be understood that terms defined in a general dictionary, such as a dictionary, should be interpreted as having a meaning consistent with their meaning in the context of the relevant art, and not as having an idealized or highly formalized meaning, unless expressly defined herein.

[0096] Techniques, methods, and equipment known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and equipment should be considered part of the specification.

[0097] In some related technologies, electric mining machinery uses a single-compressor compression refrigeration cycle system to dissipate heat from the cab and power battery.

[0098] Research has revealed that the cooling capacity of thermal management systems for mining machinery in related technologies is severely insufficient in the extreme high-temperature environments of mining areas. This fails to meet the continuous heat dissipation requirements of heavy-duty equipment, easily leading to frequent overheating shutdowns. Traditional indirect cooling systems suffer from heat exchange losses and have response delays as high as 3-5 minutes, making them ill-suited to handle transient thermal shocks in mining machinery. Furthermore, in high-temperature environments, the exhaust temperature in single-compressor mode easily exceeds safety thresholds, causing lubricating oil carbonization and valve plate deformation.

[0099] In view of this, the present disclosure provides a thermal management system and control method for mining machinery, which can effectively meet the thermal management needs during the operation of mining machinery.

[0100] Figure 1 This is a schematic diagram illustrating the principle of some embodiments of the mining machinery thermal management system disclosed herein. (Reference) Figure 1 This disclosure provides a thermal management system for mining machinery. Mining machinery can be used for mining surface or underground mineral deposits, such as excavators, loaders, rock drilling rigs, and tunneling machines.

[0101] The thermal management system for mining machinery includes: a compression condenser flow path f1, a refrigerant pump flow path f2, a power battery heat exchange flow path f3, an evaporator flow path f4, a first multi-way valve 61, a second multi-way valve 62, and a thermal management controller 63.

[0102] The compression condensation flow path f1 includes a parallel compressor assembly and a condenser assembly connected in series with the parallel compressor assembly. The parallel compressor assembly may include at least two parallel compression flow paths f11 and f12, each containing a compressor, thereby forming a parallel connection between at least two compressors. The condenser assembly is connected in series with the parallel compressor assembly and can condense and dissipate heat from the refrigerant output by the parallel compressor assembly.

[0103] The refrigerant pump flow path f2 includes a refrigerant pump 21. The refrigerant pump 21 can pump refrigerant to make the refrigerant flow in the refrigerant pump flow path f2 and other flow paths that establish a refrigerant circuit with it.

[0104] The power battery heat exchange flow path f3 includes power battery heat exchange components 31 and 32 for heat exchange of the power batteries b1 and b2 in the mining machinery, and a first control valve group connected in series with the power battery heat exchange components 31 and 32. The mining machinery may include one or more power batteries. Figure 1 The illustration shows two power batteries, b1 and b2. The power battery heat exchange components 31 and 32 can be direct cooling plates that exchange heat with power batteries b1 and b2, respectively. Correspondingly, the power battery heat exchange flow path f3 can include two parallel flow paths, each of which can be equipped with a corresponding first control valve group.

[0105] The power battery of mining machinery can serve as either the main power source or an auxiliary power source. The power battery heat exchanger can be installed independently of the power battery or integrated within it, for example, located at the bottom of the power battery housing or between individual battery cells within the housing. The first control valve assembly is connected in series with the power battery heat exchanger and can control the on / off state and / or flow rate of the power battery heat exchange path f3 where the heat exchanger is located.

[0106] The evaporator flow path f4 includes an evaporator assembly for cooling the crew compartment of the mining machinery and a second control valve assembly connected in series with the evaporator assembly. The evaporator assembly can be used for, but is not limited to, cooling the crew compartment of the mining machinery. The crew compartment here can be the driver's cab or operator's cabin of the mining machinery. The second control valve assembly, connected in series with the evaporator assembly, is capable of controlling the on / off state and / or flow rate of the evaporator flow path f4 where the evaporator assembly is located.

[0107] The first multi-way valve 61 is connected to the first end of the compression condensation flow path f1, the first end of the refrigerant pump flow path f2, the first end of the power battery heat exchange flow path f3, and the first end of the evaporator flow path f4, and is configured to control the on / off relationship between each of the first ends. The second multi-way valve 62 is connected to the second end of the compression condensation flow path f1, the second end of the refrigerant pump flow path f2, the second end of the power battery heat exchange flow path f3, and the second end of the evaporator flow path f4, and is configured to control the on / off relationship between each of the second ends.

[0108] At least one of the first multi-way valve 61 and the second multi-way valve 62 can be implemented as a single type of valve or as a valve group formed by combining multiple valves, and can be controlled by electromagnetic or electro-hydraulic means.

[0109] The first multi-way valve 61 and the second multi-way valve 62 are respectively connected to the two ends of the compression condensation flow path f1, the refrigerant pump flow path f2, the power battery heat exchange flow path f3, and the evaporator flow path f4. They can construct the connection relationship between different flow paths according to the control command to form different refrigerant circuits, thereby realizing direct cooling of the refrigerant, reducing energy transfer loss, which is conducive to improving the overall energy efficiency ratio (COP) of the system and reducing the energy consumption of mining equipment operation.

[0110] The thermal management controller 63 is signal-connected to the parallel compressor assembly, the condenser assembly, the refrigerant pump 21, the first control valve group, the evaporator assembly, the second control valve group, the first multi-way valve 61, and the second multi-way valve 62, and is configured to form corresponding refrigerant circulation loops according to different operating conditions.

[0111] The thermal management controller 63, also known as the vehicle thermal management controller, can directly transmit commands or data with at least one of the parallel compressor assembly, the condenser assembly, the refrigerant pump 21, the first control valve group, the evaporator assembly, the second control valve group, the first multi-way valve 61, and the second multi-way valve 62, or indirectly transmit commands or data with at least some of them through other controllers.

[0112] like Figure 1 As shown, the thermal management controller 63 is connected to the actuators such as pumps, compressors, valves, and fans in the mining machinery thermal management system via dashed lines with arrows. It is also connected to the battery thermal management controller 64 and the DC-DC thermal management controller 65 via dashed lines with arrows. The battery thermal management controller 64 is connected to the temperature sensing elements of the power batteries b1 and b2 via dashed lines with arrows. The DC-DC thermal management controller 65 is connected to the temperature sensing element of the DC-DC converter dd via dashed lines with arrows.

[0113] The thermal management controller 63 can control the changes in the connection relationship between the first multi-way valve 61 and the second multi-way valve 62, and can also control components such as compressors, pumps, and valves in different refrigerant flow paths. This allows for the pre-setting of control strategies for different operating conditions, establishing refrigerant circulation loops corresponding to those conditions to meet the thermal management requirements under varying circumstances. These thermal management requirements may include cooling of different parts or areas, as well as requirements related to energy consumption, reliability, and operational continuity.

[0114] In this embodiment, a compression condensation flow path including a parallel compressor assembly and a refrigerant pump flow path including a refrigerant pump are provided. With the cooperation of a first multi-way valve and a second multi-way valve, the thermal management controller can establish different refrigerant circulation loops according to the requirements of different operating conditions, so as to effectively cope with the needs of mining machinery operation such as cooling capacity, environmental adaptability and reliability in the complex environment of the mining area, and ensure the continuity of mining operations.

[0115] like Figure 1 As shown, in the compression condensation flow path f1, the two compression flow paths f11 and f12, in addition to including compressors 11 and 12 respectively, may also include a first check valve 111 and an oil separator 112 connected in series with compressor 11, and a first check valve 121 and an oil separator 122 connected in series with compressor 12.

[0116] The first check valve is located on the compressor's discharge port side to prevent refrigerant from flowing back into the compressor. The oil separator separates the mixture of refrigerant and lubricating oil discharged from the compressor, returning the separated lubricating oil to the compressor to control the amount of oil entering the circulation.

[0117] An oil return capillary tube 113 (or 123) can also be installed between the suction port and the discharge port of the compressor 11 (or 12). The oil return capillary tube can be used to return part of the lubricating oil from the compressor discharge port to the compressor suction port.

[0118] A first three-way valve 15 and a second three-way valve 16 are respectively provided at both ends of the two compression flow paths f11 and f12. The first three-way valve 15 and the second three-way valve 16 can respectively combine and split the refrigerant flow.

[0119] A fourth solenoid valve 17 may be provided on the side of the second three-way valve 16 away from the compressor suction port. This solenoid valve can be used to control the opening and closing of the entire compression condensing flow path f1, and also to control the refrigerant flow rate within the compression condensing flow path f1. A gas-liquid separator 18 may also be provided within the compression condensing flow path f1. The gas-liquid separator 18 can separate the refrigerant into gas and liquid before it enters the compressor suction port, reducing the risk of compressor liquid slugging.

[0120] like Figure 1 As shown, the refrigerant pump flow path f2 includes not only the refrigerant pump 21, but may also include a liquid receiver 22, a fifth solenoid valve 23, and a second check valve 24. The second check valve 24 is located on the outlet side of the refrigerant pump 21 to prevent refrigerant from flowing back into the refrigerant pump 21. The fifth solenoid valve 23 can be used to control the on / off state of the entire refrigerant pump flow path f2, and also to control the refrigerant flow rate within the refrigerant pump flow path f2. The liquid receiver 22 can serve as a buffer container for the refrigerant, storing excess liquid refrigerant in the circuit when the load is low, and replenishing the circuit with the required liquid refrigerant when the load is high, thereby achieving a balance in the system's refrigerant quantity.

[0121] exist Figure 1 In the process, the power battery heat exchange flow path f3 may include heat exchange flow paths of one or more power battery heat exchange components. At both ends of the heat exchange flow paths of multiple power battery heat exchange components, a third three-way valve 37 and a fourth three-way valve 38 may be respectively provided to realize the diversion and merging of refrigerant.

[0122] exist Figure 1 In some embodiments, the condenser assembly may include a condenser 13 and a condenser fan 14, the condenser fan 14 being signal-connected to the thermal management controller 63. The thermal management controller 63 can control the rotational speed of the condenser fan 14 to adjust the degree of condensation heat dissipation of the condenser 13.

[0123] Figure 2 This is a schematic diagram of the control relationship under the first operating condition according to an embodiment of the mining machinery thermal management system of this disclosure. (Reference) Figure 2 In some embodiments, the thermal management controller 63 is configured to: when the ambient temperature is in a first range and the power batteries b1 and b2 need to be cooled, connect the refrigerant pump flow path f2 and the power battery heat exchange flow path f3 through the first multi-way valve 61 and the second multi-way valve 62 to form a cooling circuit, and start the refrigerant pump 21 to drive the refrigerant in the cooling circuit.

[0124] The first temperature range can be set according to actual conditions, for example, 10℃~30℃. This can be considered the cooling condition of the power battery at room temperature. The ambient temperature can be determined based on a thermometer or received ambient temperature data.

[0125] like Figure 2 As shown, under the first operating condition, the refrigerant pump flow path f2 and the power battery heat exchange flow path f3, indicated by the thin-line rectangular frame, are connected through the first multi-way valve 61 and the second multi-way valve 62 to form a cooling circuit. The connection relationship between the flow paths is indicated by the thin lines in the first multi-way valve 61 and the second multi-way valve 62.

[0126] As can be seen, opening the fifth solenoid valve 23 in the refrigerant pump flow path f2 and starting the refrigerant pump 21 allows the refrigerant in the refrigerant pump flow path f2 to flow through the second one-way valve 24 to the first multi-way valve 61, and then through the first multi-way valve 61 into the power battery heat exchange flow path f3. The refrigerant flowing into the power battery heat exchange flow path f3 is split by the third three-way valve 37 and exchanges heat with the power batteries b1 and b2 in the two power battery heat exchange components 31 and 32, respectively. After heat exchange, the refrigerant merges through the fourth three-way valve 38 and flows into the second multi-way valve 62, then returns to the refrigerant pump flow path f2, and returns to the refrigerant pump 21 through the fifth solenoid valve 23 and the liquid storage tank 22.

[0127] For cooling the power battery at room temperature, a refrigerant pump 21 is used for refrigerant circulation. At this time, it is not necessary to start energy-intensive components such as the compressor, thereby reducing system energy consumption while meeting the cooling requirements of the power battery.

[0128] like Figure 2 As shown, the first control valve group may include first solenoid valves 33 and 34 and first electronic expansion valves 35 and 36 connected in parallel. The thermal management controller 63 may be configured to open the first solenoid valves 33 and 34 under the first operating condition. Figure 2 The √ symbol indicates the opening of the refrigerant pump 21 and the first solenoid valves 33 and 34. At this time, after the refrigerant enters the power battery heat exchange flow path f3, it passes through the first solenoid valves 33 and 34 and enters the power battery heat exchange components 31 and 32 respectively.

[0129] In the accompanying drawings corresponding to the following embodiments, elements in the open state are indicated by a √, and elements in the closed state are indicated by an ×. These elements can be refrigerant pumps or compressors, or solenoid valves or electronic expansion valves, etc. Furthermore, in these drawings, the refrigerant flow path that participates in and forms the loop is indicated by a thin-lined rectangle. This will not be elaborated upon further below.

[0130] refer to Figure 2 In some embodiments, the thermal management controller 63 is configured to: determine that the power battery needs to be cooled when the ambient temperature is in the first range and the temperature of the power battery exceeds the upper limit threshold of the preset temperature range; and after starting the refrigerant pump 21, gradually reduce the speed of the refrigerant pump 21 when the refrigerant temperature in the heat exchange component of the power battery is lower than the lower limit threshold of the preset temperature range.

[0131] Whether to activate battery cooling can be determined based on the battery's temperature. If the battery temperature exceeds the upper limit of the preset temperature range, it indicates that the battery temperature is too high and no longer within the suitable operating temperature range, therefore timely cooling is necessary. Figure 2 As shown, the battery thermal management controller 64 can collect temperature data of the power battery and dynamically compare it with a preset temperature range. The battery thermal management controller 64 can send the comparison results or directly send the temperature data to the vehicle thermal management controller.

[0132] After the refrigerant pump 21 is started, the refrigerant will increase its temperature after exchanging heat with the power battery in the power battery heat exchange component. Then, if the temperature of the refrigerant in the power battery heat exchange component is lower than the lower limit threshold of the preset temperature range, it indicates that the temperature of the power battery has dropped to a certain extent. At this time, the cooling demand is reduced, and the speed of the refrigerant pump 21 is gradually reduced, which can save energy and prevent the power battery from becoming too cold due to excessive cooling.

[0133] Figure 3This is a schematic diagram of the control relationship under the second operating condition according to an embodiment of the mining machinery thermal management system of this disclosure. (Reference) Figure 3 In some embodiments, the parallel compressor assembly includes at least two parallel compression paths f11, f12 and at least two compressors 11, 12 respectively located in the at least two compression paths f11, f12. Accordingly, the thermal management controller 63 is configured to: in a second operating condition where the ambient temperature is in a second range and cooling of the power batteries b1, b2 is required, connect the compression condensation path f1 and the power battery heat exchange path f3 through the first multi-way valve 61 and the second multi-way valve 62 to form a compression refrigeration circuit, and start some of the at least two compressors 11, 12 to drive the refrigerant in the compression refrigeration circuit, wherein the minimum value of the second range is greater than or equal to the maximum value of the first range.

[0134] As mentioned earlier, the first range can be 10℃ to 30℃. The minimum value of the second range can be set to be greater than or equal to the maximum value of the first range, such as 30℃, 31℃, 32℃, 35℃, 40℃, etc. The maximum value of the second range can be set as needed, such as 45℃, 50℃, 60℃, etc. For the second range, the second operating condition actually belongs to the high-temperature power battery cooling condition. In this case, a portion of the compressors in the parallel compressor assembly (e.g., Figure 3 The compressor 11 in the middle works with the condenser 13, the first electronic expansion valves 35 and 36 and the power battery heat exchange components 31 and 32 to form a compression refrigeration circuit. In this way, sufficient cooling capacity is provided through compression refrigeration, and a portion of the compressor is used to reduce energy consumption.

[0135] refer to Figure 3 In some embodiments, the thermal management controller 63 is configured to adjust the speed of a portion of the compressors (e.g., compressor 11 or compressor 12) according to the target evaporation temperature of the power battery heat exchangers 31 and 32 under the second operating condition. For example, the compressor 11 is set to an initial speed Rpm1, and the target evaporation temperature of the power battery heat exchangers 31 and 32 is TB0. The absolute value of the difference between the actual evaporation temperature TB1 and the target evaporation temperature TB0 of the refrigerant in the power battery heat exchangers 31 and 32 is calculated to see if it does not exceed a threshold. If it does not exceed the threshold, the compressor 11 is kept at its initial speed; otherwise, the speed of the compressor 11 is adjusted according to a preset step size. This process can be performed every t seconds.

[0136] refer to Figure 3In some embodiments, the first control valve group includes first solenoid valves 33 and 34 and first electronic expansion valves 35 and 36 connected in parallel. Accordingly, the thermal management controller 63 is configured to: close the first solenoid valves 33 and 34 in the second operating condition, and adjust the opening of the first electronic expansion valves 35 and 36 according to the target superheat of the power battery heat exchange components 31 and 32.

[0137] In the second operating condition, closing the first solenoid valve allows the refrigerant to flow through the first electronic expansion valve, which is connected in parallel with the first solenoid valve, and is subject to the throttling control of the first electronic expansion valve. At this time, the first electronic expansion valve acts as a throttling device in the compression refrigeration circuit to reduce the pressure of the refrigerant. Correspondingly, the refrigerant passing through the first electronic expansion valve will evaporate and absorb heat in the power battery heat exchanger, which acts as an evaporator, thereby reducing the temperature of the power battery.

[0138] For example, the first electronic expansion valves 35 and 36 can perform an initialization process at the start of the second operating condition and be set to the initial opening degree Step1. Then, they are adjusted according to the target superheat TEXV. The absolute value of the difference between the actual superheat and the target superheat of the power battery heat exchanger 31 and 32 is calculated to see if it does not exceed a threshold (e.g., a value of 0.5). If it does not exceed the threshold, the first electronic expansion valves 35 and 36 are kept at the initial opening degree without adjustment. Otherwise, the first electronic expansion valves 35 and 36 can be adjusted according to the absolute value of the difference.

[0139] refer to Figure 1 and Figure 3 In some embodiments, the condenser assembly includes a condenser 13 and a condenser fan 14, the condenser fan 14 being signal-connected to the thermal management controller 63. The thermal management controller 63 is configured to adjust the rotational speed of the condenser fan 14 based on the discharge pressure of the started compressor. For a started compressor, such as compressor 11, the rotational speed of the condenser fan 14 can be adjusted for different discharge pressures of compressor 11 to maintain the condensing temperature / pressure within an optimal range, thereby effectively balancing energy consumption and performance.

[0140] Figure 4 This is a schematic diagram of the control relationship under the third operating condition according to an embodiment of the mining machinery thermal management system of this disclosure. (Reference) Figure 4 In some embodiments, the thermal management controller 63 is configured to: in a third operating condition where the ambient temperature is in a first range and the crew compartment of the mining machinery needs to be cooled, connect the refrigerant pump flow path f2 and the evaporator flow path f4 through the first multi-way valve 61 and the second multi-way valve 62 to form a cooling circuit, and start the refrigerant pump 21 to drive the refrigerant in the cooling circuit.

[0141] The first temperature range can be set according to actual conditions, for example, 10℃~30℃. This can be considered the passenger compartment cooling condition at room temperature. The ambient temperature can be determined based on a thermometer or received ambient temperature data.

[0142] like Figure 4 As shown, in the third operating condition, the refrigerant pump flow path f2 and the evaporator flow path f4, indicated by the thin-lined rectangular frame, are connected to form a cooling circuit through the first multi-way valve 61 and the second multi-way valve 62. The connection relationship between the flow paths is indicated by the thin lines in both the first multi-way valve 61 and the second multi-way valve 62.

[0143] For passenger compartment cooling at normal temperature, refrigerant pump 21 is used for refrigerant circulation. At this time, it is not necessary to start energy-consuming components such as compressors, thereby meeting the cooling needs of passenger compartment while reducing system energy consumption.

[0144] refer to Figure 4 In some embodiments, the evaporator assembly includes an evaporator 41. Accordingly, the thermal management controller 63 is configured to adjust the rotational speed of the refrigerant pump 21 according to the target evaporation temperature of the evaporator 41 under the third operating condition. This allows for more precise matching of the cooling requirements of the passenger compartment, maintaining the stability of the evaporation temperature of the evaporator 41, and improving system energy efficiency.

[0145] For example, the target evaporation temperature of the core of evaporator 41 is determined according to the set temperature and the ambient temperature. The absolute value of the difference between the actual evaporation temperature Tevp and the target evaporation temperature Tevp0 is calculated to see if it does not exceed the threshold. If it does not exceed the threshold, the refrigerant pump 21 is kept at its initial speed. Otherwise, the speed of the refrigerant pump 21 is adjusted according to the preset step size. This process can be checked every t seconds.

[0146] like Figure 4 As shown, the second control valve group includes a second solenoid valve 43 and a second electronic expansion valve 44 connected in parallel. The thermal management controller 63 can open the second solenoid valve 43 under the third operating condition. At this time, the refrigerant pumped by the refrigerant pump 21 can flow into the evaporator 41 through the second solenoid valve 43.

[0147] refer to Figure 4 In some embodiments, the evaporator assembly further includes an evaporator fan 42 signal-connected to the thermal management controller 63. The thermal management controller 63 is configured to adjust the speed of the evaporator fan 42 according to the target evaporation temperature of the evaporator 41 during the third operating condition. By adjusting the speed of the evaporator fan 42, the heat absorption capacity of the evaporator 41 can be changed to match the target evaporation temperature of the evaporator 41.

[0148] Figure 5This is a schematic diagram of the control relationship under the fourth operating condition according to an embodiment of the mining machinery thermal management system of this disclosure. (Reference) Figure 5 In some embodiments, the parallel compressor assembly includes at least two parallel compression flow paths f11, f12 and at least two compressors 11, 12 located in the at least two compression flow paths f11, f12 respectively.

[0149] Accordingly, the thermal management controller 63 is configured to: in the fourth operating condition where the ambient temperature is in the second range and the crew compartment of the mining machinery needs to be cooled, connect the compression condenser flow path f1 and the evaporator flow path f4 through the first multi-way valve 61 and the second multi-way valve 62 to form a compression refrigeration circuit, and start some of the compressors of the at least two compressors 11 and 12 to drive the refrigerant in the compression refrigeration circuit, wherein the minimum value of the second range is greater than or equal to the maximum value of the first range.

[0150] As mentioned earlier, the first range can be 10℃ to 30℃. The minimum value of the second range can be set to be greater than or equal to the maximum value of the first range, such as 30℃, 31℃, 32℃, 35℃, 40℃, etc. The maximum value of the second range can be set as needed, such as 45℃, 50℃, 60℃, etc. For the second range, the fourth operating condition is actually a high-temperature occupant cabin cooling condition. In this case, a portion of the compressors in the parallel compressor assembly (e.g., Figure 5 The compressor 11 in the middle works with the condenser 13, the second electronic expansion valve 44 and the evaporator 41 to form a compression refrigeration circuit. In this way, sufficient cooling capacity is provided through compression refrigeration, and a portion of the compressor is used to reduce energy consumption.

[0151] refer to Figure 5 In some embodiments, the thermal management controller 63 is configured to adjust the rotational speed of the partial compressor (e.g., compressor 11 or compressor 12) according to the target evaporation temperature of the evaporator 41 under the fourth operating condition.

[0152] The initial speed of the compressor 11 can be determined based on a single factor or multiple factors. For example, the initial speed can be determined based on factors such as ambient temperature, the difference between return air temperature and set temperature, and the speed of the evaporator fan.

[0153] The target evaporation temperature of the evaporator core 41 is determined according to the set temperature and the ambient temperature. The absolute value of the difference between the actual evaporation temperature Tevp and the target evaporation temperature Tevp0 is calculated to see if it does not exceed the threshold. If it does not exceed the threshold, the compressor 11 is kept at its initial speed. Otherwise, the speed of the compressor 11 is adjusted according to the preset step size. This process can be checked once every t seconds.

[0154] refer to Figure 5 In some embodiments, the evaporator assembly includes an evaporator 41, and the second control valve group includes a second solenoid valve 43 and a second electronic expansion valve 44 connected in parallel. The thermal management controller 63 is configured to: in the fourth operating condition, close the second solenoid valve 43 and adjust the opening of the second electronic expansion valve 44 according to the target superheat of the evaporator 41.

[0155] In the fourth operating condition, closing the second solenoid valve 43 allows the refrigerant to flow through the second electronic expansion valve 44, which is connected in parallel with the second solenoid valve 43, and to be throttled by the second electronic expansion valve 44. At this time, the second electronic expansion valve 44 acts as a throttling device in the compression refrigeration circuit to reduce the pressure of the refrigerant. Correspondingly, the refrigerant passing through the second electronic expansion valve 44 will evaporate and absorb heat in the evaporator 41, thereby reducing the temperature of the passenger compartment.

[0156] For example, the second electronic expansion valve 44 can perform an initialization process at the start of the fourth operating condition, and be set to the initial opening degree Step1. Then, it is adjusted according to the target superheat TEXV. The absolute value of the difference between the actual superheat and the target superheat of the evaporator 41 is calculated to see if it does not exceed a threshold (e.g., a value of 0.5). If it does not exceed the threshold, the second electronic expansion valve 44 is kept at the initial opening degree without adjustment. Otherwise, the second electronic expansion valve 44 can be adjusted according to the absolute value of the difference.

[0157] refer to Figure 1 and Figure 5 In some embodiments, the condenser assembly includes a condenser 13 and a condenser fan 14, the condenser fan 14 being signal-connected to the thermal management controller 63. The thermal management controller 63 is configured to adjust the rotational speed of the condenser fan 14 based on the discharge pressure of the started compressor. For a started compressor, such as compressor 11, the rotational speed of the condenser fan 14 can be adjusted for different discharge pressures of compressor 11 to maintain the condensing temperature / pressure within an optimal range, thereby effectively balancing energy consumption and performance.

[0158] Figure 6 This is a schematic diagram of the control relationship under the fifth operating condition according to an embodiment of the mining machinery thermal management system of this disclosure. (Reference) Figure 1 and Figure 6 In some embodiments, the thermal management system for mining machinery further includes a converter flow path f5. The converter flow path f5 includes a converter heat exchanger 51 for heat exchange of the DC-DC converter dd of the mining machinery and a third control valve group connected in series with the converter heat exchanger 51, wherein the DC-DC converter dd is used to realize the DC voltage conversion between the power batteries b1 and b2 and the low-voltage electrical system of the mining machinery.

[0159] The parallel compressor assembly includes at least two parallel compression flow paths f11 and f12 and at least two compressors 11 and 12 located in the at least two compression flow paths f11 and f12, respectively.

[0160] The thermal management controller 63 is configured to: in the fifth operating condition where the DC-DC converter dd needs to be cooled, connect the compression condensation flow path f1 and the converter flow path f5 through the first multi-way valve 61 and the second multi-way valve 62 to form a compression refrigeration circuit, and start some of the compressors of the at least two compressors 11 and 12 to drive the refrigerant in the compression refrigeration circuit.

[0161] When the temperature of the DC-DC converter dd approaches the upper limit of the preset operating range, cooling of the DC-DC converter dd can be achieved in the fifth operating condition. In this case, a portion of the compressors in the parallel compressor assembly (e.g., Figure 3 The compressor 11 in the middle works with the condenser 13, the third electronic expansion valve 53 and the converter heat exchanger 51 to form a compression refrigeration circuit. In this way, sufficient cooling capacity is provided through compression refrigeration, and a portion of the compressor is used to reduce energy consumption.

[0162] refer to Figure 6 In some embodiments, the third control valve group includes a third solenoid valve 52 and a third electronic expansion valve 53 connected in parallel. The thermal management controller 63 is configured to: in the fifth operating condition, close the third solenoid valve 52 and adjust the opening of the third electronic expansion valve 53 according to the target superheat of the converter heat exchanger 51.

[0163] In the fifth operating condition, closing the third solenoid valve 52 allows the refrigerant to flow through the third electronic expansion valve 53, which is connected in parallel with the third solenoid valve 52, and to be throttled by the third electronic expansion valve 53. At this time, the third electronic expansion valve 53 acts as a throttling device in the compression refrigeration circuit to reduce the pressure of the refrigerant. Correspondingly, the refrigerant passing through the third electronic expansion valve 53 will evaporate and absorb heat in the heat exchange element 51 of the converter, which acts as an evaporator, thereby reducing the temperature of the DC-DC converter.

[0164] For example, the third electronic expansion valve 53 can perform an initialization process at the start of the fifth operating condition, and be set to the initial opening degree Step1. Then, it is adjusted according to the target superheat TEXV. The absolute value of the difference between the actual superheat and the target superheat of the heat exchanger element 51 is calculated to see if it does not exceed a threshold (e.g., a value of 0.5). If it does not exceed the threshold, the third electronic expansion valve 53 is kept at the initial opening degree without adjustment. Otherwise, the third electronic expansion valve 53 can be adjusted according to the absolute value of the difference.

[0165] refer to Figure 6 In some embodiments, the thermal management controller 63 is configured to adjust the rotational speed of the partial compressor according to the target evaporation temperature of the converter heat exchanger 51 under the fifth operating condition.

[0166] For example, the target evaporation temperature of the heat exchanger 51 of the converter is determined according to the set temperature and the ambient temperature. The absolute value of the difference between the actual evaporation temperature Tdc and the target evaporation temperature Tdc0 is calculated to see if it does not exceed the threshold. If it does not exceed the threshold, the compressor 11 is kept at its initial speed. Otherwise, the speed of the compressor 11 is adjusted according to the preset step size. This process can be checked every t seconds.

[0167] refer to Figure 1 and Figure 6 In some embodiments, the condenser assembly includes a condenser 13 and a condenser fan 14, the condenser fan 14 being signal-connected to the thermal management controller 63. The thermal management controller 63 is configured to adjust the rotational speed of the condenser fan 14 based on the discharge pressure of the started compressor. For a started compressor, such as compressor 11, the rotational speed of the condenser fan 14 can be adjusted for different discharge pressures of compressor 11 to maintain the condensing temperature / pressure within an optimal range, thereby effectively balancing energy consumption and performance.

[0168] The first to fifth working conditions mentioned above are all relatively simple working conditions. The embodiments of the mining machinery thermal management system disclosed herein can also be used for more complex working conditions, such as the sixth to eighth working conditions mentioned later.

[0169] Figure 7 This is a schematic diagram of the control relationship under the sixth operating condition according to an embodiment of the mining machinery thermal management system of this disclosure. (Reference) Figure 7 In some embodiments, the parallel compressor assembly includes at least two parallel compression flow paths f11, f12 and at least two compressors 11, 12 located in the at least two compression flow paths f11, f12 respectively.

[0170] Accordingly, the thermal management controller 63 is configured to: in the sixth operating condition where the ambient temperature is in the first range and the power batteries b1, b2 and the passenger compartment need to be cooled, connect the refrigerant pump flow path f2 and the evaporator flow path f4 through the first multi-way valve 61 and the second multi-way valve 62 to form a cooling circuit, and start the refrigerant pump 21 to drive the refrigerant in the cooling circuit; and connect the compression condensation flow path f1 and the power battery heat exchange flow path f3 through the first multi-way valve 61 and the second multi-way valve 62 to form a compression refrigeration circuit, and start some of the compressors of the at least two compressors 11, 12 to drive the refrigerant in the compression refrigeration circuit.

[0171] The first temperature range can be set according to actual conditions, for example, 10℃~30℃. In this case, the sixth operating condition can be considered a combined operating condition of cooling the power battery and the passenger compartment at room temperature. The ambient temperature can be determined based on a thermometer or received ambient temperature data.

[0172] like Figure 7 As shown, in the sixth operating condition, the refrigerant pump flow path f2 (indicated by the thin-lined rectangular frame) and the evaporator flow path f4 are connected through the first multi-way valve 61 and the second multi-way valve 62 to form a cooling circuit. The compression condensation flow path f1 (indicated by the thin-lined rectangular frame) and the power battery heat exchange flow path f3 are connected through the first multi-way valve 61 and the second multi-way valve 62 to form a compression refrigeration circuit.

[0173] As can be seen, opening the fifth solenoid valve 23 in the refrigerant pump flow path f2 and starting the refrigerant pump 21 allows the refrigerant in the refrigerant pump flow path f2 to flow through the second one-way valve 24 to the first multi-way valve 61, and then through the first multi-way valve 61 into the condenser 13. The refrigerant flowing out of the condenser 13 then flows through the first multi-way valve 61 into the evaporator flow path f4. The refrigerant flowing into the evaporator flow path f4 passes through the second solenoid valve 43 and the evaporator 41 to the second multi-way valve 62, then returns to the refrigerant pump flow path f2, and then returns to the refrigerant pump 21 through the fifth solenoid valve 23 and the liquid receiver 22.

[0174] When compressor 11 is turned on, the discharged refrigerant flows sequentially through oil separator 112, first one-way valve 111, and first three-way valve 15 to condenser 13. The refrigerant flowing from condenser 13 flows to first multi-way valve 61, and then into power battery heat exchange path f3. The refrigerant flowing into power battery heat exchange path f3 is split by third three-way valve 37 and exchanges heat with power batteries b1 and b2 in two power battery heat exchange components 31 and 32, respectively. The refrigerant after heat exchange merges through fourth three-way valve 38 and flows into second multi-way valve 62, then returns to compression-condensation path f1. The refrigerant flowing from second multi-way valve 62 sequentially passes through gas-liquid separator 18, fourth solenoid valve 17, and second three-way valve 16 back to compressor 11.

[0175] For cooling of the power battery and passenger compartment at normal temperature, a refrigerant pump 21 is used in conjunction with some compressors to circulate the refrigerant. At this time, it is not necessary to start all compressors, thereby reducing system energy consumption while meeting the cooling needs of the power battery and passenger compartment.

[0176] refer to Figure 1 and Figure 7In some embodiments, the evaporator assembly includes an evaporator 41 and an evaporator fan 42, the first control valve group includes a first solenoid valve 33, 34 and a first electronic expansion valve 35, 36 connected in parallel, the second control valve group includes a second solenoid valve 43 and a second electronic expansion valve 44 connected in parallel, and the evaporator fan 42 is signal-connected to the thermal management controller 63.

[0177] Accordingly, the thermal management controller 63 is configured to: in the sixth operating condition, close the first solenoid valves 33 and 34, adjust the opening of the first electronic expansion valves 35 and 36 according to the target superheat of the power battery heat exchange components 31 and 32, adjust the speed of the partial compressor (e.g., compressor 11) according to the target evaporation temperature of the power battery heat exchange components 31 and 32, open the second solenoid valve 43, and adjust the speed of the refrigerant pump 21 and / or the gear of the evaporator fan 42 according to the target evaporation temperature of the evaporator 41.

[0178] In the sixth operating condition, closing the first solenoid valve allows the refrigerant to flow through the first electronic expansion valve, which is connected in parallel with the first solenoid valve, and to be throttled by the first electronic expansion valve. At this time, the first electronic expansion valve acts as a throttling device in the compression refrigeration circuit to reduce the pressure of the refrigerant. Correspondingly, the refrigerant passing through the first electronic expansion valve will evaporate and absorb heat in the power battery heat exchanger, which acts as an evaporator, thereby reducing the temperature of the power battery.

[0179] For example, the first electronic expansion valves 35 and 36 can perform an initialization process at the start of the sixth operating condition, being set to an initial opening of Step1. Subsequently, they are adjusted according to the target superheat TEXV. This is achieved by calculating whether the absolute value of the difference between the actual superheat and the target superheat of the power battery heat exchangers 31 and 32 does not exceed a threshold (e.g., 0.5). If it does not exceed this threshold, the first electronic expansion valves 35 and 36 are kept at their initial opening without adjustment; otherwise, they are adjusted based on this absolute value of the difference. Furthermore, the rotational speed of the partial compressor (e.g., compressor 11) is adjusted according to the target evaporation temperature of the power battery heat exchangers 31 and 32.

[0180] In the sixth operating condition, the second solenoid valve 43 is opened, and the speed of the refrigerant pump 21 can be adjusted according to the target evaporation temperature of the evaporator 41, the speed of the evaporator fan 42 can be adjusted according to the target evaporation temperature of the evaporator 41, or both the speed of the refrigerant pump 21 and the speed of the evaporator fan 42 can be adjusted according to the target evaporation temperature of the evaporator 41.

[0181] refer to Figure 1 and Figure 7In some embodiments, the condenser assembly includes a condenser 13 and a condenser fan 14, the condenser fan 14 being signal-connected to the thermal management controller 63. The thermal management controller 63 is configured to adjust the rotational speed of the condenser fan 14 based on the discharge pressure of the started compressor. For a started compressor, such as compressor 11, the rotational speed of the condenser fan 14 can be adjusted for different discharge pressures of compressor 11 to maintain the condensing temperature / pressure within an optimal range, thereby effectively balancing energy consumption and performance.

[0182] Figure 8 This is a schematic diagram of the control relationship under the seventh operating condition according to an embodiment of the mining machinery thermal management system of this disclosure. (Reference) Figure 8 In some embodiments, the thermal management controller 63 is configured to: in a seventh operating condition where the ambient temperature is in the second range and cooling of the power batteries b1, b2 and the passenger compartment is required, connect the compression condensation flow path f1 with the power battery heat exchange flow path f3 and the evaporator flow path f4 through the first multi-way valve 61 and the second multi-way valve 62 to form a compression refrigeration circuit including two branch flow paths, the power battery heat exchange flow path f3 and the evaporator flow path f4, and start all compressors in the at least two compressors 11, 12 to drive the refrigerant in the compression refrigeration circuit, wherein the minimum value of the second range is greater than or equal to the maximum value of the first range.

[0183] As mentioned earlier, the first temperature range can be 10℃ to 30℃. The minimum value of the second temperature range can be set to be greater than or equal to the maximum value of the first temperature range, such as 30℃, 31℃, 32℃, 35℃, or 40℃. The maximum value of the second temperature range can be set as needed, such as 45℃, 50℃, or 60℃. For the second temperature range, the second operating condition actually refers to a condition where both the power battery and the passenger compartment are cooled at high temperatures. In this case, all compressors in the parallel compressor assembly are used in conjunction with the condenser to form a compression refrigeration circuit containing two branch flow paths: the power battery heat exchange flow path f3 and the evaporator flow path f4. Starting all compressors provides the cooling capacity required for cooling the power battery and passenger compartment under high-temperature conditions.

[0184] like Figure 8 As shown, compressors 11 and 12 in the compression-condensation flow path f1 are both started. The two refrigerants are combined through the first three-way valve 15 and enter the condenser 13. Then, they are split into two paths through the first multi-way valve 61 and enter the power battery heat exchange flow path f3 and the evaporator flow path f4 respectively. After being combined through the second multi-way valve 62, they return to the compression-condensation flow path f1.

[0185] refer to Figure 8In some embodiments, the evaporator assembly includes an evaporator 41, the first control valve group includes a first solenoid valve 33, 34 and a first electronic expansion valve 35, 36 connected in parallel, and the second control valve group includes a second solenoid valve 43 and a second electronic expansion valve 44 connected in parallel. Accordingly, the thermal management controller 63 is configured to: close the first solenoid valve 33, 34 and the second solenoid valve 43 in the seventh operating condition; adjust the opening of the first electronic expansion valve 35, 36 and the second electronic expansion valve 44 according to the target superheat of the power battery heat exchangers 31, 32 and the evaporator 41, respectively; and adjust the speed of all compressors 11, 12 according to the target evaporation temperature of the evaporator 41 and the power battery heat exchangers 31, 32.

[0186] In the seventh operating condition, closing the first solenoid valve and the second solenoid valve 42 allows the refrigerant to flow through the first electronic expansion valve (connected in parallel with the first solenoid valve) and the second electronic expansion valve 43 (connected in parallel with the second solenoid valve 42), and is subject to throttling control by the first and second electronic expansion valves 43 respectively. At this time, the first and second electronic expansion valves 43 act as throttling devices in the compression refrigeration circuit to reduce the pressure of the refrigerant. Correspondingly, the refrigerant passing through the first and second electronic expansion valves 43 will evaporate and absorb heat in the power battery heat exchanger (which acts as an evaporator) and the evaporator 41 respectively, thereby reducing the temperature of the power battery and the passenger compartment.

[0187] The opening control of the first electronic expansion valves 35 and 36 and the second electronic expansion valve 44, as well as the speed regulation of the compressors 11 and 12, can be referred to the simple operating conditions under high temperature mentioned above, and will not be repeated here.

[0188] Figure 9 This is a schematic diagram of the control relationship under the eighth operating condition according to an embodiment of the mining machinery thermal management system of this disclosure. (Reference) Figure 9 In some embodiments, the thermal management system for mining machinery further includes a converter flow path f5. The converter flow path f5 includes a converter heat exchanger 51 for heat exchange of the DC-DC converter dd of the mining machinery and a third control valve group connected in series with the converter heat exchanger 51, wherein the DC-DC converter dd is used to realize the DC voltage conversion between the power batteries b1 and b2 and the low-voltage electrical system of the mining machinery.

[0189] Accordingly, the thermal management controller 63 is configured to: in the eighth operating condition where the ambient temperature is in the second range and cooling of the power batteries b1 and b2, the passenger compartment, and the DC-DC converter dd is required, connect the compression condensation flow path f1 with the power battery heat exchange flow path f3, the evaporator flow path f4, and the converter flow path f5 through the first multi-way valve 61 and the second multi-way valve 62 to form a compression refrigeration circuit including the power battery heat exchange flow path f3, the evaporator flow path f4, and the converter flow path f5, and start all the compressors in the at least two compressors 11 and 12 to drive the refrigerant in the compression refrigeration circuit, wherein the minimum value of the second range is greater than or equal to the maximum value of the first range.

[0190] and Figure 8 The illustrated embodiment is similar; all compressors are activated to generate cooling capacity, and the refrigerant output from the compression condensation path f1 is branched through the first multi-way valve 61 to three branch paths: the power battery heat exchange path f3, the evaporator path f4, and the converter path f5. It then merges again via the second multi-way valve 62 and returns to the compression condensation path f1. In this way, by activating all compressors, the required cooling capacity for the power battery, passenger compartment, and DC-DC converter dd under high-temperature conditions is provided.

[0191] refer to Figure 9 In some embodiments, the evaporator assembly includes an evaporator 41, the first control valve group includes a first solenoid valve 33, 34 and a first electronic expansion valve 35, 36 connected in parallel, the second control valve group includes a second solenoid valve 43 and a second electronic expansion valve 44 connected in parallel, and the third control valve group includes a third solenoid valve 52 and a third electronic expansion valve 53 connected in parallel.

[0192] Accordingly, the thermal management controller 63 is configured to: in the eighth operating condition, close the first solenoid valves 33 and 34, the second solenoid valve 43 and the third solenoid valve 52, and adjust the opening of the first electronic expansion valves 35 and 36, the second electronic expansion valve 44 and the third electronic expansion valve 53 according to the target superheat of the power battery heat exchanger 31 and 32, the evaporator 41 and the converter heat exchanger 51, respectively; and adjust the speed of all compressors according to the target evaporation temperature of the evaporator 41, the power battery heat exchanger 31 and 32 and the converter heat exchanger 51.

[0193] In the eighth operating condition, closing the first solenoid valve, the second solenoid valve 42, and the third solenoid valve 52 allows the refrigerant to flow through the first electronic expansion valve, the second electronic expansion valve 43, and the third solenoid valve 52, and be subject to throttling control by these valves respectively. At this time, the first electronic expansion valve, the second electronic expansion valve 43, and the third solenoid valve 52 act as throttling devices in the compression refrigeration circuit to reduce the pressure of the refrigerant. Correspondingly, the refrigerant passing through the first electronic expansion valve, the second electronic expansion valve 43, and the third solenoid valve 52 will evaporate and absorb heat in the power battery heat exchanger (which acts as an evaporator), the evaporator 41, and the converter heat exchanger 51 (which also acts as an evaporator), thereby reducing the temperature of the power battery, the passenger compartment, and the DC-DC converter.

[0194] The opening control of the first electronic expansion valves 35 and 36, the second electronic expansion valve 44 and the third solenoid valve 52, as well as the speed regulation of the compressors 11 and 12, can be referred to the simple operating conditions under high temperature mentioned above, and will not be repeated here.

[0195] Figure 10 This is a flowchart illustrating some embodiments of the control method according to this disclosure. These embodiments of the control method are applicable to any of the above-described embodiments of the mining machinery thermal management system. Reference Figure 10 This disclosure provides a control method for a thermal management system of mining machinery according to any of the foregoing embodiments. The control method includes steps S1 and S2. Each step in the control method can be implemented by executing instructions from the thermal management controller.

[0196] In step S1, the current operating condition is determined.

[0197] In step S2, the thermal management controller 63 controls at least some of the parallel compressor assembly, the condenser assembly, the refrigerant pump 21, the first control valve group, the evaporator assembly, the second control valve group, the first multi-way valve 61, and the second multi-way valve 62 to form a refrigerant circulation loop corresponding to the current operating condition.

[0198] The mining machinery thermal management system and its control method described in the foregoing embodiments can achieve at least one of the following technical effects.

[0199] The parallel operation of the compressor and the refrigerant pump drive allow for start-stop and output adjustment based on actual load requirements and environmental conditions. Combined with direct refrigerant cooling technology, this reduces energy transfer losses, improves the overall system efficiency ratio (COP), and lowers the energy consumption of mining equipment. This reduces heat exchange losses and response delays in traditional indirect cooling systems, addressing the energy efficiency reduction and slow response caused by secondary heat exchange in existing indirect cooling systems. This enables the system to effectively cope with the transient and severe thermal shocks generated during the operation of mining machinery.

[0200] The parallel compressor design provides redundancy and backup capabilities. When a single compressor fails, the remaining compressors can still maintain basic system operation (or derating operation), improving system reliability and operational continuity. This enhances the system's reliability and environmental adaptability in high-temperature environments, overcomes the weakness of existing single-compressor systems lacking redundancy, and solves the problem of the entire thermal management system failing due to a single compressor failure. It also improves the reliability and operational continuity of thermal management for key equipment in the mining area. The system architecture, combining "parallel compressor direct refrigerant cooling" with "room-temperature refrigerant pump drive," effectively reduces energy consumption under normal temperature conditions and improves system energy efficiency.

[0201] Designed specifically for the characteristics of high-temperature mining areas, this system utilizes parallel compressor operation and direct refrigerant cooling cycle technology to enhance its cooling capacity under extreme high-temperature conditions. This addresses the critical issue of severe performance degradation or even failure in traditional systems at high temperatures, improving the system's adaptability to high-temperature environments. This solves the problem of insufficient cooling capacity in existing single-compressor systems under extreme high-temperature mining conditions, overcomes the shortcomings of existing single-compressor systems in meeting the continuous, high-intensity heat dissipation requirements of heavy-duty equipment, and prevents frequent equipment shutdowns due to overheating.

[0202] This specification describes multiple embodiments in a progressive manner, with each embodiment having a different focus. Similar or identical parts between embodiments can be referred to interchangeably. For method embodiments, since their overall structure and involved steps correspond to the content in system embodiments, the description is relatively simple; relevant parts can be referred to in the descriptions of the system embodiments.

[0203] The embodiments of this disclosure have now been described in detail. To avoid obscuring the concept of this disclosure, some details known in the art have not been described. Those skilled in the art can fully understand how to implement the technical solutions disclosed herein based on the above description.

[0204] While specific embodiments of this disclosure have been described in detail by way of examples, those skilled in the art should understand that the examples are for illustrative purposes only and not intended to limit the scope of this disclosure. Those skilled in the art should understand that modifications can be made to the above embodiments or equivalent substitutions can be made to some technical features without departing from the scope and spirit of this disclosure. The scope of this disclosure is defined by the appended claims.

Claims

1. A thermal management system for mining machinery, characterized in that, include: The compression condensation flow path (f1) includes a parallel compressor assembly and a condenser assembly connected in series with the parallel compressor assembly; The refrigerant pump flow path (f2) includes the refrigerant pump (21). The power battery heat exchange flow path (f3) includes a power battery heat exchange component (31; 32) for heat exchange of the power battery (b1; b2) of the mining machinery and a first control valve group connected in series with the power battery heat exchange component (31; 32); The evaporator flow path (f4) includes an evaporator assembly for cooling the crew compartment of the mining machinery and a second control valve group connected in series with the evaporator assembly; The first multi-way valve (61) is connected to the first end of the compression condensation flow path (f1), the first end of the refrigerant pump flow path (f2), the first end of the power battery heat exchange flow path (f3), and the first end of the evaporator flow path (f4), and is configured to control the on / off relationship between each of the first ends; The second multi-way valve (62) is connected to the second end of the compression condensation flow path (f1), the second end of the refrigerant pump flow path (f2), the second end of the power battery heat exchange flow path (f3), and the second end of the evaporator flow path (f4), and is configured to control the on / off relationship between each of the second ends; and The thermal management controller (63) is signal-connected to the parallel compressor assembly, the condenser assembly, the refrigerant pump (21), the first control valve group, the evaporator assembly, the second control valve group, the first multi-way valve (61), and the second multi-way valve (62), and is configured to form a corresponding refrigerant circulation loop according to different operating conditions.

2. The mining machinery thermal management system according to claim 1, characterized in that, The thermal management controller (63) is configured to: In the first operating condition where the ambient temperature is in the first range and the power battery (b1; b2) needs to be cooled, the refrigerant pump flow path (f2) and the power battery heat exchange flow path (f3) are connected through the first multi-way valve (61) and the second multi-way valve (62) to form a cooling circuit, and the refrigerant pump (21) is started to drive the refrigerant in the cooling circuit.

3. The mining machinery thermal management system according to claim 2, characterized in that, The thermal management controller (63) is configured to: When the ambient temperature is within the first range and the temperature of the power battery (b1; b2) exceeds the upper limit threshold of the preset temperature range, it is determined that the power battery (b1; b2) needs to be cooled. After the refrigerant pump (21) is started, when the refrigerant temperature in the power battery heat exchanger (31; 32) is lower than the lower limit threshold of the preset temperature range, the speed of the refrigerant pump (21) is gradually reduced.

4. The mining machinery thermal management system according to claim 2, characterized in that, The condenser assembly includes a condenser (13) and a condenser fan (14), the condenser fan (14) being signal-connected to the thermal management controller (63); the thermal management controller (63) is configured to: Under the first operating condition, the rotation speed of the condenser fan (14) is adjusted according to the target temperature of the power battery heat exchanger (31; 32).

5. The mining machinery thermal management system according to claim 2, characterized in that, The parallel compressor assembly includes at least two parallel compression flow paths (f11; f12) and at least two compressors (11; 12) respectively located in the at least two compression flow paths (f11; f12); wherein the thermal management controller (63) is configured to: In the second operating condition where the ambient temperature is in the second range and the power battery (b1; b2) needs to be cooled, the compression condensation flow path (f1) and the power battery heat exchange flow path (f3) are connected through the first multi-way valve (61) and the second multi-way valve (62) to form a compression refrigeration circuit, and some of the compressors (11; 12) of the at least two compressors (11; 12) are started to drive the refrigerant in the compression refrigeration circuit, wherein the minimum value of the second range is greater than or equal to the maximum value of the first range.

6. The mining machinery thermal management system according to claim 5, characterized in that, The first control valve assembly includes a first solenoid valve (33; 34) and a first electronic expansion valve (35; 36) connected in parallel; the thermal management controller (63) is configured to: Under the first operating condition, the first solenoid valve (33; 34) is opened. In the second operating condition, the first solenoid valve (33; 34) is closed, and the opening of the first electronic expansion valve (35; 36) is adjusted according to the target superheat of the power battery heat exchanger (31; 32).

7. The mining machinery thermal management system according to claim 5, characterized in that, The thermal management controller (63) is configured to: In the second operating condition, the rotational speed of the partial compressor (11; 12) is adjusted according to the target evaporation temperature of the power battery heat exchanger (31; 32).

8. The thermal management system for mining machinery according to claim 1, characterized in that, The thermal management controller (63) is configured to: In the third operating condition where the ambient temperature is in the first range and the crew compartment of the mining machinery needs to be cooled, the refrigerant pump flow path (f2) and the evaporator flow path (f4) are connected through the first multi-way valve (61) and the second multi-way valve (62) to form a cooling circuit, and the refrigerant pump (21) is started to drive the refrigerant in the cooling circuit.

9. The thermal management system for mining machinery according to claim 8, characterized in that, The evaporator assembly includes an evaporator (41); the thermal management controller (63) is configured to: In the third operating condition, the speed of the refrigerant pump (21) is adjusted according to the target evaporation temperature of the evaporator (41).

10. The thermal management system for mining machinery according to claim 9, characterized in that, The evaporator assembly also includes an evaporator fan (42) that is signal-connected to the thermal management controller (63); the thermal management controller (63) is configured to: In the third operating condition, the speed of the evaporation fan (42) is adjusted according to the target evaporation temperature of the evaporator (41).

11. The thermal management system for mining machinery according to claim 8, characterized in that, The parallel compressor assembly includes at least two parallel compression paths (f11; f12) and at least two compressors (11; 12) respectively located in the at least two compression paths (f11; f12); the thermal management controller (63) is configured to: In the fourth operating condition where the ambient temperature is in the second range and the crew compartment of the mining machinery needs to be refrigerated, the compression condensation flow path (f1) and the evaporator flow path (f4) are connected through the first multi-way valve (61) and the second multi-way valve (62) to form a compression refrigeration circuit, and some of the at least two compressors (11; 12) are started to drive the refrigerant in the compression refrigeration circuit, wherein the minimum value of the second range is greater than or equal to the maximum value of the first range.

12. The mining machinery thermal management system according to claim 11, characterized in that, The evaporator assembly includes an evaporator (41), and the second control valve group includes a second solenoid valve (43) and a second electronic expansion valve (44) connected in parallel; the thermal management controller (63) is configured to: In the third operating condition, the second solenoid valve (43) is opened. In the fourth operating condition, the second solenoid valve (43) is closed, and the opening of the second electronic expansion valve (44) is adjusted according to the target superheat of the evaporator (41).

13. The thermal management system for mining machinery according to claim 12, characterized in that, The thermal management controller (63) is configured to: In the fourth operating condition, the rotational speed of the partial compressors (11; 12) is adjusted according to the target evaporation temperature of the evaporator (41).

14. The thermal management system for mining machinery according to claim 1, characterized in that, Also includes: The converter flow path (f5) includes a converter heat exchanger (51) for heat exchange of the DC-DC converter (dd) of the mining machinery and a third control valve group connected in series with the converter heat exchanger (51), wherein the DC-DC converter (dd) is used to realize the DC voltage conversion between the power battery (b1; b2) and the low-voltage electrical system of the mining machinery; The parallel compressor assembly includes at least two parallel compression flow paths (f11; f12) and at least two compressors (11; 12) respectively located in the at least two compression flow paths (f11; f12); the thermal management controller (63) is configured to: In the fifth operating condition where the DC-DC converter (dd) needs to be cooled, the compression condensation flow path (f1) and the converter flow path (f5) are connected through the first multi-way valve (61) and the second multi-way valve (62) to form a compression refrigeration circuit, and some of the compressors (11; 12) of the at least two compressors (11; 12) are started to drive the refrigerant in the compression refrigeration circuit.

15. The thermal management system for mining machinery according to claim 14, characterized in that, The third control valve group includes a third solenoid valve (52) and a third electronic expansion valve (53) connected in parallel; the thermal management controller (63) is configured to: In the fifth operating condition, the third solenoid valve (52) is closed, and the opening of the third electronic expansion valve (53) is adjusted according to the target superheat of the converter heat exchanger (51).

16. The thermal management system for mining machinery according to claim 15, characterized in that, The thermal management controller (63) is configured to: In the fifth operating condition, the rotational speed of the partial compressor (11; 12) is adjusted according to the target evaporation temperature of the converter heat exchanger (51).

17. The thermal management system for mining machinery according to claim 1, characterized in that, The parallel compressor assembly includes at least two parallel compression paths (f11; f12) and at least two compressors (11; 12) respectively located in the at least two compression paths (f11; f12); the thermal management controller (63) is configured to: In the sixth operating condition, where the ambient temperature is in the first range and the power battery (b1; b2) and the passenger compartment need to be cooled, the refrigerant pump flow path (f2) and the evaporator flow path (f4) are connected through the first multi-way valve (61) and the second multi-way valve (62) to form a cooling circuit, and the refrigerant pump (21) is started to drive the refrigerant in the cooling circuit. The compression condensation flow path (f1) and the power battery heat exchange flow path (f3) are connected through the first multi-way valve (61) and the second multi-way valve (62) to form a compression refrigeration circuit, and some of the compressors (11; 12) of the at least two compressors (11; 12) are started to drive the refrigerant in the compression refrigeration circuit.

18. The thermal management system for mining machinery according to claim 17, characterized in that, The evaporator assembly includes an evaporator (41) and an evaporator fan (42). The first control valve group includes a first solenoid valve (33; 34) and a first electronic expansion valve (35; 36) connected in parallel. The second control valve group includes a second solenoid valve (43) and a second electronic expansion valve (44) connected in parallel. The evaporator fan (42) is signal-connected to the thermal management controller (63). The thermal management controller (63) is configured to: In the sixth operating condition, the first solenoid valve (33; 34) is closed, the opening of the first electronic expansion valve (35; 36) is adjusted according to the target superheat of the power battery heat exchanger (31; 32), the speed of the partial compressor (11; 12) is adjusted according to the target evaporation temperature of the power battery heat exchanger (31; 32), the second solenoid valve (43) is opened, and the speed of the refrigerant pump (21) and / or the gear of the evaporator fan (42) are adjusted according to the target evaporation temperature of the evaporator (41).

19. The thermal management system for mining machinery according to claim 17, characterized in that, The thermal management controller (63) is configured to: In the seventh operating condition where the ambient temperature is in the second range and the power battery (b1; b2) and the passenger compartment need to be cooled, the compression condensation flow path (f1) is connected to the power battery heat exchange flow path (f3) and the evaporator flow path (f4) through the first multi-way valve (61) and the second multi-way valve (62) to form a compression refrigeration circuit including two branch flow paths: the power battery heat exchange flow path (f3) and the evaporator flow path (f4). All compressors (11; 12) of the at least two compressors (11; 12) are started to drive the refrigerant in the compression refrigeration circuit, wherein the minimum value of the second range is greater than or equal to the maximum value of the first range.

20. The thermal management system for mining machinery according to claim 19, characterized in that, The evaporator assembly includes an evaporator (41), the first control valve group includes a first solenoid valve (33; 34) and a first electronic expansion valve (35; 36) connected in parallel, and the second control valve group includes a second solenoid valve (43) and a second electronic expansion valve (44) connected in parallel; the thermal management controller (63) is configured to: In the seventh operating condition, the first solenoid valve (33; 34) and the second solenoid valve (43) are closed, and the opening of the first electronic expansion valve (35; 36) and the second electronic expansion valve (44) are adjusted according to the target superheat of the power battery heat exchanger (31; 32) and the evaporator (41), respectively. The speed of all compressors (11; 12) is adjusted according to the target evaporation temperature of the evaporator (41) and the power battery heat exchanger (31; 32).

21. The thermal management system for mining machinery according to claim 17, characterized in that, Also includes: The converter flow path (f5) includes a converter heat exchanger (51) for heat exchange of the DC-DC converter (dd) of the mining machinery and a third control valve group connected in series with the converter heat exchanger (51), wherein the DC-DC converter (dd) is used to realize the DC voltage conversion between the power battery (b1; b2) and the low-voltage electrical system of the mining machinery; The thermal management controller (63) is configured as follows: In the eighth operating condition, where the ambient temperature is in the second range and the power battery (b1; b2), the passenger compartment, and the DC-DC converter (dd) need to be cooled, the compression condensation flow path (f1) is connected to the power battery heat exchange flow path (f3), the evaporator flow path (f4), and the converter flow path (f5) through the first multi-way valve (61) and the second multi-way valve (62) to form a compression refrigeration circuit containing three branch flow paths: the power battery heat exchange flow path (f3), the evaporator flow path (f4), and the converter flow path (f5). All compressors (11; 12) of the at least two compressors (11; 12) are started to drive the refrigerant in the compression refrigeration circuit, wherein the minimum value of the second range is greater than or equal to the maximum value of the first range.

22. The thermal management system for mining machinery according to claim 21, characterized in that, The evaporator assembly includes an evaporator (41), the first control valve group includes a first solenoid valve (33; 34) and a first electronic expansion valve (35; 36) connected in parallel, the second control valve group includes a second solenoid valve (43) and a second electronic expansion valve (44) connected in parallel, and the third control valve group includes a third solenoid valve (52) and a third electronic expansion valve (53) connected in parallel; the thermal management controller (63) is configured to: In the eighth operating condition, the first solenoid valve (33; 34), the second solenoid valve (43), and the third solenoid valve (52) are closed, and the opening of the first electronic expansion valve (35; 36), the second electronic expansion valve (44), and the third electronic expansion valve (53) are adjusted according to the target superheat of the power battery heat exchanger (31; 32), the evaporator (41), and the converter heat exchanger (51), respectively. The speed of all compressors (11; 12) is adjusted according to the target evaporation temperature of the evaporator (41), the power battery heat exchanger (31; 32), and the converter heat exchanger (51).

23. The thermal management system for mining machinery according to claim 5, 11, 14 or 17, characterized in that, The condenser assembly includes a condenser (13) and a condenser fan (14), the condenser fan (14) being signal-connected to the thermal management controller (63); the thermal management controller (63) is configured to: The rotational speed of the condenser fan (14) is adjusted according to the exhaust pressure of the compressor (11; 12) that is started.

24. A control method for a thermal management system for mining machinery according to any one of claims 1-23, characterized in that, include: Determine the current operating conditions; By controlling at least a portion of the parallel compressor assembly, the condenser assembly, the refrigerant pump (21), the first control valve group, the evaporator assembly, the second control valve group, the first multi-way valve (61), and the second multi-way valve (62) through the thermal management controller (63), a refrigerant circulation loop corresponding to the current operating condition is formed.

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