Vehicle-mounted refrigerating system, control method, computer equipment and storage medium

Abstract

The invention relates to the field of vehicle-mounted refrigerating systems, and discloses a vehicle-mounted refrigerating system, a control method, computer equipment and a storage medium, the vehicle-mounted refrigerating system comprises at least two refrigerating branches, and at least one refrigerating branch is controlled by an electromagnetic valve; when the vehicle-mounted refrigerating system is in a running state and the electromagnetic valve receives an on-off state change request, the control method comprises the steps that a compressor is shut down, and the high pressure of the system is obtained; when the high pressure of the system is smaller than the specified pressure threshold value or the waiting time of the electromagnetic valve reaches the first time, the on-off state of the electromagnetic valve is changed; when the high pressure of the system is smaller than a specified pressure threshold value or the shutdown time of the compressor reaches second time, the compressor is started, and the compressor is adjusted to a specified rotating speed; the first time is less than or equal to the second time. The pressure difference between the two sides of the electromagnetic valve can be reduced, and actuation sound generated by opening and closing the electromagnetic valve is reduced.

Description

Technical Field

[0001] This invention relates to the field of vehicle-mounted refrigeration systems, and more particularly to a vehicle-mounted refrigeration system, control method, computer equipment, and storage medium. Background Technology

[0002] In the thermal management system of new energy vehicles, the intelligence and efficiency of the refrigeration system are key factors in ensuring vehicle performance and passenger comfort. With the development of technology, the on-board refrigeration system not only needs to provide a suitable temperature environment for the passenger compartment, but also needs to effectively manage the temperature of the battery pack to maintain optimal battery efficiency and extend its service life.

[0003] When the battery pack is cooling, the passenger compartment activates the cooling request. If the cooling system pressure is high, the solenoid valve will make a valve noise as it opens from closed. When both the passenger compartment and the battery pack are cooling, the passenger compartment deactivates the cooling request. If the cooling system pressure is high, the solenoid valve will make a valve noise as it opens from closed. Summary of the Invention

[0004] Therefore, it is necessary to provide an in-vehicle refrigeration system, control method, computer equipment, and storage medium to address the aforementioned technical problems and solve the issue of solenoid valves generating operating noise in in-vehicle refrigeration systems.

[0005] A method for controlling an on-board refrigeration system, wherein the on-board refrigeration system includes at least two refrigeration branches, and at least one of the refrigeration branches is controlled by a solenoid valve;

[0006] When the vehicle-mounted cooling system is in operation and the solenoid valve receives a request to change its open / closed state, the control method includes:

[0007] The compressor stops and the system high pressure is obtained;

[0008] When the system high pressure is less than the specified pressure threshold, or when the waiting time of the solenoid valve reaches the first time, the opening and closing state of the solenoid valve is changed.

[0009] When the system high pressure is less than the specified pressure threshold, or the compressor downtime reaches the second time, the compressor is started and adjusted to the specified speed; the first time is less than or equal to the second time.

[0010] An on-board cooling system, comprising:

[0011] The vehicle-mounted refrigeration system includes at least two refrigeration branches, and at least one of the refrigeration branches is controlled by a solenoid valve.

[0012] When the vehicle-mounted cooling system is in operation and the solenoid valve receives a request to change its open / closed state, the vehicle-mounted cooling system performs the following steps:

[0013] The compressor stops and the system high pressure is obtained;

[0014] When the system high pressure is less than the specified pressure threshold, or when the waiting time of the solenoid valve reaches the first time, the opening and closing state of the solenoid valve is changed.

[0015] When the system high pressure is less than the specified pressure threshold, or the compressor downtime reaches the second time, the compressor is started and adjusted to the specified speed; the first time is less than or equal to the second time.

[0016] A computer device includes a memory, a processor, and computer-readable instructions stored in the memory and executable on the processor, wherein the processor implements the above-described vehicle-mounted refrigeration system control method when executing the computer-readable instructions.

[0017] One or more readable storage media storing computer-readable instructions, which, when executed by one or more processors, cause the one or more processors to perform the vehicle refrigeration system control method described above.

[0018] In the aforementioned vehicle-mounted refrigeration system, control method, computer equipment, and storage medium, when the system high pressure is less than the pressure threshold, or the solenoid valve's waiting time reaches the first time, the opening and closing state of the solenoid valve is changed; when the system high pressure is less than the pressure threshold, or the compressor's shutdown time reaches the second time, the compressor is started and adjusted to a specified speed; if the first time is less than or equal to the second time, the pressure difference across the solenoid valve can be reduced, thus reducing the operating noise generated by opening and closing the solenoid valve. Attached Figure Description

[0019] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the description of the embodiments of the present invention will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0020] Figure 1 This is a schematic diagram of a vehicle-mounted refrigeration system according to an embodiment of the present invention;

[0021] Figure 2 This is a flowchart illustrating a vehicle-mounted refrigeration system control method according to an embodiment of the present invention;

[0022] Figure 3This is a schematic diagram of a computer device according to an embodiment of the present invention. Detailed Implementation

[0023] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0024] In one embodiment, such as Figure 1 and 2 As shown, a method for controlling an on-board refrigeration system is provided. The on-board refrigeration system includes at least two refrigeration branches, and at least one of the refrigeration branches is controlled by a solenoid valve.

[0025] When the vehicle-mounted cooling system is in operation and the solenoid valve receives a request to change its open / closed state, the control method includes:

[0026] S10. The compressor stops and the system high pressure is obtained;

[0027] S20. When the high pressure of the system is less than the specified pressure threshold, or when the waiting time of the solenoid valve reaches the first time, change the opening and closing state of the solenoid valve.

[0028] S30. When the system high pressure is less than the specified pressure threshold, or the compressor downtime reaches the second time, start the compressor and adjust the compressor to the specified speed; the first time is less than or equal to the second time.

[0029] Understandably, the vehicle cooling system includes at least two cooling branches, and at least one cooling branch is controlled by a solenoid valve. Figure 2 In the example, the vehicle-mounted refrigeration system includes three refrigeration branches: a first refrigeration branch for cooling the front evaporator, a second refrigeration branch for cooling the rear evaporator, and a third refrigeration branch for cooling the battery cold plate. The main circuit of the vehicle-mounted refrigeration system includes an air-cooled condenser and a compressor. The air-cooled condenser is located at the compressor's outlet side, and a high-pressure sensor P is installed between the air-cooled condenser and the compressor to measure the system's high-pressure. A low-pressure temperature sensor and a low-pressure sensor are installed at the compressor's inlet side. The first and second refrigeration branches are controlled by solenoid valves, while the third refrigeration branch is controlled by an electronic expansion valve.

[0030] The vehicle cooling system defines several cooling operation modes (SystemCoolMode). Among them, SystemCoolMode=0 when neither the passenger compartment (CabinCoolReq) nor the battery (BatCoolReq) requests cooling; SystemCoolMode=1 when only the passenger compartment requests cooling; SystemCoolMode=2 when only the battery requests cooling; and SystemCoolMode=3 when both the passenger compartment and the battery request cooling.

[0031] Therefore, the vehicle cooling system is in operation, and the solenoid valve receives a request to change its opening and closing status, which can be either SystemCoolMode switching from 2 to 3, or SystemCoolMode switching from 3 to 2.

[0032] In some examples, when the open / closed state change request is an open request, the specified pressure threshold is an open pressure threshold, the first time is a first open time, and the second time is a second open time.

[0033] Understandably, when an open / closed state change request is changed to an open request, that is...

[0034] When SystemCoolMode switches from 2 to 3, the compressor first stops, and the system high-pressure is acquired from the high-pressure sensor P. When the system high-pressure is lower than the opening pressure threshold, or the solenoid valve's waiting time reaches the first opening time, the solenoid valve opens. When the system high-pressure is lower than the opening pressure threshold, or the compressor's shutdown time reaches the second opening time, the compressor starts and is adjusted to the specified speed. Here, the opening pressure threshold, the first opening time, the second opening time, and the specified speed are all empirical values ​​that can be obtained through experimentation. The first opening time is less than or equal to the second opening time; that is, the solenoid valve's opening time is no later than the compressor's opening time. This prevents the solenoid valve from generating excessive system high pressure, which could cause it to make an actuating noise.

[0035] In this embodiment, when the system high pressure is less than the opening pressure threshold, or the waiting time of the solenoid valve reaches the first opening time, the solenoid valve is opened; when the system high pressure is less than the opening pressure threshold, or the compressor shutdown time reaches the second opening time, the compressor is started and adjusted to a specified speed; the first opening time being less than or equal to the second opening time can reduce the pressure difference on both sides of the solenoid valve and reduce the operating noise generated by opening the solenoid valve.

[0036] In some examples, when the open / close state change request is a close request, the specified pressure threshold is a close pressure threshold, the first time is a first close time, and the second time is a second close time.

[0037] Understandably, when an open / close state change request is changed to a close request, that is...

[0038] When SystemCoolMode switches from 3 to 2, the compressor first stops, and the system high-pressure is acquired from the high-pressure sensor P. When the system high-pressure is lower than the shut-off pressure threshold, or the solenoid valve's waiting time reaches the first shut-off time, the solenoid valve closes. When the system high-pressure is lower than the shut-off pressure threshold, or the compressor's shutdown time reaches the second shut-off time, the compressor starts and adjusts to the specified speed. Here, the shut-off pressure threshold, the first shut-off time, the second shut-off time, and the specified speed are all empirical values ​​that can be obtained through experimentation. The first shut-off time is less than or equal to the second shut-off time; that is, the solenoid valve's shut-off time is no later than the compressor's restart time. This prevents the solenoid valve from generating excessive system high pressure, which could cause it to make an actuating noise when shutting down.

[0039] In this embodiment, when the system high pressure is less than the closing pressure threshold, or the waiting time of the solenoid valve reaches the first closing time, the solenoid valve is closed; when the system high pressure is less than the closing pressure threshold, or the compressor shutdown time reaches the second closing time, the compressor is started and adjusted to a specified speed; the first closing time being less than or equal to the second closing time can reduce the pressure difference on both sides of the solenoid valve and reduce the operating noise generated by opening the solenoid valve.

[0040] It is important to note that switching SystemCoolMode from 3 to 2 and switching SystemCoolMode from 2 to 3 are two different operating condition switching methods. Therefore, the first shutdown time and the first startup time are unrelated and need to be calibrated through independent testing. Similarly, the startup pressure threshold, second startup time, and specified speed corresponding to switching SystemCoolMode from 2 to 3 are also unrelated to the shutdown pressure threshold, second shutdown time, and specified speed corresponding to switching SystemCoolMode from 3 to 2, and need to be calibrated through independent testing.

[0041] Optionally, before step S30, i.e. before adjusting the compressor to the specified speed, the following steps are included:

[0042] S301. Determine the specified rotational speed according to the rotational speed calculation formula; the rotational speed calculation formula includes:

[0043] SPD(n) = SPD(n-1) + K p (F(n)-F(n-1))+K i ×F(n)

[0044] Wherein, SPD(n) is the specified rotational speed, which is the result of the nth rotational speed calculation;

[0045] SPD(n-1) is the result of the (n-1)th rotational speed calculation;

[0046] K p This is the proportionality constant in the formula for calculating rotational speed;

[0047] K i This is the integral constant in the formula for calculating rotational speed;

[0048] F(n) is the temperature difference between the cooling component temperature and the target cooling component temperature. This temperature difference is the difference between the cooling component temperature measured in the nth measurement and the target cooling component temperature. The cooling component temperature is the temperature of the cooling component in operation.

[0049] F(n-1)) is the previous value of F(n).

[0050] Understandably, the vehicle cooling system can calculate the specified speed using the aforementioned speed calculation formula. This formula can be used to assess the system's cooling requirements; higher cooling requirements necessitate higher speeds. Specifically, the specified speed SPD(n) is the result of the nth speed calculation by the PI controller (proportional-integral controller), and SPD(n-1) is the result of the (n-1)th speed calculation by the PI controller. The initial value of SPD(n) can be a test value and is related to the cooling mode. For example, when SystemCoolMode = 1, the corresponding speed is found from the first speed lookup table shown in Table 1 using the external temperature TAM and evaporator temperature EvaTemp. When SystemCoolMode = 2, the corresponding speed is found from the second speed lookup table shown in Table 2 using the external temperature TAM and battery cold plate temperature ChillerTemp.

[0051] When SystemCoolMode=3, the target temperature of the evaporator (EvaTargetTemp) and the target temperature of the battery cold plate (ChillerTargetTemp) are compared to determine the rotation speed. The smaller value corresponds to the measured temperature, which is then used to look up the table. Specifically, when the smaller value is the evaporator target temperature, Table 1 is used to determine the initial rotation speed; when the smaller value is the battery cold plate target temperature, Table 2 is used to determine the initial rotation speed.

[0052] Table 1. First Rotation Speed ​​Comparison Table

[0053]

[0054] Table 2 First Rotation Speed ​​Comparison Table

[0055]

[0056] K p K is the proportionality constant in the speed calculation formula. iK is the integral constant in the formula for calculating rotational speed. p and K i All of these are empirical constants.

[0057] In some examples, the cooling components include an evaporator and / or a battery cold plate.

[0058] Specifically, F(n) is the temperature difference between the supplying cooling component temperature and the target supplying cooling component temperature. This temperature difference is the difference between the supplying cooling component temperature measured in the nth time and the target supplying cooling component temperature; the supplying cooling component temperature is the temperature of the supplying cooling component in its operating state. F(n-1)) is the previous value of F(n). The supplying cooling components corresponding to different cooling modes are different. The supplying cooling components include the evaporator and / or battery cold plate. For example... Figure 2 As shown, the evaporator may include a front evaporator and a rear evaporator. For example, when SystemCoolMode=1, the cooling component is the evaporator, then F(n) is the difference between the evaporator temperature EvaTemp and the target evaporator temperature EvaTargetTemp; when SystemCoolMode=2, the cooling component is the battery cold plate, then F(n) is the difference between the battery cold plate temperature ChillerTemp and the battery cold plate target temperature ChillerTargetTemp.

[0059] In some examples, if the cooling components in operation include an evaporator and a battery cold plate, then F(n) is the smaller of the evaporator temperature difference and the battery cold plate temperature difference; wherein, the evaporator temperature difference is the difference between the evaporator temperature and the target evaporator temperature; and the battery cold plate temperature difference is the difference between the battery cold plate temperature and the target battery cold plate temperature.

[0060] Specifically, when SystemCoolMode=3, the target temperature of the evaporator (EvaTargetTemp) and the target temperature of the battery cold plate (ChillerTargetTemp) are compared and selected by taking the smaller value. If the target temperature of the evaporator is smaller, then F(n) is the difference between the evaporator temperature and the target temperature of the evaporator; if the target temperature of the battery cold plate is smaller, then F(n) is the difference between the battery cold plate temperature and the target temperature of the battery cold plate.

[0061] This embodiment provides a method for calculating a specified speed and a specific way to determine the temperature difference value F(n) when calculating the specified speed. The most reasonable speed can be calculated so that the compressor runs at the optimal speed to meet the vehicle cooling requirements.

[0062] Optionally, the control method further includes:

[0063] S40. When there is a refrigeration branch controlled by an electronic expansion valve and the electronic expansion valve is in the open state, adjust the electronic expansion valve to the maximum opening degree.

[0064] S50. When the system high pressure is less than the specified pressure threshold, or when the maximum opening time of the electronic expansion valve is maintained for a longer period than a third time, the electronic expansion valve is adjusted to the specified opening.

[0065] Understandably, different refrigeration circuits may be controlled using different valves. For example, in Figure 2 In the example, the first and second refrigeration branches are both controlled by solenoid valves, while the third refrigeration branch is controlled by an electronic expansion valve. When the refrigeration operation mode changes, if the refrigeration branch controlled by the electronic expansion valve is in operation (i.e., the electronic expansion valve is in the open state), then precise control of the electronic expansion valve is required.

[0066] In some examples, when the open / closed state change request is an open request, the specified pressure threshold is an open pressure threshold, the first time is a first open time, the second time is a second open time, and the third time is a third open time.

[0067] Understandably, when the request to change the on / off state is changed to an on request, that is, when SystemCoolMode switches from 2 to 3, steps S20 and S30 are executed, and steps S40 and S50 are executed in parallel. The electronic expansion valve can be adjusted to its maximum opening degree and maintained for a third opening time. When the system high pressure is less than the opening pressure threshold, or when the electronic expansion valve has been adjusted to its maximum opening degree for the third opening time, the electronic expansion valve is adjusted to a specified opening degree. Here, the opening pressure threshold, the first opening time, the second opening time, the third opening time, and the specified opening degree are all empirical values ​​that can be obtained through experimentation. Among them, the third opening time is less than or equal to the second opening time, that is, the time to adjust the electronic expansion valve to the specified opening degree is no later than the compressor's start-up time. Pre-adjusting the electronic expansion valve opening degree can help achieve a smooth transition during refrigeration system startup, optimize system efficiency, avoid refrigerant liquid slugging, more accurately control the outlet superheat of refrigeration components, and thus adjust the temperature more quickly and accurately; at the same time, it reduces the load surge during compressor startup, which can effectively extend the service life of the compressor and other key components, and reduce maintenance costs and failure rates.

[0068] In some examples, when the open / close state change request is a close request, the specified pressure threshold is a close pressure threshold, the first time is a first close time, the second time is a second close time, and the third time is a third close time.

[0069] Understandably, when the request to change the on / off state is changed to a shutdown request, that is, when SystemCoolMode switches from 3 to 2, steps S20 and S30 are executed, and steps S30 and S40 are executed in parallel. The electronic expansion valve can be adjusted to its maximum opening and maintained for a third closing time. When the system high pressure is less than the shutdown pressure threshold, or when the electronic expansion valve has been adjusted to its maximum opening for the third closing time, the electronic expansion valve is adjusted to a specified opening. Here, the shutdown pressure threshold, the first closing time, the second closing time, the third closing time, and the specified opening are all empirical values ​​that can be obtained through experimentation. Among them, the third closing time is less than or equal to the second closing time, that is, the time to adjust the electronic expansion valve to the specified opening is no later than the compressor's shutdown time. Pre-adjusting the electronic expansion valve opening can help achieve a smooth transition during refrigeration system startup, optimize system efficiency, avoid refrigerant liquid slugging, more accurately control the outlet superheat of refrigeration components, and thus adjust the temperature more quickly and accurately; at the same time, it reduces the load surge during compressor startup, which can effectively extend the service life of the compressor and other key components, and reduce maintenance costs and failure rates.

[0070] Optionally, before step S50, i.e. before adjusting the electronic expansion valve to the specified opening, the following steps are included:

[0071] S503. Determine the specified opening degree according to the opening degree calculation formula; the opening degree calculation formula includes:

[0072] Step(n) = Step(n-1) + L p (E(n)-E(n-1))+L i ×E(n)

[0073] Where Step(n) is the specified opening degree, which is the opening degree calculation result of the nth time;

[0074] Step(n-1) is the result of the opening calculation for the (n-1)th time;

[0075] L p This is the proportional constant in the formula for calculating the opening degree;

[0076] L i This is the integral constant in the formula for calculating the opening degree;

[0077] E(n) is the difference between the current battery-side refrigerant temperature and the refrigerant saturation temperature. This temperature difference is the difference between the battery-side refrigerant temperature and the refrigerant saturation temperature at the nth time.

[0078] E(n-1)) is the difference between the refrigerant temperature and the refrigerant saturation temperature on the battery side in the (n-1)th time.

[0079] Understandably, the vehicle-mounted cooling system can calculate the specified opening degree according to the above opening degree calculation formula. Specifically, the specified opening degree Step(n) is the opening degree calculation result of the PI controller (proportional-integral controller) in the nth time, and Step(n-1) is the speed calculation result of the PI controller in the (n-1)th time.

[0080] L p L is the proportionality constant in the formula for calculating the opening degree. i L is the integral constant in the formula for calculating the opening degree. p and L i All of these are empirical constants.

[0081] E(n) is the difference between the current battery-side refrigerant temperature RefriTemp and the refrigerant saturation temperature RefriSatTemp. This temperature difference is the difference between the battery-side refrigerant temperature and the refrigerant saturation temperature at the nth time. E(n-1)) is the difference between the battery-side refrigerant temperature and the refrigerant saturation temperature at the (n-1)th time.

[0082] This embodiment provides a method for calculating a specified opening degree, which can calculate the most reasonable opening degree of the electronic expansion valve to prevent liquid slugging damage to the compressor.

[0083] Optionally, before step S503, that is, before determining the specified opening degree according to the opening degree calculation formula, the method further includes:

[0084] S501, Obtain the system low-pressure;

[0085] S502. Find the refrigerant saturation temperature corresponding to the low pressure of the system from the refrigerant saturation temperature-pressure comparison table.

[0086] Understandably, the system low-pressure refers to the pressure data collected by the low-pressure sensor located between the outlet side of the refrigeration component (evaporator / cell cooling plate) and the inlet side of the compressor. The system low-pressure is positively correlated with the refrigerant saturation temperature; the higher the system low-pressure, the higher the refrigerant saturation temperature. The corresponding rotational speed can be found in the refrigerant saturation temperature-pressure comparison table shown in Table 3.

[0087] Table 3. Refrigerant Saturation Temperature-Pressure Comparison Table

[0088]

[0089] This embodiment provides a method for determining the refrigerant saturation temperature.

[0090] It should be understood that the sequence number of each step in the above embodiments does not imply the order of execution. The execution order of each process should be determined by its function and internal logic, and should not constitute any limitation on the implementation process of the embodiments of the present invention.

[0091] In one embodiment, an on-board cooling system is provided, which corresponds one-to-one with the on-board cooling system control method described in the above embodiments. For example... Figure 1 As shown, the vehicle-mounted refrigeration system includes at least two refrigeration branches, and at least one of the refrigeration branches is controlled by a solenoid valve.

[0092] When the vehicle-mounted cooling system is in operation and the solenoid valve receives a request to change its open / closed state, the vehicle-mounted cooling system performs the following steps:

[0093] The compressor stops and the system high pressure is obtained;

[0094] When the system high pressure is less than the specified pressure threshold, or when the waiting time of the solenoid valve reaches the first time, the opening and closing state of the solenoid valve is changed.

[0095] When the system high pressure is less than the specified pressure threshold, or the compressor downtime reaches the second time, the compressor is started and adjusted to the specified speed; the first time is less than or equal to the second time.

[0096] Optionally, before adjusting the compressor to the specified speed, the process includes:

[0097] The specified rotational speed is determined according to the rotational speed calculation formula; the rotational speed calculation formula includes:

[0098] SPD(n) = SPD(n-1) + K p (F(n)-F(n-1))+K i ×F(n)

[0099] Wherein, SPD(n) is the specified rotational speed, which is the result of the nth rotational speed calculation;

[0100] SPD(n-1) is the result of the (n-1)th rotational speed calculation;

[0101] K p This is the proportionality constant in the formula for calculating rotational speed;

[0102] K i This is the integral constant in the formula for calculating rotational speed;

[0103] F(n) is the temperature difference between the cooling component temperature and the target cooling component temperature. This temperature difference is the difference between the cooling component temperature measured in the nth measurement and the target cooling component temperature. The cooling component temperature is the temperature of the cooling component in operation.

[0104] F(n-1)) is the previous value of F(n).

[0105] Optionally, the cooling component includes an evaporator and / or a battery cooling plate.

[0106] Optionally, if the cooling components in operation include an evaporator and a battery cold plate, then F(n) is the smaller of the evaporator temperature difference and the battery cold plate temperature difference; wherein, the evaporator temperature difference is the difference between the evaporator temperature and the target evaporator temperature; and the battery cold plate temperature difference is the difference between the battery cold plate temperature and the target battery cold plate temperature.

[0107] Optionally, when the opening / closing status change request is an opening request, the specified pressure threshold is the opening pressure threshold, the first time is the first opening time, and the second time is the second opening time.

[0108] When the request to change the open / closed state is a request to close, the specified pressure threshold is the closing pressure threshold, the first time is the first closing time, and the second time is the second closing time.

[0109] Optionally, the on-board cooling system performs the following steps:

[0110] When there is a refrigeration branch controlled by an electronic expansion valve and the electronic expansion valve is in the open state, adjust the electronic expansion valve to the maximum opening degree;

[0111] When the system high pressure is less than the specified pressure threshold, or when the maximum opening time of the electronic expansion valve is maintained for a longer period than a third time, the electronic expansion valve is adjusted to the specified opening.

[0112] Optionally, before adjusting the electronic expansion valve to a specified opening degree, the following steps are included:

[0113] The specified opening is determined according to the opening calculation formula; the opening calculation formula includes:

[0114] Step(n) = Step(n-1) + L p (E(n)-E(n-1))+L i ×E(n)

[0115] Where Step(n) is the specified opening degree, which is the opening degree calculation result of the nth time;

[0116] Step(n-1) is the result of the opening calculation for the (n-1)th time;

[0117] L p This is the proportional constant in the formula for calculating the opening degree;

[0118] L i This is the integral constant in the formula for calculating the opening degree;

[0119] E(n) is the difference between the current battery-side refrigerant temperature and the refrigerant saturation temperature. This temperature difference is the difference between the battery-side refrigerant temperature and the refrigerant saturation temperature at the nth time.

[0120] E(n-1)) is the difference between the refrigerant temperature and the refrigerant saturation temperature on the battery side in the (n-1)th time.

[0121] Optionally, before determining the specified opening degree according to the opening degree calculation formula, the method further includes:

[0122] Obtain the system low pressure;

[0123] Find the refrigerant saturation temperature corresponding to the low pressure of the system from the refrigerant saturation temperature-pressure lookup table.

[0124] Optionally, when the opening / closing status change request is an opening request, the specified pressure threshold is the opening pressure threshold, the first time is the first opening time, the second time is the second opening time, and the third time is the third opening time.

[0125] When the open / close state change request is a close request, the specified pressure threshold is the close pressure threshold, the first time is the first close time, the second time is the second close time, and the third time is the third close time.

[0126] Specific limitations regarding the vehicle-mounted cooling system can be found in the above description of the control method for the vehicle-mounted cooling system, and will not be repeated here. Each module in the aforementioned vehicle-mounted cooling system can be implemented entirely or partially through software, hardware, or a combination thereof. These modules can be embedded in hardware or independently of the processor in a computer device, or stored in software in the memory of a computer device, so that the processor can call and execute the corresponding operations of each module.

[0127] In one embodiment, a computer device is provided, which may be a terminal, and its internal structure diagram may be as follows: Figure 3 As shown, the computer device includes a processor, memory, network interface, display screen, and input device connected via a system bus. The processor provides computing and control capabilities. The memory includes a readable storage medium and internal memory. The non-volatile storage medium stores an operating system and computer-readable instructions. The internal memory provides an environment for the operation of the operating system and computer-readable instructions in the readable storage medium. The network interface is used to communicate with an external server via a network connection. When the computer-readable instructions are executed by the processor, they implement a vehicle-mounted cooling system control method. The readable storage medium provided in this embodiment includes both non-volatile and volatile readable storage media.

[0128] In one embodiment, a computer device is provided, including a memory, a processor, and computer-readable instructions stored in the memory and executable on the processor, wherein the processor performs the following steps when executing the computer-readable instructions:

[0129] The compressor stops and the system high pressure is obtained;

[0130] When the system high pressure is less than the specified pressure threshold, or when the waiting time of the solenoid valve reaches the first time, the opening and closing state of the solenoid valve is changed.

[0131] When the system high pressure is less than the specified pressure threshold, or the compressor downtime reaches the second time, the compressor is started and adjusted to the specified speed; the first time is less than or equal to the second time.

[0132] In one embodiment, one or more computer-readable storage media storing computer-readable instructions are provided. The readable storage media provided in this embodiment include non-volatile readable storage media and volatile readable storage media. The readable storage media stores computer-readable instructions, which, when executed by one or more processors, perform the following steps:

[0133] The compressor stops and the system high pressure is obtained;

[0134] When the system high pressure is less than the specified pressure threshold, or when the waiting time of the solenoid valve reaches the first time, the opening and closing state of the solenoid valve is changed.

[0135] When the system high pressure is less than the specified pressure threshold, or the compressor downtime reaches the second time, the compressor is started and adjusted to the specified speed; the first time is less than or equal to the second time.

[0136] Those skilled in the art will understand that all or part of the processes in the methods of the above embodiments can be implemented by instructing related hardware with computer-readable instructions. These computer-readable instructions can be stored in a non-volatile readable storage medium or a volatile readable storage medium. When executed, these computer-readable instructions can include the processes of the embodiments of the above methods. Any references to memory, storage, databases, or other media used in the embodiments provided in this application can include non-volatile and / or volatile memory. Non-volatile memory may include read-only memory (ROM), programmable ROM (PROM), electrically programmable ROM (EPROM), electrically erasable programmable ROM (EEPROM), or flash memory. Volatile memory may include random access memory (RAM) or external cache memory. By way of illustration and not limitation, RAM is available in a variety of forms, such as static RAM (SRAM), dynamic RAM (DRAM), synchronous DRAM (SDRAM), dual data rate SDRAM (DDRSDRAM), enhanced SDRAM (ESDRAM), synchronous link DRAM (SLDRAM), RAMbus direct RAM (RDRAM), direct memory bus dynamic RAM (DRDRAM), and memory bus dynamic RAM (RDRAM).

[0137] Those skilled in the art will clearly understand that, for the sake of convenience and brevity, the above-described division of functional units and modules is used as an example. In practical applications, the above functions can be assigned to different functional units and modules as needed, that is, the internal structure of the device can be divided into different functional units or modules to complete all or part of the functions described above.

[0138] The above-described embodiments are only used to illustrate the technical solutions of the present invention, and are not intended to limit it. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention, and should all be included within the protection scope of the present invention.

Claims

1. A control method for an on-board refrigeration system, characterized in that, The vehicle-mounted refrigeration system includes at least two refrigeration branches, and at least one of the refrigeration branches is controlled by a solenoid valve. When the vehicle-mounted cooling system is in operation and the solenoid valve receives a request to change its open / closed state, the control method includes: The compressor stops and the system high pressure is obtained; When the system high pressure is less than the specified pressure threshold, or when the waiting time of the solenoid valve reaches the first time, the opening and closing state of the solenoid valve is changed. When the system high pressure is less than the specified pressure threshold, or the compressor downtime reaches the second time, the compressor is started and adjusted to the specified speed; the first time is less than or equal to the second time.

2. The vehicle-mounted refrigeration system control method as described in claim 1, characterized in that, Before adjusting the compressor to the specified speed, the following steps are included: The specified rotational speed is determined according to the rotational speed calculation formula; the rotational speed calculation formula includes: SPD(n)=SPD(n-1)+K p (F(n)-F(n-1))+K i ×F(n) Wherein, SPD(n) is the specified rotational speed, which is the result of the nth rotational speed calculation; SPD(n-1) is the result of the (n-1)th rotational speed calculation; K p This is the proportionality constant in the formula for calculating rotational speed; K i This is the integral constant in the formula for calculating rotational speed; F(n) is the temperature difference between the cooling component temperature and the target cooling component temperature. This temperature difference is the difference between the cooling component temperature measured in the nth measurement and the target cooling component temperature. The cooling component temperature is the temperature of the cooling component in operation. F(n-1)) is the previous value of F(n).

3. The vehicle-mounted refrigeration system control method as described in claim 2, characterized in that, The cooling components include an evaporator and / or a battery cooling plate.

4. The vehicle-mounted refrigeration system control method as described in claim 3, characterized in that, If the cooling components in operation include an evaporator and a battery cold plate, then F(n) is the smaller of the evaporator temperature difference and the battery cold plate temperature difference; where the evaporator temperature difference is the difference between the evaporator temperature and the target evaporator temperature; and the battery cold plate temperature difference is the difference between the battery cold plate temperature and the target battery cold plate temperature.

5. The vehicle-mounted refrigeration system control method as described in claim 1, characterized in that, When the opening / closing status change request is an opening request, the specified pressure threshold is the opening pressure threshold, the first time is the first opening time, and the second time is the second opening time. When the request to change the open / closed state is a request to close, the specified pressure threshold is the closing pressure threshold, the first time is the first closing time, and the second time is the second closing time.

6. The vehicle-mounted refrigeration system control method as described in claim 1, characterized in that, The control method further includes: When there is a refrigeration branch controlled by an electronic expansion valve and the electronic expansion valve is in the open state, adjust the electronic expansion valve to the maximum opening degree; When the system high pressure is less than the specified pressure threshold, or when the maximum opening time of the electronic expansion valve is maintained for a longer period than a third time, the electronic expansion valve is adjusted to the specified opening.

7. The vehicle-mounted refrigeration system control method as described in claim 6, characterized in that, Before adjusting the electronic expansion valve to the specified opening degree, the following steps are included: The specified opening is determined according to the opening calculation formula; the opening calculation formula includes: Step(n)=Step(n-1)+L p (E(n)-E(n-1))+L i ×E(n) Where Step(n) is the specified opening degree, which is the opening degree calculation result of the nth time; Step(n-1) is the result of the opening calculation for the (n-1)th time; L p This is the proportional constant in the formula for calculating the opening degree; L i This is the integral constant in the formula for calculating the opening degree; E(n) is the difference between the current battery-side refrigerant temperature and the refrigerant saturation temperature. This temperature difference is the difference between the battery-side refrigerant temperature and the refrigerant saturation temperature at the nth time. E(n-1)) is the difference between the refrigerant temperature and the refrigerant saturation temperature on the battery side in the (n-1)th time.

8. The vehicle-mounted refrigeration system control method as described in claim 7, characterized in that, Before determining the specified opening degree according to the opening degree calculation formula, the method further includes: Obtain the system low pressure; Find the refrigerant saturation temperature corresponding to the low pressure of the system from the refrigerant saturation temperature-pressure lookup table.

9. The vehicle-mounted refrigeration system control method as described in claim 6, characterized in that, When the opening / closing status change request is an opening request, the specified pressure threshold is the opening pressure threshold, the first time is the first opening time, the second time is the second opening time, and the third time is the third opening time. When the open / close state change request is a close request, the specified pressure threshold is the close pressure threshold, the first time is the first close time, the second time is the second close time, and the third time is the third close time.

10. A vehicle-mounted refrigeration system, characterized in that, The vehicle-mounted refrigeration system includes at least two refrigeration branches, and at least one of the refrigeration branches is controlled by a solenoid valve. When the vehicle-mounted cooling system is in operation and the solenoid valve receives a request to change its open / closed state, the vehicle-mounted cooling system performs the following steps: The compressor stops and the system high pressure is obtained; When the system high pressure is less than the specified pressure threshold, or when the waiting time of the solenoid valve reaches the first time, the opening and closing state of the solenoid valve is changed. When the system high pressure is less than the specified pressure threshold, or the compressor downtime reaches the second time, the compressor is started and adjusted to the specified speed; the first time is less than or equal to the second time.

11. The vehicle-mounted refrigeration system as described in claim 10, characterized in that, Before adjusting the compressor to the specified speed, the following steps are included: The specified rotational speed is determined according to the rotational speed calculation formula; the rotational speed calculation formula includes: SPD(n)=SPD(n-1)+K p (F(n)-F(n-1))+K i ×F(n) Wherein, SPD(n) is the specified rotational speed, which is the result of the nth rotational speed calculation; SPD(n-1) is the result of the (n-1)th rotational speed calculation; K p This is the proportionality constant in the formula for calculating rotational speed; K i This is the integral constant in the formula for calculating rotational speed; F(n) is the temperature difference between the cooling component temperature and the target cooling component temperature. This temperature difference is the difference between the cooling component temperature measured in the nth measurement and the target cooling component temperature. The cooling component temperature is the temperature of the cooling component in operation. F(n-1)) is the previous value of F(n).

12. The vehicle-mounted refrigeration system as described in claim 10, characterized in that, The on-board cooling system also performs the following steps: When there is a refrigeration branch controlled by an electronic expansion valve and the electronic expansion valve is in the open state, adjust the electronic expansion valve to the maximum opening degree; When the system high pressure is less than the specified pressure threshold, or when the maximum opening time of the electronic expansion valve is maintained for a longer period than a third time, the electronic expansion valve is adjusted to the specified opening.

13. The vehicle-mounted refrigeration system as described in claim 12, characterized in that, Before adjusting the electronic expansion valve to the specified opening degree, the following steps are included: The specified opening is determined according to the opening calculation formula; the opening calculation formula includes: Step(n)=Step(n-1)+L p (E(n)-E(n-1))+L i ×E(n) Where Step(n) is the specified opening degree, which is the opening degree calculation result of the nth time; Step(n-1) is the result of the opening calculation for the (n-1)th time; L p This is the proportional constant in the formula for calculating the opening degree; L i This is the integral constant in the formula for calculating the opening degree; E(n) is the temperature difference between the current battery-side refrigerant temperature and the refrigerant saturation temperature. This temperature difference is the difference between the battery-side refrigerant temperature and the refrigerant saturation temperature at the nth time. E(n-1)) is the difference between the refrigerant temperature and the refrigerant saturation temperature on the battery side in the (n-1)th time.

14. A computer device comprising a memory, a processor, and computer-readable instructions stored in the memory and running on the processor, characterized in that, When the processor executes the computer-readable instructions, it implements the vehicle-mounted refrigeration system control method as described in any one of claims 1 to 9.

15. One or more readable storage media storing computer-readable instructions, which, when executed by one or more processors, cause the one or more processors to perform the vehicle cooling system control method as described in any one of claims 1 to 9.

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