Cascade combined cooling and heating system and cooling and heating load regulation and control method and device thereof

Abstract

The invention discloses a cascade combined cooling and heating system and a cooling and heating load regulation and control method and device thereof. The method comprises the following steps: acquiring a heating load demand and a refrigeration load demand of a system; if the heating load requirement is not changed and the refrigeration load requirement is adjusted, detecting the freezing water temperature, and regulating and controlling a high-temperature-stage throttling valve and a low-temperature-stage throttling valve according to the freezing water temperature, so that the high-temperature-stage evaporation temperature is adjusted to the first target high-temperature-stage evaporation temperature; and if the refrigeration load requirement is not changed and the heating load requirement is adjusted, the temperature of the hot water is detected, and a high-temperature-stage throttling valve and a low-temperature-stage throttling valve are adjusted and controlled according to the temperature of the hot water, so that the high-temperature-stage evaporation temperature is adjusted to the second target high-temperature-stage evaporation temperature. The variable high-temperature-stage evaporation temperature design is adopted, the operation loads of the high-temperature-stage system and the low-temperature-stage system are correspondingly adjusted in a matched mode, the proportion of the system output refrigerating capacity to the system output heating capacity is adjusted, and meanwhile the actual refrigerating load and heating load changes are met.

Description

Technical Field

[0001] The present invention relates to the technical field of units, and in particular to a cascade cooling and heating cogeneration system and a cooling and heating load control method and device thereof. Background Art

[0002] The cascade cooling and heating cogeneration system is an efficient energy utilization system that combines two independent refrigerant cycles. Its technical background is derived from the traditional single cascade cycle refrigeration system or the traditional single cascade cycle heating system integrator, which can handle cooling and heating needs at the same time.

[0003] By combining high-temperature and low-temperature cycles, cascade cooling and heating systems can process high-temperature and low-temperature heat sources separately, matching cooling and heating load requirements and achieving efficient energy utilization. The high-temperature cycle is typically responsible for processing high-temperature heat sources or providing high-temperature heat output, while the low-temperature cycle is responsible for low-temperature heat sources or low-temperature cooling output. Heat is transferred between the two cycles through a heat exchanger. Intelligent control strategies are also used to dynamically adjust the operating parameters of each subsystem, such as compressor frequency and refrigerant flow, to ensure efficient and stable operation under different operating conditions, significantly improving energy efficiency and reducing operating costs.

[0004] However, when it is necessary to simultaneously meet the cooling and heating needs of different temperature ranges, ordinary systems often have difficulty operating efficiently. However, the cooling and heat output of actual cascade cooling and heating systems are usually designed according to a certain ratio. When the actual user's cooling load or heating load exceeds this ratio, the unit may not be able to meet the demand through self-regulation, resulting in a decrease in system operating efficiency or failure to work properly. For example, when the cooling load significantly exceeds the design ratio, the system needs to generate more cooling capacity, but the heat output may not increase accordingly, resulting in heat accumulation or imbalance in heat distribution within the system, which in turn affects the normal operation of the refrigeration cycle. Conversely, if the heating load exceeds the ratio, the system may need to generate more heat, but the cooling output may not be reduced accordingly, resulting in excess cooling capacity or overcooling of the system, affecting the heat output capacity.

[0005] In this case, the solution requires additional auxiliary cooling or heating units to supplement the excess capacity to ensure that the system's cooling and heating supply can meet the actual needs of users. This not only increases system complexity and investment costs, but may also reduce overall energy efficiency and affect economic efficiency.

[0006] Currently, no effective solution has been proposed to the problem that the cascade cooling and heating cogeneration system in the prior art cannot adaptively achieve cooling and heating load balance. Summary of the Invention

[0007] The embodiment of the present invention provides a cascade cooling and heating cogeneration system and a cooling and heating load control method thereof to solve the problem in the prior art that the cascade cooling and heating cogeneration system cannot adaptively achieve cooling and heating load balance.

[0008] To solve the above technical problems, the present invention provides a cascade cooling and heating cogeneration system and a method for controlling cooling and heating loads thereof. The method comprises:

[0009] Obtain the heating load demand and cooling load demand of the cascade cogeneration system;

[0010] If the heating load demand remains unchanged and the cooling load demand is adjusted, the chilled water temperature is detected, and a corresponding control strategy is executed according to the chilled water temperature to control the high-temperature stage throttle valve and the low-temperature stage throttle valve so that the high-temperature stage evaporation temperature is adjusted to the first target high-temperature stage evaporation temperature;

[0011] If the cooling load demand remains unchanged and the heating load demand is adjusted, the hot water temperature is detected, and the corresponding control strategy is executed according to the size of the hot water temperature to control the high-temperature throttle valve and the low-temperature throttle valve so that the high-temperature evaporation temperature is adjusted to the second target high-temperature evaporation temperature.

[0012] Furthermore, after detecting the chilled water temperature, the method further includes: if the chilled water temperature is greater than a preset maximum chilled water temperature, confirming that the refrigeration load needs to be increased; if the chilled water temperature is less than a preset minimum chilled water temperature, confirming that the refrigeration load needs to be reduced.

[0013] Furthermore, after detecting the chilled water temperature, the method further includes: calculating the first target high-temperature-stage evaporation temperature according to the chilled water inlet and outlet temperature difference, the cooling capacity deviation, and the actual high-temperature-stage evaporation temperature.

[0014] Furthermore, the first target high-temperature-stage evaporation temperature is calculated based on the chilled water inlet and outlet temperature difference, the cooling capacity deviation, and the actual high-temperature-stage evaporation temperature, which is achieved by the following formula:

[0015] δQ 冷 =Q 冷 (△t 冷 / △t' 冷 -1),

[0016] T'=aδQ 冷 2 +bδQ 冷 +c,

[0017] T h =T+T';

[0018] Among them, T his the first target high-temperature stage evaporation temperature, T is the actual high-temperature stage evaporation temperature, T' is the target high-temperature stage evaporation temperature deviation, δQ 冷 is the cooling capacity deviation, Q 冷 is the rated cooling capacity, △t 冷 is the preset chilled water inlet and outlet temperature difference, △t' 冷 is the current chilled water inlet and outlet temperature difference, and a, b, and c are the preset cooling capacity adjustment constants.

[0019] Furthermore, a corresponding control strategy is executed according to the temperature of the chilled water to control the high-temperature throttle valve and the low-temperature throttle valve, including:

[0020] If the chilled water temperature is greater than the preset maximum chilled water temperature, a corresponding control strategy is executed: the high-temperature stage throttle valve opening is reduced, and the low-temperature stage throttle valve opening is increased until the high-temperature stage evaporation temperature of the cascade cooling and heating cogeneration system is adjusted to a first target high-temperature stage evaporation temperature;

[0021] If the chilled water temperature is lower than the preset minimum chilled water temperature, the corresponding control strategy is executed: the high-temperature stage throttle valve opening is increased, and the low-temperature stage throttle valve opening is decreased until the high-temperature stage evaporation temperature of the cascade cooling and heating cogeneration system is adjusted to the first target high-temperature stage evaporation temperature.

[0022] Furthermore, after detecting the hot water temperature, the method further includes: if the hot water temperature is greater than a preset maximum hot water temperature, confirming that the heating load needs to be reduced; if the hot water temperature is less than a preset minimum hot water temperature, confirming that the heating load needs to be increased.

[0023] Furthermore, after detecting the hot water temperature, the method further includes: calculating the second target high-temperature-stage evaporation temperature according to the hot water inlet and outlet temperature difference, the heating amount deviation, and the actual high-temperature-stage evaporation temperature.

[0024] Furthermore, the second target high-temperature-stage evaporation temperature is calculated based on the hot water inlet and outlet temperature difference, the heating amount deviation, and the actual high-temperature-stage evaporation temperature, which is achieved by the following formula:

[0025] δQ 热 =Q 热 (△t 热 / △t' 热 -1),

[0026] T'=xδQ 热 2 +yδQ 热 +z,

[0027] T h =T+T';

[0028] Among them, T his the second target high-temperature stage evaporation temperature, T is the actual high-temperature stage evaporation temperature, T' is the target high-temperature stage evaporation temperature deviation, δQ 热 is the heating capacity deviation, Q 热 is the rated heat capacity, △t 热 is the preset hot water inlet and outlet temperature difference, △t' 热 is the current hot water inlet and outlet temperature difference, and x, y, and z are the preset heating amount adjustment constants.

[0029] Furthermore, a corresponding control strategy is executed according to the temperature of the hot water to control the high-temperature throttle valve and the low-temperature throttle valve, including:

[0030] If the hot water temperature is greater than the preset maximum hot water temperature, a corresponding control strategy is executed: the high-temperature stage throttle valve opening is increased, and the low-temperature stage throttle valve opening is decreased until the high-temperature stage evaporation temperature of the cascade cooling and heating cogeneration system is adjusted to a second target high-temperature stage evaporation temperature;

[0031] If the hot water temperature is lower than the preset minimum hot water temperature, the corresponding control strategy is executed: the high-temperature stage throttle valve opening is reduced, and the low-temperature stage throttle valve opening is increased until the high-temperature stage evaporation temperature of the cascade cooling and heating cogeneration system is adjusted to the second target high-temperature stage evaporation temperature.

[0032] The present invention also provides a cooling and heating load control device for a cascade cooling and heating cogeneration system, wherein the device comprises:

[0033] An acquisition module is used to obtain the heating load demand and the cooling load demand of the cascade cooling and heating system;

[0034] a first adjustment module, configured to detect a chilled water temperature when the heating load demand remains unchanged and the cooling load demand is adjusted, and execute a corresponding control strategy according to the chilled water temperature to control the high-temperature throttle valve and the low-temperature throttle valve so that the high-temperature evaporation temperature is adjusted to a first target high-temperature evaporation temperature;

[0035] The second adjustment module is used to detect the hot water temperature when the cooling load demand remains unchanged and the heating load demand is adjusted, and to execute a corresponding control strategy according to the size of the hot water temperature to adjust the high-temperature throttle valve and the low-temperature throttle valve so that the high-temperature evaporation temperature is adjusted to the second target high-temperature evaporation temperature.

[0036] The present invention also provides a cascade cooling and heating cogeneration system, wherein the system at least includes the cooling and heating load control device of the cascade cooling and heating cogeneration system mentioned above.

[0037] The present invention also provides a computer-readable storage medium having a computer program stored thereon, wherein the program implements the above method when executed by a processor.

[0038] The present invention also provides an electronic device, which includes: one or more processors; a storage device for storing one or more programs, when the one or more programs are executed by the one or more processors, the one or more processors implement the method as described above.

[0039] Applying the technical solution of the present invention, the present invention provides a cascade combined cooling and heating system with an adjustable cooling and heating load output ratio. It adopts a variable intermediate temperature (high-temperature evaporation temperature) design, and adapts to and adjusts the operating loads of the high-temperature system and the low-temperature system, and the changes in refrigerant flow, and adjusts the ratio of the system output cooling capacity to heating capacity, while meeting the actual cooling load and heating load changes. There is no need to additionally configure heating or refrigeration units to supplement user loads, which simplifies the overall system solution design, reduces system investment costs, and avoids the problem of heat and cold imbalance under combined cooling and heating. BRIEF DESCRIPTION OF THE DRAWINGS

[0040] Figure 1 is a structural block diagram of a cascade cooling and heating cogeneration system according to an embodiment of the present invention;

[0041] Figure 2 2. It is a schematic diagram of the connection between the cascade cooling and heating cogeneration system and the user's heating load and the user's cooling load according to an embodiment of the present invention;

[0042] Figure 3 2 is a schematic structural diagram of a cascade cooling and heating cogeneration system according to an embodiment of the present invention;

[0043] Figure 4 is a flow chart of a method for controlling cooling and heating loads of a cascade cooling and heating cogeneration system according to an embodiment of the present invention;

[0044] Figure 5 This is a control flow chart of a system for stabilizing hot water temperature and adjusting chilled water temperature according to an embodiment of the present invention;

[0045] Figure 6 This is a control flow chart of a system for stabilizing chilled water temperature and adjusting hot water temperature according to an embodiment of the present invention;

[0046] Figure 7 4 is a structural block diagram of a cooling and heating load control device for a cascade cooling and heating cogeneration system according to an embodiment of the present invention. DETAILED DESCRIPTION

[0047] To make the objectives, technical solutions, and advantages of the present invention more apparent, the present invention will be further described in detail below with reference to the accompanying drawings. It is apparent that the embodiments described are only some, not all, of the present invention. All other embodiments derived by persons of ordinary skill in the art based on the embodiments of the present invention without creative effort are intended to fall within the scope of protection of the present invention.

[0048] The terms used in the embodiments of the present invention are for the purpose of describing specific embodiments only and are not intended to limit the present invention. The singular forms "a," "an," "the," and "the" used in the embodiments of the present invention and the appended claims are also intended to include plural forms, and unless the context clearly indicates otherwise, "a plurality" generally includes at least two.

[0049] It should be understood that the term "and / or" as used herein is merely a description of the relationship between associated objects, indicating that three possible relationships exist. For example, "A and / or B" can represent: A exists alone, A and B exist simultaneously, or B exists alone. Furthermore, the character " / " in this document generally indicates that the associated objects are in an "or" relationship.

[0050] It should be understood that although the terms "first" and "second" may be used to describe the target high-temperature evaporation temperature in embodiments of the present invention, the present invention should not be limited to these terms. These terms are merely used to distinguish the target high-temperature evaporation temperatures. For example, without departing from the scope of embodiments of the present invention, the first target high-temperature evaporation temperature may also be referred to as the second target high-temperature evaporation temperature, and similarly, the second target high-temperature evaporation temperature may also be referred to as the first target high-temperature evaporation temperature.

[0051] As used herein, the words "if" and "if" may be interpreted as "at the time of" or "when" or "in response to determining" or "in response to detecting," depending on the context. Similarly, the phrases "if it is determined" or "if (stated condition or event) is detected" may be interpreted as "when it is determined" or "in response to the determination" or "when detecting (stated condition or event)" or "in response to detecting (stated condition or event)," depending on the context.

[0052] It should also be noted that the terms "include," "comprises," or any other variations thereof are intended to encompass non-exclusive inclusion, such that a product or device comprising a series of elements includes not only those elements but also other elements not explicitly listed, or elements inherent to such product or device. In the absence of further limitations, an element defined by the phrase "comprises a..." does not exclude the presence of other identical elements in the product or device comprising the element.

[0053] The optional embodiments of the present invention are described in detail below with reference to the accompanying drawings.

[0054] Example 1

[0055] The cooling and heating load control scheme provided by the present invention enables adjustable cooling and heating load output ratios in a cascade cooling and heating cogeneration system. By employing a variable intermediate temperature (high-temperature evaporation temperature) design, the system's output cooling capacity and heating capacity ratio can be adjusted to accommodate changes in the operating loads and refrigerant flow rates of the high- and low-temperature systems, while simultaneously meeting actual cooling and heating load variations. This eliminates the need for additional heating or refrigeration units to supplement user loads. The following describes the cascade cooling and heating cogeneration system.

[0056] Figure 1 : is a structural block diagram of a cascade cooling and heating cogeneration system according to an embodiment of the present invention. Figure 1 As shown, the cascade cooling and heating system includes a high-temperature system and a low-temperature system;

[0057] The high temperature stage system includes: a high temperature condenser, a high temperature compressor, and an evaporative condenser connected in sequence; a high temperature stage throttle valve is provided on the pipeline between the high temperature condenser and the evaporative condenser;

[0058] The low-temperature stage system includes: an evaporative condenser, a low-temperature compressor, and a low-temperature evaporator connected in sequence; a low-temperature stage throttle valve is provided on the pipeline between the low-temperature evaporator and the evaporative condenser;

[0059] It should be noted that the high-temperature and low-temperature systems are connected via an evaporative condenser. The high-temperature system connects the hot water inlet and outlet, with a hot water outlet temperature sensor installed on the hot water outlet pipe. A high-temperature evaporation pressure sensor is installed on the pipe between the high-temperature compressor and the evaporative condenser. The low-temperature system connects the chilled water inlet and outlet, with a chilled water outlet temperature sensor installed on the chilled water outlet pipe, and a low-temperature evaporation pressure sensor is installed on the pipe between the low-temperature compressor and the low-temperature evaporator.

[0060] The various components of a cascade cooling and heating system work together to form an efficient heating and cooling supply system. The high-temperature compressor compresses the refrigerant to a high temperature and pressure state, which then enters the high-temperature condenser, releasing heat for heating. The high-temperature throttle valve reduces the refrigerant's pressure before it enters the evaporative condenser, absorbing heat and generating cooling. The low-temperature compressor compresses the low-temperature refrigerant and exchanges heat with the high-temperature refrigerant through the evaporative condenser, further improving the system's heating efficiency. The low-temperature throttle valve regulates the flow of the low-temperature refrigerant, ensuring a heat balance between the evaporator and the evaporative condenser. The entire system responds to user heating and cooling demands in real time by dynamically adjusting the throttle valve opening and compressor frequency, ensuring a balanced and optimized ratio of heating and cooling loads. Temperature and pressure sensors monitor system status in real time and provide feedback signals for precise regulation, thereby improving overall system efficiency and reliability.

[0061] Figure 2 FIG. 1 is a schematic diagram showing the connection between the cascade cooling and heating cogeneration system and the user's heat load and the user's cooling load according to an embodiment of the present invention. Figure 2 As shown, the high-temperature system of the cascade combined cooling and heating system (also known as a cascade combined cooling and heating unit) is connected to the user's heat load, and the low-temperature system is connected to the user's cooling load.

[0062] Figure 3 FIG. 1 is a schematic structural diagram of a cascade cooling and heating cogeneration system according to an embodiment of the present invention. Figure 3 As shown, the cascade cooling and heating system of the present invention utilizes a semi-hermetic, single-stage, two-stage compressor cascade, as opposed to a single-stage compressor cascade. The overall design is frameless, with the high-temperature condenser, evaporator, and evaporative condenser forming the main unit. The high- and low-temperature compressors corresponding to the higher operating temperatures are located on the high-temperature condenser and evaporative condenser, isolated from the low-temperature components to minimize cooling capacity degradation. The relatively low-temperature refrigerant is placed on the shell side of the evaporative condenser, further minimizing the impact of high temperatures on the low-temperature evaporator.

[0063] According to an embodiment of the present invention, an embodiment of a method for controlling the cooling and heating loads of a cascade cooling and heating cogeneration system is provided. It should be noted that the steps shown in the flowchart of the accompanying drawings can be executed in a computer system such as a set of computer-executable instructions, and although a logical order is shown in the flowchart, in some cases, the steps shown or described can be executed in an order different from that shown here.

[0064] Figure 4 FIG. 1 is a flow chart of a method for controlling cooling and heating loads of a cascade cooling and heating cogeneration system according to an embodiment of the present invention. Figure 4 As shown, the method includes the following steps:

[0065] Step S401, obtaining the heating load demand and cooling load demand of the cascade cooling and heating cogeneration system;

[0066] Step S402: If the heating load demand remains unchanged and the cooling load demand has been adjusted, the chilled water temperature is detected and a corresponding control strategy is implemented based on the chilled water temperature to adjust the high-temperature throttle valve and the low-temperature throttle valve so that the high-temperature evaporation temperature is adjusted to a first target high-temperature evaporation temperature.

[0067] In step S403, if the cooling load demand remains unchanged and the heating load demand is adjusted, the hot water temperature is detected, and the corresponding control strategy is executed according to the hot water temperature to control the high-temperature throttle valve and the low-temperature throttle valve so that the high-temperature evaporation temperature is adjusted to the second target high-temperature evaporation temperature.

[0068] This embodiment provides a cascade combined cooling and heating system with an adjustable cooling and heating load output ratio. The system adopts a variable intermediate temperature (high-temperature evaporation temperature) design to adapt to and adjust the operating loads of the high-temperature and low-temperature systems and changes in refrigerant flow, and adjust the ratio of the system's output cooling capacity to heating capacity, while meeting actual cooling and heating load changes. There is no need to configure additional heating or refrigeration units to supplement user loads, which simplifies the overall system design, reduces system investment costs, and avoids the problem of heat and cold imbalance under combined cooling and heating.

[0069] In order to meet the actual changes in cooling load and heating load and avoid the problem of heat and cold imbalance under combined cooling and heating, this embodiment needs to obtain the heating load demand and cooling load demand of the cascade combined cooling and heating system in real time or periodically. If the heating load demand remains unchanged and the cooling load demand is adjusted, the corresponding control strategy is executed; if the heating load demand remains unchanged and the cooling load demand is adjusted, the corresponding control strategy is executed. Within the adjustable operating temperature range, the imbalance problem of the heat and cold load ratio can be solved by adjusting the opening of the high-temperature and low-temperature throttle valves and the load output. The above two situations are introduced below.

[0070] 1. The heating load demand remains unchanged, but the cooling load demand is adjusted

[0071] The chilled water temperature is detected in real time by a temperature sensor. If the chilled water temperature is higher than the preset maximum chilled water temperature, it is confirmed that the cooling load needs to be increased; if the chilled water temperature is lower than the preset minimum chilled water temperature, it is confirmed that the cooling load needs to be reduced.

[0072] After detecting the chilled water temperature, a first target high-temperature-stage evaporation temperature is calculated based on the chilled water inlet and outlet temperature difference, the cooling capacity deviation, and the actual high-temperature-stage evaporation temperature. This first target high-temperature-stage evaporation temperature serves as the target value for adjusting the high-temperature-stage evaporation temperature. This embodiment adjusts the ratio of the output cooling capacity to the heating capacity of the cascade cogeneration system by varying the intermediate temperature (the high-temperature-stage evaporation temperature) to adjust the load of the high- and low-temperature-stage systems.

[0073] The first target high-temperature stage evaporation temperature is calculated using the following formula:

[0074] δQ 冷 =Q 冷 (△t 冷 / △t' 冷 -1),

[0075] T'=aδQ 冷 2 +bδQ 冷 +c,

[0076] T h =T+T';

[0077] Among them, T h is the first target high-temperature stage evaporation temperature, T is the actual high-temperature stage evaporation temperature, T' is the target high-temperature stage evaporation temperature deviation, δQ 冷 is the cooling capacity deviation (the deviation between the actual cooling capacity demand and the rated cooling capacity), Q 冷 is the rated cooling capacity, △t 冷 is the preset chilled water inlet and outlet temperature difference, △t' 冷 is the current chilled water inlet and outlet temperature difference, and a, b, and c are the preset cooling capacity adjustment constants.

[0078] (1) If the chilled water temperature is greater than the preset maximum chilled water temperature, it indicates that the refrigeration load needs to be increased, and the corresponding control strategy is executed: the high-temperature stage throttle valve opening is reduced, and the low-temperature stage throttle valve opening is increased until the high-temperature stage evaporation temperature of the cascade cooling and heating system is adjusted to the first target high-temperature stage evaporation temperature.

[0079] After closing the high temperature stage throttle valve, the current chilled water inlet and outlet temperature difference △t' 冷 Will reduce the cooling capacity deviation δQ 冷 The target high-temperature stage evaporation temperature deviation T' will increase, as determined by the above calculation formula. Decreasing the high-temperature stage throttle valve opening can lower the low-temperature stage evaporation temperature. Simultaneously, increasing the high-temperature stage compressor output capacity and ensuring the heating capacity in the high-temperature stage cycle can keep the heating load constant.

[0080] At this point, the low-temperature stage's condensing and evaporating temperatures, influenced by the high-temperature stage's evaporating temperature, will decrease. Therefore, the low-temperature stage's throttle valve is opened wider to maintain a stable low-temperature evaporating temperature. This also increases the low-temperature stage's compressor output and the refrigerant flow rate within the low-temperature stage's circulation. This adjustment increases the system's cooling capacity while maintaining the same heating capacity, thus meeting user needs.

[0081] PID control can be used to control the opening of the high- and low-temperature throttle valves. The low-temperature throttle valve can be controlled using conventional throttling methods, not limited to PID control based on suction superheat or heat exchanger temperature difference, proportional control, or other tuning methods. The actual hardware configuration of a specific chiller unit directly impacts the target values. Specific opening adjustment is performed through testing and debugging for a specific chiller unit. The high- and low-temperature throttle valve openings are determined for various temperatures and cooling capacity requirements. After the parameters are recorded and the target values ​​are fixed, the chiller unit is finalized. When the unit's internal structure or hardware is modified, or when a new chiller is developed, re-commissioning is required to obtain and fix new target values. During the opening adjustment of the high- and low-temperature throttle valves, the high-temperature evaporation temperature of the cascade cooling and heating system will change accordingly. When the high-temperature evaporation temperature reaches the first target high-temperature evaporation temperature, opening adjustment of the high- and low-temperature throttle valves can be discontinued.

[0082] (2) If the chilled water temperature is lower than the preset minimum chilled water temperature, it indicates that the refrigeration load needs to be reduced, and the corresponding control strategy is executed: the high-temperature stage throttle valve opening is increased, and the low-temperature stage throttle valve opening is decreased, until the high-temperature stage evaporation temperature of the cascade cooling and heating system is adjusted to the first target high-temperature stage evaporation temperature.

[0083] Opening the high-temperature stage throttle valve can reduce the output of the high-temperature stage compressor to ensure the heating capacity in the high-temperature stage cycle. At the same time, closing the low-temperature stage throttle valve can reduce the flow of refrigerant in the low-temperature stage cycle, thereby reducing the cooling capacity of the system.

[0084] Similarly, a PID control method can be used to control the opening of the high- and low-temperature throttle valves. During the process of controlling the opening of the high- and low-temperature throttle valves, the high-temperature evaporation temperature of the cascade cooling and heating cogeneration system will change accordingly. When the high-temperature evaporation temperature reaches the first target high-temperature evaporation temperature, the control of the opening of the high- and low-temperature throttle valves can be stopped.

[0085] 2. Heating load demand remains unchanged, but cooling load demand is adjusted

[0086] The hot water temperature is detected in real time by the temperature sensor. If the hot water temperature is higher than the preset maximum hot water temperature, it is confirmed that the heating load needs to be reduced; if the hot water temperature is lower than the preset minimum hot water temperature, it is confirmed that the heating load needs to be increased.

[0087] After detecting the hot water temperature, a second target high-temperature evaporation temperature is calculated based on the hot water inlet and outlet temperature difference, the heating capacity deviation, and the actual high-temperature evaporation temperature. This second target high-temperature evaporation temperature serves as the target value for adjusting the high-temperature evaporation temperature. This embodiment adjusts the ratio of the output cooling capacity to the heating capacity of the cascade cogeneration system by varying the intermediate temperature (the high-temperature evaporation temperature) to adjust the load of the high- and low-temperature systems.

[0088] The second target high-temperature stage evaporation temperature is calculated using the following formula:

[0089] δQ 热 =Q 热 (△t 热 / △t' 热 -1),

[0090] T'=xδQ 热 2 +yδQ 热 +z,

[0091] T h =T+T';

[0092] Among them, T h is the second target high temperature stage evaporation temperature, T is the actual high temperature stage evaporation temperature, T' is the target high temperature stage evaporation temperature deviation, δQ 热 is the heating capacity deviation (the deviation between the actual heating capacity demand and the rated heating capacity), Q 热 is the rated heat capacity, △t 热 is the preset hot water inlet and outlet temperature difference, △t' 热 is the current hot water inlet and outlet temperature difference, and x, y, and z are the preset heating amount adjustment constants.

[0093] When calculating the first target high-temperature stage evaporating temperature or the second target high-temperature stage evaporating temperature, different refrigerants have different calculation coefficients according to different cooling capacity or heating capacity deviations. It is necessary to determine the cooling capacity adjustment constant or the heating capacity adjustment constant based on the corresponding refrigerant adjustment coefficient.

[0094] (1) If the hot water temperature is greater than the preset maximum hot water temperature, it means that the heating load needs to be reduced and the heating ratio needs to be reduced, then the corresponding control strategy is executed: the high-temperature stage throttle valve opening is increased and the low-temperature stage throttle valve opening is decreased until the high-temperature stage evaporation temperature of the cascade cooling and heating system is adjusted to the second target high-temperature stage evaporation temperature.

[0095] The system detects changes in the high-temperature stage evaporation pressure relative to the evaporation temperature through a pressure sensor. The system then increases the high-temperature stage throttle valve opening to raise the high-temperature stage evaporation temperature while simultaneously reducing the high-temperature stage compressor output, causing the high-temperature stage cycle heating capacity to decline. Simultaneously, the low-temperature stage compressor output is increased, increasing the refrigerant flow in the low-temperature stage cycle, thereby reducing the system heating capacity while stabilizing the system cooling capacity.

[0096] (2) If the hot water temperature is lower than the preset minimum hot water temperature, it indicates that the heating load needs to be increased and the heating ratio needs to be increased, and the corresponding control strategy is executed: the high-temperature stage throttle valve opening is closed and the low-temperature stage throttle valve opening is opened until the high-temperature stage evaporation temperature of the cascade cooling and heating system is adjusted to the second target high-temperature stage evaporation temperature.

[0097] The system will detect the change in the evaporation temperature corresponding to the evaporation pressure of the high-temperature stage through the pressure sensor. The system will close the opening of the high-temperature stage throttle valve to reduce the evaporation temperature of the high-temperature stage, and at the same time increase the output capacity of the high-temperature stage compressor, so that the high-temperature stage circulating heating capacity is on an upward trend.

[0098] At this point, the low-temperature stage condensing temperature will drop due to the influence of the high-temperature stage evaporating temperature, and the low-temperature stage cooling capacity will increase. Therefore, it is necessary to reduce the output of the low-temperature stage compressor capacity and reduce the flow of refrigerant in the low-temperature stage cycle to stabilize the system cooling capacity. This adjustment allows the system heating capacity to be increased while maintaining the cooling capacity unchanged to meet user needs.

[0099] Example 2

[0100] Figure 5 FIG. 1 is a control flow chart of a system for stabilizing hot water temperature and adjusting chilled water temperature according to an embodiment of the present invention. Figure 5 As shown, it includes the following processes:

[0101] (1) The user's required heating load remains unchanged and the cooling load is adjusted.

[0102] (2) Real-time detection of T by temperature sensor 冷冻水温 Too high (T 冷冻水温 When the system cooling capacity ratio is increased (exceeds the maximum preset value), the high temperature level P is detected by the pressure sensor. 蒸发压力 In response to changes in evaporation and condensation temperatures, the system reduces the high-temperature stage throttle valve opening, lowering the low-temperature stage evaporation temperature. Simultaneously, it increases the high-temperature stage compressor output to ensure heating capacity in the high-temperature stage cycle, thus ensuring a constant heating load.

[0103] At this point, the low-temperature stage's condensing and evaporating temperatures, influenced by the high-temperature stage's evaporating temperature, will decrease. Therefore, the low-temperature stage's throttle valve is opened wider to maintain a stable low-temperature evaporating temperature. This also increases the low-temperature stage's compressor output and the refrigerant flow rate within the low-temperature stage's circulation. This adjustment increases the system's cooling capacity while maintaining the same heating capacity, thus meeting user needs.

[0104] (3) Real-time detection of T by temperature sensor 冷冻水温 Too low (T 冷冻水温 When the pressure drops below the minimum preset value and the system cooling capacity ratio needs to be reduced, the system detects the change in the high-temperature stage evaporation temperature corresponding to the P evaporation pressure through the pressure sensor, opens the high-temperature stage throttle valve, reduces the high-temperature stage compressor output capacity, and ensures the heating capacity in the high-temperature stage cycle. At the same time, close the low-temperature stage throttle valve, reducing the refrigerant flow in the low-temperature stage cycle, thereby reducing the system cooling capacity.

[0105] (4) Opening control of high temperature stage throttle valve.

[0106] The high-temperature throttle valve uses the high-temperature evaporation temperature as the adjustment target. The specific opening is related to the high and low temperature refrigerants actually used. Assuming the low-temperature water outlet demand index is 7°C and the high-temperature water outlet demand index is 130°C, the high-temperature target evaporation temperature range is adjusted to between 65 and 40°C. The target high-temperature evaporation temperature is calculated using the following formula:

[0107] δQ 冷 =Q 冷 (△t 冷 / △t' 冷 -1),

[0108] T'=aδQ 冷 2 +bδQ 冷 +c,

[0109] T h =T+T';

[0110] Where Th is the target high temperature stage evaporation temperature, T is the actual high temperature stage evaporation temperature, T' is the target high temperature stage evaporation temperature deviation, δQ 冷 is the cooling capacity deviation (the deviation between the actual cooling capacity demand and the rated cooling capacity), Q 冷 is the rated cooling capacity, △t 冷 is the preset chilled water inlet and outlet temperature difference, △t' 冷 is the actual chilled water inlet and outlet temperature difference. a, b, and c are the cooling capacity adjustment constants that vary according to the different high and low temperature refrigerant media.

[0111] Figure 6FIG. 1 is a control flow chart of a system for stabilizing the chilled water temperature and adjusting the hot water temperature according to an embodiment of the present invention. Figure 6 As shown, it includes the following processes:

[0112] (1) The user's required cooling load remains unchanged, and the heating load is adjusted.

[0113] (2) Real-time detection of T by temperature sensor 热水水温 Too low (T 热水水温 When the heating ratio needs to be increased, the high temperature level P is detected by the pressure sensor. 蒸发压力 In response to changes in the evaporating temperature, the system closes the high-temperature stage throttle valve opening to reduce the high-temperature stage evaporating temperature, while increasing the high-temperature stage compressor capacity output, so that the high-temperature stage circulating heating capacity is on an upward trend.

[0114] At this point, the low-temperature stage condensing temperature will drop due to the influence of the high-temperature stage evaporating temperature, and the low-temperature stage cooling capacity will increase. Therefore, it is necessary to reduce the output of the low-temperature stage compressor capacity and reduce the flow of refrigerant in the low-temperature stage cycle to stabilize the system cooling capacity. This adjustment allows the system heating capacity to be increased while maintaining the cooling capacity unchanged to meet user needs.

[0115] (3) Real-time detection of T by temperature sensor 热水水温 Too high (T 热水水温 Higher than the highest preset value), when the heating ratio needs to be reduced, the system will detect the high temperature level P through the pressure sensor. 蒸发压力 In response to changes in evaporating temperature, the system increases the high-temperature stage throttle valve opening, raising the high-temperature stage evaporating temperature while simultaneously reducing the high-temperature stage compressor output, causing the high-temperature stage cycle heating capacity to decline. Simultaneously, the low-temperature stage compressor output is increased, increasing the refrigerant flow in the low-temperature stage cycle, thereby reducing the system heating capacity while stabilizing the system cooling capacity.

[0116] (4) Opening control of high temperature stage throttle valve

[0117] The high-temperature throttle valve uses the high-temperature evaporation temperature as the adjustment target. The specific opening is related to the high and low temperature refrigerants actually used. Assuming the low-temperature water outlet demand index is 7°C and the high-temperature water outlet demand index is 130°C, the high-temperature target evaporation temperature range is adjusted to between 65 and 40°C. The target high-temperature evaporation temperature is calculated using the following formula:

[0118] δQ 热 =Q 热 (△t 热 / △t' 热 -1),

[0119] T'=xδQ 热 2 +yδQ热 +z,

[0120] T h =T+T';

[0121] Where Th is the target high temperature stage evaporation temperature, T is the actual high temperature stage evaporation temperature, T' is the target high temperature stage evaporation temperature deviation, δQ 热 is the heating deviation (the deviation between the actual heating demand and the rated heating), Q 热 is the rated heat capacity, △t 热 is the preset hot water inlet and outlet temperature difference, △t' 热 is the actual hot water inlet and outlet temperature difference. x, y, and z are the heating capacity adjustment constants that vary according to the high and low temperature refrigerant media.

[0122] This embodiment dynamically adjusts the opening of the high- and low-temperature throttle valves and the compressor load output to change the refrigerant flow rate and pressure, thereby adjusting the cooling and heating output ratio, effectively resolving the imbalance between cooling and heating loads. This approach not only improves system efficiency but also enhances its adaptability and reliability, ensuring that energy consumption and operating costs are minimized while meeting user needs.

[0123] Example 3

[0124] Corresponding to Figure 4 The present embodiment provides a method for controlling the cooling and heating loads of a cascade cooling and heating cogeneration system. Figure 7 The structural block diagram of the cooling and heating load control device of the cascade cooling and heating cogeneration system shown in FIG. includes:

[0125] An acquisition module 10 is used to obtain the heating load demand and the cooling load demand of the cascade cooling and heating cogeneration system;

[0126] The first adjustment module 20 is connected to the acquisition module 10 and is used to detect the chilled water temperature when the heating load demand remains unchanged and the cooling load demand is adjusted, and to execute a corresponding control strategy according to the chilled water temperature to control the high-temperature stage throttle valve and the low-temperature stage throttle valve so that the high-temperature stage evaporation temperature is adjusted to a first target high-temperature stage evaporation temperature;

[0127] The second adjustment module 30 is connected to the acquisition module 10 and is used to detect the hot water temperature when the cooling load demand remains unchanged and the heating load demand is adjusted, and to execute a corresponding control strategy according to the hot water temperature to adjust the high-temperature throttle valve and the low-temperature throttle valve so that the high-temperature evaporation temperature is adjusted to the second target high-temperature evaporation temperature.

[0128] This embodiment also provides a cascade cooling and heating cogeneration system, which includes at least the above-mentioned cooling and heating load control device.

[0129] This embodiment provides a cascade combined cooling and heating system with an adjustable cooling and heating load output ratio. The system adopts a variable intermediate temperature (high-temperature evaporation temperature) design to adapt to and adjust the operating loads of the high-temperature and low-temperature systems and changes in refrigerant flow, and adjust the ratio of the system's output cooling capacity to heating capacity, while meeting actual cooling and heating load changes. There is no need to configure additional heating or refrigeration units to supplement user loads, which simplifies the overall system design, reduces system investment costs, and avoids the problem of heat and cold imbalance under combined cooling and heating.

[0130] Compared with conventional solutions, this embodiment does not require additional heating or cooling units. Through the cooling and heating load control device, it can simultaneously meet the user's cooling or heating needs, meet the independent cooling load or heating load changes of the cascade cooling and heating system, simplify the overall system solution design, and reduce the system investment cost.

[0131] Example 4

[0132] This embodiment provides an electronic device for use in a method for controlling cooling and heating loads in a cascade cooling and heating cogeneration system. The electronic device includes: at least one processor; and a memory communicatively connected to the at least one processor; wherein:

[0133] The memory stores instructions executable by the one processor, the instructions being executed by the at least one processor to enable the at least one processor to:

[0134] Obtain the heating load demand and cooling load demand of the cascade cogeneration system; if the heating load demand remains unchanged and the cooling load demand is adjusted, detect the chilled water temperature, execute the corresponding control strategy according to the size of the chilled water temperature, and regulate the high-temperature throttle valve and the low-temperature throttle valve to adjust the high-temperature evaporation temperature to the first target high-temperature evaporation temperature; if the cooling load demand remains unchanged and the heating load demand is adjusted, detect the hot water temperature, execute the corresponding control strategy according to the size of the hot water temperature, and regulate the high-temperature throttle valve and the low-temperature throttle valve to adjust the high-temperature evaporation temperature to the second target high-temperature evaporation temperature.

[0135] Example 5

[0136] An embodiment of the present invention provides a software for executing the technical solutions described in the above embodiment and preferred implementation manner.

[0137] An embodiment of the present invention provides a non-volatile computer storage medium storing computer-executable instructions capable of executing the cooling and heating load control method for a cascade cooling and heating cogeneration system in any of the above method embodiments.

[0138] The above-mentioned software is stored in the above-mentioned storage medium, which includes but is not limited to: a CD, a floppy disk, a hard disk, a rewritable memory, etc.

[0139] The serial numbers of the above embodiments of the present invention are for description only and do not represent the advantages or disadvantages of the embodiments.

[0140] In the above embodiments of the present invention, the description of each embodiment has its own focus. For parts that are not described in detail in a certain embodiment, reference can be made to the relevant descriptions of other embodiments.

[0141] In the several embodiments provided in this application, it should be understood that the disclosed technical content can be implemented in other ways. Among them, the device embodiments described above are only exemplary. For example, the division of the units can be a logical function division. In actual implementation, there may be other division methods, such as multiple units or components can be combined or integrated into another system, or some features can be ignored or not executed. Another point is that the mutual coupling or direct coupling or communication connection shown or discussed can be through some interfaces, indirect coupling or communication connection of units or modules, which can be electrical or other forms.

[0142] The units described as separate components may or may not be physically separate, and the components shown as units may or may not be physical units, that is, they may be located in one place or distributed across multiple units. Some or all of the units may be selected according to actual needs to achieve the purpose of the present embodiment.

[0143] In addition, the functional units in the various embodiments of the present invention may be integrated into a single processing unit, each unit may exist physically separately, or two or more units may be integrated into a single unit. The aforementioned integrated units may be implemented in the form of hardware or software functional units.

[0144] If the integrated unit is implemented in the form of a software functional unit and sold or used as an independent product, it can be stored in a computer-readable storage medium. Based on this understanding, the technical solution of the present invention, or the part that contributes to the prior art, or all or part of the technical solution can be embodied in the form of a software product. The computer software product is stored in a storage medium and includes several instructions for enabling a computer device (which can be a personal computer, server or network device, etc.) to perform all or part of the steps of the method described in each embodiment of the present invention. The aforementioned storage medium includes: various media that can store program codes, such as a USB flash drive, a read-only memory (ROM), a random access memory (RAM), a mobile hard disk, a magnetic disk or an optical disk.

[0145] The above-mentioned product can execute the method provided by the embodiment of the present invention, and has the functional modules and beneficial effects corresponding to the execution method. For technical details not fully described in this embodiment, please refer to the method provided by the embodiment of the present invention.

[0146] The electronic devices of the embodiments of the present invention exist in various forms, including but not limited to:

[0147] (1) Mobile communication devices: These devices are characterized by their mobile communication capabilities and are primarily designed to provide voice and data communications. These terminals include smartphones (e.g., iPhones), multimedia phones, feature phones, and low-end phones.

[0148] (2) Ultra-mobile personal computer devices: These devices fall under the category of personal computers, have computing and processing capabilities, and generally also have mobile Internet access. These terminals include PDAs, MIDs, and UMPCs, such as the iPad.

[0149] (3) Portable entertainment devices: These devices can display and play multimedia content. These devices include audio and video players (such as iPods), handheld game consoles, e-books, smart toys, and portable car navigation devices.

[0150] (4) Server: A device that provides computing services. The server consists of a processor, hard disk, memory, device bus, etc. The server is similar to a general computer architecture, but because it needs to provide highly reliable services, it has higher requirements in terms of processing power, stability, reliability, security, scalability, and manageability.

[0151] (5) Other electronic devices with data interaction functions, such as televisions, large-screen cars, etc.

[0152] The device embodiments described above are merely illustrative. The units described as separate components may or may not be physically separate, and the components shown as units may or may not be physical units, that is, they may be located in one place or distributed across multiple network units. Some or all of the modules may be selected based on actual needs to achieve the objectives of this embodiment.

[0153] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some of the technical features therein. However, these modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the various embodiments of the present invention.

Claims

1. A method for controlling the cooling and heating loads of a cascade cooling and heating cogeneration system, characterized in that: The method comprises: Obtain the heating load demand and cooling load demand of the cascade cogeneration system; If the heating load demand remains unchanged and the cooling load demand is adjusted, the chilled water temperature is detected, and a corresponding control strategy is executed according to the chilled water temperature to control the high-temperature stage throttle valve and the low-temperature stage throttle valve so that the high-temperature stage evaporation temperature is adjusted to the first target high-temperature stage evaporation temperature; If the cooling load demand remains unchanged and the heating load demand is adjusted, the hot water temperature is detected, and the corresponding control strategy is executed according to the size of the hot water temperature to control the high-temperature throttle valve and the low-temperature throttle valve so that the high-temperature evaporation temperature is adjusted to the second target high-temperature evaporation temperature.

2. The method according to claim 1, characterized in that After detecting the chilled water temperature, the method further includes: If the chilled water temperature is greater than the preset maximum chilled water temperature, it is determined that the refrigeration load needs to be increased; If the chilled water temperature is lower than the preset minimum chilled water temperature, it is determined that the refrigeration load needs to be reduced.

3. The method according to claim 1, characterized in that After detecting the chilled water temperature, the method further includes: The first target high-temperature-stage evaporation temperature is calculated according to the chilled water inlet and outlet temperature difference, the cooling capacity deviation, and the actual high-temperature-stage evaporation temperature.

4. The method according to claim 3, characterized in that The first target high-temperature stage evaporation temperature is calculated based on the chilled water inlet and outlet temperature difference, the cooling capacity deviation, and the actual high-temperature stage evaporation temperature, using the following formula: δQ 冷 =Q 冷 (△t 冷 / △t’ 冷 -1), T’=aδQ 冷 2 +bδQ 冷 +c, T h =T+T’; Among them, T h is the first target high-temperature stage evaporation temperature, T is the actual high-temperature stage evaporation temperature, T' is the target high-temperature stage evaporation temperature deviation, δQ 冷 is the cooling capacity deviation, Q 冷 is the rated cooling capacity, △t 冷 is the preset chilled water inlet and outlet temperature difference, △t' 冷 is the current chilled water inlet and outlet temperature difference, and a, b, and c are the preset cooling capacity adjustment constants.

5. The method according to claim 1, wherein Executing a corresponding control strategy according to the temperature of the chilled water to control the high-temperature throttle valve and the low-temperature throttle valve includes: If the chilled water temperature is greater than the preset maximum chilled water temperature, a corresponding control strategy is executed: the high-temperature stage throttle valve opening is reduced, and the low-temperature stage throttle valve opening is increased until the high-temperature stage evaporation temperature of the cascade cooling and heating cogeneration system is adjusted to a first target high-temperature stage evaporation temperature; If the chilled water temperature is lower than the preset minimum chilled water temperature, the corresponding control strategy is executed: the high-temperature stage throttle valve opening is increased, and the low-temperature stage throttle valve opening is decreased until the high-temperature stage evaporation temperature of the cascade cooling and heating cogeneration system is adjusted to the first target high-temperature stage evaporation temperature.

6. The method according to claim 1, wherein After detecting the hot water temperature, the method further includes: If the hot water temperature is greater than the preset maximum hot water temperature, it is determined that the heating load needs to be reduced; If the hot water temperature is lower than the preset minimum hot water temperature, it is determined that the heating load needs to be increased.

7. The method according to claim 1, characterized in that After detecting the hot water temperature, the method further includes: The second target high-temperature-stage evaporation temperature is calculated according to the hot water inlet and outlet temperature difference, the heating amount deviation, and the actual high-temperature-stage evaporation temperature.

8. The method according to claim 7, characterized in that The second target high-temperature stage evaporation temperature is calculated based on the hot water inlet and outlet temperature difference, heating deviation, and actual high-temperature stage evaporation temperature using the following formula: δQ 热 =Q 热 (△t 热 / △t’ 热 -1), T’=xδQ 热 2 +yδQ 热 +z, T h =T+T’; Among them, T h is the second target high-temperature stage evaporation temperature, T is the actual high-temperature stage evaporation temperature, T' is the target high-temperature stage evaporation temperature deviation, δQ 热 is the heating capacity deviation, Q 热 is the rated heat capacity, △t 热 is the preset hot water inlet and outlet temperature difference, △t' 热 is the current hot water inlet and outlet temperature difference, and x, y, and z are the preset heating amount adjustment constants.

9. The method according to claim 1, characterized in that Executing a corresponding control strategy according to the hot water temperature to control the high-temperature throttle valve and the low-temperature throttle valve includes: If the hot water temperature is greater than the preset maximum hot water temperature, a corresponding control strategy is executed: the high-temperature stage throttle valve opening is increased, and the low-temperature stage throttle valve opening is decreased until the high-temperature stage evaporation temperature of the cascade cooling and heating cogeneration system is adjusted to a second target high-temperature stage evaporation temperature; If the hot water temperature is lower than the preset minimum hot water temperature, the corresponding control strategy is executed: the high-temperature stage throttle valve opening is reduced, and the low-temperature stage throttle valve opening is increased until the high-temperature stage evaporation temperature of the cascade cooling and heating cogeneration system is adjusted to the second target high-temperature stage evaporation temperature.

10. A cooling and heating load control device for a cascade cooling and heating cogeneration system, characterized in that: The device comprises: An acquisition module is used to obtain the heating load demand and the cooling load demand of the cascade cooling and heating system; a first adjustment module, configured to detect a chilled water temperature when the heating load demand remains unchanged and the cooling load demand is adjusted, and execute a corresponding control strategy according to the chilled water temperature to control the high-temperature throttle valve and the low-temperature throttle valve so that the high-temperature evaporation temperature is adjusted to a first target high-temperature evaporation temperature; The second adjustment module is used to detect the hot water temperature when the cooling load demand remains unchanged and the heating load demand is adjusted, and to execute a corresponding control strategy according to the size of the hot water temperature to adjust the high-temperature throttle valve and the low-temperature throttle valve so that the high-temperature evaporation temperature is adjusted to the second target high-temperature evaporation temperature.

11. A cascade cooling and heating cogeneration system, characterized in that: The cascade cooling and heating cogeneration system at least includes the cooling and heating load control device of the cascade cooling and heating cogeneration system according to claim 10.

12. A computer-readable storage medium having a computer program stored thereon, characterized in that: When the program is executed by a processor, the method according to any one of claims 1 to 9 is implemented.

13. An electronic device, characterized in that: include: one or more processors; A storage device for storing one or more programs, which, when executed by the one or more processors, causes the one or more processors to implement the method according to any one of claims 1 to 9.

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