Exhaust control method, device, and system for a heat pump system with an economizer

Abstract

The present disclosure provides an exhaust control method, device and system of a heat pump system with an economizer, and relates to the field of control. The method comprises: adjusting an opening degree of a first throttling element to make a suction superheat degree of a compressor be in a first preset range and a refrigerant supercooling liquefaction degree of a main refrigerant line be in a second preset range when the heat pump system is in a heating state, the first throttling element being located between an evaporator and the economizer in the main refrigerant line; and adjusting an opening degree of a second throttling element to make a charge superheat degree of the compressor be in a third preset range and an exhaust temperature be in a fourth preset range when the refrigerant supercooling liquefaction degree of the main refrigerant line is in the second preset range, the second throttling element being located on a charge branch line and being located upstream of the economizer.

Description

Technical Field

[0001] This disclosure relates to the field of control, and more particularly to an exhaust control method, apparatus and system for a heat pump system with an economizer. Background Technology

[0002] Air source heat pumps often suffer from high exhaust temperatures under low evaporation and high condensation conditions. Gas injection enthalpy-boosting heat pump systems can effectively control exhaust temperatures and increase heating capacity at low temperatures. Most heat pump manufacturers' gas injection enthalpy-boosting heat pump systems control exhaust temperature using the superheat of the gas injection circuit, the pressure at the gas injection port, or the exhaust superheat. This method is simplistic and inflexible, failing to ensure stable and reliable operation of the unit across all operating conditions. Summary of the Invention

[0003] One technical problem this disclosure aims to solve is to provide an exhaust control method, device, and system for a heat pump system with an economizer, which can efficiently and stably control the exhaust temperature and improve the operational stability of the unit.

[0004] According to one aspect of this disclosure, an exhaust control method for a heat pump system with an economizer is proposed, comprising: when the heat pump system is in heating mode, adjusting the opening of a first throttling element so that the superheat of the compressor intake is within a first preset range and the degree of refrigerant subcooling liquefaction in the refrigerant main circuit is within a second preset range, wherein the first throttling element is located in the refrigerant main circuit between the evaporator and the economizer; when the degree of refrigerant subcooling liquefaction in the refrigerant main circuit is within the second preset range, adjusting the opening of a second throttling element so that the superheat of the compressor injection gas is within a third preset range and the exhaust temperature is within a fourth preset range, wherein the second throttling element is located in the injection gas branch circuit and upstream of the economizer.

[0005] In some embodiments, adjusting the opening degree of the first throttling element includes: obtaining a first difference between the compressor's suction temperature and the refrigerant temperature entering the evaporator, and a second difference between the refrigerant temperature entering the economizer in the refrigerant main circuit and the refrigerant temperature exiting the economizer; and adjusting the opening degree of the first throttling element based on the first difference and the second difference.

[0006] In some embodiments, adjusting the opening degree of the first throttling element based on a first difference and a second difference includes: increasing the opening degree of the first throttling element when the first difference is greater than or equal to a first threshold; maintaining the opening degree of the first throttling element when the first difference is less than the first threshold and greater than the second threshold, wherein when the first difference is less than the first threshold and greater than the second threshold, the compressor's suction superheat is within a first preset range and the refrigerant subcooling liquefaction degree in the refrigerant main circuit is within a second preset range; and adjusting the opening degree of the first throttling element based on the second difference when the first difference is less than or equal to the second threshold.

[0007] In some embodiments, when the first difference is less than or equal to a second threshold, adjusting the opening of the first throttling element based on the second difference includes: increasing the opening of the first throttling element when the second difference is greater than a third threshold; maintaining the opening of the first throttling element when the second difference is less than or equal to the third threshold and greater than or equal to a fourth threshold, wherein when the second difference is less than or equal to the third threshold and greater than or equal to the fourth threshold, the compressor's suction superheat is within a first preset range and the refrigerant subcooling liquefaction degree in the refrigerant main circuit is within a second preset range; and decreasing the opening of the first throttling element when the second difference is less than the fourth threshold.

[0008] In some embodiments, when the degree of refrigerant subcooling liquefaction in the refrigerant main circuit is within a second preset range, adjusting the opening of the second throttling element includes: obtaining a third difference between the refrigerant temperature exiting the economizer in the make-up gas branch and the refrigerant temperature entering the economizer, and the compressor discharge temperature; and controlling the second throttling element based on the third difference and the discharge temperature.

[0009] In some embodiments, adjusting the opening of the second throttling element based on the third difference and the exhaust temperature includes: increasing the opening of the second throttling element when the third difference is greater than the fifth threshold; and adjusting the opening of the second throttling element based on the exhaust temperature when the third difference is less than or equal to the fifth threshold, wherein the superheat of the compressor's gas supply is within a third preset range when the third difference is less than or equal to the fifth threshold.

[0010] In some embodiments, when the third difference is less than or equal to the fifth threshold, adjusting the opening of the second throttling element based on the exhaust temperature includes: increasing the opening of the second throttling element when the exhaust temperature is greater than or equal to a temperature threshold, or when the fourth difference between the exhaust temperature and the target temperature is greater than or equal to a sixth threshold; maintaining the opening of the second throttling element when the fourth difference is less than the sixth threshold and greater than the seventh threshold, wherein the exhaust temperature is within a fourth preset range when the fourth difference is less than the sixth threshold and greater than the seventh threshold; and decreasing the opening of the second throttling element when the fourth difference is less than or equal to the seventh threshold.

[0011] In some embodiments, when the exhaust temperature is greater than an eighth threshold, the opening of the second throttling element is increased during the adjustment of the first throttling element so that the exhaust temperature is within a fourth preset range.

[0012] According to another aspect of this disclosure, an exhaust control device for a heat pump system with an economizer is also proposed, comprising: a first regulating module configured to, when the heat pump system is in heating mode, regulate the opening of a first throttling element so that the compressor suction superheat is within a first preset range and the refrigerant subcooling liquefaction degree in the refrigerant main circuit is within a second preset range, wherein the first throttling element is located in the refrigerant main circuit between the evaporator and the economizer; and a second regulating module configured to, when the refrigerant subcooling liquefaction degree in the refrigerant main circuit is within the second preset range, regulate the opening of a second throttling element so that the compressor makeup gas superheat is within a third preset range and the exhaust temperature is within a fourth preset range, wherein the second throttling element is located in the makeup gas branch and upstream of the economizer.

[0013] According to another aspect of this disclosure, an exhaust control device for a heat pump system with an economizer is also proposed, comprising: a processor; and a memory coupled to the processor for storing instructions, which, when executed by the processor, cause the processor to perform the exhaust control method as described above.

[0014] According to another aspect of this disclosure, an exhaust control system for a heat pump system with an economizer is also provided, comprising: the exhaust control device described above; and a heat pump system with an economizer.

[0015] In some embodiments, the heat pump system includes: an economizer located between a first heat exchanger and a compressor inlet, the first heat exchanger serving as a condenser when the heat pump system is in heating mode; a first throttling element located in the refrigerant main line between a second heat exchanger and the economizer, the second heat exchanger serving as an evaporator when the heat pump system is in heating mode; and a second throttling element located in the inlet branch and upstream of the economizer.

[0016] In some embodiments, the heat pump system further includes: a first temperature sensing element configured to detect the suction temperature of the compressor; a second temperature sensing element configured to detect the refrigerant temperature entering the second heat exchanger; a third temperature sensing element configured to detect the refrigerant temperature entering the economizer in the refrigerant main circuit; a fourth temperature sensing element configured to detect the refrigerant temperature exiting the economizer in the refrigerant main circuit; a fifth temperature sensing element configured to detect the refrigerant temperature entering the economizer in the make-up gas branch circuit; a sixth temperature sensing element configured to detect the refrigerant temperature exiting the economizer in the make-up gas branch circuit; and a seventh temperature sensing element configured to detect the discharge temperature of the compressor.

[0017] According to another aspect of this disclosure, a computer-readable storage medium is also provided, on which computer instructions are stored, wherein the computer instructions, when executed by a processor, implement the exhaust control method described above.

[0018] According to another aspect of this disclosure, a computer program product is also proposed, comprising: computer instructions that, when executed by a processor, implement the exhaust control method described above.

[0019] In this embodiment, the first throttling element located in the refrigerant main circuit and the second throttling element located in the supplementary gas branch circuit are controlled in a coordinated manner. Furthermore, the action of the second throttling element is triggered after the first throttling element has been adjusted, thus avoiding the situation where the two throttling elements are adjusted and controlled simultaneously, thereby improving the stability, reliability and flexibility of exhaust temperature control.

[0020] Other features and advantages of this disclosure will become clear from the following detailed description of exemplary embodiments with reference to the accompanying drawings. Attached Figure Description

[0021] The accompanying drawings, which form part of this specification, illustrate embodiments of this disclosure and, together with the specification, serve to explain the principles of this disclosure.

[0022] This disclosure will become clearer with reference to the accompanying drawings and the following detailed description, wherein:

[0023] Figure 1 This is a schematic flowchart illustrating some embodiments of the exhaust control method for a heat pump system with an economizer disclosed herein;

[0024] Figure 2 This is a schematic flowchart illustrating some embodiments of adjusting the opening of the first throttling element according to the present disclosure;

[0025] Figure 3 This is a schematic flowchart illustrating some other embodiments of adjusting the opening of the first throttling element according to the present disclosure;

[0026] Figure 4 This is a schematic flowchart illustrating some embodiments of adjusting the opening of the second throttling element according to the present disclosure;

[0027] Figure 5 This is a schematic flowchart illustrating some other embodiments of adjusting the opening of the second throttling element according to the present disclosure;

[0028] Figure 6 These are schematic diagrams illustrating the structure of some embodiments of the heat pump system disclosed herein;

[0029] Figure 7 Block diagrams of some embodiments of the exhaust control device for a heat pump system with an economizer disclosed herein;

[0030] Figure 8 Block diagrams of some embodiments of the electronic devices disclosed herein;

[0031] Figure 9This is a block diagram of some embodiments of the exhaust control system of a heat pump system with an economizer disclosed herein. Detailed Implementation

[0032] Various exemplary embodiments of the present disclosure will now be described in detail with reference to the accompanying drawings. It should be noted that, unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the present disclosure.

[0033] At the same time, it should be understood that, for ease of description, the dimensions of the various parts shown in the accompanying drawings are not drawn according to actual scale.

[0034] The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit this disclosure or its application or use.

[0035] Techniques, methods, and equipment known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and equipment should be considered part of the specification.

[0036] In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values.

[0037] It should be noted that similar labels and letters in the following figures indicate similar items; therefore, once an item is defined in one figure, it does not need to be discussed further in subsequent figures.

[0038] To make the objectives, technical solutions, and advantages of this disclosure clearer, the following detailed description is provided in conjunction with specific embodiments and the accompanying drawings.

[0039] The lower the evaporation rate and the higher the condensation rate, the more difficult it is to control exhaust gas. When the unit is operating under extreme conditions, it relies solely on the superheat of the fuel gas in the economizer's fuel gas supply branch, the pressure at the fuel gas inlet, or the exhaust superheat to control the exhaust temperature. This control method is simplistic, inflexible, and unreliable. This disclosure provides an exhaust gas control scheme that can efficiently and stably control the exhaust temperature, improving the unit's operational stability. The scheme will be described below using specific embodiments as examples.

[0040] Figure 1 This is a schematic flowchart of some embodiments of the exhaust control method for a heat pump system with an economizer disclosed herein, which includes steps S1-S2.

[0041] In step S1, when the heat pump system is in heating mode, the opening of the first throttling element is adjusted so that the superheat of the compressor suction is within a first preset range and the degree of refrigerant subcooling liquefaction in the refrigerant main circuit is within a second preset range. The first throttling element is located in the refrigerant main circuit between the evaporator and the economizer.

[0042] The economizer of this heat pump system is, for example, a plate heat exchanger. This heat pump system has a gas injection enthalpy enhancement function.

[0043] This heat pump system can be applied to energy-saving air conditioners, etc.

[0044] The first throttling element is, for example, an expansion valve, specifically, an electronic expansion valve.

[0045] In some embodiments, the opening degree of the first throttling element is first adjusted to ensure that the compressor's suction superheat is within a first preset range, that is, to ensure that the compressor's suction superheat is not excessive. Then, the opening degree of the first throttling element is further adjusted to ensure that the degree of refrigerant subcooling liquefaction in the refrigerant main circuit is within a second preset range, that is, the refrigerant drawdown by the economizer is appropriate. At this point, the adjustment of the first throttling element located on the refrigerant main circuit is complete.

[0046] In step S2, when the degree of refrigerant subcooling liquefaction in the refrigerant main circuit is within the second preset range, the opening of the second throttling element is adjusted so that the superheat of the compressor's gas supply is within the third preset range and the exhaust temperature is within the fourth preset range. The second throttling element is located on the gas supply branch and upstream of the economizer.

[0047] The second throttling element is, for example, an expansion valve, specifically an electronic expansion valve.

[0048] After adjusting the first throttling element, adjust the second throttling element located on the gas supply branch. For example, first adjust the opening of the second throttling element to ensure that the superheat of the gas supply to the compressor is within the third preset range, that is, the superheat of the gas supply is not too high. Then further adjust the opening of the second throttling element to ensure that the exhaust temperature of the compressor is within the fourth preset range, that is, the exhaust temperature is not too high.

[0049] In the above embodiments, the first throttling element located in the refrigerant main circuit and the second throttling element located in the supplementary gas branch circuit are controlled in a coordinated manner. Furthermore, the action of the second throttling element is triggered after the first throttling element is adjusted, thus avoiding the situation where the two throttling elements are adjusted and controlled simultaneously, thereby improving the stability, reliability and flexibility of exhaust temperature control.

[0050] In some embodiments, adjusting the opening degree of the first throttling element includes: obtaining a first difference between the compressor's suction temperature and the refrigerant temperature entering the evaporator, and a second difference between the refrigerant temperature entering the economizer in the refrigerant main circuit and the refrigerant temperature exiting the economizer; and adjusting the opening degree of the first throttling element based on the first difference and the second difference.

[0051] For example, the first difference between the compressor's suction temperature and the refrigerant temperature entering the evaporator reflects the compressor's suction superheat; the second difference between the refrigerant temperature entering and exiting the economizer in the main refrigerant circuit reflects the degree of refrigerant subcooling liquefaction in the main refrigerant circuit, i.e., the degree of liquid extraction by the economizer. Therefore, by collecting the compressor's suction temperature, the refrigerant temperature entering the evaporator, and the refrigerant temperatures entering and exiting the economizer in the main refrigerant circuit, and then adjusting the opening of the first throttling element based on the first and second differences, the compressor's suction superheat is kept within acceptable limits while the economizer's liquid extraction degree is appropriate, thereby regulating the compressor's discharge temperature. This method of controlling the opening of the first throttling element is simple and flexible.

[0052] Figure 2 This is a schematic flowchart of some embodiments of adjusting the opening of the first throttling element according to the present disclosure, which includes steps S11-S14.

[0053] In step S11, a first difference is determined. If the first difference is greater than or equal to the first threshold T1, step S12 is executed. If the first difference is less than the first threshold T1 and greater than the second threshold T2, step S13 is executed. If the first difference is less than or equal to the second threshold T2, step S14 is executed.

[0054] In step S12, the opening degree of the first throttling element is increased.

[0055] If the first difference is greater than or equal to the first threshold T1, it indicates that the compressor suction overheating is too large, which means that the opening of the first throttling element is too small and needs to be increased to the normal range.

[0056] In step S13, the opening of the first throttling element is maintained. That is, the current step number of the first throttling element is maintained.

[0057] When the first difference is less than the first threshold and greater than the second threshold, the compressor's suction superheat is within the first preset range, and the refrigerant subcooling liquefaction degree in the refrigerant main circuit is within the second preset range. That is, the suction superheat is normal, and the second difference between the refrigerant temperature entering the economizer and the refrigerant temperature exiting the economizer in the refrigerant main circuit is also within the normal range.

[0058] In step S14, the opening degree of the first throttling element is adjusted based on the second difference.

[0059] If the first difference is less than or equal to the second threshold T2, it indicates that the compressor's suction superheat is within the normal range, but the degree of refrigerant subcooling liquefaction in the main refrigerant circuit is still uncertain. Therefore, it is necessary to determine whether the first throttling element needs to be adjusted further by comparing the second difference between the refrigerant temperature entering the economizer and the refrigerant temperature exiting the economizer in the main refrigerant circuit.

[0060] In the above embodiments, if the heat absorption is too high, the degree of refrigerant subcooling liquefaction in the main refrigerant circuit is adjusted, for example, by reducing the opening of the first throttling element. At this time, the compressor absorbs even more heat, resulting in a higher compressor discharge temperature. Therefore, the suction superheat is first brought within the normal range based on the first difference between the compressor suction temperature and the refrigerant temperature entering the evaporator. Then, the degree of refrigerant subcooling liquefaction in the main refrigerant circuit is adjusted based on the second difference between the refrigerant temperature entering the economizer and the refrigerant temperature exiting the economizer. This ensures more accurate adjustment of the throttling element and more stable operation of the heat pump system.

[0061] Below, in conjunction with Figure 3 The method of adjusting the opening of the first throttling element based on the second threshold when the first difference is less than or equal to the second threshold will be further described. For example... Figure 3 As shown, Figure 3 This is a flowchart illustrating another embodiment of adjusting the opening of the first throttling element according to the present disclosure, which includes steps S141-S144.

[0062] In step S141, a second difference is determined. If the second difference is greater than the third threshold T3, step S142 is executed; if the second difference is less than or equal to the third threshold T3 and greater than or equal to the fourth threshold T4, step S143 is executed; if the second difference is less than the fourth threshold T4, step S144 is executed.

[0063] In step S142, the opening degree of the first throttling element is increased.

[0064] A large temperature difference in the main circuit indicates that the condenser is fully liquefied, allowing the gas injection branch to draw more liquid refrigerant for heat exchange in the economizer before being added to the compressor to lower the discharge temperature. A second temperature difference greater than the third threshold T3 indicates that the economizer is drawing too much liquid, which may lead to an excessively low compressor discharge temperature. Therefore, it is necessary to increase the opening of the first throttling element to increase the refrigerant flow in the main circuit, reduce the gas injection, and raise the compressor discharge temperature.

[0065] In step S143, the opening of the first throttling element is maintained. That is, the first throttling element is kept inactive.

[0066] When the second difference is less than or equal to the third threshold and greater than or equal to the fourth threshold, the compressor's suction superheat is within the first preset range, and the refrigerant subcooling liquefaction degree in the main refrigerant circuit is within the second preset range. That is, the compressor's suction superheat is within the normal range, and the economizer's liquid intake degree is also within the normal range.

[0067] In step S144, the opening degree of the first throttling element is reduced.

[0068] If the main circuit subcooling temperature difference does not meet the requirements, the amount of liquid refrigerant in the make-up air branch will be insufficient, resulting in less medium-pressure refrigerant being supplied to the compressor and the exhaust temperature failing to decrease. Therefore, it is necessary to reduce the opening of the first throttling element, thereby reducing the amount of refrigerant flowing into the condenser and increasing the amount of refrigerant entering the economizer through the make-up air branch, thus lowering the exhaust temperature.

[0069] In this embodiment, the second difference between the refrigerant temperature entering the economizer in the refrigerant main circuit and the refrigerant temperature exiting the economizer reflects the degree of refrigerant subcooling liquefaction in the refrigerant main circuit. Therefore, the opening of the first throttling element is adjusted according to the second difference, that is, the amount of refrigerant entering the economizer through the make-up gas branch is adjusted, thereby affecting the compressor's exhaust temperature.

[0070] In some embodiments, when the degree of refrigerant subcooling liquefaction in the refrigerant main circuit is within a second preset range, adjusting the opening of the second throttling element includes: obtaining a third difference between the refrigerant temperature exiting the economizer in the make-up gas branch and the refrigerant temperature entering the economizer, and the compressor discharge temperature; and controlling the second throttling element based on the third difference and the discharge temperature.

[0071] The third difference between the refrigerant temperature exiting the economizer in the gas supply branch and the refrigerant temperature entering the economizer reflects the compressor's gas supply superheat. Therefore, by collecting the refrigerant temperatures exiting and entering the economizer in the gas supply branch, as well as the compressor's discharge temperature, the opening of the second throttling element can be adjusted based on this third difference and the discharge temperature to ensure that both the compressor's gas supply superheat and discharge temperature are within the normal range. This method of controlling the opening of the second throttling element is simple and flexible.

[0072] Figure 4 This is a schematic flowchart of some embodiments of adjusting the opening of the second throttling element according to the present disclosure, which includes steps S21-S24.

[0073] In step S21, the second difference and the third difference are determined. If the second difference is less than the fourth threshold T4, step S22 is executed. If the second difference is greater than or equal to the fourth threshold T4 and the third difference is greater than the fifth threshold T5, step S23 is executed. If the second difference is greater than or equal to the fourth threshold T4 and the third difference is less than or equal to the fifth threshold, step S24 is executed.

[0074] In step S22, the opening of the second throttling element is maintained.

[0075] If the second difference is less than the fourth threshold T4, it means that the first throttling element has not been adjusted, that is, the degree of refrigerant subcooling liquefaction in the main refrigerant circuit is not within the second preset range. Therefore, no action is taken to open the second throttling element.

[0076] In step S23, the opening degree of the second throttling element is increased.

[0077] If the second difference is greater than or equal to the fourth threshold T4 and the third difference is greater than the fifth threshold T5, it indicates that the compressor's gas injection superheat is too high. Therefore, it is necessary to increase the opening of the second throttling element so that more refrigerant passes through the gas injection branch to the economizer, thereby reducing the compressor's gas injection superheat.

[0078] In step S24, the opening of the second throttling element is adjusted based on the exhaust temperature.

[0079] If the third difference is less than or equal to the fifth threshold, it indicates that the compressor's gas supply superheat is within the third preset range, i.e., within the normal range. In this case, it is only necessary to adjust the opening of the second throttling element according to the compressor's exhaust temperature.

[0080] In this embodiment, adjusting the second throttling element after adjusting the first throttling element in the refrigerant main circuit reduces the likelihood of instability in the heat pump system caused by simultaneous adjustment of both elements. Furthermore, adjusting the exhaust temperature immediately when the compressor's intake superheat is excessive, such as by reducing the size of the second throttling element, would lead to even greater intake superheat in the compressor, causing instability in the heat pump system. Therefore, by first determining the third difference between the refrigerant temperature exiting the economizer and the refrigerant temperature entering the economizer in the intake branch, ensuring the compressor's intake superheat is within the normal range, and then adjusting the opening of the second throttling element based on the exhaust temperature to maintain the exhaust temperature within the normal range, the heat pump system operates more stably.

[0081] Below, in conjunction with Figure 5 The following section further explains how, when the third difference is less than or equal to the fifth threshold, the opening of the second throttling element is adjusted based on the exhaust temperature. For example... Figure 5 As shown, Figure 5 This is a flowchart illustrating another embodiment of adjusting the opening of the second throttling element according to the present disclosure, which includes steps S241-S244.

[0082] In step S241, the exhaust temperature is determined. If the exhaust temperature is greater than or equal to a temperature threshold, or if the fourth difference between the exhaust temperature and the target temperature is greater than or equal to a sixth threshold T6, step S242 is executed. If the fourth difference is less than the sixth threshold T6 but greater than the seventh threshold T7, step S243 is executed. If the fourth difference is less than or equal to the seventh threshold T7, step S244 is executed.

[0083] In step S242, the opening degree of the second throttling element is increased.

[0084] If the exhaust temperature is greater than or equal to the temperature threshold, or if the fourth difference between the exhaust temperature and the target temperature is greater than or equal to the sixth threshold, it indicates that the compressor exhaust temperature is too high. Therefore, it is necessary to increase the opening of the throttling element so that more liquid refrigerant can exchange heat in the economizer before being added to the compressor to reduce the exhaust temperature.

[0085] In step S243, the opening of the second throttling element is maintained.

[0086] If the fourth difference is less than the sixth threshold and greater than the seventh threshold, it indicates that the exhaust temperature is within the fourth preset range, that is, the exhaust temperature is within the normal range. Therefore, the current step number of the second throttling element is maintained.

[0087] In step S244, the opening degree of the second throttling element is reduced.

[0088] If the fourth difference is less than or equal to the seventh threshold, it indicates that the compressor discharge temperature is too low. Therefore, it is necessary to reduce the opening of the second throttling element and reduce the amount of medium-pressure refrigerant supplied to the compressor, thereby increasing the compressor discharge temperature.

[0089] In this embodiment, when the superheat of the replenished gas is within the normal range, the opening of the second throttling element is adjusted according to the exhaust temperature to keep the exhaust temperature within the normal range, which enables the heat pump system to operate more stably.

[0090] In other embodiments, when the exhaust temperature is greater than an eighth threshold, the opening of the second throttling element is increased during the adjustment of the first throttling element so that the exhaust temperature is within a fourth preset range.

[0091] For example, when extreme exhaust control conditions are triggered, such as excessively high exhaust temperatures leading to impending compressor lubricant carbonization and failure, motor insulation damage, or deformation or damage to mechanical components, the opening of the second throttling element should not be adjusted only after the opening of the first throttling element has been adjusted. This should be done when the exhaust temperature is less than or equal to the eighth threshold, i.e., the exhaust temperature is unlikely to cause equipment damage. Figure 1 The steps shown enable the high-performance solution to operate stably under extreme low ambient temperature and high water temperature conditions, thus improving the adaptability of the solution.

[0092] Below, in conjunction with Figure 6 The present disclosure will be described with reference to a specific embodiment. Figure 6This is a schematic diagram of the structure of some embodiments of the heat pump system disclosed herein. The heat pump system includes a compressor 1, a four-way valve 2, a first heat exchanger 3, an economizer 4, a second heat exchanger 5, and a gas-liquid separator 6. The exhaust port of the compressor 1 is connected to the first heat exchanger 3 and the second heat exchanger 5 via the four-way valve 2, and is also connected to one end of the gas-liquid separator 6 via the four-way valve 2. The other end of the gas-liquid separator 6 is connected to the suction port of the compressor 1. The first heat exchanger 3 is connected to the main inlet of the economizer 4, the makeup gas outlet of the economizer 4 is connected to the makeup gas port of the compressor 1, and the makeup gas inlet and main outlet of the economizer 4 are connected to one end of the second heat exchanger 5. The economizer 4 is, for example, a plate heat exchanger economizer.

[0093] In heating mode, the first heat exchanger 3 of this heat pump system functions as a condenser, and the second heat exchanger 5 functions as an evaporator, such as a finned evaporator. In defrosting mode, the first heat exchanger 3 functions as an evaporator, and the second heat exchanger 5 functions as a condenser. A fan 7 can also be installed at the second heat exchanger 5.

[0094] A first throttling element 8 is provided on the main line of the economizer 4 and the second heat exchanger 5. The first throttling element 8 is, for example, a main line electronic expansion valve. A second throttling element 9 is provided on the gas supply branch of the economizer 4 and upstream of the economizer 4. The second throttling element 9 is, for example, a gas supply branch electronic expansion valve.

[0095] The heat pump system can also be equipped with a first temperature detection element 10, a second temperature detection element 11, a third temperature detection element 12, a fourth temperature detection element 13, a fifth temperature detection element 14, a sixth temperature detection element 15, and a seventh temperature detection element 16, etc.

[0096] The first temperature sensing element 10 is configured to detect the suction temperature of the compressor. The first temperature sensing element 10, for example, a suction temperature sensor, is located between the four-way valve 2 and the gas-liquid separator 6.

[0097] The second temperature sensing element 11 is configured to detect the temperature of the refrigerant entering the second heat exchanger. The second temperature sensing element 11 is, for example, a pipe temperature sensing bulb, located, for example, between the second heat exchanger and the first throttling valve, and close to the second heat exchanger.

[0098] The third temperature sensing element 12 is configured to detect the temperature of the refrigerant entering the economizer in the refrigerant main circuit. The third temperature sensing element 12 is, for example, a plate heat exchanger main circuit inlet temperature sensor located at the refrigerant main circuit inlet of the economizer.

[0099] The fourth temperature sensing element 13 is configured to detect the refrigerant temperature at the outlet of the economizer in the main refrigerant line. The fourth temperature sensing element 13 is, for example, a temperature sensor at the outlet of the main heat exchanger line, located at the outlet of the main refrigerant line of the economizer, or located between the intersection of the main refrigerant line and the make-up gas branch line of the economizer and the first throttling element.

[0100] The fifth temperature sensing element 14 is configured to detect the temperature of the refrigerant entering the economizer in the make-up gas branch. The fifth temperature sensing element 14 is, for example, a plate heat exchanger make-up gas inlet temperature sensor, located in the make-up gas branch, for example, near the make-up gas inlet of the economizer.

[0101] The sixth temperature sensing element 15 is configured to detect the refrigerant temperature at the economizer outlet in the gas supply branch. The sixth temperature sensing element 15 is, for example, a plate heat exchanger gas supply outlet temperature sensor, located in the gas supply branch near the economizer gas supply outlet.

[0102] The seventh temperature sensing element 16 is configured to detect the compressor's exhaust temperature. The seventh temperature sensing element 16 is, for example, an exhaust temperature sensor located at the compressor's exhaust port.

[0103] Those skilled in the art should understand that the above is merely an example of a heat pump system. A driving radiator can also be installed in a heat pump system. This driving radiator is only present in refrigerant-driven heat dissipation and not in air-cooled driven heat dissipation. The driving radiator is located between the economizer and the first heat exchanger. A filter can also be installed between the driving radiator and the first heat exchanger. Filters can also be installed on both sides of the first throttling element. A high-pressure switch, a high-pressure sensor, etc., can also be installed between the compressor discharge port and the four-way valve. A low-pressure switch can also be installed between the gas-liquid separator and the compressor suction port. An ambient temperature sensor can also be installed near the second heat exchanger. This disclosure does not limit the structure of the heat pump system.

[0104] In northern-type heat pumps, the ultra-low evaporation temperature and ultra-high condensation temperature, among other harsh operating conditions, exacerbate the problem of high compressor exhaust temperature. While enthalpy-increasing heat pump systems can effectively reduce exhaust temperature and increase the heating capacity of low-temperature heat pumps, efficiently and stably controlling the enthalpy-increasing system remains a pressing issue. This disclosure addresses this problem by collaboratively controlling exhaust temperature using a main circuit electronic expansion valve and a supplementary circuit electronic expansion valve. For example, the main circuit electronic expansion valve controls the suction superheat and the liquid intake of the economizer. The supplementary circuit electronic expansion valve controls the exhaust temperature and the supplementary superheat. When the main circuit electronic expansion valve completes its adjustment or triggers extreme exhaust control conditions, the opening of the supplementary circuit electronic expansion valve is adjusted to improve the stability of exhaust temperature control. By placing a temperature sensor near the economizer to collect the main circuit inlet and outlet temperatures, as well as the supplementary gas inlet and outlet temperatures, the economizer's state can be accurately determined, allowing for supplementary gas adjustment. This disclosed solution effectively controls exhaust temperature with flexibility and adaptability, enabling stable operation under extreme low evaporation and high condensation conditions.

[0105] The above describes some embodiments of the exhaust control method. Below, the exhaust control device of a heat pump system with an economizer will be described in conjunction with the accompanying drawings.

[0106] like Figure 7 As shown, Figure 7This is a block diagram of some embodiments of an exhaust control device for a heat pump system with an economizer disclosed herein, the exhaust control device being, for example, a controller, including a first regulating module 71 and a second regulating module 72.

[0107] The first adjustment module 71 is configured to adjust the opening of the first throttling element when the heat pump system is in heating mode so that the superheat of the compressor suction is within a first preset range and the degree of refrigerant subcooling liquefaction in the refrigerant main circuit is within a second preset range. The first throttling element is located in the refrigerant main circuit between the evaporator and the economizer.

[0108] The second adjustment module 72 is configured to adjust the opening of the second throttling element when the degree of refrigerant subcooling liquefaction in the refrigerant main circuit is within the second preset range, so that the superheat of the compressor's gas supply is within the third preset range and the exhaust temperature is within the fourth preset range. The second throttling element is located on the gas supply branch and upstream of the economizer.

[0109] In this embodiment, the first throttling element located in the refrigerant main circuit and the second throttling element located in the supplementary gas branch circuit are controlled in a coordinated manner. Furthermore, the action of the second throttling element is triggered after the first throttling element has been adjusted, thus avoiding the situation where the two throttling elements are adjusted and controlled simultaneously, thereby improving the stability, reliability and flexibility of exhaust temperature control.

[0110] In some embodiments, the first adjustment module 71 is configured to acquire a first difference between the compressor suction temperature and the refrigerant temperature entering the evaporator, and a second difference between the refrigerant temperature entering the economizer in the refrigerant main circuit and the refrigerant temperature exiting the economizer; and adjust the opening degree of the first throttling element based on the first difference and the second difference.

[0111] In this embodiment, the compressor's suction temperature, refrigerant temperature entering the evaporator, and refrigerant temperatures entering and exiting the economizer in the main refrigerant circuit are collected. The opening of the first throttling element is then adjusted based on a first difference and a second difference to ensure that the compressor's suction superheat is not excessive and the economizer's liquid intake is appropriate, thereby regulating the compressor's discharge temperature. This method provides simple and flexible control over the opening of the first throttling element.

[0112] In some embodiments, the first adjustment module 71 is configured to increase the opening degree of the first throttling element when the first difference is greater than or equal to a first threshold; and maintain the opening degree of the first throttling element when the first difference is less than the first threshold and greater than a second threshold, wherein when the first difference is less than the first threshold and greater than the second threshold, the compressor's suction superheat is within a first preset range and the refrigerant subcooling liquefaction degree in the refrigerant main circuit is within a second preset range; and adjust the opening degree of the first throttling element based on the second difference when the first difference is less than or equal to the second threshold.

[0113] In the above embodiments, if the heat absorption is too high, the degree of refrigerant subcooling liquefaction in the main refrigerant circuit is adjusted, for example, by reducing the opening of the first throttling element. At this time, the compressor absorbs even more heat, resulting in a higher compressor discharge temperature. Therefore, the suction superheat is first brought within the normal range based on the first difference between the compressor suction temperature and the refrigerant temperature entering the evaporator. Then, the degree of refrigerant subcooling liquefaction in the main refrigerant circuit is adjusted based on the second difference between the refrigerant temperature entering the economizer and the refrigerant temperature exiting the economizer. This ensures more accurate adjustment of the throttling element and more stable operation of the heat pump system.

[0114] In some embodiments, the first adjustment module 71 is configured to increase the opening of the first throttling element when the second difference is greater than a third threshold; and to maintain the opening of the first throttling element when the second difference is less than or equal to the third threshold and greater than or equal to a fourth threshold, wherein when the second difference is less than or equal to the third threshold and greater than or equal to the fourth threshold, the compressor's suction superheat is within a first preset range and the refrigerant subcooling liquefaction degree in the refrigerant main circuit is within a second preset range; and to decrease the opening of the first throttling element when the second difference is less than the fourth threshold.

[0115] In this embodiment, the second difference between the refrigerant temperature entering the economizer in the refrigerant main circuit and the refrigerant temperature exiting the economizer reflects the degree of refrigerant subcooling liquefaction in the refrigerant main circuit. Therefore, the opening of the first throttling element is adjusted according to the second difference, that is, the amount of refrigerant entering the economizer through the make-up gas branch is adjusted, thereby affecting the compressor's exhaust temperature.

[0116] In some embodiments, the second regulating module 72 is configured to acquire a third difference between the refrigerant temperature at the outlet of the economizer and the refrigerant temperature at the inlet of the economizer in the gas supply branch, and the compressor discharge temperature; and control the second throttling element based on the third difference and the discharge temperature.

[0117] In this embodiment, the refrigerant temperature at the outlet and inlet of the economizer in the gas supply branch, as well as the compressor's discharge temperature, are collected. The opening of the second throttling element is then adjusted based on the third difference and the discharge temperature to ensure that the compressor's gas supply superheat is within the normal range and the discharge temperature is also within the normal range. This method provides simple and flexible control over the opening of the second throttling element.

[0118] In some embodiments, the second adjustment module 72 is configured to increase the opening of the second throttling element when the third difference is greater than the fifth threshold; and to adjust the opening of the second throttling element based on the exhaust temperature when the third difference is less than or equal to the fifth threshold, wherein the superheat of the compressor's gas supply is within a third preset range when the third difference is less than or equal to the fifth threshold.

[0119] In this embodiment, adjusting the second throttling element after adjusting the first throttling element in the refrigerant main circuit reduces the likelihood of instability in the heat pump system caused by simultaneous adjustment of both elements. Furthermore, adjusting the exhaust temperature immediately when the compressor's intake superheat is excessive, such as by reducing the size of the second throttling element, would lead to even greater intake superheat in the compressor, causing instability in the heat pump system. Therefore, by first determining the third difference between the refrigerant temperature exiting the economizer and the refrigerant temperature entering the economizer in the intake branch, ensuring the compressor's intake superheat is within the normal range, and then adjusting the opening of the second throttling element based on the exhaust temperature to maintain the exhaust temperature within the normal range, the heat pump system operates more stably.

[0120] In some embodiments, the second adjustment module 72 is configured to increase the opening of the second throttling element when the exhaust temperature is greater than or equal to a temperature threshold, or when the fourth difference between the exhaust temperature and the target temperature is greater than or equal to a sixth threshold; maintain the opening of the second throttling element when the fourth difference is less than the sixth threshold and greater than a seventh threshold, wherein the exhaust temperature is within a fourth preset range when the fourth difference is less than the sixth threshold and greater than the seventh threshold; and decrease the opening of the second throttling element when the fourth difference is less than or equal to the seventh threshold.

[0121] In this embodiment, when the superheat of the replenished gas is within the normal range, the opening of the second throttling element is adjusted according to the exhaust temperature to keep the exhaust temperature within the normal range, which enables the heat pump system to operate more stably.

[0122] In other embodiments, the second adjustment module 72 is further configured to increase the opening of the second throttling element during the adjustment of the first throttling element when the exhaust temperature is greater than the eighth threshold, so that the exhaust temperature is within the fourth preset range.

[0123] This embodiment enables the high-performance solution to operate stably under extreme low ambient temperature and high water temperature conditions, thus improving the adaptability of the solution.

[0124] It should be noted that the above modules are logical modules divided according to their specific functions, and are not used to restrict the specific implementation method. For example, they can be implemented in software, hardware, or a combination of software and hardware. In actual implementation, the above modules can be implemented as independent physical entities, or they can be implemented by a single entity (e.g., a processor (CPU or DSP, etc.), integrated circuit, etc.).

[0125] The exhaust control device for a heat pump system with an economizer can also exist in the form of electronic equipment, such as... Figure 8 As shown, Figure 8This is a block diagram of some embodiments of the electronic device 8 disclosed herein, which includes a memory 81 and a processor 82. The memory 81 may be a disk, flash memory, or any other non-volatile storage medium. The memory is used to store instructions as described in the above embodiments. The processor 82 is coupled to the memory 81 and may be implemented as one or more integrated circuits, such as a microprocessor or microcontroller. The processor 82 is used to execute the instructions stored in the memory.

[0126] In some embodiments, the processor 82 is coupled to the memory 81 via a BUS bus 8. The electronic device 8 can also be connected to an external storage device 85 via a storage interface 84 to access external data, and can also be connected to a network or another computer system (not shown) via a network interface 86. Further details are omitted here.

[0127] In this embodiment, the electronic device stores data instructions in a memory and then processes the instructions through a processor, thereby improving the stability, reliability, and flexibility of exhaust temperature control.

[0128] Figure 9 This is a block diagram of some embodiments of the exhaust control system of a heat pump system with an economizer disclosed herein, the exhaust control system including an exhaust control device 91 and a heat pump system 92 with an economizer.

[0129] The exhaust control device 91 has been described in detail in the above embodiments and will not be elaborated further here. The heat pump system 92 with an economizer has a gas replenishment and enthalpy increase function. Compared with a conventional heat pump system, it has an additional economizer and an electronic expansion valve and related pipelines on the gas replenishment branch. By controlling the valves in the heat pump system through the exhaust control device to achieve gas replenishment regulation, the exhaust temperature can be effectively controlled, and the control is flexible and highly adaptable. It can operate stably under extreme low evaporation and high condensation conditions.

[0130] In some embodiments, the heat pump system includes: an economizer located between a first heat exchanger and a compressor inlet, the first heat exchanger serving as a condenser when the heat pump system is in heating mode; a first throttling element located in the refrigerant main line between a second heat exchanger and the economizer, the second heat exchanger serving as an evaporator when the heat pump system is in heating mode; and a second throttling element located in the inlet branch and upstream of the economizer.

[0131] In other embodiments, the heat pump system further includes: a first temperature sensing element configured to detect the suction temperature of the compressor; a second temperature sensing element configured to detect the refrigerant temperature entering the second heat exchanger; a third temperature sensing element configured to detect the refrigerant temperature entering the economizer in the main refrigerant path; a fourth temperature sensing element configured to detect the refrigerant temperature exiting the economizer in the main refrigerant path; a fifth temperature sensing element configured to detect the refrigerant temperature entering the economizer in the make-up gas branch; a sixth temperature sensing element configured to detect the refrigerant temperature exiting the economizer in the make-up gas branch; and a seventh temperature sensing element configured to detect the discharge temperature of the compressor.

[0132] The specific locations of the various components in this embodiment can be referred to Figure 6 As shown.

[0133] This disclosure utilizes a main-line electronic expansion valve and a makeup gas branch electronic expansion valve to collaboratively control exhaust temperature. For example, the main-line electronic expansion valve controls the intake superheat and the liquid intake level of the economizer. The makeup gas branch electronic expansion valve controls the exhaust temperature and makeup gas superheat. When the main-line electronic expansion valve completes its adjustment or triggers extreme exhaust control conditions, the opening of the makeup gas branch electronic expansion valve is adjusted to improve the stability of exhaust temperature control. By placing a temperature sensor near the economizer to collect the main-line inlet and outlet temperatures of the economizer, as well as the makeup gas inlet and outlet temperatures, the state of the economizer can be accurately determined, thereby enabling makeup gas adjustment. The solution disclosed herein effectively controls exhaust temperature with flexible and adaptable control, and can operate stably under extreme low evaporation and high condensation conditions across all operating conditions.

[0134] In other embodiments, this application provides a computer-readable storage medium having computer program instructions stored thereon, which, when executed by a processor, implement the steps of the methods described above. Those skilled in the art will understand that embodiments of this application can be provided as methods, apparatus, or computer program products. Therefore, this application can take the form of a completely hardware embodiment, a completely software embodiment, or an embodiment combining software and hardware aspects. Furthermore, this application can take the form of a computer program product embodied on one or more computer-usable non-transitory storage media (including but not limited to disk storage, CD-ROM, optical storage, etc.) containing computer-usable program code.

[0135] In some embodiments of the application, a computer program product is also provided, including computer program instructions that, when executed by a processor, implement the method of any of the above embodiments.

[0136] The description of the various embodiments above tends to emphasize the differences between the various embodiments. The similarities or similarities between them can be referred to, and for the sake of brevity, they will not be repeated here.

[0137] This concludes the detailed description of the present disclosure. To avoid obscuring the concept of the disclosure, some details known in the art have not been described. Those skilled in the art will fully understand how to implement the technical solutions disclosed herein based on the above description.

[0138] The methods and apparatus of this disclosure may be implemented in many ways. For example, they may be implemented by software, hardware, firmware, or any combination of software, hardware, and firmware. The above-described order of steps for the methods is for illustrative purposes only, and the steps of the methods of this disclosure are not limited to the order specifically described above unless otherwise specifically stated. Furthermore, in some embodiments, this disclosure may also be implemented as a program recorded on a recording medium, the program including machine-readable instructions for implementing the methods according to this disclosure. Thus, this disclosure also covers recording media storing programs for performing the methods according to this disclosure.

[0139] While specific embodiments of this disclosure have been described in detail by way of example, those skilled in the art should understand that the examples are for illustrative purposes only and not intended to limit the scope of this disclosure. Those skilled in the art should understand that modifications can be made to the above embodiments without departing from the scope and spirit of this disclosure. The scope of this disclosure is defined by the appended claims.

Claims

1. A method for controlling discharge of a heat pump system having an economizer, comprising: adjusting an opening degree of a first throttling element to make a suction superheat degree of a compressor be in a first preset range and a supercooling liquefaction degree of a main refrigerant line be in a second preset range, when the heat pump system is in a heating state, the first throttling element being located in the main refrigerant line between an evaporator and the economizer, a second difference between a temperature of refrigerant entering the economizer and a temperature of refrigerant exiting the economizer in the main refrigerant line reflecting the supercooling liquefaction degree of the main refrigerant line, a main line inlet of the economizer being connected with a condenser, a charge outlet of the economizer being connected with a charge inlet of the compressor, a charge inlet of the economizer and a main line outlet being connected with one end of the evaporator; adjusting an opening degree of a second throttling element to make a charge superheat degree of the compressor be in a third preset range and a discharge temperature be in a fourth preset range, when the supercooling liquefaction degree of the main refrigerant line is in the second preset range, the second throttling element being located on a charge branch line and being located upstream of the economizer.

2. The exhaust control method according to claim 1, wherein, The adjusting of the opening degree of the first throttling element comprises: obtaining a first difference between a suction temperature of the compressor and a temperature of refrigerant entering the evaporator, and a second difference between the temperature of refrigerant entering the economizer and the temperature of refrigerant exiting the economizer in the main refrigerant line; adjusting the opening degree of the first throttling element based on the first difference and the second difference.

3. The exhaust control method according to claim 2, wherein The adjusting of the opening degree of the first throttling element based on the first difference and the second difference comprises: increasing the opening degree of the first throttling element, when the first difference is greater than or equal to a first threshold value; maintaining the opening degree of the first throttling element, when the first difference is less than the first threshold value and greater than a second threshold value, wherein, when the first difference is less than the first threshold value and greater than the second threshold value, the suction superheat degree of the compressor is in the first preset range and the supercooling liquefaction degree of the main refrigerant line is in the second preset range; adjusting the opening degree of the first throttling element based on the second difference, when the first difference is less than or equal to the second threshold value.

4. The exhaust control method according to claim 3, wherein The adjusting of the opening degree of the first throttling element based on the second difference, when the first difference is less than or equal to the second threshold value, comprises: increasing the opening degree of the first throttling element, when the second difference is greater than a third threshold value; maintaining the opening degree of the first throttling element, when the second difference is less than or equal to the third threshold value and greater than or equal to a fourth threshold value, wherein, when the second difference is less than or equal to the third threshold value and greater than or equal to the fourth threshold value, the suction superheat degree of the compressor is in the first preset range and the supercooling liquefaction degree of the main refrigerant line is in the second preset range; decreasing the opening degree of the first throttling element, when the second difference is less than the fourth threshold value.

5. The exhaust control method as set forth in any one of claims 1 to 4, wherein The adjusting of the opening degree of the second throttling element, when the supercooling liquefaction degree of the main refrigerant line is in the second preset range, comprises: obtaining a third difference between a temperature of refrigerant exiting the economizer and a temperature of refrigerant entering the economizer, and a discharge temperature of the compressor; controlling the second throttling element based on the third difference and the discharge temperature.

6. The exhaust control method according to claim 5, wherein adjusting an opening degree of the second throttling element based on the third difference and the discharge temperature includes: increasing the opening degree of the second throttling element when the third difference is greater than a fifth threshold value; adjusting the opening degree of the second throttling element based on the discharge temperature when the third difference is less than or equal to the fifth threshold value, wherein the superheat of the charge air of the compressor is in a third preset range when the third difference is less than or equal to the fifth threshold value.

7. The exhaust control method according to claim 6, wherein adjusting the opening degree of the second throttling element based on the discharge temperature when the third difference is less than or equal to the fifth threshold value includes: increasing the opening degree of the second throttling element when the discharge temperature is greater than or equal to a temperature threshold value, or a fourth difference between the discharge temperature and a target temperature is greater than or equal to a sixth threshold value; maintaining the opening degree of the second throttling element when the fourth difference is less than the sixth threshold value and greater than a seventh threshold value, wherein the discharge temperature is in a fourth preset range when the fourth difference is less than the sixth threshold value and greater than the seventh threshold value; decreasing the opening degree of the second throttling element when the fourth difference is less than or equal to the seventh threshold value.

8. The exhaust control method of any one of claims 1 to 4, further comprising: increasing the opening degree of the second throttling element during the adjusting of the first throttling element when the discharge temperature is greater than an eighth threshold value, so that the discharge temperature is in the fourth preset range.

9. An exhaust control device of a heat pump system having an economizer, comprising: a first adjusting module configured to adjust an opening degree of a first throttling element to make a suction superheat of a compressor in a first preset range and a degree of subcooled liquefaction of a main line of refrigerant in a second preset range when the heat pump system is in a heating state, the first throttling element being located in the main line of refrigerant between an evaporator and the economizer, a second difference between a temperature of refrigerant entering the economizer and a temperature of refrigerant exiting the economizer in the main line of refrigerant reflecting the degree of subcooled liquefaction of the main line of refrigerant, a main line inlet of the economizer being connected to a condenser, a charge air outlet of the economizer being connected to a charge air inlet of the compressor, and a charge air inlet and a main line outlet of the economizer being connected to one end of the evaporator; a second adjusting module configured to adjust an opening degree of a second throttling element to make a charge air superheat of the compressor in a third preset range and a discharge temperature in a fourth preset range when the degree of subcooled liquefaction of the main line of refrigerant is in the second preset range, the second throttling element being located on a charge air branch and upstream of the economizer.

10. An exhaust control device of a heat pump system having an economizer, comprising: a processor; and A memory coupled to the processor for storing instructions that, when executed by the processor, cause the processor to perform the exhaust control method of any one of claims 1 to 8.

11. An exhaust control system of a heat pump system with an economizer, comprising: the exhaust control device of claim 9 or 10; and the heat pump system with the economizer.

12. The exhaust control system according to claim 11, wherein, The heat pump system comprises: the economizer located between a first heat exchanger and a charge air port of a compressor, the first heat exchanger serving as a condenser when the heat pump system is in a heating mode; a first throttling element located in a main refrigerant line between a second heat exchanger and the economizer, the second heat exchanger serving as an evaporator when the heat pump system is in the heating mode; a second throttling element located in a charge air branch and upstream of the economizer.

13. The exhaust control system according to claim 12, wherein, The heat pump system further comprises: a first temperature detecting element configured to detect a suction temperature of the compressor; a second temperature detecting element configured to detect a temperature of refrigerant entering the second heat exchanger; a third temperature detecting element configured to detect a temperature of refrigerant entering the economizer in the main refrigerant line; a fourth temperature detecting element configured to detect a temperature of refrigerant exiting the economizer in the main refrigerant line; a fifth temperature detecting element configured to detect a temperature of refrigerant entering the economizer in the charge air branch; a sixth temperature detecting element configured to detect a temperature of refrigerant exiting the economizer in the charge air branch; a seventh temperature detecting element configured to detect a discharge temperature of the compressor.

14. A computer readable storage medium having stored thereon computer instructions, wherein, The computer instructions, when executed by the processor, implement the exhaust control method of any one of claims 1 to 8.

15. A computer program product, comprising: The computer program product comprising computer instructions, which, when executed by the processor, implement the exhaust control method of any one of claims 1 to 8.

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