Heating system, method and device for controlling a heating system

Abstract

The application discloses a heat supply system, a control method and equipment thereof. The heat supply system comprises a high-pressure compressor, a heat recovery condenser, a first heat exchanger, an evaporator, a second heat exchanger, a low-pressure throttling valve, a medium-pressure throttling valve, a first reversing valve, a second reversing valve, a low-pressure compressor, a heat storage water tank and a controller. The controller is used for controlling the conduction state of the first reversing valve and the second reversing valve, so that the system works in a first heat energy recovery mode or a second heat energy recovery mode. The application can fully utilize the waste water heat or the shallow soil heat by adjusting the changeable multi-heat source heat recovery structure, can realize heat energy recovery in multiple heat energy recovery modes, can improve the heat utilization rate of the waste water and the underground soil heat, and can improve the heating energy efficiency.

Description

Technical Field

[0001] This application belongs to the field of heat energy recovery technology, and in particular relates to a heating system, a control method for the heating system, and equipment. Background Technology

[0002] As an electrically driven low-carbon heating technology, heat pump technology can achieve high-efficiency heating with a high energy efficiency ratio by utilizing clean electricity. With the continuous development of solar, wind and nuclear energy, and the increasing cleanliness of electricity, heat pump technology is expected to replace gas and coal heating systems and become an important technology for achieving zero-carbon building heating.

[0003] However, in the building sector, traditional heat pumps are severely affected by low-temperature environments, while a large amount of high-quality waste heat in buildings is not fully utilized, resulting in significant energy waste in buildings. Summary of the Invention

[0004] This application provides a heating system, a control method for the heating system, and an apparatus that can significantly improve the heating efficiency and energy recovery rate of the heating system.

[0005] In a first aspect, embodiments of this application provide a heating system, which includes: a high-pressure compressor, a heat recovery condenser, a first heat exchanger, an evaporator, a second heat exchanger, a low-pressure throttling valve, a medium-pressure throttling valve, a first reversing valve, a second reversing valve, a low-pressure compressor, a hot water storage tank, and a controller.

[0006] The heat recovery condenser is used to exchange heat between the mixed refrigerant output from the high-pressure compressor and the heating medium from the heating equipment, and to discharge the first refrigerant and the second refrigerant; the first refrigerant and the second refrigerant exchange heat in the second heat exchanger;

[0007] The first heat exchanger is used to absorb the thermal energy of the target heat source based on the heat storage medium output from the hot water storage tank;

[0008] The evaporator is used to recover heat energy by exchanging heat between the heat storage medium and the refrigerant after collecting the heat energy from the target heat source.

[0009] The controller is used to control the conduction state of the first reversing valve and the second reversing valve so that the system operates in the first heat recovery mode or the second heat recovery mode.

[0010] In the first heat recovery mode, the target heat source is wastewater; the first refrigerant flows sequentially through the heat recovery condenser, the second heat exchanger, the low-pressure throttling valve, the first reversing valve, the second reversing valve, the low-pressure compressor, and the high-pressure compressor; the second refrigerant flows sequentially through the heat recovery condenser, the medium-pressure throttling valve, the first reversing valve, the evaporator, the second reversing valve, the second heat exchanger, and the high-pressure compressor.

[0011] In the second heat recovery mode, the target heat source is soil and wastewater; the first refrigerant flows sequentially through the heat recovery condenser, the second heat exchanger, the low-pressure throttling valve, the first reversing valve, the evaporator, the second reversing valve, the low-pressure compressor, and the high-pressure compressor; the second refrigerant flows sequentially through the heat recovery condenser, the medium-pressure throttling valve, the first reversing valve, the second reversing valve, the second heat exchanger, and the high-pressure compressor.

[0012] In some embodiments, the system further includes at least one of the following: a low-pressure evaporator for heat exchange between the first refrigerant discharged through the low-pressure throttling valve and the mixed air for heat recovery; the mixed air is obtained by mixing exhaust gas entering through the exhaust gas inlet and fresh air entering through the fresh air inlet; the first refrigerant flows into the low-pressure evaporator before flowing into the low-pressure compressor from the low-pressure throttling valve; and a medium-pressure evaporator for heat exchange between the second refrigerant discharged through the medium-pressure throttling valve and the exhaust gas entering through the exhaust gas inlet; the second refrigerant flows into the medium-pressure evaporator before flowing into the first reversing valve from the medium-pressure throttling valve.

[0013] In some embodiments, the system further includes at least one of the following: a multi-way valve for controlling the inflow of a first refrigerant and a second refrigerant into the multi-way valve through different channels; the first refrigerant flows into the multi-way valve before flowing from the low-pressure compressor into the high-pressure compressor; the second refrigerant flows into the multi-way valve before flowing from the second heat exchanger into the high-pressure compressor; a first circulation pump connected to the heat recovery condenser for driving the heating medium from the heating equipment to exchange heat with the mixed refrigerant in the heat recovery condenser; a second circulation pump connected to the first heat exchanger and the hot water storage tank respectively for driving the heat storage medium to flow in the first heat exchanger and the hot water storage tank; the refrigerant is a non-azeotropic refrigerant.

[0014] In some embodiments, the high-pressure compressor is a variable-frequency high-pressure compressor, and the low-pressure compressor is a variable-frequency low-pressure compressor; the controller is used to control the variable-frequency low-pressure compressor to a first preset frequency and the variable-frequency high-pressure compressor to a second preset frequency; when the variable-frequency low-pressure compressor is at the first preset frequency and the variable-frequency high-pressure compressor is at the second preset frequency, the first refrigerant flows from the low-pressure compressor into the multi-way valve at a first preset flow rate, and the second refrigerant flows from the second heat exchanger into the multi-way valve at a second preset flow rate.

[0015] In some embodiments, the controller is configured to control the conduction state of the first reversing valve and the second reversing valve based on a comparison between the target water temperature of the hot water storage tank and the target wastewater temperature; wherein, when the target wastewater temperature is higher than the target water temperature, the system operates in a first heat recovery mode under the control of the controller, the controller being configured to control the first reversing valve to conduct the low-pressure throttling valve and the second reversing valve, and to control the second reversing valve to conduct the first reversing valve and the low-pressure compressor; and, the controller being configured to control the first reversing valve to conduct the medium-pressure throttling valve and the evaporator before the second refrigerant flows into the second heat exchanger. The controller controls the second reversing valve to connect the second heat exchanger and the evaporator. When the target wastewater temperature is lower than or equal to the target water tank temperature, the system operates in a second heat recovery mode under the control of the controller. In the second heat recovery mode, the controller controls the first reversing valve to connect the low-pressure throttling valve and the evaporator, and controls the second reversing valve to connect the evaporator and the low-pressure compressor. Furthermore, before the second refrigerant flows into the second heat exchanger, the controller controls the first reversing valve to connect the medium-pressure throttling valve and the second reversing valve, and controls the second reversing valve to connect the first reversing valve and the second heat exchanger.

[0016] In some embodiments, the system further includes an exhaust gas fan connected to the controller, the controller controlling the exhaust gas flow rate at the exhaust gas inlet by controlling the rotational speed of the exhaust gas fan; a fresh air flow control valve connected to the controller and located at the inlet of the fresh air duct, the controller controlling the opening degree of the fresh air flow control valve to control the fresh air flow rate flowing into the fresh air duct, and controlling the exhaust gas flow rate flowing out of the indoor space to the exhaust gas duct connected to the exhaust gas inlet of the system; and a fresh air heat exchanger connected to the heating equipment and located at the inlet of the fresh air duct, for transmitting heating medium from the heating equipment. The system heats the fresh air by exchanging heat with the fresh air to be introduced into the fresh air duct. A fresh air heat exchange control valve is connected to the controller, the fresh air heat exchanger, and the heating equipment. The controller controls the entry of the heating medium from the heating equipment into the fresh air heat exchanger by controlling the opening and closing state of the fresh air heat exchange control valve. Specifically, when the exhaust fan is running, the controller opens the fresh air heat exchange control valve to allow the heating medium to flow into the fresh air heat exchanger; and when the exhaust fan stops running, the controller closes the fresh air heat exchange control valve to prevent the heating medium from flowing into the fresh air heat exchanger.

[0017] Secondly, embodiments of this application provide a control method for a heating system, the control method for the heating system including:

[0018] By controlling the conduction state of the first reversing valve and the second reversing valve, the system is controlled to be in the target heat recovery mode; wherein, the target heat recovery mode is the first heat recovery mode and the second heat recovery mode.

[0019] In some embodiments, controlling the system to be in the target heat recovery mode by controlling the conduction state of the first reversing valve and the second reversing valve includes: controlling the system to be in the target heat recovery mode by controlling the conduction state of the first reversing valve and the second reversing valve based on a temperature comparison result between the target water tank temperature of the hot water storage tank and the target wastewater temperature; wherein, when the temperature comparison result is that the target wastewater temperature is higher than the target water tank temperature, the target heat recovery mode is the first heat recovery mode, and when the temperature comparison result is that the target wastewater temperature is lower than or equal to the target water tank temperature, the target heat recovery mode is the second heat recovery mode.

[0020] In some embodiments, the above method further includes at least one of the following: controlling the variable frequency low-pressure compressor to a first preset frequency and the variable frequency high-pressure compressor to a second preset frequency; controlling the opening degree of the fresh air flow control valve of the system to control the fresh air flow into the fresh air duct of the system and the exhaust gas flow out of the indoor space to the exhaust gas duct connected to the exhaust gas inlet of the system; controlling the on / off state of the fresh air heat exchange control valve of the system to control the entry state of the heating medium into the fresh air heat exchanger; wherein, when the exhaust fan is running, the fresh air heat exchange control valve is controlled to open; wherein, when the fresh air heat exchange control valve is open, the heating medium flows into the fresh air heat exchanger; when the exhaust fan stops running, the fresh air heat exchange control valve is controlled to close; wherein, when the fresh air heat exchange control valve is closed, the heating medium is prevented from flowing into the fresh air heat exchanger.

[0021] Thirdly, embodiments of this application provide a control device for a heating system, the device comprising:

[0022] The mode switching module is used to control the system to be in a target heat recovery mode by controlling the conduction state of the first reversing valve and the second reversing valve; wherein the target heat recovery mode is either the first heat recovery mode or the second heat recovery mode.

[0023] Fourthly, embodiments of this application provide an electronic device, which includes the heating system described in the first aspect;

[0024] Alternatively, the electronic device includes a processor and a memory storing computer program instructions; the processor, when executing the computer program instructions, implements the control method of the heating system as described in the second aspect.

[0025] Fifthly, embodiments of this application provide a computer-readable storage medium storing computer program instructions, which, when executed by a processor, implement the control method for the heating system as described in the second aspect.

[0026] In a sixth aspect, embodiments of this application provide a computer program product in which instructions, when executed by a processor of an electronic device, cause the electronic device to perform the control method for the heating system as described in the second aspect.

[0027] The heating system, control method, apparatus, equipment, storage medium, and product of this application embodiment include a high-pressure compressor, a heat recovery condenser, a first heat exchanger, an evaporator, a second heat exchanger, a low-pressure throttling valve, a medium-pressure throttling valve, a first reversing valve, a second reversing valve, a low-pressure compressor, a hot water storage tank, and a controller. The controller can control the conduction state of the first and second reversing valves to put the system in a target heat energy recovery mode, which is either the first or second heat energy recovery mode, to utilize the heat from high-quality heat sources such as wastewater and underground soil, thereby improving the energy recovery rate of the heat source and the heating efficiency of the heating system. Attached Figure Description

[0028] To more clearly illustrate the technical solutions of the embodiments of this application, the accompanying drawings used in the embodiments of this application will be briefly introduced below. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0029] Figure 1 This is a system schematic diagram of the heating system provided in the embodiments of this application when operating in the first heat recovery mode;

[0030] Figure 2 This is an application diagram of the heating system provided in the embodiments of this application;

[0031] Figure 3 This is a flowchart illustrating the control method of the heating system provided in the embodiments of this application;

[0032] Figure 4 This is a system temperature entropy diagram of the heating system provided in the embodiments of this application when operating in the first heat recovery mode;

[0033] Figure 5 This is a system schematic diagram of the heating system provided in the embodiments of this application when operating in the second heat recovery mode;

[0034] Figure 6 This is a system temperature entropy diagram of the heating system provided in this application embodiment when operating in the second heat recovery mode;

[0035] Figure 7 This is a schematic diagram of the structure of the control device of the heating system provided in the embodiments of this application;

[0036] Figure 8 This is a schematic diagram of the structure of the electronic device provided in the embodiments of this application. Detailed Implementation

[0037] The features and exemplary embodiments of various aspects of this application will be described in detail below. To make the objectives, technical solutions, and advantages of this application clearer, the application will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be understood that the specific embodiments described herein are only intended to explain this application and not to limit it. For those skilled in the art, this application can be implemented without some of these specific details. The following description of the embodiments is merely to provide a better understanding of this application by illustrating examples.

[0038] It should be noted that, in this document, relational terms such as "first" and "second" are used merely to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising..." does not exclude the presence of additional identical elements in the process, method, article, or apparatus that includes said element.

[0039] To address the related technical problems, embodiments of this application provide a heating system, as well as a control method, apparatus, equipment, storage medium, and computer program product for the heating system. The heating system provided in the embodiments of this application will be described below.

[0040] Figure 1 A schematic diagram of the heating system provided in an embodiment of this application is shown. It should be noted that... Figure 1 The structural diagram shown is an example of the system principle diagram of the heating system in the first heat recovery mode. Figure 1 As shown, the heating system includes a high-pressure compressor COM2, a heat recovery condenser CON, a first heat exchanger GHE, an evaporator EVA3, a second heat exchanger ECO, a low-pressure throttling valve EV1, a medium-pressure throttling valve EV2, a first reversing valve FV1, a second reversing valve FV2, a low-pressure compressor COM1, a high-pressure compressor COM2, a hot water storage tank TAN1, and a controller.

[0041] Specifically, the outlet of the high-pressure compressor COM2 is connected to the inlet of the heat recovery condenser CON. The outlet of the heat recovery condenser CON is connected to the inlet of the medium-pressure throttling valve EV2 and the inlet of the second heat exchanger ECO. The outlet of the second heat exchanger ECO is connected to the inlet of the low-pressure throttling valve EV1. The first reversing valve FV1 is connected to the outlet of the medium-pressure throttling valve EV2, the outlet of the low-pressure throttling valve EV1, the inlet of the evaporator EVA3, and the second reversing valve FV2. The second reversing valve FV2 is connected to the inlet of the second heat exchanger ECO, the inlet of the low-pressure compressor COM1, and the outlet of the evaporator EVA3. The outlet of the low-pressure compressor COM1 is connected to the inlet of the high-pressure compressor COM2. The outlet of the second heat exchanger ECO is connected to the inlet of the high-pressure compressor COM2.

[0042] The outlet of the heat recovery condenser CON is connected to the inlet of the second heat exchanger ECO. The inlet of the second heat exchanger ECO, which is connected to the first reversing valve FV1, can be a different inlet of the second heat exchanger ECO. The inlet of the low-pressure throttling valve EV1 is connected to the outlet of the second heat exchanger ECO. The outlet of the second heat exchanger ECO, which is connected to the inlet of the high-pressure compressor COM2, can be a different outlet of the second heat exchanger ECO. The second reversing valve FV2 can be connected to the inlet of the second heat exchanger ECO, the inlet of the low-pressure compressor COM1, the outlet of the evaporator EVA3, and the first reversing valve FV1 through different interfaces. The first reversing valve FV1 can be connected to the outlet of the medium-pressure throttling valve EV2, the outlet of the low-pressure throttling valve EV1, the inlet of the evaporator EVA3, and the second reversing valve FV2 through different interfaces.

[0043] The heat recovery condenser CON is used to exchange heat between the mixed refrigerant output from the high-pressure compressor COM2 and the heating medium from the heating equipment TAN2, and to discharge the first refrigerant and the second refrigerant.

[0044] The aforementioned heating equipment can be used to supply heat to heating devices, and the aforementioned heating devices can be used to supply heat to the outside environment.

[0045] The first refrigerant and the second refrigerant exchange heat in the second heat exchanger ECO.

[0046] The first heat exchanger, GHE, is used to absorb the thermal energy of the target heat source based on the heat storage medium output from the hot water storage tank TAN1.

[0047] The evaporator EVA3 is used to recover heat energy by exchanging heat between the heat storage medium and the refrigerant after collecting the heat energy from the target heat source.

[0048] Specifically, the evaporator EVA3 is located inside the hot water storage tank TAN1. When the target heat source is wastewater, the evaporator EVA3 is used to recover waste heat by exchanging heat between the heat storage medium (after absorbing wastewater heat) and the second refrigerant discharged from the medium-pressure throttling valve EV2 before the first and second refrigerants exchange heat in the second heat exchanger ECO, and then discharges the second refrigerant to the second heat exchanger ECO. Alternatively, when the target heat source is wastewater, the evaporator EVA3 is used to recover waste heat by exchanging heat between the heat storage medium (after absorbing soil heat and wastewater heat) and the first refrigerant discharged from the low-pressure throttling valve EV1 after the first and second refrigerants exchange heat in the second heat exchanger ECO, and then discharges the first refrigerant to the low-pressure compressor COM1.

[0049] The aforementioned heat exchange between the first refrigerant and the second refrigerant in the second heat exchanger ECO can be either the second refrigerant discharged from the evaporator EVA3 exchanging heat with the first refrigerant discharged from the heat recovery condenser CON, or the first refrigerant discharged from the heat recovery condenser CON exchanging heat with the second refrigerant discharged from the intermediate-pressure throttling valve EV2. The second heat exchanger ECO can be used to discharge the first refrigerant to the low-pressure throttling valve EV1 and the second refrigerant to the high-pressure compressor COM2 after the heat exchange between the first and second refrigerants in the second heat exchanger ECO.

[0050] Specifically, the low-pressure throttling valve EV1 is used to throttle the first refrigerant discharged from the second heat exchanger ECO, and the medium-pressure throttling valve EV2 is used to throttle the second refrigerant discharged from the heat recovery condenser CON. The first reversing valve FV1 and the second reversing valve FV2 are used to control the conduction relationship between the second heat exchanger ECO, the low-pressure throttling valve EV1, the medium-pressure throttling valve EV2, the low-pressure compressor COM1, and the evaporator EVA3.

[0051] The controller is used to control the conduction state of the first reversing valve FV1 and the second reversing valve FV2 so that the system operates in the first heat recovery mode or the second heat recovery mode.

[0052] In the first heat recovery mode, the target heat source is wastewater. The first refrigerant flows successively through the heat recovery condenser CON, the second heat exchanger ECO, the low-pressure throttling valve EV1, the first reversing valve FV1, the second reversing valve FV2, the low-pressure compressor COM1, and the high-pressure compressor COM2. The second refrigerant flows successively through the heat recovery condenser CON, the medium-pressure throttling valve EV2, the first reversing valve FV1, the evaporator EVA3, the second reversing valve FV2, the second heat exchanger ECO, and the high-pressure compressor COM2.

[0053] In the second heat recovery mode, the target heat source is soil and wastewater. The first refrigerant flows successively through the heat recovery condenser CON, the second heat exchanger ECO, the low-pressure throttling valve EV1, the first reversing valve FV1, the evaporator EVA3, the second reversing valve FV2, the low-pressure compressor COM1, and the high-pressure compressor COM2. The second refrigerant flows successively through the heat recovery condenser CON, the medium-pressure throttling valve EV2, the first reversing valve FV1, the second reversing valve FV2, the second heat exchanger ECO, and the high-pressure compressor COM2.

[0054] The aforementioned high-pressure compressor COM2 can be a variable frequency high-pressure compressor, and the low-pressure compressor COM1 can be a variable frequency low-pressure compressor. The controller can be used to control the flow rate of refrigerant discharged by the compressor by controlling the compressor frequency.

[0055] In some embodiments, the refrigerant described above may be a non-azeotropic refrigerant.

[0056] In some embodiments, the controller is used to control the conduction state of the first reversing valve FV1 and the second reversing valve FV2 based on the comparison result between the target water tank temperature of the hot water storage tank TAN1 and the target wastewater temperature.

[0057] Specifically, when the target wastewater temperature is higher than the target water tank temperature, the heating system operates in the first heat recovery mode under the control of the controller. The controller controls the first reversing valve FV1 to open the low-pressure throttling valve EV1 and the second reversing valve FV2, and controls the second reversing valve FV2 to open the first reversing valve FV1 and the low-pressure compressor COM1. Furthermore, before the second refrigerant flows into the second heat exchanger ECO, the controller controls the first reversing valve FV1 to open the medium-pressure throttling valve EV2 and the evaporator EVA3, and controls the second reversing valve FV2 to open the second heat exchanger ECO and the evaporator EVA3.

[0058] When the target wastewater temperature is lower than or equal to the target water tank temperature, the heating system operates in the second heat recovery mode under the control of the controller. In the second heat recovery mode, the controller controls the first reversing valve FV1 to open the low-pressure throttling valve EV1 and the evaporator EVA3, and controls the second reversing valve FV2 to open the evaporator EVA3 and the low-pressure compressor COM1. Furthermore, before the second refrigerant flows into the second heat exchanger ECO, the controller controls the first reversing valve FV1 to open the medium-pressure throttling valve EV2 and the second reversing valve FV2, and controls the second reversing valve FV2 to open the first reversing valve FV1 and the second heat exchanger ECO.

[0059] In some embodiments, the controller is used to control the conduction state of the first reversing valve FV1 and the second reversing valve FV2 according to the target wastewater temperature.

[0060] When the target wastewater temperature exceeds a preset temperature threshold, the heating system operates in a first heat recovery mode under the control of the controller. When the target wastewater temperature does not exceed the preset temperature threshold, the heating system operates in a second heat recovery mode under the control of the controller.

[0061] In one embodiment, the first heat exchanger GHE can be a gravity film heat exchanger, the heat recovery condenser CON can be a plate condenser, the second heat exchanger ECO can be an economic heat exchanger, the evaporator EVA3 can be an immersion evaporator, the low-pressure throttling valve EV1 can be a low-pressure electronic expansion valve, the medium-pressure throttling valve EV2 can be a medium-pressure electronic expansion valve, and both the first reversing valve FV1 and the second reversing valve FV2 can be four-way reversing valves.

[0062] In some embodiments, the heating system further includes a low-pressure evaporator EVA1. The low-pressure evaporator EVA1 is used to exchange heat between the first refrigerant discharged through the low-pressure throttling valve EV1 and the mixed air for heat recovery.

[0063] The aforementioned heating system may also include an exhaust gas inlet AI2 and a fresh air inlet AI1, wherein the mixed air is obtained by mixing the exhaust gas entering through the exhaust gas inlet AI2 and the fresh air entering through the fresh air inlet AI1.

[0064] Specifically, the inlet of the low-pressure evaporator EVA1 is connected to the outlet of the low-pressure throttling valve EV1, and the outlet of the low-pressure evaporator EVA1 is connected to the first reversing valve FV1.

[0065] The first refrigerant flows into the low-pressure evaporator EVA1 before flowing from the low-pressure throttling valve EV1 into the first reversing valve FV1. That is, the first refrigerant flows sequentially through the heat recovery condenser CON, the second heat exchanger ECO, the low-pressure throttling valve EV1, the first reversing valve FV1, the second reversing valve FV2, the low-pressure compressor COM1, and the high-pressure compressor COM2. Alternatively, the first refrigerant can flow sequentially through the heat recovery condenser CON, the second heat exchanger ECO, the low-pressure throttling valve EV1, the low-pressure evaporator EVA1, the first reversing valve FV1, the second reversing valve FV2, the low-pressure compressor COM1, and the high-pressure compressor COM2. The refrigerant flows sequentially through the heat recovery condenser CON, the second heat exchanger ECO, the low-pressure throttling valve EV1, the first reversing valve FV1, the evaporator EVA3, the second reversing valve FV2, the low-pressure compressor COM1, and the high-pressure compressor COM2.

[0066] In one embodiment, the aforementioned low-pressure evaporator EVA1 can be a low-pressure tube-fin evaporator.

[0067] In some embodiments, the heating system further includes a medium-pressure evaporator EVA2, which is used to exchange heat between the second refrigerant discharged through the medium-pressure throttling valve EV2 and the exhaust gas entering through the exhaust gas inlet AI2.

[0068] Specifically, the inlet of the medium-pressure evaporator EVA2 is connected to the outlet of the medium-pressure throttling valve EV2, and the outlet of the medium-pressure evaporator EVA2 is connected to the first reversing valve FV1.

[0069] The second refrigerant flows into the medium-pressure evaporator EVA2 before flowing from the medium-pressure throttling valve EV2 into the first reversing valve FV1. The second refrigerant flows sequentially through the heat recovery condenser CON, the intermediate-pressure throttling valve EV2, the first reversing valve FV1, the evaporator EVA3, the second reversing valve FV2, the second heat exchanger ECO, and the high-pressure compressor COM2. Alternatively, the second refrigerant can flow sequentially through the heat recovery condenser CON, the intermediate-pressure throttling valve EV2, the intermediate-pressure evaporator EVA2, the first reversing valve FV1, the evaporator EVA3, the second reversing valve FV2, the second heat exchanger ECO, and the high-pressure compressor COM2.

[0070] In one embodiment, the medium-pressure evaporator EVA2 can be a medium-pressure tube-fin evaporator.

[0071] In some embodiments, the heating system further includes a multi-pass valve TV, which controls the first refrigerant and the second refrigerant to flow into the multi-pass valve TV through different channels.

[0072] The inlet of the aforementioned multi-way valve TV is connected to the outlet of the second heat exchanger ECO and the outlet of the low-pressure compressor COM1, respectively. The outlet of the second heat exchanger ECO and the outlet of the low-pressure compressor COM1 are connected to different inlet channels of the multi-way valve TV. The outlet of the multi-way valve TV is connected to the inlet of the high-pressure compressor COM2.

[0073] Before flowing from the low-pressure compressor COM1 into the high-pressure compressor COM2, the first refrigerant flows into the multi-way valve. This first refrigerant then flows sequentially through the heat recovery condenser CON, the second heat exchanger ECO, the low-pressure throttling valve EV1, the first reversing valve FV1, the second reversing valve FV2, the low-pressure compressor COM1, and the high-pressure compressor COM2. Alternatively, the first refrigerant can flow sequentially through the heat recovery condenser CON, the second heat exchanger ECO, the low-pressure throttling valve EV1, the first reversing valve FV1, the second reversing valve FV2, the low-pressure compressor COM1, and the multi-way valve TV. The first refrigerant flows sequentially through the heat recovery condenser CON, the second heat exchanger ECO, the low-pressure throttling valve EV1, the first reversing valve FV1, the evaporator EVA3, the second reversing valve FV2, the low-pressure compressor COM1, and the high-pressure compressor COM2.

[0074] Before flowing from the second heat exchanger ECO into the high-pressure compressor COM2, the second refrigerant flows into the multi-way valve. The second refrigerant then flows sequentially through the heat recovery condenser CON, the intermediate-pressure throttling valve EV2, the first reversing valve FV1, the evaporator EVA3, the second reversing valve FV2, the second heat exchanger ECO, and the high-pressure compressor COM2. Alternatively, the second refrigerant can flow sequentially through the heat recovery condenser CON, the intermediate-pressure throttling valve EV2, the first reversing valve FV1, the evaporator EVA3, the second reversing valve FV2, the second heat exchanger ECO, the multi-way valve TV, and the high-pressure compressor COM2.

[0075] In one embodiment, the aforementioned multi-way valve TV can be a three-way valve.

[0076] In some embodiments, the high-pressure compressor COM2 can be a variable frequency high-pressure compressor, and the low-pressure compressor COM1 can be a variable frequency low-pressure compressor.

[0077] The controller is used to control the variable frequency low-pressure compressor to a first preset frequency and the variable frequency high-pressure compressor to a second preset frequency. When the variable frequency low-pressure compressor is at the first preset frequency and the variable frequency high-pressure compressor is at the second preset frequency, the first refrigerant flows into the multi-way valve from the low-pressure compressor COM1 at a first preset flow rate, and the second refrigerant flows into the multi-way valve from the second heat exchanger ECO at a second preset flow rate.

[0078] The main purpose of a multi-channel valve (TV) can also be to decouple the flow rates of the first and second refrigerants, allowing the two refrigerants to be regulated separately.

[0079] The controller can be used to determine a first preset frequency of the variable frequency low-pressure compressor and a second preset frequency of the variable frequency high-pressure compressor based on the target indoor temperature of the building heated by the heating system and the target water tank temperature of the hot water storage tank. In one embodiment, the first preset frequency of the variable frequency low-pressure compressor and the second preset frequency of the variable frequency high-pressure compressor can be determined based on the target indoor temperature of the building heated by the heating system, the target water tank temperature, and a first mapping rule. The aforementioned first mapping rule is used to characterize the correspondence between the indoor temperature, the water tank temperature, the frequency of the variable frequency low-pressure compressor, and the frequency of the variable frequency high-pressure compressor.

[0080] The above-mentioned determination of the first preset frequency of the variable frequency low-pressure compressor and the second preset frequency of the variable frequency high-pressure compressor based on the target indoor temperature of the building heated by the heating system, the target water tank temperature of the hot water storage tank, and the first mapping rule can be achieved by determining the frequency of the variable frequency low-pressure compressor corresponding to the target indoor temperature and the target water tank temperature in the first mapping rule as the first preset frequency, and determining the frequency of the variable frequency high-pressure compressor corresponding to the target indoor temperature and the target water tank temperature in the first mapping rule as the second preset frequency.

[0081] In some embodiments, the controller can also be used to determine the first opening degree of the low-pressure throttling valve and the second opening degree of the medium-pressure throttling valve based on the target indoor temperature of the building heated by the heating system and the target water tank temperature of the hot water storage tank. In one embodiment, the first opening degree of the low-pressure throttling valve and the second opening degree of the medium-pressure throttling valve can be determined based on the target indoor temperature of the building heated by the heating system, the target water tank temperature, and a second mapping rule. The second mapping rule is used to characterize the correspondence between the indoor temperature, the water tank temperature, the opening degree of the low-pressure throttling valve, and the opening degree of the medium-pressure throttling valve.

[0082] The above-mentioned determination of the first opening degree of the low-pressure throttling valve and the second opening degree of the medium-pressure throttling valve based on the target indoor temperature of the building heated by the heating system, the target water tank temperature of the hot water storage tank, and the second mapping rule can be achieved by determining the opening degree of the low-pressure throttling valve corresponding to the target indoor temperature and the target water tank temperature in the second mapping rule as the first opening degree, and determining the opening degree of the medium-pressure throttling valve corresponding to the target indoor temperature and the target water tank temperature in the second mapping rule as the second opening degree.

[0083] In some embodiments, the heating system further includes a first circulating pump PUM1, which is connected to a heat recovery condenser CON and is used to drive the heating medium from the heating equipment TAN2 to exchange heat with the mixed refrigerant in the heat recovery condenser CON.

[0084] In some embodiments, the heating system further includes a second circulation pump PUM2, which is connected to the first heat exchanger GHE and the hot water storage tank TAN1 respectively. The second circulation pump PUM2 is used to drive the heat storage medium to flow in the first heat exchanger GHE and the hot water storage tank TAN1.

[0085] Reference Figure 2 , Figure 2 This is an application diagram of the heating system provided in the embodiments of this application, such as... Figure 2 As shown, in some embodiments, the heating system further includes a fresh air handling device, which includes a fresh air duct (FAD) and a fresh air flow control valve (DAM).

[0086] The controller, connected to the fresh air flow control valve DAM, controls the flow rate of fresh air entering the fresh air duct FAD and the flow rate of exhaust gas exiting the indoor space to the exhaust gas duct EAD, which connects to the system's exhaust gas inlet, by controlling the opening of the fresh air flow control valve DAM. The heating system also includes an exhaust gas duct EAD, which connects the exhaust gas inlet AI2 to the building interior. The fresh air duct FAD connects the building exterior and interior, and the fresh air flow control valve DAM can be located at the inlet of the fresh air duct FAD. The aforementioned indoor space can be the indoor space of the building heated by the heating system.

[0087] In some embodiments, the above-mentioned fresh air handling equipment further includes a fresh air heat exchanger FHX and a fresh air heat exchange control valve CV.

[0088] The fresh air heat exchanger FHX is connected to the heating equipment TAN2 and located at the inlet of the fresh air duct FAD. It is used to heat the fresh air by exchanging heat with the fresh air to be introduced into the fresh air duct FAD through the heating medium from the heating equipment TAN2.

[0089] The fresh air heat exchange control valve CV is connected to the controller, the fresh air heat exchanger FHX, and the heating equipment TAN2. The controller controls the entry of the heating medium from the heating equipment TAN2 into the fresh air heat exchanger FHX by controlling the opening and closing state of the fresh air heat exchange control valve CV.

[0090] The heating system also includes an exhaust gas fan FAN1. A controller is connected to the exhaust gas fan FAN1 and is used to control the exhaust gas flow rate at the exhaust gas inlet by controlling the speed of the exhaust gas fan FAN1.

[0091] The controller is used to open the fresh air heat exchange control valve CV when the exhaust fan FAN1 is running, so that the heating medium flows into the fresh air heat exchanger FHX; and to close the fresh air heat exchange control valve CV when the exhaust fan FAN1 is not running, so as to prevent the heating medium from flowing into the fresh air heat exchanger FHX.

[0092] In one embodiment, the exhaust gas fan FAN1 can be a variable frequency exhaust gas fan.

[0093] In one embodiment, the heating system further includes a hot water pump PUM3, which is connected to both the fresh air heat exchanger and the heating equipment. The hot water pump PUM3 is used to transport the heating medium in the heating equipment to the fresh air heat exchanger FHX for heat exchange with the outdoor fresh air flowing through it, thereby heating the fresh air.

[0094] In some embodiments, the heating system further includes an exhaust fan FAN2 and a one-way valve. The one-way valve is located at the fresh air inlet AI1 and is used to control the entry of fresh air into the fresh air inlet AI1. The controller can also be used to acquire the inlet temperature of the low-pressure compressor COM1. If the inlet temperature of the low-pressure compressor COM1 does not reach a preset temperature threshold, the controller controls the exhaust fan FAN2 to be stopped, the low-pressure compressor COM1 and the high-pressure compressor COM2 to be stopped, and the controller controls the exhaust fan FAN1 to be turned on. When the exhaust fan FAN2 is stopped, the low-pressure compressor COM1 and the high-pressure compressor COM2 are stopped, and the exhaust fan FAN1 is turned on, the one-way valve closes, preventing outdoor air from flowing into the system. The exhaust air flows through the low-pressure evaporator EVA1, gradually melting the frost on the evaporator surface, thereby achieving defrosting.

[0095] In one embodiment, the exhaust fan FAN2 can be a variable frequency exhaust fan.

[0096] The structure of the heating system has been introduced above. The control method of the heating system is introduced below. This control method can be applied to the heating system. The main body executing this control method can be a controller or other control devices used to control the controller.

[0097] Reference Figure 3 , Figure 3 This is a flowchart illustrating a control method for a heating system provided in an embodiment of this application. The control method may specifically include:

[0098] In step S101, by controlling the conduction state of the first reversing valve FV1 and the second reversing valve FV2, the control system is in the target heat recovery mode.

[0099] The target heat recovery mode is either the first heat recovery mode or the second heat recovery mode.

[0100] In some embodiments, step S101 may further include the following steps:

[0101] Based on the temperature comparison between the target water temperature of the hot water storage tank and the target wastewater temperature, the control system is in the target heat energy recovery mode by controlling the conduction state of the first reversing valve FV1 and the second reversing valve FV2.

[0102] Specifically, when the temperature comparison result shows that the target wastewater temperature is higher than the target water tank temperature, the target heat energy recovery mode is the first heat energy recovery mode; when the temperature comparison result shows that the target wastewater temperature is lower than or equal to the target water tank temperature, the target heat energy recovery mode is the second heat energy recovery mode.

[0103] In some embodiments, the control method described above may further include:

[0104] The variable frequency low-pressure compressor is controlled at the first preset frequency and the variable frequency high-pressure compressor is controlled at the second preset frequency.

[0105] In one implementation, controlling the variable frequency low-pressure compressor to a first preset frequency and the variable frequency high-pressure compressor to a second preset frequency can be achieved by determining the first preset frequency of the variable frequency low-pressure compressor and the second preset frequency of the variable frequency high-pressure compressor based on the target indoor temperature of the building heated by the heating system and the target water tank temperature of the hot water storage tank, and then controlling the variable frequency low-pressure compressor to the first preset frequency and the variable frequency high-pressure compressor to the second preset frequency.

[0106] In one embodiment, a first preset frequency of the variable frequency low-pressure compressor and a second preset frequency of the variable frequency high-pressure compressor can be determined based on the target indoor temperature of the building heated by the heating system, the target water tank temperature of the hot water storage tank, and a first mapping rule. The aforementioned first mapping rule is used to characterize the correspondence between the indoor temperature, the water tank temperature, the frequency of the variable frequency low-pressure compressor, and the frequency of the variable frequency high-pressure compressor.

[0107] The above-mentioned determination of the first preset frequency of the variable frequency low-pressure compressor and the second preset frequency of the variable frequency high-pressure compressor based on the target indoor temperature of the building heated by the heating system, the target water tank temperature of the hot water storage tank, and the first mapping rule can be achieved by determining the frequency of the variable frequency low-pressure compressor corresponding to the target indoor temperature and the target water tank temperature in the first mapping rule as the first preset frequency, and determining the frequency of the variable frequency high-pressure compressor corresponding to the target indoor temperature and the target water tank temperature in the first mapping rule as the second preset frequency.

[0108] In some embodiments, the control method described above may further include:

[0109] Based on the target indoor temperature of the building supplied by the heating system and the target water tank temperature of the hot water storage tank, determine the first opening degree of the low-pressure throttling valve and the second opening degree of the medium-pressure throttling valve.

[0110] In one embodiment, the first opening degree of the low-pressure throttling valve and the second opening degree of the medium-pressure throttling valve can be determined based on the target indoor temperature of the building heated by the heating system, the target water tank temperature of the hot water storage tank, and a second mapping rule. The aforementioned second mapping rule is used to characterize the correspondence between the indoor temperature, the water tank temperature, the opening degree of the low-pressure throttling valve, and the opening degree of the medium-pressure throttling valve.

[0111] The above-mentioned determination of the first opening degree of the low-pressure throttling valve and the second opening degree of the medium-pressure throttling valve based on the target indoor temperature of the building heated by the heating system, the target water tank temperature of the hot water storage tank, and the second mapping rule can be achieved by determining the opening degree of the low-pressure throttling valve corresponding to the target indoor temperature and the target water tank temperature in the second mapping rule as the first opening degree, and determining the opening degree of the medium-pressure throttling valve corresponding to the target indoor temperature and the target water tank temperature in the second mapping rule as the second opening degree.

[0112] In some embodiments, the control method described above may further include:

[0113] The control system controls the opening of the fresh air flow control valve DAM to control the fresh air flow into the system's fresh air duct FAD, as well as the exhaust air flow out of the indoor space to the exhaust air duct EAD, which is connected to the system's exhaust air inlet.

[0114] In one implementation, the target opening degree of the fresh air flow control valve DAM can be determined based on the target indoor temperature of the building heated by the heating system, the target water tank temperature of the hot water storage tank, and a third mapping rule. The aforementioned third mapping rule characterizes the correspondence between indoor temperature, water tank temperature, and the opening degree of the fresh air flow control valve.

[0115] The above-mentioned determination of the target opening degree of the fresh air flow control valve DAM based on the target indoor temperature of the building heated by the heating system, the target water tank temperature of the hot water storage tank, and the third mapping rule can be achieved by determining the opening degree of the fresh air flow control valve corresponding to the target indoor temperature and the target water tank temperature in the third mapping rule as the target opening degree.

[0116] In some embodiments, the control method described above may further include:

[0117] The on / off state of the fresh air heat exchange control valve CV in the control system controls the entry of the heating medium into the fresh air heat exchanger FHX.

[0118] In some embodiments, controlling the on / off state of the fresh air heat exchange control valve CV to control the entry state of the heating medium into the fresh air heat exchanger FHX may include:

[0119] When the exhaust fan FAN1 is running, the fresh air heat exchange control valve CV is opened; when the fresh air heat exchange control valve CV is open, the heating medium flows into the fresh air heat exchanger FHX; when the exhaust fan FAN1 stops running, the fresh air heat exchange control valve CV is closed; when the fresh air heat exchange control valve CV is closed, the heating medium is prevented from flowing into the fresh air heat exchanger FHX.

[0120] In some embodiments, the above control method may further include the following:

[0121] The system acquires the inlet temperature of the low-pressure compressor COM1. If the inlet temperature of COM1 does not reach a preset temperature threshold, it controls the exhaust fan FAN2 to be stopped, the low-pressure compressor COM1 and the high-pressure compressor COM2 to be stopped, and the waste gas fan FAN1 to be turned on. Specifically, when the exhaust fan FAN2, the low-pressure compressor COM1 and the high-pressure compressor COM2 are stopped, and the waste gas fan FAN1 is on, the one-way valve closes to prevent outdoor air from flowing into the system. This allows waste gas to flow through the low-pressure evaporator EVA1, gradually melting the frost on the evaporator surface, thus achieving defrosting.

[0122] The heating system provided by this invention may include a variable frequency low-pressure compressor, a variable frequency high-pressure compressor, a plate condenser, an economical heat exchanger, a low-pressure electronic expansion valve, a low-pressure tube-fin evaporator, a medium-pressure electronic expansion valve, a medium-pressure tube-fin evaporator, an immersion evaporator, a three-way valve, a first four-way reversing valve, a second four-way reversing valve, a gravity film heat exchanger, a first hot water storage tank, a first circulating pump, a second circulating pump, an exhaust fan, and an exhaust fan. This invention utilizes an adjustable multi-heat-source heat recovery structure to fully leverage waste heat from building exhaust gases, wastewater, shallow soil, and outdoor air, achieving whole-house heat recovery while improving the system's heating efficiency ratio. It also employs waste heat from building exhaust gases to suppress frost formation on the tube-fin evaporator and effectively defrost, significantly reducing defrosting energy consumption and improving seasonal energy efficiency. Furthermore, it features an innovative system structure design with dual variable-frequency compressors, dual variable-frequency fans, and dual four-way reversing valves to achieve adaptive matching under varying operating conditions, thereby improving the system's seasonal energy efficiency ratio. Additionally, by utilizing the temperature glide characteristics of a non-azeotropic refrigerant, it can adaptively match the temperature changes of multiple heat sources, improving the heat exchange efficiency of each heat exchanger, further enhancing the system's energy efficiency ratio, and reducing heating energy consumption and costs.

[0123] To better understand the above scheme, the complete operation process of the heating system is explained below.

[0124] This heating system can be applied indoors to buildings, enabling whole-house heat recovery. The wastewater and exhaust gas mentioned above can be classified as building wastewater and exhaust gas, respectively.

[0125] Reference Figure 1 , Figure 1 The diagram below illustrates the structure of a heating system provided in this application embodiment. The heating system includes a variable frequency low-pressure compressor COM1, a variable frequency high-pressure compressor COM2, a plate condenser CON, an economic heat exchanger ECO, a low-pressure electronic expansion valve EV1, a low-pressure tube-fin evaporator EVA1, a medium-pressure electronic expansion valve EV2, a medium-pressure tube-fin evaporator EVA2, an immersion evaporator EVA3, a three-way valve TV, a first four-way reversing valve FV1, a second four-way reversing valve FV2, a gravity film heat exchanger GHE, a hot water storage tank TAN1, a first circulating pump PUM1, a second circulating pump PUM2, a variable frequency exhaust fan FAN1, a variable frequency exhaust fan FAN2, an exhaust gas inlet AI2, a fresh air inlet AI1, and a controller.

[0126] The heating system can operate in two modes based on the waste heat from building wastewater: wastewater heat recovery mode (the first heat recovery mode mentioned above) and soil heat recovery mode (the second heat recovery mode mentioned above). The operation mode can be switched by controlling the first four-way reversing valve FV1 and the second four-way reversing valve FV2.

[0127] The aforementioned four-way directional valves each have four ports: upper port 1, lower port 2, left port 3, and right port 4. In the wastewater heat recovery mode, the heating system connects ports 1 and 2 of the first four-way directional valve FV1, and ports 3 and 4. At the same time, ports 1 and 2 of the second four-way directional valve FV2 are connected, and ports 3 and 4 are connected, forming the system connection method shown in Figure 1.

[0128] The aforementioned variable frequency high-pressure compressor COM2 compresses the mixed refrigerant to a high-pressure superheated gaseous state and then discharges it. The high-pressure superheated gaseous refrigerant then flows into the plate condenser CON and exchanges heat with the heating medium driven by the first circulating pump PUM1. During this process, the high-pressure superheated gaseous refrigerant is condensed into a high-pressure liquid refrigerant, while the heating medium is heated. Subsequently, the high-pressure liquid refrigerant at the outlet of the plate condenser CON is divided into two refrigerants, namely the first refrigerant and the second refrigerant.

[0129] The first refrigerant flows to the economic heat exchanger ECO for further cooling, becoming a high-pressure subcooled liquid. This first refrigerant then flows into the low-pressure throttling valve EV1 (low-pressure electronic expansion valve EV1) where it is throttled into a low-pressure two-phase state. The first refrigerant in this low-pressure two-phase state flows into the low-pressure tube-fin evaporator EVA1. In EVA1, the first refrigerant in this low-pressure two-phase state exchanges heat with the mixed air. During this process, the first refrigerant absorbs heat and evaporates into a low-pressure superheated gaseous state. This low-pressure superheated gaseous first refrigerant flows into the three-way valve TV, and then into the variable frequency low-pressure compressor COM1. In COM1, it is compressed into a medium-pressure superheated gaseous state.

[0130] After leaving the plate condenser CON, the second refrigerant immediately flows into the medium-pressure throttling valve EV2 (medium-pressure electronic expansion valve EV2), where it is throttled into a medium-pressure two-phase state. Subsequently, the second refrigerant in this two-phase state flows into the medium-pressure tube-fin evaporator EVA2. In EVA2, the second refrigerant exchanges heat with the building exhaust gas, absorbing heat and evaporating, thus increasing its dryness. Then, the second refrigerant continues to flow into the immersion evaporator EVA3, exchanging heat with the heat storage medium in the hot water storage tank TAN1, absorbing heat from the storage medium and further increasing its dryness. Finally, the second refrigerant... The second refrigerant flows to the economic heat exchanger (ECO). In the ECO, the second refrigerant exchanges heat with the first refrigerant. During this process, the first refrigerant releases heat and becomes a high-pressure subcooled liquid, while the second refrigerant absorbs heat and becomes a medium-pressure superheated gas. The medium-pressure superheated gaseous second refrigerant eventually flows into the three-way valve (TV) and mixes with the medium-pressure superheated gaseous first refrigerant to form a medium-pressure superheated gaseous mixed refrigerant. Finally, the medium-pressure superheated gaseous mixed refrigerant flows into the variable frequency high-pressure compressor (COM2) and is further compressed to a high-pressure superheated gaseous state, completing one heating cycle.

[0131] The system consists of a hot water storage tank (TAN1) connected to a gravity membrane heat exchanger (GHE). A second circulation pump (PUM2) drives the flow of the heat storage medium, which exchanges heat with the building wastewater within the GHE. During this process, the waste heat from the wastewater is absorbed by the heat storage medium and stored in the TAN1 tank. Finally, it is recovered by the second refrigerant through an immersion evaporator (EVA3). The GHE can be buried in the soil and is made of polyvinyl chloride (PVC), a corrosion-resistant material suitable for shallow soil burial. Its structure can be a spiral-tube heat exchanger, with the wastewater flowing inside the straight tube and the heat exchange pipe spirally wound around the outside, containing the heat storage medium. In the wastewater heat recovery mode, the circulating heat storage medium in the GHE reaches a high temperature of 25-35℃, matching the 30-40℃ temperature of the wastewater, effectively recovering the waste heat from the wastewater.

[0132] The aforementioned variable frequency exhaust fan FAN1 can extract building exhaust gas and blow it towards the medium-pressure tube-fin evaporator EVA2. During this process, most of the waste heat of the building exhaust gas is recovered by the second refrigerant in the medium-pressure two-phase state. Furthermore, while the variable frequency exhaust fan FAN2 draws in building exhaust gas, it also draws in outdoor air (the outdoor air is fresh air entering through the fresh air inlet AI1). The outdoor air and building exhaust gas will mix in the duct between the medium-pressure tube-fin evaporator EVA2 and the low-pressure tube-fin evaporator EVA1 to obtain mixed air. The outdoor low-temperature air and building exhaust gas will be mixed with the building exhaust gas to obtain mixed air with a higher temperature. Driven by the variable frequency exhaust fan FAN2, the mixed air continues to flow towards the low-pressure tube-fin evaporator EVA1. During this process, the heat of the mixed air will be completely absorbed by the first refrigerant in the low-pressure two-phase state and finally discharged from the system.

[0133] Figure 4 This is a system temperature-entropy diagram of the heating system provided in this embodiment of the invention when operating in the first heat recovery mode. The refrigerant used in the heating system can be a non-azeotropic refrigerant, such as a mixture of ethane R170 and propane R290. Therefore, during the refrigerant phase change process, the phase change temperature shifts, the condensation temperature gradually decreases as the refrigerant dryness decreases, and the evaporation temperature gradually increases as the refrigerant dryness increases. Figure 4 As shown, after the variable frequency high-pressure compressor COM2 compresses the mixed refrigerant to point 1, the plate condenser CON condenses the superheated gaseous mixed refrigerant to point 2. During the condensation process, the phase change temperature of the mixed refrigerant gradually decreases, matching the gradually heating medium, thereby reducing the pinch temperature difference in the heat transfer process, reducing irreversible energy loss in the heat transfer process, and improving heat exchange efficiency. Subsequently, the high-pressure saturated liquid mixed refrigerant at the outlet of the plate condenser CON is divided into two streams. The first refrigerant flows to the economic heat exchanger ECO and is further subcooled to point 3. Then, the first refrigerant in the high-pressure subcooled state at point 3 is first throttled by the low-pressure throttling valve EV1 to the low-pressure gas-liquid two-phase state point 4, and then flows into the low-pressure tube-fin evaporator EVA1 to absorb the waste heat of the mixed air of outdoor air and building exhaust gas, evaporates to the low-pressure superheated gaseous state point 5, and finally flows into the variable frequency low-pressure compressor COM1 to be compressed to the medium-pressure superheated gaseous state point 6.

[0134] Meanwhile, the second refrigerant separated at the plate condenser outlet immediately flows to the medium-pressure throttling valve EV2, throttling it to the medium-pressure gas-liquid two-phase state point 7. The second refrigerant in the medium-pressure gas-liquid two-phase state then flows into the medium-pressure tube-fin evaporator EVA2. In the medium-pressure tube-fin evaporator EVA2, the second refrigerant absorbs the waste heat from the building exhaust gas and evaporates to state point 8. Then it flows into the immersion evaporator EVA3. In the immersion evaporator EVA3, the second refrigerant absorbs the waste heat from the building wastewater stored in the hot water storage tank and evaporates to state point 9. Finally, it flows into the economic heat exchanger ECO, where the second refrigerant recovers the heat from the first refrigerant and evaporates to the superheated state point 10. The temperature of the second refrigerant at the medium-pressure superheated state point 10 is lower than that of the first refrigerant compressed to the medium-pressure superheated state point 6. Therefore, the two refrigerants flow into the three-way valve TV, mix, and reach state point 11, obtaining a medium-pressure mixed refrigerant at an intermediate temperature and increasing the refrigerant flow rate. This increases the heating capacity while reducing the inlet temperature of the variable frequency high-pressure compressor COM2, thereby reducing the compressor discharge temperature and power consumption.

[0135] The waste heat from building exhaust gas flows through the medium-pressure tube-fin evaporator EVA2 and the low-pressure tube-fin evaporator EVA1, achieving two-stage heat recovery. This effectively reduces the temperature difference between the high-temperature building exhaust gas and the refrigerant, minimizing irreversible losses during heat transfer and thus significantly improving the system's energy efficiency ratio.

[0136] Furthermore, the waste heat from the building wastewater is recovered by the gravity membrane heat exchanger GHE and stored in the hot water storage tank TAN1, and then recovered by the second refrigerant through the immersion evaporator EVA3.

[0137] Since the temperature of construction wastewater is higher than that of construction exhaust gas, the temperature glide characteristic of the non-azeotropic refrigerant evaporation process is utilized. In wastewater heat recovery mode, connecting the immersion evaporator EVA3 to the medium-pressure tube-fin evaporator EVA2 reduces the heat transfer temperature difference between the second refrigerant and the construction wastewater, thereby improving heat transfer efficiency. Similarly, the final design of the economic heat exchanger ECO ensures that the second refrigerant exchanges heat with the highest-temperature, high-pressure saturated liquid phase of the first refrigerant within the ECO. Utilizing the phase change temperature glide characteristic of the non-azeotropic working fluid, the heat transfer temperature difference between the two refrigerants is further reduced, thus improving heat transfer efficiency. Finally, by controlling the frequency of the variable frequency low-pressure compressor COM1 and the opening of the low-pressure throttling valve EV1, the flow rate and pressure of the first refrigerant are adjusted. Similarly, by controlling the frequency of the variable frequency high-pressure compressor COM2 and the opening of the medium-pressure throttling valve EV2, the flow rate and pressure of the second refrigerant are adjusted. This allows for system matching of changes in waste heat from construction exhaust gas and wastewater, thereby achieving the optimal heating efficiency ratio.

[0138] Figure 5This is a system schematic diagram of the heating system provided in this application embodiment when operating in the second heat recovery mode. When the temperature of the building wastewater drops to 10-20℃, resulting in less residual heat, the first four-way reversing valve FV1 and the second four-way reversing valve FV2 will switch the connection direction, with interface 1 connected to interface 4 and interface 2 connected to interface 3. Therefore, in the soil heat recovery mode, the inlet of the soaking evaporator EVA3 is connected to the outlet of the low-pressure tube-fin evaporator EVA1, and the outlet of the soaking evaporator EVA3 is connected to the inlet of the variable frequency low-pressure compressor COM1, while the outlet of the medium-pressure tube-fin evaporator EVA2 will be connected to the economic heat exchanger ECO.

[0139] In the soil heat recovery mode, the mixed refrigerant passing through the plate condenser CON will be divided into two streams. First, the high-pressure liquid refrigerant will flow through the economic heat exchanger ECO for further subcooling, and then be throttled by the low-pressure throttling valve EV1 to a low-pressure gas-liquid two-phase state. Subsequently, the low-pressure gas-liquid two-phase refrigerant flows into the low-pressure tube-fin evaporator EVA1 to absorb the waste heat of the mixed air. After evaporation, the first refrigerant with a higher dryness will flow into the immersion evaporator EVA3 to absorb the heat of the heat storage medium and further evaporate to a low-pressure superheated gas phase state. Finally, it flows into the variable frequency low-pressure compressor COM1 and is compressed to a medium-pressure superheated state.

[0140] Meanwhile, after the second refrigerant leaves the plate condenser CON, it is immediately throttled by the medium-pressure throttling valve EV2 to a medium-pressure gas-liquid two-phase state. It then flows into the medium-pressure tube-fin evaporator EVA2 to absorb the waste heat from the building exhaust gas. The medium-pressure second refrigerant with a higher dryness after evaporation flows into the economic heat exchanger ECO to exchange heat with the first refrigerant and further evaporate to a superheated gas phase state. Finally, it flows into the three-way valve TV to mix with the evaporated first refrigerant. Ultimately, the mixed refrigerant flows into the variable frequency high-pressure compressor COM2 and is compressed to a high-pressure superheated gas phase state, completing one cycle.

[0141] When the heating system operates in soil heat recovery mode, the evaporation temperature of the immersion evaporator EVA3 decreases after the connection method is switched, causing the temperature of the heat storage medium to drop to 5-10℃ simultaneously. This allows it to simultaneously absorb the waste heat of the low-temperature construction wastewater (10-20℃) and the heat of the surrounding shallow soil (5-15℃), storing it in the hot water storage tank TAN1. The heat storage medium in the hot water storage tank TAN1 can be a mixture of ethanol and water. When it has a low condensation temperature (-15℃), it can effectively recover the low-grade shallow soil heat energy and the low-temperature construction wastewater waste heat.

[0142] Figure 6This is a system temperature entropy diagram of the heating system provided in this application embodiment when operating in the second heat energy recovery mode. In the soil heat energy recovery mode, after the heating system changes the connection direction of the two four-way reversing valves, it utilizes the evaporation temperature sliding characteristics of the non-azeotropic refrigerant. The first refrigerant in the low-pressure pipeline flows through the low-pressure tube-fin evaporator EVA1 and the immersion evaporator EVA3, respectively, and exchanges heat with the mixed air at 0-5℃ and the heat storage medium at 5-10℃, thus achieving the matching of the evaporation temperature with the temperature of the two low-grade heat sources. The second refrigerant in the medium-pressure pipeline flows through the medium-pressure tube-fin evaporator EVA2 and the economic heat exchanger ECO, respectively, and exchanges heat with the building exhaust gas at 20-25℃ and the first refrigerant at 40-45℃, thus achieving the matching of the evaporation temperature with the temperature of the two high-grade heat sources.

[0143] Furthermore, since the medium-pressure pipeline has changed from a three-heat-exchanger series structure to a two-heat-exchanger series structure, and the low-pressure pipeline has changed from a one-heat-exchanger series structure to a two-heat-exchanger series structure, the variable frequency low-pressure compressor COM1 will increase its speed, increasing the flow rate of the first refrigerant in the low-pressure pipeline. At the same time, the variable frequency high-pressure compressor COM2 will decrease its speed, reducing the flow rate of the second refrigerant in the medium-pressure pipeline. This achieves the best match between the evaporation heat exchange and the changes in the waste heat of building exhaust gas and wastewater, resulting in the best system heating efficiency ratio.

[0144] Referring to Figure 2, the heating system includes the heating system HP, building exhaust duct EAD, building fresh air duct FAD, fresh air heat exchanger FHX, fresh air flow control valve DAM, fresh air heat exchange control valve CV, hot water tank TAN2, hot water pump PUM3, domestic hot water terminal DHW, immersion heat exchanger IHX, tap water pipe GRID, sewer SEWER, indoor temperature sensor T1, hot water temperature sensor T2, stored hot water temperature sensor T3, and building wastewater temperature sensor T4. The hot water tank TAN2 can be used to heat heating devices such as bathroom radiators RAD1 and bedroom radiators RAD2. The aforementioned heating equipment can be used to heat these devices, such as the hot water tank TAN2, which can be located in an equipment room.

[0145] This invention relates to a specific embodiment of a heat pump heating system integrated with a building, such as... Figure 2 As shown, the heating system HP is connected to the building's exhaust duct EAD, hot water tank TAN2, and sewer system SEWER.

[0146] The exhaust duct EAD is connected to the exhaust vents of the bedrooms and bathrooms. When the heating system HP is running, the variable frequency exhaust fan FAN1 drives the building exhaust gas from the exhaust vents to flow along the exhaust duct EAD to the heating system HP. Two-stage exhaust gas heat recovery is achieved through the medium-pressure tube-fin evaporator EVA2 and the low-pressure tube-fin evaporator EVA1. At the same time, because the variable frequency exhaust fan FAN1 extracts indoor exhaust gas, the building interior is in a negative pressure state. Outdoor fresh air flows into the interior through the fresh air duct FAD, realizing indoor ventilation and thus meeting the fresh air demand.

[0147] A fresh air flow control valve (DAM) is installed at the inlet of the fresh air duct. The fresh air flow is controlled by adjusting the opening of the valve, and the exhaust gas flow is also controlled.

[0148] The fresh air duct is equipped with a fresh air heat exchanger FHX. The hot water pump PUM3 delivers the heating medium to the fresh air heat exchanger FHX to exchange heat with the outdoor fresh air flowing through it, thereby heating the fresh air and reducing the increase in indoor heat load caused by the inflow of fresh air.

[0149] The fresh air heat exchange control valve CV is installed at the inlet of the fresh air heat exchanger FHX. It controls its opening and closing by detecting the operation of the variable frequency exhaust fan FAN1. When the variable frequency exhaust fan FAN1 is running, the fresh air heat exchange control valve CV is open, allowing the heating medium to flow in and heat the fresh air; when the variable frequency exhaust fan FAN1 is stopped, no fresh air flows into the room, and the fresh air heat exchange control valve CV is closed, preventing the heating medium from flowing in.

[0150] The hot water tank TAN2 is connected to the end of the building's heating components, such as the bathroom radiator RAD1, bedroom radiator RAD2, and fresh air heat exchanger FHX. The other end is connected to the plate condenser CON of the heating system HP. During HP operation, the variable frequency high-pressure compressor COM2 discharges high-temperature, high-pressure gaseous refrigerant mixture, transferring heat to the heating medium and completing heat storage.

[0151] The heating medium can be a mixture of ethanol and water, which will not freeze at an ambient temperature of -15℃.

[0152] The heating system HP monitors the water temperature T2 in the hot water tank TAN2 and controls the hot water temperature between 55-65℃ by starting and stopping the heat pump system. When the water temperature is below 55℃, the heat pump system starts and when the water temperature reaches 65℃, the heat pump system stops. The hot water pump PUM3 monitors the indoor temperature T1 and controls the indoor temperature to be maintained between 18-25℃ by starting and stopping it.

[0153] Domestic hot water exchanges heat with the heating medium through the immersion heat exchanger IHX inside the hot water tank TAN2. When the domestic hot water terminal DHW is turned on, tap water flows into the immersion heat exchanger IHX through the tap water pipe GRID, and the tap water is heated from 5-15℃ to 40-50℃. The sewer system (SEWER) is the building's original sewage system. The gravity membrane heat exchanger (GHE) of the heating system (HP) is connected to the existing sewer system (SEWER) via modular installation. When the building generates domestic wastewater, the wastewater temperature sensor T4 downstream of the sewer system detects the wastewater temperature and compares it with the inlet water temperature T3 of the heat pump system's hot water storage tank (TAN1). When T4 is higher than T3, the heat pump system will operate in wastewater heat recovery mode, and the second circulation pump PUM2 will drive the heat storage medium into the gravity membrane heat exchanger (GHE) to absorb the waste heat from the building wastewater. When T4 is lower than T3, the heat pump system will operate in soil heat recovery mode, and the second circulation pump PUM2 will drive the heat storage medium into the gravity membrane heat exchanger (GHE) to absorb heat from the shallow soil and the building wastewater.

[0154] The HP heating system introduces building exhaust gas during heating, thus the air temperature flowing through the medium-pressure finned evaporator EVA2 and the low-pressure finned evaporator EVA1 is higher than the outdoor temperature, effectively suppressing frequent frosting of the outdoor heat exchanger during winter operation. After the HP heating system has operated in frigid climates for a period, if frosting appears on the fins of the low-pressure finned evaporator EVA1, the inlet temperature of the variable frequency low-pressure compressor COM1 will drop significantly due to insufficient refrigerant superheating, triggering the system's defrosting mode. The variable frequency low-pressure compressor COM1 and the variable frequency high-pressure compressor COM2 will stop working, the variable frequency exhaust fan FAN2 will stop working, and the variable frequency exhaust fan FAN1 will start. Because the variable frequency exhaust fan FAN1 continuously draws in high-temperature building exhaust gas, the one-way valve at the fresh air inlet AI1 will close under the positive pressure of the variable frequency exhaust fan. By preventing low-temperature outdoor air from flowing into the system, high-temperature building exhaust gas will flow through the low-pressure tube-fin evaporator EVA1, gradually melting the frost on the evaporator surface, thus achieving near-zero energy consumption defrosting.

[0155] The HP heating system utilizes a dual-compressor, dual-fan, and dual four-way reversing valve structure, employing four evaporators to achieve whole-house waste heat recovery and utilization from building exhaust gas and wastewater. It also fully leverages the low-grade heat energy from outdoor air and shallow soil to achieve efficient building heating. Through automatic switching of heating modes, this invention relates to a novel high-efficiency multi-heat-source whole-house heat recovery heat pump heating system that can actively adapt to changes in environmental conditions and building waste heat, optimizing system performance. It also utilizes building waste heat for defrosting and frost suppression, improving the system's energy efficiency ratio while significantly reducing seasonal heating energy consumption and carbon emissions from building heating.

[0156] In summary, the overall intelligent control strategy of the system can be as follows:

[0157] For the refrigerant cycle side:

[0158] By controlling the first four-way reversing valve FV1 and the second four-way reversing valve FV2, the switching between wastewater heat energy recovery mode and soil heat energy recovery mode can be realized.

[0159] In wastewater heat recovery mode, the flow rate and pressure of the first refrigerant are adjusted by controlling the frequency of the variable frequency low-pressure compressor COM1 and the opening of the low-pressure throttle valve EV1 to match the temperature of the mixed air; the flow rate and pressure of the second refrigerant are adjusted by controlling the frequency of the variable frequency high-pressure compressor COM2 and the opening of the medium-pressure throttle valve EV2 to match the temperature of the building exhaust gas and the water temperature of the hot water storage tank.

[0160] In soil heat recovery mode, the flow rate and pressure of the first refrigerant are adjusted by controlling the frequency of the variable frequency low-pressure compressor COM1 and the opening of the low-pressure throttle valve EV1 to match the temperature of the mixed air and the water temperature of the hot water storage tank. The flow rate and pressure of the second refrigerant are adjusted by controlling the frequency of the variable frequency high-pressure compressor COM2 and the opening of the medium-pressure throttle valve EV2 to match the temperature of the building exhaust gas.

[0161] Based on the experimental test results, the above adjustments were written into a control program and executed by a microcontroller. According to the indoor temperature sensor T1 and the water temperature T2 supplied to the hot water tank, the program was adjusted according to the set ratio to achieve the optimal heating energy efficiency ratio.

[0162] For the airflow side:

[0163] By controlling the fresh air flow control valve DAM, the fresh air heat exchange control valve CV, the variable frequency exhaust fan FAN1, and the variable frequency exhaust fan FAN2, two-stage recovery of waste heat from building exhaust gas and efficient defrosting of building exhaust gas are achieved.

[0164] When the system is operating in heating mode, the fresh air flow control valve DAM opens, the fresh air heat exchange control valve CV, the variable frequency exhaust fan FAN1, and the variable frequency exhaust fan FAN2 are all open. The variable frequency exhaust fan FAN1 drives the indoor exhaust gas from the exhaust vent to flow into the system along the exhaust gas duct EAD. Two stages of exhaust gas heat energy recovery are achieved through the medium-pressure tube-fin evaporator EVA2 and the low-pressure tube-fin evaporator EVA1. Simultaneously, because the variable frequency exhaust fan FAN1 extracts indoor exhaust gas, the indoor space is under negative pressure, allowing outdoor fresh air to flow into the room through the fresh air duct FAD, thus achieving indoor ventilation and meeting the fresh air demand.

[0165] A fresh air flow control valve (DAM) is installed at the inlet of the fresh air duct. The fresh air flow is controlled by adjusting the valve opening, and the exhaust gas flow is also controlled. The exhaust gas can make the air temperature flowing through the medium-pressure tube-fin evaporator EVA2 and the low-pressure tube-fin evaporator EVA1 higher than the outdoor temperature, thereby effectively suppressing the problem of frequent frosting of the outdoor heat exchanger during winter operation.

[0166] A fresh air heat exchanger FHX is installed in the fresh air duct. The hot water pump PUM3 delivers the heating medium to the fresh air heat exchanger FHX to exchange heat with the outdoor fresh air flowing through it, thereby heating the fresh air and reducing the increase in indoor heat load caused by the inflow of fresh air. The fresh air heat exchange control valve CV is installed at the inlet of the fresh air heat exchanger FHX. It controls its opening and closing by detecting the operation of the variable frequency exhaust fan FAN1 of the heat pump. When the variable frequency exhaust fan FAN1 is running, the fresh air heat exchange control valve CV opens, allowing the heating medium to flow in and heat the fresh air.

[0167] When the system is in defrost mode, the fresh air flow control valve DAM opens, the fresh air heat exchange control valve CV opens, the variable frequency exhaust fan FAN1 starts, the variable frequency exhaust fan FAN2 closes, the variable frequency low-pressure compressor COM1 stops, and the variable frequency high-pressure compressor COM2 stops. Because the variable frequency exhaust fan continuously draws in high-temperature building exhaust gas, the one-way valve at the fresh air inlet AI1 will close under the positive pressure of the exhaust fan, preventing low-temperature outdoor air from flowing into the system. At this time, the high-temperature building exhaust gas will flow through the low-pressure tube-fin evaporator EVA1, gradually melting the frost on the evaporator surface, thus achieving near-zero energy consumption defrosting.

[0168] The above controls are adjusted according to the compressor's operating status. The compressor has a self-protection program; it will automatically shut down and enter defrost mode when the inlet or outlet temperature or pressure is too high. This is a standard control measure. By monitoring the compressor's status, the system automatically adjusts the fresh air flow control valve DAM, the fresh air heat exchange control valve CV, the variable frequency exhaust fan FAN1, and the variable frequency exhaust fan FAN2.

[0169] For the water circulation side:

[0170] The system controls the heating and heat storage by controlling the first circulating water pump PUM1, the second circulating water pump PUM2, and the hot water pump PUM3.

[0171] The heating system HP monitors the water temperature T2 of the hot water tank TAN2 and controls the hot water temperature between 55-65℃ by starting and stopping the heat pump system. When the water temperature is below 55℃, the heat pump system starts and when the water temperature reaches 65℃, the heat pump system stops. The hot water pump PUM3 monitors the indoor temperature T1 and controls the indoor temperature to be maintained between 18-25℃ by starting and stopping it.

[0172] When the system is in heating mode, the heating medium driven by the first circulation pump PUM1 flows into the plate condenser CON and exchanges heat with the high-pressure superheated gaseous refrigerant. During this process, the high-pressure superheated gaseous refrigerant is condensed into high-pressure liquid refrigerant, while the heating medium is heated, thereby storing the heat in the hot water tank TAN2.

[0173] When the building generates domestic wastewater, the wastewater temperature sensor T4 at the downstream end of the sewer detects the wastewater temperature and compares it with the inlet water temperature T3 of the heat pump system's hot water storage tank TAN1. When the temperature T4 is higher than T3, the heat pump system will operate in wastewater heat recovery mode, and the second circulation pump PUM2 will drive the heat storage medium into the gravity membrane heat exchanger GHE to absorb the waste heat from the building wastewater. When the temperature T4 is lower than T3, the heat pump system will operate in soil heat recovery mode, and the second circulation pump PUM2 will drive the heat storage medium into the gravity membrane heat exchanger GHE to absorb the heat from the shallow soil and the heat from the building wastewater.

[0174] The above control system monitors temperatures T1, T2, T3, and T4, compares the temperature measurement points with the set points, and controls the water circulation flow to achieve heating start / stop, heating mode start / stop, and system mode switching.

[0175] To better implement the above control method, this application provides a control device for a heating system, referring to... Figure 7 , Figure 7 This is a schematic diagram of the structure of a control device for a heating system provided in an embodiment of this application. The control device 700 of the heating system specifically includes:

[0176] The mode switching module 701 is used to control the system to be in the target heat recovery mode by controlling the conduction state of the first reversing valve and the second reversing valve; wherein the target heat recovery mode is either the first heat recovery mode or the second heat recovery mode.

[0177] In one embodiment, the mode switching module 701 is specifically used to: control the system to be in the target heat recovery mode by controlling the conduction state of the first reversing valve and the second reversing valve based on the temperature comparison result between the target water tank temperature of the hot water storage tank and the target wastewater temperature; wherein, when the temperature comparison result is that the target wastewater temperature is higher than the target water tank temperature, the target heat recovery mode is the first heat recovery mode, and when the temperature comparison result is that the target wastewater temperature is lower than or equal to the target water tank temperature, the target heat recovery mode is the second heat recovery mode.

[0178] In one embodiment, the mode switching module 701 is specifically used to: control the variable frequency low-pressure compressor to a first preset frequency and the variable frequency high-pressure compressor to a second preset frequency.

[0179] In one embodiment, the mode switching module 701 is specifically used to: control the opening degree of the fresh air flow control valve to control the fresh air flow into the fresh air duct and the exhaust gas flow out of the indoor space to the exhaust gas duct connected to the exhaust gas inlet of the system.

[0180] In one embodiment, the mode switching module 701 is specifically used to: control the on / off state of the fresh air heat exchange control valve to control the entry state of the heating medium into the fresh air heat exchanger; wherein, when the exhaust fan is running, the fresh air heat exchange control valve is controlled to open; wherein, when the fresh air heat exchange control valve is open, the heating medium flows into the fresh air heat exchanger; when the exhaust fan stops running, the fresh air heat exchange control valve is controlled to close; wherein, when the fresh air heat exchange control valve is closed, the heating medium is prevented from flowing into the fresh air heat exchanger.

[0181] The control device 700 for the heating system provided in this application embodiment can execute the control method of the heating system described above. Its implementation principle and beneficial effects are similar, and will not be described again here.

[0182] This application also provides an electronic device, which may include the heating system described above. Alternatively, the electronic device may include a processor and a memory storing computer program instructions; the processor executes the computer program instructions to implement the control method for the heating system described above.

[0183] Figure 8 A schematic diagram of the hardware structure of the electronic device provided in an embodiment of this application is shown.

[0184] Electronic devices may include a processor 801 and a memory 802 storing computer program instructions.

[0185] Specifically, the processor 801 may include a central processing unit (CPU), an application-specific integrated circuit (ASIC), or one or more integrated circuits that can be configured to implement the embodiments of this application.

[0186] Memory 802 may include mass storage for data or instructions. For example, and not limitingly, memory 802 may include a hard disk drive (HDD), floppy disk drive, flash memory, optical disk, magneto-optical disk, magnetic tape, or Universal Serial Bus (USB) drive, or a combination of two or more of these. Where appropriate, memory 802 may include removable or non-removable (or fixed) media. Where appropriate, memory 802 may be internal or external to the integrated gateway disaster recovery device. In a particular embodiment, memory 802 is non-volatile solid-state memory.

[0187] In some embodiments, memory 802 may include read-only memory (ROM), random access memory (RAM), disk storage media device, optical storage media device, flash memory device, electrical, optical, or other physical / tangible memory storage device. Thus, generally, memory includes one or more tangible (non-transitory) computer-readable storage media (e.g., memory devices) encoded with software including computer-executable instructions, and when the software is executed (e.g., by one or more processors), it is operable to perform the operations described with reference to the method according to one aspect of this disclosure.

[0188] The processor 801 reads and executes computer program instructions stored in the memory 802 to implement any of the heating system control methods in the above embodiments.

[0189] In one example, the electronic device may also include a communication interface 803 and a bus 810. For example, Figure 8 As shown, the processor 801, memory 802, and communication interface 803 are connected through bus 810 and complete communication with each other.

[0190] The communication interface 803 is mainly used to realize communication between various modules, devices, units and / or equipment in the embodiments of this application.

[0191] Bus 810 includes hardware, software, or both, that couples components of an electronic device together. For example, and not limitingly, the bus may include an Accelerated Graphics Port (AGP) or other graphics bus, an Enhanced Industry Standard Architecture (EISA) bus, a Front Side Bus (FSB), HyperTransport (HT) interconnect, an Industry Standard Architecture (ISA) bus, an Infinite Bandwidth Interconnect, a Low Pin Count (LPC) bus, a memory bus, a Microchannel Architecture (MCA) bus, a Peripheral Component Interconnect (PCI) bus, a PCI-Express (PCI-X) bus, a Serial Advanced Technology Attachment (SATA) bus, a Video Electronics Standards Association Local (VLB) bus, or other suitable buses, or combinations of two or more of these. Where appropriate, bus 810 may include one or more buses. Although specific buses are described and illustrated in embodiments of this application, this application contemplates any suitable bus or interconnect.

[0192] The electronic device can execute the control method of the heating system in the embodiments of this application, thereby achieving the combination Figure 2 and Figure 7 The control methods and devices for the heating system are described.

[0193] Furthermore, in conjunction with the control methods of the heating system in the above embodiments, this application embodiment can provide a computer-readable storage medium for implementation. This computer-readable storage medium stores computer program instructions; when executed by a processor, these computer program instructions implement any of the control methods of the heating system in the above embodiments.

[0194] It should be clarified that this application is not limited to the specific configurations and processes described above and shown in the figures. For the sake of brevity, detailed descriptions of known methods are omitted here. In the above embodiments, several specific steps are described and shown as examples. However, the method process of this application is not limited to the specific steps described and shown. Those skilled in the art can make various changes, modifications, and additions, or change the order of steps, after understanding the spirit of this application.

[0195] The functional blocks shown in the above-described structural diagram can be implemented as hardware, software, firmware, or a combination thereof. When implemented in hardware, they can be, for example, electronic circuits, application-specific integrated circuits (ASICs), appropriate firmware, plug-ins, function cards, etc. When implemented in software, the elements of this application are programs or code segments used to perform the required tasks. Programs or code segments can be stored on a machine-readable medium or transmitted over a transmission medium or communication link via data signals carried on a carrier wave. "Machine-readable medium" can include any medium capable of storing or transmitting information. Examples of machine-readable media include electronic circuits, semiconductor memory devices, ROM, flash memory, erasable ROM (EROM), floppy disks, CD-ROMs, optical disks, hard disks, fiber optic media, radio frequency (RF) links, etc. Code segments can be downloaded via computer networks such as the Internet, intranets, etc.

[0196] It should also be noted that the exemplary embodiments mentioned in this application describe methods or systems based on a series of steps or apparatus. However, this application is not limited to the order of the above steps; that is, the steps can be performed in the order mentioned in the embodiments, or in a different order, or several steps can be performed simultaneously.

[0197] The aspects of this disclosure have been described above with reference to flowchart illustrations and / or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of this disclosure. It should be understood that each block in the flowchart illustrations and / or block diagrams, and combinations of blocks in the flowchart illustrations and / or block diagrams, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, a special-purpose computer, or other programmable data processing apparatus to produce a machine such that these instructions, executable via the processor of the computer or other programmable data processing apparatus, enable the implementation of the functions / actions specified in one or more blocks of the flowchart illustrations and / or block diagrams. Such a processor can be, but is not limited to, a general-purpose processor, a special-purpose processor, a special application processor, or a field-programmable logic circuit. It is also understood that each block in the block diagrams and / or flowcharts, and combinations of blocks in the block diagrams and / or flowcharts, can also be implemented by special-purpose hardware performing the specified functions or actions, or can be implemented by a combination of special-purpose hardware and computer instructions.

[0198] The above description is merely a specific implementation of this application. Those skilled in the art will clearly understand that, for the sake of convenience and brevity, the specific working processes of the systems, modules, and units described above can be referred to the corresponding processes in the foregoing method embodiments, and will not be repeated here. It should be understood that the protection scope of this application is not limited thereto. Any person skilled in the art can easily conceive of various equivalent modifications or substitutions within the technical scope disclosed in this application, and these modifications or substitutions should all be covered within the protection scope of this application.

Claims

1. A heating system, characterized in that, The system includes: a high-pressure compressor, a heat recovery condenser, a first heat exchanger, an evaporator, a second heat exchanger, a low-pressure throttling valve, a medium-pressure throttling valve, a first reversing valve, a second reversing valve, a low-pressure compressor, a hot water storage tank, and a controller; The heat recovery condenser is used to exchange heat between the mixed refrigerant output from the high-pressure compressor and the heating medium from the heating equipment, and to discharge the first refrigerant and the second refrigerant; the first refrigerant and the second refrigerant exchange heat in the second heat exchanger; The first heat exchanger is used to absorb the thermal energy of the target heat source based on the heat storage medium output from the hot water storage tank; The evaporator is used to recover heat energy by exchanging heat between the heat storage medium and the refrigerant after collecting the heat energy from the target heat source. The controller is used to control the conduction state of the first reversing valve and the second reversing valve so that the system operates in the first heat recovery mode or the second heat recovery mode. In the first heat recovery mode, the target heat source is wastewater; the first refrigerant flows sequentially through the heat recovery condenser, the second heat exchanger, the low-pressure throttling valve, the first reversing valve, the second reversing valve, the low-pressure compressor, and the high-pressure compressor; the second refrigerant flows sequentially through the heat recovery condenser, the medium-pressure throttling valve, the first reversing valve, the evaporator, the second reversing valve, the second heat exchanger, and the high-pressure compressor. In the second heat recovery mode, the target heat source is soil and wastewater; the first refrigerant flows sequentially through the heat recovery condenser, the second heat exchanger, the low-pressure throttling valve, the first reversing valve, the evaporator, the second reversing valve, the low-pressure compressor, and the high-pressure compressor; the second refrigerant flows sequentially through the heat recovery condenser, the medium-pressure throttling valve, the first reversing valve, the second reversing valve, the second heat exchanger, and the high-pressure compressor.

2. The system according to claim 1, characterized in that, The system also includes at least one of the following: A low-pressure evaporator is used to exchange heat between the first refrigerant discharged through the low-pressure throttling valve and the mixed air for heat recovery; the mixed air is obtained by mixing the exhaust gas entering through the exhaust gas inlet and the fresh air entering through the fresh air inlet. The first refrigerant flows into the low-pressure evaporator before flowing into the low-pressure compressor from the low-pressure throttling valve; A medium-pressure evaporator is used for heat exchange between the second refrigerant discharged through the medium-pressure throttling valve and the exhaust gas entering through the exhaust gas inlet; the second refrigerant flows into the medium-pressure evaporator before flowing from the medium-pressure throttling valve into the first reversing valve.

3. The system according to claim 1, characterized in that, The system also includes at least one of the following: A multi-way valve is used to control the flow of a first refrigerant and a second refrigerant into the multi-way valve through different channels; the first refrigerant flows into the multi-way valve before flowing from the low-pressure compressor into the high-pressure compressor; the second refrigerant flows into the multi-way valve before flowing from the second heat exchanger into the high-pressure compressor; A first circulation pump, connected to the heat recovery condenser, is used to drive the heating medium from the heating equipment to exchange heat with the mixed refrigerant in the heat recovery condenser; The second circulation pump is connected to the first heat exchanger and the hot water storage tank respectively, and is used to drive the heat storage medium to flow in the first heat exchanger and the hot water storage tank; The refrigerant is a non-azeotropic refrigerant.

4. The system according to claim 3, characterized in that, The high-pressure compressor is a variable frequency high-pressure compressor, and the low-pressure compressor is a variable frequency low-pressure compressor; The controller is used to control the variable frequency low-pressure compressor to a first preset frequency and the variable frequency high-pressure compressor to a second preset frequency; When the variable frequency low-pressure compressor is at the first preset frequency and the variable frequency high-pressure compressor is at the second preset frequency, the first refrigerant flows from the low-pressure compressor into the multi-way valve at a first preset flow rate, and the second refrigerant flows from the second heat exchanger into the multi-way valve at a second preset flow rate.

5. The system according to claim 1, characterized in that, The controller is used to control the conduction state of the first reversing valve and the second reversing valve based on the comparison result between the target water temperature of the hot water storage tank and the target wastewater temperature. Wherein, when the target wastewater temperature is higher than the target water tank temperature, the system operates in a first heat recovery mode under the control of the controller. The controller is used to control the first reversing valve to open the low-pressure throttling valve and the second reversing valve, and to control the second reversing valve to open the first reversing valve and the low-pressure compressor. Furthermore, before the second refrigerant flows into the second heat exchanger, the controller is used to control the first reversing valve to open the medium-pressure throttling valve and the evaporator, and to control the second reversing valve to open the second heat exchanger and the evaporator. When the target wastewater temperature is lower than or equal to the target water tank temperature, the system operates in a second heat recovery mode under the control of the controller. In the second heat recovery mode, the controller controls the first reversing valve to open the low-pressure throttling valve and the evaporator, and controls the second reversing valve to open the evaporator and the low-pressure compressor. Furthermore, before the second refrigerant flows into the second heat exchanger, the controller controls the first reversing valve to open the medium-pressure throttling valve and the second reversing valve, and controls the second reversing valve to open the first reversing valve and the second heat exchanger.

6. The system according to claim 1, characterized in that, The system also includes at least one of the following: An exhaust gas fan is connected to the controller, which controls the exhaust gas flow rate at the exhaust gas inlet by controlling the rotation speed of the exhaust gas fan. A fresh air flow control valve is connected to the controller and located at the entrance of the fresh air duct. The controller is used to control the fresh air flow into the fresh air duct and the exhaust gas flow out of the indoor space to the exhaust gas duct connected to the exhaust gas inlet of the system by controlling the opening of the fresh air flow control valve. The fresh air heat exchanger is connected to the heating equipment and located at the entrance of the fresh air duct. It is used to heat the fresh air by exchanging heat between the heating medium from the heating equipment and the fresh air to be entered into the fresh air duct. The fresh air heat exchange control valve is connected to the controller, the fresh air heat exchanger, and the heating equipment. The controller controls the entry of the heating medium from the heating equipment into the fresh air heat exchanger by controlling the opening and closing state of the fresh air heat exchange control valve. Specifically, the controller controls the fresh air heat exchange control valve to open when the exhaust fan is running, allowing the heating medium to flow into the fresh air heat exchanger; and controls the fresh air heat exchange control valve to close when the exhaust fan is not running, preventing the heating medium from flowing into the fresh air heat exchanger.

7. A control method for a heating system, characterized in that, Applied to the heating system as described in any one of claims 1-6, the method comprises: By controlling the conduction state of the first reversing valve and the second reversing valve, the system is controlled to be in a target heat recovery mode; wherein the target heat recovery mode is either the first heat recovery mode or the second heat recovery mode.

8. The method according to claim 7, characterized in that, The step of controlling the system to be in the target heat recovery mode by controlling the conduction state of the first and second directional valves includes: Based on the temperature comparison results of the target water temperature of the hot water storage tank and the target wastewater temperature, the system is controlled to be in the target heat energy recovery mode by controlling the conduction state of the first reversing valve and the second reversing valve. Wherein, if the temperature comparison result is that the target wastewater temperature is higher than the target water tank temperature, the target heat energy recovery mode is the first heat energy recovery mode; if the temperature comparison result is that the target wastewater temperature is lower than or equal to the target water tank temperature, the target heat energy recovery mode is the second heat energy recovery mode.

9. The method according to claim 7, characterized in that, The method further includes at least one of the following: The variable frequency low-pressure compressor is controlled at a first preset frequency and the variable frequency high-pressure compressor is controlled at a second preset frequency. The opening of the fresh air flow control valve of the system is controlled to control the fresh air flow into the fresh air duct of the system, and the exhaust air flow out of the indoor space to the exhaust air duct connected to the exhaust air inlet of the system. The system controls the on / off state of the fresh air heat exchange control valve to control the entry of the heating medium into the fresh air heat exchanger; wherein, when the exhaust fan is running, the fresh air heat exchange control valve is opened; wherein, when the fresh air heat exchange control valve is open, the heating medium flows into the fresh air heat exchanger; when the exhaust fan stops running, the fresh air heat exchange control valve is closed; wherein, when the fresh air heat exchange control valve is closed, the heating medium is prevented from flowing into the fresh air heat exchanger.

10. An electronic device, characterized in that, The electronic device includes the heating system according to any one of claims 1-6; Alternatively, the electronic device may include: a processor and a memory storing computer program instructions; When the processor executes the computer program instructions, it implements the control method of the heating system as described in any one of claims 7-9.

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