Double high-efficiency double-inverter air source heat pump unit and temperature regulating system

Abstract

This application discloses a dual high-efficiency dual-frequency conversion air source heat pump unit and its temperature control system. The dual high-efficiency dual-frequency conversion air source heat pump unit includes a shell-and-tube heat exchanger, a first working system, and a second working system. The shell-and-tube heat exchanger includes a first opening, a second opening, and a third opening, with the third opening used to connect to the indoor working water pipe. The first working system includes a variable frequency compressor, a four-way reversing valve, a variable frequency fan, a first sub-circuit, a second sub-circuit, and a third branch. The first sub-circuit is connected sequentially from the first opening to the condenser interface, exhaust interface, and outlet of the four-way reversing valve and the variable frequency compressor. The third branch is connected in parallel with the main heating electronic expansion valve and includes a one-way valve and an auxiliary cooling electronic expansion valve, with the valve port diameter of the auxiliary cooling electronic expansion valve being larger than that of the main heating electronic expansion valve. The variable frequency fan is configured to blow airflow at ambient temperature onto the finned heat exchanger. The second working system has the same structure as the first working system.

Description

Technical Field

[0001] This application relates to the field of heat pump technology, and in particular to a dual high-efficiency dual-frequency conversion air source heat pump unit and temperature control system. Background Technology

[0002] In conventional air source heat pump applications, the variable frequency compressor and fan operate at a fixed frequency, and cannot flexibly adjust the output power according to the actual load and environmental changes. They cannot adjust the operating power automatically according to seasonal changes or load changes, resulting in serious energy waste and low overall system energy efficiency.

[0003] Subsequently, the designers devised a dual-frequency conversion system, utilizing a variable-frequency compressor and a variable-frequency fan to achieve efficient energy regulation and output.

[0004] However, in current dual-system heat pumps, the heating and cooling circuits share the same refrigerant circuit. Under medium-temperature conditions, the compression efficiency will decrease due to the mismatch in compression ratios, affecting the overall energy efficiency and performance of the heat pump. Utility Model Content

[0005] The first aspect of this application provides a dual high-efficiency dual-frequency conversion air source heat pump unit, which includes...

[0006] A shell-and-tube heat exchanger, the shell-and-tube heat exchanger including at least a first opening, at least a second opening and at least a third opening, the third opening being used to connect an indoor working water pipe;

[0007] The first working system and the second working system are connected in parallel; the first working system includes a variable frequency compressor, a four-way reversing valve, a variable frequency fan, a first sub-circuit, a second sub-circuit, and a third branch;

[0008] The first sub-circuit is connected in sequence from the first opening to the condenser port of the four-way reversing valve, the exhaust port of the four-way reversing valve, and the second opening end of the variable frequency compressor;

[0009] The second sub-circuit is connected in sequence through the second opening to the main heating electronic expansion valve, the finned heat exchanger, the evaporator interface of the four-way reversing valve, the suction interface of the four-way reversing valve, the gas-liquid separator, and the inlet end of the variable frequency compressor.

[0010] The third branch is connected in parallel with the main heating electronic expansion valve. The third branch includes a one-way valve and an auxiliary cooling electronic expansion valve arranged in sequence. The conduction direction of the one-way valve is towards the second opening of the finned heat exchanger. The valve port diameter of the auxiliary cooling electronic expansion valve is larger than that of the main heating electronic expansion valve.

[0011] The variable frequency fan is configured to blow airflow at ambient temperature onto the finned heat exchanger.

[0012] The second working system has the same structure as the first working system.

[0013] In some modified embodiments of the first aspect of this application, the aforementioned dual high-efficiency dual frequency conversion air source heat pump unit, wherein the first working system further includes a compensation branch, the compensation branch being disposed between the main heating electronic expansion valve and the second opening;

[0014] The compensation branch includes a plate heat exchanger economizer. The main inlet of the plate heat exchanger economizer is connected to the second opening. The main outlet of the plate heat exchanger economizer is connected to the main heating electronic expansion valve. The gas injection inlet of the plate heat exchanger economizer is connected between the main outlet and the main heating electronic expansion valve through a fourth branch. The gas injection outlet of the plate heat exchanger economizer is connected to the inlet end of the variable frequency compressor.

[0015] The fourth branch is equipped with an auxiliary electronic expansion valve.

[0016] In some modified embodiments of the first aspect of this application, the aforementioned dual high-efficiency dual variable frequency air source heat pump unit is provided with a flash evaporator between the gas supply outlet of the plate heat exchanger and the inlet end of the variable frequency compressor.

[0017] In some modified embodiments of the first aspect of this application, the aforementioned dual high-efficiency dual frequency conversion air source heat pump unit, wherein a first filter is provided between the second opening and the plate heat exchanger economizer.

[0018] In some modified embodiments of the first aspect of this application, the aforementioned dual high-efficiency dual frequency conversion air source heat pump unit is provided with a second filter between the auxiliary electronic expansion valve and the air inlet of the plate heat exchanger economizer.

[0019] In some modified embodiments of the first aspect of this application, the aforementioned dual high-efficiency dual frequency conversion air source heat pump unit is provided with a third filter between the main heating electronic expansion valve and the finned heat exchanger.

[0020] In some modified embodiments of the first aspect of this application, the aforementioned dual high-efficiency dual variable frequency air source heat pump unit is provided with a charging valve between the variable frequency compressor and the four-way reversing valve for charging refrigerant into the first working system.

[0021] In some modified embodiments of the first aspect of this application, the aforementioned dual high-efficiency dual variable frequency air source heat pump unit is provided with a high-pressure switch and a first temperature sensor between the variable frequency compressor and the four-way reversing valve.

[0022] In some modified embodiments of the first aspect of this application, the aforementioned dual high-efficiency dual frequency conversion air source heat pump unit, wherein a low-pressure sensor, a low-pressure switch and a fifth temperature sensor are provided between the gas-liquid separator and the frequency conversion compressor.

[0023] A second aspect of this application provides a temperature control system, which includes...

[0024] A working water pipe, wherein the working water pipe is installed indoors;

[0025] A dual-high-efficiency dual-frequency conversion air source heat pump unit, wherein the dual-high-efficiency dual-frequency conversion air source heat pump unit is installed outdoors, and the dual-high-efficiency dual-frequency conversion air source heat pump unit includes:

[0026] A shell-and-tube heat exchanger, the shell-and-tube heat exchanger including at least a first opening, at least a second opening, and at least a third opening, the third opening being connected to the working water pipe;

[0027] The first working system and the second working system are connected in parallel; the first working system includes a variable frequency compressor, a four-way reversing valve, a variable frequency fan, a first sub-circuit, a second sub-circuit, and a third branch;

[0028] The first sub-circuit is connected in sequence from the first opening to the condenser port of the four-way reversing valve, the exhaust port of the four-way reversing valve, and the outlet end of the variable frequency compressor;

[0029] The second sub-circuit is connected in sequence through the second opening to the main heating electronic expansion valve, the finned heat exchanger, the evaporator interface of the four-way reversing valve, the suction interface of the four-way reversing valve, the gas-liquid separator, and the inlet end of the variable frequency compressor.

[0030] The third branch is connected in parallel with the main heating electronic expansion valve. The third branch includes a one-way valve and an auxiliary cooling electronic expansion valve arranged in sequence. The conduction direction of the one-way valve is towards the second opening of the finned heat exchanger. The valve port diameter of the auxiliary cooling electronic expansion valve is larger than that of the main heating electronic expansion valve.

[0031] The variable frequency fan is configured to blow airflow at ambient temperature onto the finned heat exchanger.

[0032] The second working system has the same structure as the first working system.

[0033] Compared to existing technologies, the dual high-efficiency dual-frequency air source heat pump unit provided in this application achieves high energy output through a first and second working system with identical and independent structures. The two working systems can also serve as backups for each other to prevent failures from affecting the operation of the entire unit. At the same time, with the optimized design and switching of the third branch, the refrigerant fluid path is different in cooling mode and heating mode. The large valve port size of the auxiliary cooling electronic expansion valve reduces refrigerant flow resistance, meets the requirements of high-speed refrigerant flow, and improves cooling efficiency. In addition, with the one-way valve, reverse leakage can be used to balance pressure in heating mode, while reducing wear on the main heating electronic expansion valve. This solves the problem in current dual-system heat pumps where the heating and cooling circuits share the same refrigerant circuit, and the compression efficiency decreases due to compression ratio mismatch under medium temperature conditions, affecting the overall energy efficiency and performance of the heat pump. Attached Figure Description

[0034] The above and other objects, features, and advantages of exemplary embodiments of this application will become readily understood by reading the following detailed description with reference to the accompanying drawings. In the drawings, several embodiments of this application are illustrated by way of example and not limitation, with the same or corresponding reference numerals denoteing the same or corresponding parts, wherein:

[0035] Figure 1 A schematic diagram of the first structure of the dual high-efficiency dual frequency conversion air source heat pump unit provided in this embodiment is shown.

[0036] Figure 2 A schematic diagram of the second structure of the dual high-efficiency dual frequency conversion air source heat pump unit provided in this embodiment is shown.

[0037] Figure 3 A schematic diagram of the third structure of the dual high-efficiency dual frequency conversion air source heat pump unit provided in this embodiment is shown.

[0038] Reference numerals: Shell and tube heat exchanger 1, First opening 11, Second opening 12, Third opening 13, Third temperature sensor 14, First working system 2, Variable frequency compressor 21, Four-way reversing valve 22, Condenser interface C, Exhaust interface D, Evaporator interface E, Suction interface S, Variable frequency fan 23, First sub-circuit 24, First filter 241, Second sub-circuit 25, Main heating electronic expansion valve 251, Finned heat exchanger 252, Gas-liquid separator 253, Third filter 254, High-pressure switch 255 First temperature sensor 256, fourth temperature sensor 257, low pressure sensor 258, low pressure switch 259, third branch 26, one-way valve 261, auxiliary refrigeration electronic expansion valve 262, charging valve 27, second working system 3, working water pipe 4, compensation branch 5, plate heat exchanger economizer 51, main inlet 52, main outlet 53, make-up gas inlet 54, make-up gas outlet 55, flash evaporator 56, fourth branch 6, auxiliary electronic expansion valve 61, second filter 62, second temperature sensor 63, liquid receiver 7. Detailed Implementation

[0039] Exemplary embodiments of the present disclosure will now be described in more detail with reference to the accompanying drawings. While exemplary embodiments of the present disclosure are shown in the drawings, it should be understood that the present disclosure may be implemented in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art.

[0040] It should be noted that, unless otherwise stated, the technical or scientific terms used in this application shall have the ordinary meaning as understood by one of ordinary skill in the art to which this application pertains.

[0041] The technical solution of this application embodiment is to solve the above-mentioned technical problems, and the general idea is as follows:

[0042] Example 1

[0043] Reference Appendix Figure 1The dual high-efficiency dual-frequency conversion air source heat pump unit provided in this application embodiment includes a shell-and-tube heat exchanger 1 and a first working system 2 and a second working system 3 connected in parallel. The shell-and-tube heat exchanger 1 includes at least one first opening 11, at least one second opening 12, and at least one third opening 13, the third opening 13 being used to connect to the indoor working water pipe 4. The first working system 2 includes a frequency conversion compressor 21, a four-way reversing valve 22, a frequency conversion fan 23, a first sub-circuit 24, a second sub-circuit 25, and a third branch 26. The first sub-circuit 24 is connected sequentially from the first opening 11 to the condenser interface C of the four-way reversing valve 22, the exhaust interface D of the four-way reversing valve 22, and the outlet end of the frequency conversion compressor 21. The second sub-circuit 25 is connected sequentially from the second opening 12 to the main heating electronic expansion valve 251, the finned heat exchanger 252, the evaporator interface E of the four-way reversing valve 22, the suction interface S of the four-way reversing valve 22, the gas-liquid separator 253, and the frequency conversion compressor. The inlet end of 21; the third branch 26 is connected in parallel with the main heating electronic expansion valve 251, the third branch 26 includes a one-way valve 261 and an auxiliary cooling electronic expansion valve 262 arranged in sequence, the conduction direction of the one-way valve 261 is from the finned heat exchanger 252 to the second opening 12, the valve port diameter of the auxiliary cooling electronic expansion valve 262 is larger than the valve port diameter of the main heating electronic expansion valve 251; the variable frequency fan 23 is arranged corresponding to the finned heat exchanger 252 to blow airflow at ambient temperature to the finned heat exchanger 252; wherein, the second working system 3 has the same structure as the first working system 2.

[0044] Understandably, in order to address the technical problem that current dual-system heat pumps share the same refrigerant circuit for both heating and cooling, leading to decreased compression efficiency due to mismatched compression ratios under medium-temperature conditions, thus affecting the overall energy efficiency and performance of the heat pump, this embodiment provides a dual high-efficiency dual-frequency conversion air source heat pump unit. This unit separates the cooling and heating paths by setting a third branch 26 in the first working system 2 and the second working system 3. The large-diameter auxiliary cooling electronic expansion valve 262 reduces the refrigerant flow resistance, meets the requirements for high-speed refrigerant flow, and at least improves energy efficiency in cooling mode, optimizing mode switching. At the same time, the cooperative setting of the one-way valve 261 can balance the system pressure through a small amount of reverse leakage in heating mode, reducing the risk of liquid slugging in the variable frequency compressor.

[0045] The dual high-efficiency dual-frequency conversion air source heat pump unit provided in this embodiment can be applied in, but is not limited to, residential, commercial buildings, industrial plants, and other fields. The dual high-efficiency dual-frequency conversion air source heat pump unit is an outdoor unit structure.

[0046] The shell-and-tube heat exchanger 1 enables efficient heat exchange between gas and liquid fluids. The internal structure and working principle of the shell-and-tube heat exchanger 1 are easily understood and implemented by those skilled in the art, and will not be elaborated upon here. In this embodiment, the shell-and-tube heat exchanger 1 can be, but is not limited to, a BC-GK-30HP*2 model, utilizing its larger size to achieve more efficient heat exchange and further improve the overall system energy efficiency. It should be noted that the number and position of the first opening 11 and the second opening 12 on the shell-and-tube heat exchanger 1 in this embodiment can be designed and adjusted according to actual needs. For example, each of the first opening 11 and the second opening 12 can be set to one, with the first sub-loop 24 of the first working system 2 and the second working system 3 sharing the first opening 11, and the second sub-loop 25 of the first working system 2 and the second working system 3 sharing the second opening 12. This arrangement simplifies the structure of the shell-and-tube heat exchanger 1. Alternatively, a set of first openings 11 and second openings 12 can be set for the first working system 2, and a set of first openings 11 and second openings 12 can be set for the second working system 3, i.e. Figure 1 As shown, this configuration improves the efficiency of both working systems. Correspondingly, the number of third openings 13 can also be designed and adjusted according to actual needs, such as the number of working water pipes 4 in the user's room, for example: refer to the attached... Figure 1 A third opening 13 is provided on each side of the bottom of the shell-and-tube heat exchanger 1 to connect to the working water pipe 4 for water outlet and return. The liquid to be heated or cooled flows into the user's room through the working water pipe 4 to regulate the room temperature. This configuration is easily understood by those skilled in the art. In this embodiment, a third temperature sensor 14 can be provided at the third opening 13 to detect the temperature of the fluid entering the working water pipe 4, determine whether the user's target has been reached, and generate corresponding adjustment operations to improve temperature regulation efficiency and energy efficiency. The specific adjustment operations are easily understood and implemented by those skilled in the art and will not be described in detail here.

[0047] The variable frequency compressor 21 can dynamically adjust the refrigerant flow by adjusting the motor speed. In this embodiment, it can adjust the motor input frequency in conjunction with the detection of outdoor and indoor environmental temperatures to control the working state, thereby achieving dynamic adjustment according to the target temperature load and reducing energy consumption. The above content is easily understood and implemented by those skilled in the art, and will not be elaborated further here. It is not difficult to understand that the dual high-efficiency dual variable frequency air source heat pump unit provided in this embodiment also includes a controller (not shown in the figure). The controller can perform data transmission, analysis, comparison, and program editing. It can perform intelligent control of the unit according to preset control logic. The controller can control the variable frequency compressor 21 according to relevant temperature detection.

[0048] The variable frequency fan 23 is a fan structure that can control the air volume by adjusting the motor speed. In this embodiment, it can adjust the motor input frequency in conjunction with the detection of outdoor and indoor environmental temperatures to control the air volume, thereby achieving dynamic adjustment according to the target speed load and reducing energy consumption. The above content is understandable and achievable by those skilled in the art, and will not be elaborated further here. It is not difficult to understand that the controller can control the variable frequency fan 23 by relevant temperature detection.

[0049] The four-way reversing valve 22 can switch the flow direction of the refrigerant passing through it, realizing the switching between cooling mode and heating mode in the heat pump. The four-way reversing valve 22 has an exhaust port D, an evaporator port E, an intake port S, and a condenser port C; the exhaust port D is used to connect to the outlet end of the variable frequency compressor 21 to receive high-temperature and high-pressure gas; the evaporator port E is used to connect to the evaporator, and in this embodiment, it is used to connect to the finned heat exchanger 252; the intake port S is used to connect to the condenser, and in this embodiment, it is used to connect to the shell and tube heat exchanger 21; the condenser port C is used to return low-temperature and low-pressure gas to the variable frequency compressor 21 to maintain circulation, and in this embodiment, it is used to connect to the inlet end of the variable frequency compressor 21.

[0050] Accordingly, see Appendix Figure 1 The first working system 2 and the second working system 3 can simultaneously cool, heat, and defrost. Alternatively, one of the first working system 2 and the second working system 3 can perform cooling while the other performs defrosting. The conditions for heating, cooling, and defrosting are easily understood by those skilled in the art, and this embodiment does not improve or protect them, so they will not be elaborated here.

[0051] When heating is required:

[0052] The controller starts the variable frequency compressor 21, drawing in the low-temperature, low-pressure gas from the second sub-circuit 25 and compressing it into high-temperature, high-pressure gas. This high-temperature, high-pressure gas then moves to the four-way reversing valve 22, passing through its exhaust port D and condenser port C, and enters the first sub-circuit 24. It then flows back to the shell-and-tube heat exchanger 1 through the first opening 11 for heat exchange, allowing the heated liquid to flow into the user's room through the working water pipe 4 for heating. Simultaneously, the high-temperature, high-pressure gas, after heat exchange, becomes a low-temperature, high-pressure liquid, which then enters the second sub-circuit 24 through the second opening 12. In circuit 25, the liquid first enters the main heating circuit through the electronic expansion valve 251, where it is throttled to become a low-temperature, low-pressure liquid. This liquid then flows to the finned heat exchanger 252 for heat exchange. The variable frequency fan 23 blows ambient air (at a lower temperature) towards the finned heat exchanger 252, causing the low-temperature, low-pressure liquid to become a low-temperature, low-pressure gas. This gas then flows to the four-way reversing valve 22, passes through its evaporator port E, and is drawn in by the suction port S. It then flows to the gas-liquid separator 253 for gas-liquid separation, allowing the low-temperature, low-pressure gas to return to the variable frequency compressor 21, completing a full heating process. During heating, a small amount of reverse leakage (i.e., leakage from the second sub-circuit 25 to the third branch 26) can occur at the one-way valve 261 to balance the system pressure and improve system stability. It is understood that in heating mode, the auxiliary cooling circuit electronic expansion valve 262 is controlled to be closed. The finned heat exchanger 252 can perform heat exchange by providing a large heat transfer area in conjunction with airflow disturbance. The structure and working principle of the finned heat exchanger 252 are easily understood and implemented by those skilled in the art, and will not be described in detail here. In this embodiment, a finned heat exchanger of model 89.52-4-52-U can be selected, but is not limited to, to achieve more efficient heat exchange and further improve the energy efficiency of the overall system by utilizing its larger size.

[0053] When cooling is required:

[0054] The controller starts the variable frequency compressor 21, drawing in the low-temperature, low-pressure gas from the second sub-circuit 25 and compressing it into high-temperature, high-pressure gas. This high-temperature, high-pressure gas then moves to the four-way reversing valve 22, entering the second sub-circuit 25 via its exhaust port D and evaporator port E, where it reaches the finned heat exchanger 252 for heat exchange. The variable frequency fan 23 blows the higher ambient temperature gas towards the finned heat exchanger 252, causing the high-temperature, high-pressure gas to become a low-temperature, high-pressure liquid. This low-temperature, high-pressure liquid is then throttled by the one-way valve 261 and the auxiliary refrigeration electronic expansion valve 262, becoming a low-temperature, low-pressure liquid. The low-temperature, low-pressure liquid flows into the shell-and-tube heat exchanger 1 through the second opening 12 for heat exchange. This liquid can then flow into the user's room via the working water pipe 4 for cooling. Inside the shell-and-tube heat exchanger 1, the liquid transforms into a low-temperature, low-pressure gas, which then passes through the first opening 11 and the first sub-circuit 24 to the condenser port C of the four-way reversing valve 22. The gas is then drawn in by the suction port S and directed to the gas-liquid separator 253 for gas-liquid separation. The low-temperature, low-pressure gas is then returned to the inlet of the variable frequency compressor 21, completing a full cooling process. Understandably, in cooling mode, the auxiliary cooling electronic expansion valve 262 is opened, while the main heating electronic expansion valve 251 is closed. The auxiliary cooling electronic expansion valve 262 and the main heating electronic expansion valve 251 can be electronic expansion valves with the same structure but different specifications. The electronic expansion valve can precisely regulate the refrigerant flow through electronic control to achieve a throttling effect. In this embodiment, the flow capacity and valve port diameter of the auxiliary cooling electronic expansion valve 262 can be set to be larger than the corresponding parameters of the main heating electronic expansion valve 251 to optimize the switching between cooling and heating modes and ensure that the refrigerant fluid path is different in cooling mode and heating mode. The large valve port and large flow capacity of the auxiliary cooling electronic expansion valve 262 can reduce the refrigerant flow resistance, meet the requirements of high-speed refrigerant flow, and improve the overall cooling energy efficiency of the system. Furthermore, the switching between the auxiliary cooling electronic expansion valve 262 and the main heating electronic expansion valve 251 can effectively reduce the wear of the main heating electronic expansion valve 251.

[0055] When defrosting is required:

[0056] The controller starts the variable frequency compressor 21, which draws in the low-temperature, low-pressure gas from the second sub-circuit 25 and compresses it into high-temperature, high-pressure gas. The high-temperature, high-pressure gas moves to the four-way reversing valve 22 and enters the second sub-circuit 25 through its exhaust port D and evaporator port E, reaching the finned heat exchanger 252 for heat exchange. The variable frequency fan 23 blows the higher ambient temperature gas towards the finned heat exchanger 252, causing the high-temperature, high-pressure gas to become a low-temperature, high-pressure liquid for defrosting. The low-temperature, high-pressure liquid is throttled by the main heating electronic expansion valve 251 and becomes a low-temperature, low-pressure liquid. The low-temperature, low-pressure liquid flows into the shell-and-tube heat exchanger 1 through the second opening 12. The low-temperature, low-pressure liquid is heated in the shell-and-tube heat exchanger 1 and becomes a low-temperature, low-pressure gas. It then passes through the first opening 11 and the first sub-circuit 24 to the condenser port C of the four-way reversing valve 22 and is drawn in by the suction port S. It is then directed to the gas-liquid separator 253 for gas-liquid separation, after which the low-temperature, low-pressure gas is returned to the inlet of the variable frequency compressor 21, completing a full defrosting process.

[0057] It is understood that the second working system 3 in this embodiment has the same structure and working principle as the first working system 2. For a detailed description, please refer to the above content, which will not be repeated here.

[0058] As listed above, the dual high-efficiency dual-frequency conversion air source heat pump unit provided in this application achieves high energy output through a first working system 2 and a second working system 3, which are structurally identical and independent. The two working systems can also serve as backups for each other to prevent failures from affecting the operation of the entire unit. At the same time, with the optimized design and switching of the third branch 26, the fluid path of the refrigerant is different in the cooling mode and the heating mode. The large valve port size of the auxiliary cooling electronic expansion valve 262 reduces the refrigerant flow resistance, meets the requirements of high-speed refrigerant flow, and improves the cooling efficiency. In addition, with the one-way valve 261, it can balance the pressure in the case of a small amount of reverse leakage in the heating mode, and can effectively reduce the wear of the main heating electronic expansion valve 251. Thus, it solves the problem that in the current dual-system heat pump, the heating circuit and the cooling circuit share the same refrigerant circuit, and the compression efficiency will decrease due to the mismatch of compression ratio under medium temperature conditions, which affects the overall energy efficiency and performance of the heat pump.

[0059] In this article, the term "and / or" is merely a description of the relationship between related objects, indicating that there can be three relationships, such as A and / or B. Specifically, it can be understood as: A and B can be included at the same time, A can exist alone, or B can exist alone, and any of the above three situations can be met.

[0060] Further, see attached document. Figure 2In this embodiment, the dual high-efficiency dual frequency conversion air source heat pump unit, in specific implementation, the first working system 2 also includes a compensation branch 5. The compensation branch 5 is set between the main heating electronic expansion valve 251 and the second opening 12 and mainly uses the plate heat exchanger economizer 51 for gas replenishment. It can be understood that when the outdoor ambient temperature is not less than 7 degrees Celsius, the compensation branch 5 is not opened, and correspondingly, when the outdoor ambient temperature is less than 7 degrees Celsius, the compensation branch 5 is opened to improve the gas replenishment efficiency. The compensation branch 5 includes a plate heat exchanger economizer 51. The main inlet 52 of the plate heat exchanger economizer 51 is connected to the second opening 12. The main outlet 53 of the plate heat exchanger economizer 51 is connected to the main heating electronic expansion valve 251. The gas supply inlet 54 of the plate heat exchanger economizer 51 is connected between the main outlet 53 and the main heating electronic expansion valve 251 through the fourth branch 6. The gas supply outlet 55 of the plate heat exchanger economizer 51 is connected to the inlet end of the variable frequency compressor 21. The fourth branch 6 is equipped with an auxiliary electronic expansion valve 61.

[0061] Understandably, in order to cooperate with the variable frequency compressor 21 to achieve the effect of intermediate gas replenishment or subcooling efficiency enhancement, a compensation branch 5 is added in this embodiment. The compensation branch 5 can convert part of the working gas in the second sub-loop 25 into the low temperature and low pressure gas required by the variable frequency compressor 21 to compensate for it. This not only increases the power consumption of the variable frequency compressor 21, but also increases the refrigerant mass flow rate, compensates for the problem of insufficient heat absorption of the system at low temperature, and also improves the heating capacity at low temperature and shortens the defrosting time. The plate heat exchanger economizer 51 includes a main inlet 52, a main outlet 53, a make-up gas inlet 54, and a make-up gas outlet 55. The main inlet 52 is used to connect to the shell-and-tube heat exchanger 1 to introduce the high-temperature liquid refrigerant into the plate heat exchanger economizer 51 for heat exchange to generate gaseous refrigerant. The main outlet 53 is used to connect to the main heating electronic expansion valve 251 to transfer the high-temperature liquid refrigerant to the finned radiator 252. The make-up gas inlet 54 is used to connect to the auxiliary electronic expansion valve 61 to allow the throttled liquid refrigerant to flow back to the plate heat exchanger economizer 51 for heat exchange to form gaseous refrigerant. The make-up gas outlet 55 is used to connect to the intermediate make-up gas port of the variable frequency compressor 21 to replenish the variable frequency compressor 21 with gaseous refrigerant.

[0062] It is not difficult to understand that when the ambient temperature is not less than 7 degrees, the auxiliary electronic expansion valve 61 is closed, and the low-temperature high-pressure liquid from the shell and tube heat exchanger 1 flows directly upward through the main inlet 52 and main outlet 53 of the plate heat exchanger economizer 51 to the main heating electronic expansion valve 252 for throttling and becomes low-temperature low-pressure liquid, thus carrying out the aforementioned heating process. When the ambient temperature is less than 7 degrees, the auxiliary electronic expansion valve 61 is opened, and part of the low-temperature high-pressure liquid flowing out through the main outlet 53 is throttled by the auxiliary electronic expansion valve 61 and then returns to the plate heat exchanger economizer 251 through the gas inlet 54 to absorb the heat between the main inlet 52 and the main outlet 53, thus becoming low-temperature low-pressure gas. The low-temperature low-pressure gas flows back to the intermediate gas inlet of the variable frequency compressor 21 through the gas outlet 55 of the plate heat exchanger economizer 51, or it can be the inlet end of the variable frequency compressor 21, thus completing one compensation process. It is also understood that, for the first working system 2 and the second working system 3, in this embodiment, the compensation branches 5 in the two working systems can be connected by pipelines, and control valves can be installed on the pipelines. When there are special heating requirements or certain fault conditions, the two compensation branches 5 can be used to replenish gas to the same variable frequency compressor 21 at the same time to meet the high power heating requirements, etc.

[0063] Further, see attached document. Figure 2 In the specific implementation of the dual high-efficiency dual variable frequency air source heat pump unit provided in this embodiment, a flash evaporator 56 is provided between the gas supply outlet 55 of the plate heat exchanger 51 and the inlet end of the variable frequency compressor 21.

[0064] Understandably, in order to further optimize the quality of the supplementary gas and the system energy efficiency, a flash evaporator 56 is provided between the supplementary gas outlet 55 and the variable frequency compressor 21 in this embodiment. The flash evaporator 56 can separate the low-temperature and low-pressure gas (which may contain droplets) from the supplementary gas outlet 55 into gas and liquid, ensuring that the gas entering the variable frequency compressor 21 is water-free and saturated, thus preventing the variable frequency compressor 21 from experiencing liquid slugging risk. The flash evaporator 56 can also act as a pressure buffer container to balance the pressure fluctuations between the plate heat exchanger 51 and the variable frequency compressor 21, avoiding sudden changes in the supplementary gas flow rate from affecting the operational stability of the variable frequency compressor 21 and even the entire system.

[0065] Further, see attached document. Figure 3 In the specific implementation of the dual high-efficiency dual frequency conversion air source heat pump unit provided in this embodiment, a first filter 241 is provided between the second opening 12 and the plate heat exchanger 51.

[0066] Understandably, to improve the operational stability of the two systems and the operational safety of each loop, a first filter 241 is installed between the second opening 12 and the plate heat exchanger 51 in this embodiment. The first filter 241 can separate solids and liquids, preventing liquid flowing from the shell-and-tube heat exchanger 1 from carrying particulate matter into the second sub-loop 25 and / or the first sub-loop 24. Once particulate matter enters any sub-loop, it will not only affect the mass flow rate of the refrigerant but also cause damage to the pipeline. In this embodiment, a liquid receiver 7 can also be installed between the second opening 12 and the first filter 241 to store excess liquid refrigerant during a certain mode of operation of the variable frequency compressor 21, thus acting as a buffer in conjunction with the variable frequency.

[0067] Further, see attached document. Figure 3 In the specific implementation of the dual high-efficiency dual frequency conversion air source heat pump unit provided in this embodiment, a second filter 62 is provided between the auxiliary electronic expansion valve 61 and the air inlet 54 of the plate heat exchanger economizer 51.

[0068] Understandably, in order to improve the working stability of the two working systems and the working safety of each circuit, a second filter 62 is provided between the auxiliary electronic expansion valve 61 and the gas inlet 54 of the plate heat exchanger economizer 51 in this embodiment. The second filter 62 can separate solids and liquids to prevent particulate matter from being mixed in with the gas entering the variable frequency compressor 21. In this embodiment, the second filter 62 can be the same as or different from the first filter 241. For example, the filtration accuracy of the second filter 62 is less than that of the first filter 241, which effectively ensures the safety of the variable frequency compressor 21.

[0069] Further, see attached document. Figure 3 In the specific implementation of the dual high-efficiency dual frequency conversion air source heat pump unit provided in this embodiment, a third filter 254 is provided between the main heating electronic expansion valve 251 and the finned heat exchanger 252.

[0070] It is understandable that, in order to improve the operational stability of the two working systems and the operational safety of each circuit, a third filter 254 is provided between the main heating electronic expansion valve 251 and the finned heat exchanger 252 in this embodiment. The third filter 254 can perform solid-liquid separation to prevent the liquid refrigerant entering the finned heat exchanger 252 from being mixed with particulate matter and causing blockages inside the finned heat exchanger 252. In this embodiment, the third filter 254 can be the same as or different from the first filter 241 and the second filter 62. For example, the filtration accuracy of the third filter 254 is lower than that of the second filter 62. In this embodiment, a distributor 8 can also be provided after the third filter to realize the diversion and adjustment of multiple inlets corresponding to the finned heat exchanger 252. This setting can be easily understood and implemented by those skilled in the art, and will not be described in detail here.

[0071] Further, see attached document. Figure 3 In the specific implementation of the dual high-efficiency dual variable frequency air source heat pump unit provided in this embodiment, a charging valve 27 is provided between the variable frequency compressor 21 and the four-way reversing valve 22 for charging refrigerant into the first working system 2.

[0072] It is understood that, in order to enable the operation and maintenance of the heat pump unit, a charging valve 27 is provided between the variable frequency compressor 21 and the four-way reversing valve 22 in this embodiment. The charging valve 27 can inject or remove liquid refrigerant into the working system. This charging valve 27 is located close to the variable frequency compressor 21, so that the variable frequency compressor 21 can be quickly replenished once the system is low on refrigerant, avoiding prolonged shutdown that could affect the temperature control effect. In this embodiment, a charging valve 27 can also be provided between the gas-liquid separator 253 and the four-way reversing valve 22, so that the charging valve 27 is closer to the gas-liquid separator 253. This not only allows for buffering and storage of newly injected refrigerant but also enables rapid supply of refrigerant to the variable frequency compressor 21 through the second sub-circuit 25. It is understood that the refrigerant used in this embodiment can be, but is not limited to, fluorine. It is not difficult to understand that the filling valve 27 is filled with liquid refrigerant or gas-liquid mixture. During the injection process, the variable frequency fan 23 can be turned on simultaneously to accelerate the phase conversion of liquid refrigerant to gaseous refrigerant. This setting can be easily understood and implemented by those skilled in the art, and will not be elaborated on here.

[0073] Further, see attached document. Figure 3 In the specific implementation of the dual high-efficiency dual frequency conversion air source heat pump unit provided in this embodiment, a high-pressure switch 255 and a first temperature sensor 256 are provided between the frequency conversion compressor 21 and the four-way reversing valve 22.

[0074] Understandably, to ensure stable operation and optimize system efficiency, this embodiment includes a high-pressure switch 255 and a first temperature sensor 256. The high-pressure switch 255 detects the pressure level within the system and transmits this information to the controller. The controller can determine whether there is overpressure based on a preset pressure threshold. If overpressure is detected, it indicates potential issues such as excessive refrigerant or poor heat dissipation. In this case, the inverter compressor 21 and inverter fan 23 can be controlled to stop operating or reduce their power to prevent excessive pressure from causing equipment damage or safety accidents, and to effectively extend the overall lifespan of the unit. The first temperature sensor 256 detects the internal temperature between the inverter compressor 21 and the four-way reversing valve 22. If the current outdoor ambient temperature is lower than a preset value and the heating mode needs to be activated, the monitoring result of the first temperature sensor 256 represents the outdoor ambient temperature. The controller will then reduce the operating frequency of the inverter compressor 21 based on this data, reducing refrigerant flow and avoiding energy waste caused by over-compression.

[0075] Further, see attached document. Figure 3 In the specific implementation of the dual high-efficiency dual frequency conversion air source heat pump unit provided in this embodiment, a low-pressure sensor 258, a low-pressure switch 259 and a fifth temperature sensor 257 are provided between the gas-liquid separator 253 and the frequency conversion compressor 21.

[0076] Understandably, to optimize the overall unit's control logic, this embodiment incorporates a low-pressure sensor 258 and a low-pressure switch 259. If the pressure at the inlet of the inverter compressor 21 is detected to be lower than a preset value, it indicates a possible shortage of refrigerant or insufficient system load. In this case, the output power of the inverter compressor 21 can be reduced to achieve optimal energy utilization efficiency. Correspondingly, when the data detected by the low-pressure sensor 258 is lower than a target set value, which is less than the aforementioned preset value, it indicates a severe refrigerant shortage in the system, preventing normal operation. In this case, the low-pressure switch 259 can be controlled to disconnect and stop the inverter compressor 21 from operation, preventing damage to the inverter compressor 21 or system overheating. The fourth temperature sensor 257 detects whether the refrigerant gas returning to the inverter compressor 21 meets its operating requirements. Based on the monitoring data of the fourth temperature sensor 257, the overall system can be quickly and efficiently adjusted. The specific adjustment operation method is easily understood and implemented by those skilled in the art and will not be elaborated here.

[0077] It is understood that in this embodiment, a second temperature sensor 63 can also be installed between the second filter 62 and the plate heat exchanger economizer 51 to detect the refrigerant temperature at the gas injection inlet 54. Simultaneously, the fifth temperature sensor 257 can detect the temperature of the refrigerant entering the variable frequency compressor 21. If the refrigerant temperature is too high, it indicates that there may be insufficient refrigerant or excessive system load. This allows for corresponding adjustments to the opening of each electronic expansion valve or the replenishment of refrigerant within the system, ensuring system operating efficiency and achieving optimal energy utilization.

[0078] Example 2

[0079] This embodiment provides a temperature control system, which includes a working water pipe 4 and a dual high-efficiency dual-frequency conversion air source heat pump unit; the working water pipe 4 is installed indoors; the dual high-efficiency dual-frequency conversion air source heat pump unit is installed outdoors, and the dual high-efficiency dual-frequency conversion air source heat pump unit includes a shell and tube heat exchanger 1 and a first working system 2 and a second working system 3 connected in parallel. The shell-and-tube heat exchanger 1 includes at least one first opening 11, at least one second opening 12, and at least one third opening 13, with the third opening 13 connected to the working water pipe 4. The first working system 2 includes a variable frequency compressor 21, a four-way reversing valve 22, a variable frequency fan 23, a first sub-circuit 24, a second sub-circuit 25, and a third branch 26. The first sub-circuit 24 is connected sequentially from the first opening 11 to the condenser port C of the four-way reversing valve 22, the exhaust port D of the four-way reversing valve, and the outlet end of the variable frequency compressor 21. The second sub-circuit 25 is connected sequentially from the second opening 12 to the main heating electronic expansion valve 251, the finned heat exchanger 252, the evaporator port E of the four-way reversing valve 22, and the four-way reversing fan 26. The system includes the intake port S of valve 22, the gas-liquid separator 253, and the inlet end of the variable frequency compressor 21; the third branch 26 is connected in parallel with the main heating electronic expansion valve 251, and the third branch 26 includes a one-way valve 261 and an auxiliary cooling electronic expansion valve 262 arranged in sequence. The conduction direction of the one-way valve 261 is from the finned heat exchanger 252 toward the second opening 12, and the valve port diameter of the auxiliary cooling electronic expansion valve 262 is larger than the valve port diameter of the main heating electronic expansion valve 251; the variable frequency fan 23 is arranged corresponding to the finned heat exchanger 252 to blow airflow at ambient temperature onto the finned heat exchanger 252; wherein, the second working system 3 has the same structure as the first working system 2.

[0080] It is understood that the dual high-efficiency dual-frequency conversion air source heat pump unit provided in this embodiment is the same as the dual high-efficiency dual-frequency conversion air source heat pump unit described in Embodiment 1. For its specific structure and working principle, please refer to the detailed description of Embodiment 1, which will not be repeated here. The temperature control system provided in this embodiment can be applied, but is not limited to, in residential, commercial buildings, industrial plants, and other fields.

[0081] The above description is merely a specific embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. A double high-efficiency double-inverter air source heat pump unit, characterized in that, It includes: A shell-and-tube heat exchanger, the shell-and-tube heat exchanger including at least a first opening, at least a second opening and at least a third opening, the third opening being used to connect an indoor working water pipe; The first working system and the second working system are connected in parallel; the first working system includes a variable frequency compressor, a four-way reversing valve, a variable frequency fan, a first sub-circuit, a second sub-circuit, and a third branch; The first sub-circuit is connected in sequence from the first opening to the condenser port of the four-way reversing valve, the exhaust port of the four-way reversing valve, and the outlet end of the variable frequency compressor; The second sub-circuit is connected in sequence through the second opening to the main heating electronic expansion valve, the finned heat exchanger, the evaporator interface of the four-way reversing valve, the suction interface of the four-way reversing valve, the gas-liquid separator, and the inlet end of the variable frequency compressor. The third branch is connected in parallel with the main heating electronic expansion valve. The third branch includes a one-way valve and an auxiliary cooling electronic expansion valve arranged in sequence. The conduction direction of the one-way valve is towards the second opening of the finned heat exchanger. The valve port diameter of the auxiliary cooling electronic expansion valve is larger than that of the main heating electronic expansion valve. The variable frequency fan is configured to blow airflow at ambient temperature onto the finned heat exchanger. The second working system has the same structure as the first working system.

2. The dual high-efficiency dual frequency conversion air source heat pump unit according to claim 1, characterized in that: The first working system also includes a compensation branch, which is disposed between the main heating electronic expansion valve and the second opening; The compensation branch includes a plate heat exchanger economizer. The main inlet of the plate heat exchanger economizer is connected to the second opening. The main outlet of the plate heat exchanger economizer is connected to the main heating electronic expansion valve. The gas injection inlet of the plate heat exchanger economizer is connected between the main outlet and the main heating electronic expansion valve through a fourth branch. The gas injection outlet of the plate heat exchanger economizer is connected to the inlet end of the variable frequency compressor. The fourth branch is equipped with an auxiliary electronic expansion valve.

3. The dual high-efficiency dual frequency conversion air source heat pump unit according to claim 2, characterized in that: A flash evaporator is provided between the gas supply outlet of the plate heat exchanger and the inlet of the variable frequency compressor.

4. The dual high-efficiency dual frequency conversion air source heat pump unit according to claim 2, characterized in that: A first filter is provided between the second opening and the plate heat exchanger economizer.

5. The dual high-efficiency dual frequency conversion air source heat pump unit according to claim 2, characterized in that: A second filter is provided between the auxiliary electronic expansion valve and the air inlet of the plate heat exchanger economizer.

6. The dual high-efficiency dual frequency conversion air source heat pump unit according to claim 1, characterized in that: A third filter is provided between the main heating electronic expansion valve and the finned heat exchanger.

7. The dual high-efficiency dual frequency conversion air source heat pump unit according to claim 1, characterized in that: A charging valve is provided between the variable frequency compressor and the four-way reversing valve for charging refrigerant into the first working system.

8. The dual high-efficiency dual frequency conversion air source heat pump unit according to claim 1 or 7, characterized in that: A high-pressure switch and a first temperature sensor are provided between the variable frequency compressor and the four-way reversing valve.

9. The dual high-efficiency dual frequency conversion air source heat pump unit according to claim 1, characterized in that: A low-pressure sensor, a low-pressure switch, and a fifth temperature sensor are provided between the gas-liquid separator and the variable frequency compressor.

10. A tempering system characterized in that, It includes: Working water pipe, the working water pipe being installed indoors ； A dual-high-efficiency dual-frequency conversion air source heat pump unit, wherein the dual-high-efficiency dual-frequency conversion air source heat pump unit is installed outdoors, and the dual-high-efficiency dual-frequency conversion air source heat pump unit includes: A shell-and-tube heat exchanger, the shell-and-tube heat exchanger including at least a first opening, at least a second opening, and at least a third opening, the third opening being connected to the working water pipe; A first working system and a second working system are connected in parallel to the first opening; the first working system includes a variable frequency compressor, a four-way reversing valve, a variable frequency fan, a first sub-circuit, a second sub-circuit, and a third branch; The first sub-circuit is connected in sequence from the first opening to the condenser port of the four-way reversing valve, the exhaust port of the four-way reversing valve, and the outlet end of the variable frequency compressor; The second sub-circuit is connected in sequence through the second opening to the main heating electronic expansion valve, the finned heat exchanger, the evaporator interface of the four-way reversing valve, the suction interface of the four-way reversing valve, the gas-liquid separator, and the inlet end of the variable frequency compressor. The third branch is connected in parallel with the main heating electronic expansion valve. The third branch includes a one-way valve and an auxiliary cooling electronic expansion valve arranged in sequence. The conduction direction of the one-way valve is towards the second opening of the finned heat exchanger. The valve port diameter of the auxiliary cooling electronic expansion valve is larger than that of the main heating electronic expansion valve. The variable frequency fan is configured to blow airflow at ambient temperature onto the finned heat exchanger. The second working system has the same structure as the first working system.

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