heat pump cycle system

Abstract

This invention relates to a heat pump cycle system, comprising a compressor, an indoor heat exchanger, a throttling device, and an outdoor heat exchanger connected via a main refrigerant pipeline. It further includes: a receiver, disposed between the outdoor heat exchanger and the compressor's return port, for storing liquid refrigerant flowing from the outdoor heat exchanger; an auxiliary refrigerant pipeline connected between the receiver and the compressor's return port; a drive device disposed on the auxiliary refrigerant pipeline for controlled driving of the liquid refrigerant in the receiver into the auxiliary refrigerant pipeline; and a heating device for providing heat to the liquid refrigerant in the auxiliary refrigerant pipeline, causing the liquid refrigerant to vaporize and flow to the compressor's return port. Thus, liquid refrigerant that cannot participate in the effective cycle can be stored in the receiver, and the gaseous refrigerant formed after receiving heat from the heating device returns to the compressor, increasing the system's refrigerant flow rate and low-pressure output, while maintaining low cost.

Description

Technical Field

[0001] This invention relates to the field of heating technology, and in particular to a heat pump circulation system. Background Technology

[0002] Heating systems based on the heat pump principle may experience excessively low compressor suction pressure when outdoor ambient temperatures are low. This leads to a decrease in refrigerant circulation flow, an increase in compressor pressure ratio, and increased system power consumption, resulting in poor system adaptability under low-temperature conditions. Specifically, when outdoor ambient temperatures are low, the evaporation pressure of the air source heat pump unit decreases, consequently leading to a low compressor suction pressure. With the heating water temperature set constant, the system condensing pressure changes little, ultimately resulting in an increased system pressure ratio, increased compressor power consumption, and reduced system energy efficiency. Over time, this significantly reduces the system's economic efficiency. Simultaneously, the low evaporation pressure increases the compressor's suction specific volume. At the same compressor speed and displacement, an increased suction specific volume reduces the refrigerant circulation mass flow rate within the system, further decreasing the overall heating capacity of the system.

[0003] Currently, the mainstream solution for improving the low-temperature adaptability of air source heat pump systems is to adopt quasi-two-stage compression technology, increasing the compressor's suction pressure and the system's refrigerant circulation flow rate. This involves replacing the traditional single-stage compressor with a dedicated compressor for injecting gas and increasing enthalpy. Utilizing the principle of quasi-two-stage compression, an injection port is opened at an appropriate location on the compressor to supplement the refrigerant at an intermediate pressure state, thus improving the system's low-temperature adaptability. However, this solution has drawbacks: the system configuration is more complex, increasing the overall cost; furthermore, it reduces the amount of refrigerant at intermediate pressure, thus decreasing the heat exchange efficiency. Summary of the Invention

[0004] One object of the present invention is to overcome at least one defect of the prior art and to provide a heat pump cycle system with better heating performance and lower cost at low temperatures.

[0005] A further object of the present invention is to avoid the adverse effects of adding refrigerant to the compressor.

[0006] Another further objective of the present invention is to simplify the structure of the heat pump cycle system.

[0007] According to a first aspect of the present invention, a heat pump cycle system is provided, comprising a compressor, an indoor heat exchanger, a throttling device, and an outdoor heat exchanger connected via a refrigerant main pipeline, and further comprising:

[0008] A liquid receiver is disposed between the outdoor heat exchanger and the return port of the compressor for storing liquid refrigerant flowing out of the outdoor heat exchanger.

[0009] A refrigerant auxiliary pipeline is connected between the liquid receiver and the compressor return port;

[0010] A driving device, disposed on the refrigerant auxiliary pipeline, is used to controllably drive the liquid refrigerant in the receiver into the refrigerant auxiliary pipeline; and

[0011] A heating device is used to provide heat to the liquid refrigerant in the refrigerant auxiliary pipeline so that the liquid refrigerant vaporizes and flows to the return port of the compressor.

[0012] Optionally, the heating device is an auxiliary heat exchanger, which is configured to absorb heat from the fluid medium and transfer it to the liquid refrigerant in the refrigerant auxiliary pipeline.

[0013] Optionally, the auxiliary heat exchanger has two auxiliary heat exchange pipes that exchange heat with each other. One of the auxiliary heat exchange pipes is a section of the refrigerant auxiliary pipe, and the other is a section of the auxiliary heat exchange pipe for flowing a high-temperature heat exchanger, so that the heat of the high-temperature heat exchanger in the auxiliary heat exchanger is transferred to the liquid refrigerant in the refrigerant auxiliary pipe; wherein

[0014] The auxiliary heating pipeline is circulated in connection with the heat exchanger supply source used to provide the high-temperature heat exchanger.

[0015] Optionally, the heat pump cycle system further includes:

[0016] The first temperature acquisition device is used to acquire the refrigerant temperature at the refrigerant outlet of the refrigerant auxiliary pipeline;

[0017] The second temperature acquisition device is used to acquire the evaporation temperature of the heat pump cycle system; and

[0018] The auxiliary heating pipeline is equipped with a first circulation pump, which is configured to controllably adjust the flow rate of the high-temperature heat exchanger in the auxiliary heating pipeline according to the difference between the refrigerant temperature obtained by the first temperature acquisition device and the evaporation temperature obtained by the second temperature acquisition device.

[0019] Optionally, the first circulating pump is further configured to keep the flow rate of the high-temperature heat exchanger in the auxiliary heating pipeline constant when the difference is within a first preset temperature difference range, increase the flow rate of the high-temperature heat exchanger in the auxiliary heating pipeline when the difference is less than the first preset temperature difference range, and decrease the flow rate of the high-temperature heat exchanger in the auxiliary heating pipeline when the difference is greater than the first preset temperature difference range.

[0020] Optionally, the heat pump cycle system further includes:

[0021] A second temperature acquisition device is used to acquire the evaporation temperature of the heat pump cycle system; and

[0022] A third temperature acquisition device is used to acquire the refrigerant temperature at the compressor's return port; and

[0023] The drive device is configured to controllably adjust the flow rate of liquid refrigerant in the refrigerant auxiliary pipeline based on the difference between the refrigerant temperature obtained by the third temperature acquisition device and the evaporation temperature obtained by the second temperature acquisition device.

[0024] Optionally, the driving device is further configured to keep the flow rate of liquid refrigerant in the refrigerant auxiliary pipeline constant when the difference is within the second preset temperature difference range, increase the flow rate of liquid refrigerant in the refrigerant auxiliary pipeline when the difference is less than the second preset temperature difference range, and decrease the flow rate of liquid refrigerant in the refrigerant auxiliary pipeline when the difference is greater than the second preset temperature difference range.

[0025] Optionally, the indoor heat exchanger has two indoor heat exchange pipes that exchange heat with each other. One of the indoor heat exchange pipes is a section of the main refrigerant pipe, and the other indoor heat exchange pipe is a section of a heating pipe for flowing heating fluid, so that the heat of the refrigerant in the main refrigerant pipe is transferred to the heating fluid in the heating pipe; wherein

[0026] The heating pipeline is circulated in connection with a heating fluid tank for storing the heating fluid.

[0027] Optionally, the heat exchanger source is the heating fluid tank, so as to use the heating fluid in the heating fluid tank to heat the liquid refrigerant in the refrigerant auxiliary pipeline.

[0028] Optionally, the heat pump cycle system further includes:

[0029] A heat dissipation device is installed in the indoor environment and connected between the indoor heat exchanger and the heating fluid tank, so that the heating fluid, after absorbing heat at the indoor heat exchanger, exchanges heat with the air in the indoor environment through the heat dissipation device, thereby transferring heat to the indoor environment.

[0030] Optionally, the refrigerant auxiliary pipeline is further provided with a solenoid valve, which is used to control the on / off state of the refrigerant auxiliary pipeline and / or the refrigerant flow rate in the refrigerant auxiliary pipeline.

[0031] In addition to a conventional compressor, indoor heat exchanger, throttling device, and outdoor heat exchanger, the heat pump cycle system of this invention also includes a liquid receiver between the outdoor heat exchanger and the compressor's return port. A refrigerant auxiliary pipeline, connected in parallel with a section of the main refrigerant pipeline, is also provided between the liquid receiver and the compressor's return port. Furthermore, a drive device and a heating device are installed on the refrigerant auxiliary pipeline. Thus, liquid refrigerant that cannot participate in effective circulation can be stored in the liquid receiver. The drive device can draw liquid refrigerant from the receiver, causing it to vaporize upon receiving heat from the heating device as it flows through the refrigerant auxiliary pipeline. The resulting gaseous refrigerant, along with the gaseous refrigerant in the main refrigerant pipeline, returns to the compressor's return port, increasing the refrigerant flow rate drawn into the compressor. This increases the refrigerant flow rate and low-pressure level throughout the system, improving the system's heating performance and enhancing its reliability and adaptability during low-temperature operation. Furthermore, the present invention only requires the addition of a low-cost liquid receiver, drive device, and heating device to the traditional compression refrigeration cycle device. Compared with replacing the compressor with a dedicated compressor for gas injection and enthalpy enhancement, the heat pump cycle system of the present invention has a very low cost.

[0032] Furthermore, the heating device of this application is preferably an auxiliary heat exchanger. This auxiliary heat exchanger can transfer the heat from the high-temperature heat exchanger in the auxiliary heating pipeline to the liquid refrigerant in the refrigerant auxiliary pipeline. It has high heat transfer efficiency and a stable heat source, which can improve the vaporization efficiency of the liquid refrigerant. More importantly, this application determines the refrigerant state (liquid or gaseous) at the refrigerant outlet of the refrigerant auxiliary pipeline by the difference between the refrigerant temperature and the evaporation temperature. Based on this, the flow rate of the high-temperature heat exchanger in the auxiliary heating pipeline is adjusted to appropriately increase or decrease the heat that the high-temperature heat exchanger can provide. This effectively ensures that all the refrigerant flowing out of the refrigerant outlet of the refrigerant auxiliary pipeline is gaseous refrigerant, avoiding liquid refrigerant entering the compressor and causing liquid compression or adverse effects on the compressor.

[0033] Furthermore, this application sets the heat exchanger supply source for providing high-temperature heat exchanger as a heating fluid tank for storing heating fluid. In other words, the excess heat of the heating fluid accumulated in the heating fluid tank can be used to heat the liquid refrigerant in the refrigerant auxiliary pipeline. There is no need to set up an additional heat exchanger supply source, nor is it necessary to heat the high-temperature heat exchanger in the heat exchanger supply source. This fully utilizes the structure and energy of the heat pump cycle system and simplifies the structure of the heat pump cycle system.

[0034] The above and other objects, advantages and features of the present invention will become more apparent to those skilled in the art from the following detailed description of specific embodiments of the invention in conjunction with the accompanying drawings. Attached Figure Description

[0035] The following sections will describe some specific embodiments of the invention in detail by way of example and not limitation, with reference to the accompanying drawings. The same reference numerals in the drawings denote the same or similar parts or portions. Those skilled in the art should understand that these drawings are not necessarily drawn to scale. In the drawings:

[0036] Figure 1 This is a schematic structural diagram of a heat pump cycle system according to an embodiment of the present invention;

[0037] Figure 2 This is a schematic structural diagram of a heat pump cycle system according to another embodiment of the present invention;

[0038] Figure 3 This is a schematic structural diagram of a heat pump cycle system according to yet another embodiment of the present invention. Detailed Implementation

[0039] This invention provides a heat pump circulation system. Figure 1 This is a schematic structural diagram of a heat pump cycle system according to an embodiment of the present invention. The heat pump cycle system 1 of the present invention includes a compressor 10, an indoor heat exchanger 20, a throttling device 30, and an outdoor heat exchanger 40, all connected by a refrigerant main pipeline 101. During heating (including heating demand or hot water demand), the indoor heat exchanger 20 is used as a condenser, and the outdoor heat exchanger 40 is used as an evaporator. The compressor 10 provides circulation power for the heat pump cycle system 1. After the compressor 10 starts, it compresses the refrigerant into a high-temperature, high-pressure gaseous refrigerant. The high-temperature, high-pressure gaseous refrigerant is cooled and condensed in the indoor heat exchanger 20, which acts as a condenser, and becomes a medium-temperature, high-pressure liquid refrigerant. It then flows through the throttling device 30 for throttling and cooling. The throttled and cooled refrigerant flows to the outdoor heat exchanger 20, which acts as an evaporator. It absorbs heat from the outdoor environment and vaporizes in the outdoor heat exchanger 20, finally returning to the compressor 10, thus forming a complete main cycle.

[0040] When the outdoor ambient temperature is low, the suction pressure is low, and most of the excess refrigerant in the heat pump cycle system 1 deposits in the outdoor heat exchanger 40, which is equivalent to the evaporator, and cannot effectively participate in the system cycle. Therefore, the heat pump cycle system 1 of this application also includes a liquid receiver 50 disposed between the outdoor heat exchanger 40 and the return port 12 of the compressor 10, for storing the liquid refrigerant flowing out of the outdoor heat exchanger 40. That is, the liquid receiver 50 is connected in series between the outdoor heat exchanger 40 and the return port 12 of the compressor 10. The gaseous refrigerant flowing out of the outdoor heat exchanger 40 returns to the return port of the compressor 10 for the next cycle, while the liquid refrigerant flowing out of the outdoor heat exchanger 40 can be stored in the liquid receiver 50 to prevent liquid refrigerant from entering the compressor 10 and causing liquid compression of the compressor 10.

[0041] The applicant recognizes that when outdoor temperatures are low, the liquid refrigerant in receiver 50 cannot participate in the main cycle. To increase the refrigerant flow rate and low-pressure circulation throughout the system, the liquid refrigerant in receiver 50 that is not participating in the main cycle due to low temperature can be mobilized. This increases the total amount of gaseous refrigerant flowing back to compressor 10 without reducing the amount of gaseous refrigerant at high pressure in the main cycle path.

[0042] Therefore, the heat pump cycle system 1 of this application also includes a refrigerant auxiliary pipeline 102, which is connected between the receiver 50 and the return port 12 of the compressor 10. The configuration of the refrigerant auxiliary pipeline 102 provides a path for the refrigerant in the receiver 50 to flow to the return port 12 of the compressor 10. It is understood that the refrigerant auxiliary pipeline 102 and the main refrigerant pipeline 101 are two independent refrigerant pipelines. A portion of the refrigerant auxiliary pipeline 102 and a portion of the main refrigerant pipeline 101 are connected in parallel. This portion of the pipeline is all or part of the section of the main refrigerant pipeline 101 located between the receiver 50 and the return port 12 of the compressor 10. It should be noted that the parallel connection mentioned here refers to a physical structural parallel connection, not a circuit parallel connection.

[0043] Furthermore, the heat pump cycle system 1 also includes a drive unit 61 and a heating unit 71. The drive unit 61 is disposed on the refrigerant auxiliary pipeline 102 and is used to controllably drive the liquid refrigerant in the receiver 50 into the refrigerant auxiliary pipeline 102. The drive unit 61 provides power for the liquid refrigerant in the receiver 50 to flow into the refrigerant auxiliary pipeline 102. The heating unit 71 provides heat to the liquid refrigerant in the refrigerant auxiliary pipeline 102, causing the liquid refrigerant to vaporize and flow to the return port 12 of the compressor 10. That is, the heating unit 71 provides heat to the liquid refrigerant in the refrigerant auxiliary pipeline 102, causing it to flow to the return port 12 of the compressor 10 in gaseous form.

[0044] As can be seen, the liquid refrigerant that cannot participate in the effective circulation in the heat pump cycle system 1 of this application can be stored in the liquid receiver 50. The liquid refrigerant in the liquid receiver 50 can be drawn out by the drive device 61 and vaporized when it receives heat from the heating device 71 as it flows through the refrigerant auxiliary pipeline 102. The vaporized gaseous refrigerant and the gaseous refrigerant in the refrigerant main pipeline 101 return to the return port 12 of the compressor 10 together, which increases the refrigerant flow rate sucked into the compressor 10, thereby increasing the refrigerant flow rate and compressor suction pressure circulating throughout the system, improving the heating performance of the system at low temperatures, and improving the reliability and adaptability of the system at low temperatures.

[0045] Furthermore, the present invention only requires the addition of a low-cost liquid receiver 50, a drive device 61, and a heating device 71 to the traditional compression refrigeration cycle system, without changing the type of compressor. Compared to replacing the compressor with a dedicated compressor for gas injection and enthalpy enhancement, the heat pump cycle system 1 of the present invention has a very low cost.

[0046] Preferably, the drive device 61 can be a circulating pump.

[0047] In some embodiments, the heating device 71 is an auxiliary heat exchanger configured to absorb heat from the fluid medium and transfer it to the liquid refrigerant in the refrigerant auxiliary pipeline 102. Specifically, the auxiliary heat exchanger can absorb heat from flowing air and transfer it to the liquid refrigerant in the refrigerant auxiliary pipeline 102, or it can absorb heat from flowing liquid and transfer it to the liquid refrigerant in the refrigerant auxiliary pipeline 102. The flowing liquid can be water or other liquids with high heat storage capacity and low cost.

[0048] In other embodiments, the heating device 71 may also be a heating device that uses electromagnetic principles, radiation principles, or the like to heat the liquid refrigerant in the refrigerant auxiliary pipeline 102. For example, the heating device 71 may also be an electromagnetic induction heating device, which can uniformly heat the refrigerant auxiliary pipeline 102 and has high heating efficiency, so that the liquid refrigerant in the refrigerant auxiliary pipeline 102 can be heated uniformly and efficiently.

[0049] Compared to heating devices that use electromagnetic or radiation principles for heating, heat exchangers consume less energy. Therefore, the heating device 71 of the present invention is preferably an auxiliary heat exchanger.

[0050] Figure 2 This is a schematic structural diagram of a heat pump cycle system according to another embodiment of the present invention. In some embodiments, when the heating device 71 is an auxiliary heat exchanger, it may include two auxiliary heat exchange pipelines capable of exchanging heat with each other. One auxiliary heat exchange pipeline is a section of a refrigerant auxiliary pipeline 102, and the other auxiliary heat exchange pipeline is a section of an auxiliary heat exchange pipeline 103 for flowing a high-temperature heat exchanger, so that the heat of the high-temperature heat exchanger in the auxiliary heat exchange pipeline 103 is transferred to the liquid refrigerant in the refrigerant auxiliary pipeline 102. The auxiliary heat exchange pipeline 103 is cyclically connected to a heat exchanger supply source 72 for providing the high-temperature heat exchanger, and the high-temperature heat exchanger can circulate between the auxiliary heat exchange pipeline 103 and the heat exchanger supply source 72.

[0051] It can be seen that the auxiliary heat exchanger can transfer the heat of the high-temperature heat exchanger in the auxiliary heat pipe 103 to the liquid refrigerant in the refrigerant auxiliary pipe 102. The heat transfer efficiency is high and the heat source is stable, which can improve the efficiency of liquid refrigerant vaporization.

[0052] Furthermore, a portion of the refrigerant auxiliary pipeline 102 and a portion of the auxiliary heat pipeline 103, which form the two auxiliary heat exchange pipelines of the auxiliary heat exchanger, are arranged adjacent to or close to each other to improve the heat exchange efficiency between them.

[0053] Specifically, the auxiliary heat exchanger can be formed in various flexible ways. For example, the auxiliary heat exchanger may have a shell, through which both the auxiliary heating pipe 103 and the refrigerant auxiliary pipe 102 pass. The auxiliary heating pipe 103 and the refrigerant auxiliary pipe 102, located within the shell, form the two auxiliary heat exchange pipes. These two auxiliary heat exchange pipes can be distributed in an S-shape or other meandering pattern within the shell to improve heat exchange efficiency. Alternatively, the auxiliary heat exchanger can be formed by directly binding or welding together sections of the auxiliary heating pipe 103 and the refrigerant auxiliary pipe 102, without the shell. Regardless of the form, heat exchange can be achieved between the high-temperature heat exchanger in the auxiliary heating pipe 103 and the liquid refrigerant in the refrigerant auxiliary pipe 102.

[0054] In some embodiments, the heat pump cycle system 1 further includes a first temperature acquisition device and a second temperature acquisition device. The first temperature acquisition device is used to acquire the refrigerant temperature at the refrigerant outlet of the refrigerant auxiliary pipeline 102. The second temperature acquisition device is used to acquire the evaporation temperature of the heat pump cycle system 1. Specifically, the first temperature acquisition device may be located at the refrigerant outlet of the refrigerant auxiliary pipeline 102. It is understood that, generally, the evaporation temperature of the heat pump cycle system 1 can be approximated to the coil temperature of its evaporator, i.e., the coil temperature of the outdoor heat exchanger 40. Therefore, the second temperature acquisition device may be located at the heat exchange coil of the outdoor heat exchanger 40.

[0055] Furthermore, a first circulation pump 62 is provided on the auxiliary heating pipe 103. The first circulation pump 62 is configured to controllably adjust the flow rate of the high-temperature heat exchanger in the auxiliary heating pipe 103 according to the difference between the refrigerant temperature obtained by the first temperature acquisition device and the evaporation temperature obtained by the second temperature acquisition device. The applicant recognizes that the superheat obtained by subtracting the refrigerant temperature from the evaporation temperature at the refrigerant outlet of the refrigerant auxiliary pipe 102 can reflect the refrigerant state at the refrigerant outlet of the refrigerant auxiliary pipe 102, i.e., whether it is gaseous or liquid. Therefore, the difference between the refrigerant temperature and the evaporation temperature at the refrigerant outlet of the refrigerant auxiliary pipeline 102 can be used to determine whether the heat provided by the auxiliary heating pipeline 103 to the refrigerant auxiliary pipeline 102 is sufficient to convert all the liquid refrigerant in the refrigerant auxiliary pipeline 102 into gaseous refrigerant. Then, when the provided heat does not match the demand, the flow rate of the high-temperature heat exchanger in the auxiliary heating pipeline 103 can be appropriately adjusted to increase or decrease the heat provided by the high-temperature heat exchanger. This can effectively ensure that all the refrigerant flowing out of the refrigerant outlet of the refrigerant auxiliary pipeline 102 is gaseous refrigerant, and prevent liquid refrigerant from entering the compressor 10 and causing liquid compression or adverse effects on the compressor 10.

[0056] Specifically, the first circulating pump 62 is further configured to maintain the flow rate of the high-temperature heat exchanger in the auxiliary heating pipeline 103 unchanged when the above-mentioned difference (i.e., the difference between the refrigerant temperature and the evaporation temperature at the refrigerant outlet of the refrigerant auxiliary pipeline 102) is within the first preset temperature difference range; increase the flow rate of the high-temperature heat exchanger in the auxiliary heating pipeline 103 when the above-mentioned difference is less than the first preset temperature difference range; and decrease the flow rate of the high-temperature heat exchanger in the auxiliary heating pipeline 103 when the above-mentioned difference is greater than the first preset temperature difference range.

[0057] Preferably, the first preset temperature difference range can be 15 to 20°C.

[0058] In some embodiments, the heat pump cycle system 1 includes a second temperature acquisition device for acquiring the evaporation temperature of the heat pump cycle system 1, and a third temperature acquisition device for acquiring the refrigerant temperature at the return port 12 of the compressor 10. Specifically, the third temperature acquisition device may be located at the return port 12 of the compressor 10.

[0059] Furthermore, the drive unit 61 is configured to controllably adjust the flow rate of liquid refrigerant in the refrigerant auxiliary pipeline 102 based on the difference between the refrigerant temperature obtained by the third temperature acquisition device and the evaporation temperature obtained by the second temperature acquisition device. The applicant recognizes that the compressor suction superheat, obtained by subtracting the refrigerant temperature from the evaporation temperature at the compressor 10's return port 12, reflects the total amount of gaseous refrigerant returning to the compressor 10 via the compressor 10's return port 12. Therefore, this compressor suction superheat can be used to determine whether the sum of the liquid refrigerant drawn from the receiver 50 and the gaseous refrigerant in the main refrigerant pipeline 101 meets the overall return volume requirement of the compressor 10. If the requirements are not met, the amount of liquid refrigerant drawn from the receiver 50 and flowing in the refrigerant auxiliary pipeline 102 can be appropriately adjusted to regulate the amount of gaseous refrigerant flowing back to the compressor 10 through the refrigerant auxiliary pipeline 102, thereby adjusting the total return gas volume of the compressor 10 and ensuring that the heat pump cycle system 1 has sufficient circulating refrigerant and a good heating effect.

[0060] Specifically, the drive device 61 is further configured to maintain the flow rate of liquid refrigerant in the refrigerant auxiliary pipeline 102 unchanged when the difference (the difference between the refrigerant temperature and the evaporation temperature at the return port 12 of the compressor 10) is within the second preset temperature difference range; increase the flow rate of liquid refrigerant in the refrigerant auxiliary pipeline 102 when the difference is less than the second preset temperature difference range; and decrease the flow rate of liquid refrigerant in the refrigerant auxiliary pipeline 102 when the difference is greater than the second preset temperature difference range.

[0061] Preferably, the second preset temperature difference range can be 2 to 5°C.

[0062] In some embodiments, the heat pump circulation system 1 can provide heating by supplying hot water to the room. In other embodiments, the heat pump circulation system 1 can also provide heating by supplying hot air or warm air to the room. Since hot water can be distributed throughout the room through coils, radiators, etc., and does not cause users the uncomfortable experience of direct hot air blowing like air conditioning, hot water heating is more widely used and provides greater user comfort.

[0063] Therefore, in some embodiments, the indoor heat exchanger 20 of the present invention can transfer its heat to a heating fluid, such as heating water. In this case, the indoor heat exchanger 20 has two indoor heat exchange pipes that exchange heat with each other. One indoor heat exchange pipe is a section of the refrigerant main pipe 101, and the other indoor heat exchange pipe is a section of the heating pipe 104 for flowing the heating fluid, so that the heat of the refrigerant in the refrigerant main pipe 101 is transferred to the heating fluid in the heating pipe 104, thereby providing heating to the room through the heating fluid. The heating pipe 104 is circulatedly connected to a heating fluid tank 73 for storing the heating fluid, and the heating fluid can circulate between the heating pipe 104 and the heating fluid tank 73.

[0064] Specifically, the heating fluid tank 73 can be a pressurized water tank.

[0065] Furthermore, sections of the refrigerant main pipeline 101 and the heating pipeline 104 used to form the two indoor heat exchange pipelines of the indoor heat exchanger 20 are arranged adjacent to or close to each other to improve the heat exchange efficiency between them.

[0066] Specifically, the indoor heat exchanger 20 can be formed in various ways. For example, the indoor heat exchanger 20 may have an outer shell, through which both the refrigerant main pipe 101 and the heating pipe 104 pass. The refrigerant main pipe 101 and the heating pipe 104, located within the shell, form two indoor heat exchange pipes within the indoor heat exchanger 20. These two indoor heat exchange pipes can be distributed in an S-shape or other meandering pattern within the shell to improve heat exchange efficiency. Alternatively, the indoor heat exchanger 20 can also be formed by directly binding or welding together sections of the refrigerant main pipe 101 and heating pipe 104, i.e., without the outer shell. Regardless of the form, heat exchange can be exchanged between the high-temperature refrigerant in the refrigerant main pipe 101 and the heating fluid in the heating pipe 104.

[0067] Figure 3This is a schematic structural diagram of a heat pump cycle system according to another embodiment of the present invention. To ensure basic heating performance, the heating fluid tank 73 typically stores a large amount of heating fluid at a high temperature, while the amount of heating fluid flowing in the heating pipe 104 is limited. Therefore, there is excess heat in the heating fluid tank 73. To fully utilize this excess heat, in some embodiments, the heat exchanger supply source 72 can be the heating fluid tank 73, so as to use the heating fluid in the heating fluid tank 73 to heat the liquid refrigerant in the refrigerant auxiliary pipe 102. In other words, at this time, the high-temperature heat exchanger used to heat the liquid refrigerant in the refrigerant auxiliary pipeline 102 is the heating fluid in the heating fluid tank 73. The excess heat of the heating fluid accumulated in the heating fluid tank 73 can be used to heat the liquid refrigerant in the refrigerant auxiliary pipeline 102. There is no need to set up an additional heat exchanger supply source, nor is it necessary to heat the high-temperature heat exchanger in the heat exchanger supply source. This fully utilizes the structure and energy of the heat pump cycle system 1 and simplifies the structure of the heat pump cycle system 1.

[0068] In some embodiments, the heat pump circulation system 1 further includes a heat dissipation device 74, which is disposed in the indoor environment and connected between the indoor heat exchanger 20 and the heating fluid tank 73, so that the heating fluid that absorbs heat at the indoor heat exchanger 20 exchanges heat with the air in the indoor environment through the heat dissipation device 74, thereby transferring heat to the indoor environment. The heating fluid after heat transfer returns to the heating fluid tank 73 to enter the next cycle.

[0069] Specifically, the heat dissipation device 74 can be a heating coil, radiator, or fan coil unit, etc. The heat dissipation device 74 can be located above or below the floor in the room.

[0070] In some embodiments, the refrigerant auxiliary pipeline 102 is further provided with a solenoid valve 91, which is used to control the on / off state of the refrigerant auxiliary pipeline 102 and / or the refrigerant flow rate in the refrigerant auxiliary pipeline 102.

[0071] Furthermore, the opening and closing of the solenoid valve 91 can be determined based on the outdoor ambient temperature. When the outdoor ambient temperature is lower than the first preset temperature threshold, the solenoid valve 91 can be opened to conduct the refrigerant auxiliary pipeline 102, facilitating the vaporization of the liquid refrigerant in the receiver 50 and its delivery to the return port 12 of the compressor 10. When the outdoor ambient temperature is higher than the second preset temperature threshold, the solenoid valve 91 can be closed to block the refrigerant auxiliary pipeline 102.

[0072] Specifically, the first preset temperature threshold can be any temperature value between -5 and -9°C. Both the first and second preset temperature thresholds can be adjusted according to the actual operating conditions of the heat pump cycle system 1.

[0073] In some embodiments, the heat pump cycle system 1 may further include a four-way valve 92, which is connected to the exhaust port 11 of the compressor 10 to adjust the flow direction of the refrigerant coming out of the compressor 10.

[0074] In some embodiments, a second circulation pump 63 may also be provided on the heating pipe 104, the second circulation pump 63 being used to drive the heating fluid to circulate between the heating pipe 104 and the heating fluid tank 73.

[0075] The working process of the heat pump cycle system 1 is summarized and described below using one embodiment of the present invention.

[0076] Under normal outdoor conditions, solenoid valve 91 is closed, and no refrigerant flows through refrigerant auxiliary pipeline 102. The refrigerant circulates through refrigerant main pipeline 101 between compressor 10, indoor heat exchanger 20, throttling device 30, and outdoor heat exchanger 40. This is the refrigerant cycle, which will not be described further. During this process, the high-temperature refrigerant flowing through indoor heat exchanger 20 exchanges heat with the heating fluid flowing out of heating fluid tank 73 and flowing through indoor heat exchanger 20. The heat is transferred from the refrigerant to the heating fluid, which flows through heating pipeline 104 to heat dissipation device 74, where the heat is dissipated to the indoor environment, providing heating. After dissipating heat, the heating fluid flows back to heating fluid tank 73, thus completing one heating cycle.

[0077] When the outdoor ambient temperature is low, the solenoid valve 91 opens, the refrigerant auxiliary pipeline 102 is connected, and the drive device 61 and the first circulation pump 62 start. The gaseous refrigerant flowing from the outdoor heat exchanger 40 returns to the compressor 10 and circulates between the compressor 10, indoor heat exchanger 20, throttling device 30, and outdoor heat exchanger 40 via the refrigerant main pipeline 101. The liquid refrigerant flowing from the outdoor heat exchanger 40 remains in the receiver 50. The drive device 61 drives a portion of the liquid refrigerant in the receiver 50 into the refrigerant auxiliary pipeline 102, flowing through the heating device 71. Simultaneously, the heating fluid driven by the first circulation pump 62 flows to the heating device 71 via the auxiliary heating pipeline 103. Inside the heating device 71, the heating fluid exchanges heat with the liquid refrigerant; heat is transferred from the heating fluid to the liquid refrigerant, which absorbs heat, vaporizes, and returns to the compressor 10 as a gaseous refrigerant. In this case, the refrigerant returning to the compressor 10 return port 12 is the sum of the refrigerant in the main refrigerant line 101 and the refrigerant auxiliary line 102. The heating cycle is the same as under normal conditions, and will not be described in detail here.

[0078] Therefore, those skilled in the art should recognize that although numerous exemplary embodiments of the present invention have been shown and described in detail herein, many other variations or modifications conforming to the principles of the present invention can be directly determined or derived from the disclosure of the present invention without departing from the spirit and scope of the invention. Thus, the scope of the present invention should be understood and construed as covering all such other variations or modifications.

Claims

1. A heat pump cycle system, comprising a compressor, an indoor heat exchanger, a throttling device, and an outdoor heat exchanger connected via a refrigerant main pipeline, characterized in that, Also includes: A liquid receiver is disposed between the outdoor heat exchanger and the return port of the compressor for storing liquid refrigerant flowing out of the outdoor heat exchanger. A refrigerant auxiliary pipeline is connected between the liquid receiver and the compressor return port; A driving device is provided on the refrigerant auxiliary pipeline for controlled driving of the liquid refrigerant in the receiver into the refrigerant auxiliary pipeline; as well as A heating device is used to provide heat to the liquid refrigerant in the refrigerant auxiliary pipeline so that the liquid refrigerant vaporizes and flows to the return port of the compressor. The heating device is an auxiliary heat exchanger, which has two auxiliary heat exchange pipelines that exchange heat with each other. One of the auxiliary heat exchange pipelines is a section of the refrigerant auxiliary pipeline, and the other auxiliary heat exchange pipeline is a section of the auxiliary heat exchange pipeline used for the flow of high-temperature heat exchanger. The heat pump cycle system also includes: The first temperature acquisition device is used to acquire the refrigerant temperature at the refrigerant outlet of the refrigerant auxiliary pipeline; The second temperature acquisition device is used to acquire the evaporation temperature of the heat pump cycle system; and The auxiliary heating pipeline is equipped with a first circulation pump, which is configured to controllably adjust the flow rate of the high-temperature heat exchanger in the auxiliary heating pipeline according to a first difference between the refrigerant temperature obtained by the first temperature acquisition device and the evaporation temperature obtained by the second temperature acquisition device.

2. The heat pump cycle system according to claim 1, characterized in that, The auxiliary heat exchanger is configured to absorb heat from the fluid medium and transfer it to the liquid refrigerant in the refrigerant auxiliary pipeline.

3. The heat pump cycle system according to claim 2, characterized in that, The auxiliary heating pipeline is circulated in connection with the heat exchanger supply source used to provide the high-temperature heat exchanger.

4. The heat pump cycle system according to claim 1, characterized in that, The first circulating pump is further configured to maintain a constant flow rate of the high-temperature heat exchanger in the auxiliary heating pipeline when the first difference is within a first preset temperature difference range, increase the flow rate of the high-temperature heat exchanger in the auxiliary heating pipeline when the first difference is less than the first preset temperature difference range, and decrease the flow rate of the high-temperature heat exchanger in the auxiliary heating pipeline when the first difference is greater than the first preset temperature difference range.

5. The heat pump cycle system according to claim 3, characterized in that, Also includes: The second temperature acquisition device is used to acquire the evaporation temperature of the heat pump cycle system; as well as A third temperature acquisition device is used to acquire the refrigerant temperature at the compressor's return port; and The drive device is configured to controllably adjust the flow rate of liquid refrigerant in the refrigerant auxiliary pipeline based on a second difference between the refrigerant temperature obtained by the third temperature acquisition device and the evaporation temperature obtained by the second temperature acquisition device.

6. The heat pump cycle system according to claim 5, characterized in that, The drive device is further configured to maintain a constant flow rate of liquid refrigerant in the refrigerant auxiliary pipeline when the second difference is within the second preset temperature difference range, increase the flow rate of liquid refrigerant in the refrigerant auxiliary pipeline when the second difference is less than the second preset temperature difference range, and decrease the flow rate of liquid refrigerant in the refrigerant auxiliary pipeline when the second difference is greater than the second preset temperature difference range.

7. The heat pump cycle system according to claim 3, characterized in that, The indoor heat exchanger has two indoor heat exchange pipes that exchange heat with each other. One indoor heat exchange pipe is a section of the main refrigerant pipe, and the other indoor heat exchange pipe is a section of the heating pipe for flowing heating fluid, so that the heat of the refrigerant in the main refrigerant pipe is transferred to the heating fluid in the heating pipe; wherein The heating pipeline is circulated in connection with a heating fluid tank for storing the heating fluid.

8. The heat pump cycle system according to claim 7, characterized in that, The heat exchanger is supplied by the heating fluid tank, so as to use the heating fluid in the heating fluid tank to heat the liquid refrigerant in the refrigerant auxiliary pipeline.

9. The heat pump cycle system according to claim 7, characterized in that, Also includes: A heat dissipation device is installed in the indoor environment and connected between the indoor heat exchanger and the heating fluid tank, so that the heating fluid, after absorbing heat at the indoor heat exchanger, exchanges heat with the air in the indoor environment through the heat dissipation device, thereby transferring heat to the indoor environment.

10. The heat pump cycle system according to claim 1, characterized in that, The refrigerant auxiliary pipeline is also equipped with a solenoid valve, which is used to control the on / off state of the refrigerant auxiliary pipeline and / or the refrigerant flow rate in the refrigerant auxiliary pipeline.

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