Heat pump hot water system and air source heat pump unit

Abstract

The utility model discloses a kind of heat pump hot water system and air source heat pump unit, comprising: by compressor, the pipe passage of partition wall type liquid storage heat exchanger, the pipe passage of partition wall type heat exchanger, throttling device and heat exchanger are sequentially connected to form closed refrigerant circuit;Sequentially connected water supplementing device, the shell side of the partition wall type heat exchanger, the shell side of the partition wall type liquid storage heat exchanger and liquid storage device, the liquid storage device is used to deliver fluid stored in its inside to user end.Overheated gaseous refrigerant discharged by compressor is used to carry out secondary heat exchange to hot water stored in partition wall type liquid storage heat exchanger, which is once heat exchanged by partition wall type heat exchanger, to effectively improve the highest outlet water temperature of heat pump hot water system, satisfy higher water temperature use demand.

Description

Technical Field

[0001] This utility model relates to the field of heat pump system technology, and in particular to a heat pump hot water system and an air source heat pump unit. Background Technology

[0002] A heat pump system is a highly efficient heating system based on the reverse Carnot cycle. Different heat pump systems are suitable for different operating conditions due to variations in system design, structure, and refrigerant. Unlike other heat pump systems, air-source heat pump water heating systems absorb heat from the air through an evaporator to evaporate the refrigerant, and then condense the refrigerant in a condenser, releasing heat that is transferred to the water, raising its temperature to the desired level.

[0003] Limited by factors such as air heat source temperature, compressor compression ratio, and refrigerant critical temperature, the discharge pressure of the compressor and the condensation temperature of the refrigerant in a heat pump water heating system cannot exceed a certain range. This results in the maximum outlet water temperature of the heat pump water heating system being only close to the refrigerant critical temperature, thus limiting the maximum outlet water temperature of the heat pump water heating system and failing to meet the demand for higher water temperatures. Utility Model Content

[0004] This utility model provides a heat pump water heating system and an air source heat pump unit to solve the problem that the maximum outlet water temperature of the existing heat pump water heating system is limited and cannot meet the use requirements of higher water temperatures.

[0005] The technical solution of this utility model is a heat pump water heating system, comprising:

[0006] A closed refrigerant circuit is formed by connecting the compressor, the tube side of the indirect liquid receiver heat exchanger, the tube side of the indirect heat exchanger, the throttling device, and the heat exchanger in series.

[0007] The water supply device, the shell side of the indirect heat exchanger, the shell side of the indirect liquid storage heat exchanger, and the liquid storage device are connected in series. The liquid storage device is used to transport the fluid stored inside to the user end.

[0008] Furthermore, multiple indirect heat exchangers can be provided, and multiple indirect heat exchangers can be connected in series.

[0009] Furthermore, the diameter of the tube side of the indirect heat exchanger gradually decreases from the tube side of the indirect liquid storage heat exchanger to the throttling device.

[0010] Furthermore, the shell-side outlet of the indirect liquid storage heat exchanger is connected to the inlet and first outlet of the liquid storage device, respectively, and a first valve is provided on the first pipe between the shell-side outlet of the indirect liquid storage heat exchanger and the first outlet of the liquid storage device.

[0011] Furthermore, the second outlet side of the liquid storage device is connected to the shell side of the indirect liquid storage heat exchanger via a second pipe, and a second valve is provided on the second pipe.

[0012] Furthermore, the height of the shell-side inlet side of the indirect-flow heat exchanger connected to the second outlet side of the liquid storage device is lower than the height of the shell-side outlet side of the indirect-flow heat exchanger.

[0013] Furthermore, a first temperature detection component is provided in the shell side of the indirect liquid storage heat exchanger, and a second temperature detection component is provided in the liquid storage device.

[0014] Furthermore, a check valve and a first water pump are provided on the first outlet side of the liquid storage device.

[0015] Furthermore, a third valve and a second water pump are installed on the third pipe between the outlet side of the water replenishment device and the shell-side inlet side of the partition wall heat exchanger.

[0016] This utility model also proposes an air source heat pump unit, which includes the heat pump hot water system described above.

[0017] Compared with the prior art, the present invention has at least the following beneficial effects:

[0018] This invention utilizes superheated gaseous refrigerant discharged from the compressor to perform secondary heat exchange on the hot water stored in the indirect heat exchanger that has undergone primary heat exchange in the indirect heat exchanger. This achieves a gradual increase in water temperature, bringing the temperature of the hot water in the shell side of the indirect heat exchanger close to the compressor's exhaust temperature. Consequently, it effectively increases the maximum outlet water temperature of the heat pump water heating system, meeting the demand for higher water temperatures. Attached Figure Description

[0019] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains; the terminology used herein in the specification is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention; the terms "comprising" and "having," and any variations thereof, in the specification, claims, and accompanying drawings of this invention are intended to cover non-exclusive inclusion. The terms "first," "second," etc., in the specification, claims, or accompanying drawings of this invention are used to distinguish different objects and not to describe a particular order.

[0020] To more clearly illustrate the technical solutions in the embodiments of this utility model, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0021] Figure 1 This is a schematic diagram of the first heat pump water heating system proposed in this utility model;

[0022] Figure 2 This is a schematic diagram of the fluid flow in the first heat pump water heating system proposed in this utility model.

[0023] Figure 3 This is a schematic diagram of the second type of heat pump water heating system proposed in this utility model;

[0024] Figure 4 This is a schematic diagram of the fluid flow in the second type of heat pump water heating system proposed in this utility model.

[0025] Figure 5 This is a schematic diagram of the third type of heat pump water heating system proposed in this utility model.

[0026] Figure label:

[0027] 10. Compressor;

[0028] 101. Exhaust pressure sensor; 102. Exhaust temperature sensor;

[0029] 20. Indirect-contact liquid storage heat exchanger;

[0030] 201. First valve; 202. Second valve; 203. First temperature detection component;

[0031] 30. Indirect heat exchanger;

[0032] 40. Throttling device;

[0033] 50. Heat exchanger;

[0034] 60. Water supply device;

[0035] 601. Third valve; 602. Second water pump;

[0036] 70. Liquid storage device;

[0037] 701. Second temperature detection component; 702. Check valve; 703. First water pump. Detailed Implementation

[0038] To make the technical problem to be solved, the technical solution, and the beneficial effects of this utility model clearer, the present utility model will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present utility model and are not intended to limit the present utility model. Therefore, a feature pointed out in this specification is used to describe one feature of one embodiment of the present utility model, and does not imply that every embodiment of the present utility model must have the described feature. Furthermore, it should be noted that this specification describes many features. Although certain features may be combined to illustrate possible system designs, these features may also be used in other combinations not explicitly stated. Therefore, unless otherwise stated, the described combinations are not intended to be limiting.

[0039] The principle and structure of this utility model will be described in detail below with reference to the accompanying drawings and embodiments.

[0040] A heat pump system is a highly efficient heating system based on the reverse Carnot cycle. Different heat pump systems are suitable for different operating conditions due to variations in system design, structure, and refrigerant. Unlike other heat pump systems, air-source heat pump water heating systems absorb heat from the air through an evaporator to evaporate the refrigerant, and then condense the refrigerant in a condenser, releasing heat that is transferred to the water, raising its temperature to the desired level.

[0041] Limited by factors such as air heat source temperature, compressor compression ratio, and refrigerant critical temperature, the discharge pressure of the compressor and the condensation temperature of the refrigerant in a heat pump water heating system cannot exceed a certain range. This results in the maximum outlet water temperature of the heat pump water heating system being only close to the refrigerant critical temperature, thus limiting the maximum outlet water temperature of the heat pump water heating system and failing to meet the demand for higher water temperatures.

[0042] Therefore, in some embodiments, such as Figures 1-2 As shown, this utility model proposes a heat pump water heating system that can increase the maximum outlet water temperature, comprising:

[0043] A closed refrigerant circuit is formed by connecting the compressor 10, the tube side of the indirect liquid receiver heat exchanger 20, the tube side of the indirect heat exchanger 30, the throttling device 40, and the heat exchanger 50 in series.

[0044] The water supply device 60, the shell side of the indirect heat exchanger 30, the shell side of the indirect liquid storage heat exchanger 20, and the liquid storage device 70 are connected in series. The liquid storage device 70 is used to transport the fluid stored inside to the user end.

[0045] It should be noted that the indirect heat exchanger 30 proposed in this embodiment is exemplified by a shell-and-tube condenser or a coaxial condenser, and the heat exchanger 50 is exemplified by an evaporator; furthermore, the tube side and shell side of the indirect liquid storage heat exchanger 20 and the indirect heat exchanger 30 are interchangeable. The fluid proposed in this embodiment is exemplified by water. The water supply device 60, the shell side of the indirect heat exchanger 30, the shell side of the indirect liquid storage heat exchanger 20, and the liquid storage device 70 are all connected by pipelines. The throttling device 40 proposed in this embodiment is preferably a capillary tube or a thermostatic expansion valve.

[0046] Thus, when the heat pump water heating system starts, the compressor 10 discharges superheated gaseous refrigerant. This superheated gaseous refrigerant passes sequentially through the tube side of the indirect heat exchanger 20, the tube side of the indirect heat exchanger 30, the throttling device 40, and the heat exchanger 50 before flowing back to the compressor 10. At this time, the water supply device 60 supplies room temperature water or water to the shell side of the indirect heat exchanger 30. This causes a phase change (latent heat portion) in the refrigerant within the tube side of the indirect heat exchanger 30, thereby transferring the heat of the refrigerant to the water within the shell side of the indirect heat exchanger 30, achieving a single heat exchange. However, the latent heat released during this single heat exchange is insufficient to heat the water above the critical temperature of the refrigerant; that is, the hot water formed by the single heat exchange can at most approach the critical temperature of the refrigerant. After the hot water undergoes a first heat exchange, it flows into the shell side of the indirect heat exchanger 20 for storage. Then, the superheated gaseous refrigerant discharged from the compressor 10 enters the tube side of the indirect heat exchanger 20 and undergoes a second heat exchange with the hot water in the shell side (because the temperature of the superheated gaseous refrigerant discharged from the compressor 10 is higher than the critical temperature of the refrigerant, the sensible heat carried by the superheated gaseous refrigerant can be used to further heat the water). That is, the sensible heat of the superheated gaseous refrigerant discharged from the compressor 10 is transferred to the hot water after the first heat exchange, so that the water temperature is gradually increased. This makes the temperature of the hot water in the shell side of the indirect heat exchanger 20 close to the discharge temperature of the compressor 10 (supercritical temperature or the maximum temperature limit of the heat pump water heating system), thereby increasing the maximum outlet water temperature of the heat pump water heating system and meeting the demand for higher water temperatures.

[0047] Therefore, this utility model uses the superheated gaseous refrigerant discharged from the compressor 10 to perform secondary heat exchange on the hot water stored in the partitioned liquid storage heat exchanger 20 that has undergone primary heat exchange in the partitioned heat exchanger 30, thereby effectively increasing the maximum outlet water temperature of the heat pump hot water system and meeting the demand for higher water temperatures.

[0048] The heat exchange process of the refrigerant includes two parts: latent heat (phase change heat) and sensible heat (temperature change heat). When the hot water in the indirect liquid heat exchanger 20 approaches the critical temperature of the refrigerant, the refrigerant in the tube side of the indirect liquid heat exchanger 20 cannot condense into a liquid state (i.e., cannot trigger a phase change), and can only exchange heat through sensible heat.

[0049] In some embodiments, to ensure that the refrigerant can release heat step by step, and to allow the water passing through the partition heat exchanger 30 to fully exchange heat, thereby improving heat exchange efficiency, such as... Figures 3-4 As shown, multiple indirect heat exchangers 30 can be provided, and multiple indirect heat exchangers 30 can be connected in series.

[0050] It should be noted that the indirect heat exchanger 30 closest to the indirect liquid storage heat exchanger 20 is the first indirect heat exchanger, while the indirect heat exchanger 30 closest to the throttling device 40 is the last indirect heat exchanger. The water supply device 60 is connected to the shell-side inlet side of the last indirect heat exchanger via a pipe. Then, the shell-side outlet side of the last indirect heat exchanger is connected in series with the shell sides of multiple indirect heat exchangers 30 and then connected to the shell-side inlet side of the first indirect heat exchanger. Finally, the shell-side outlet side of the first indirect heat exchanger is connected to the shell-side inlet side of the indirect liquid storage heat exchanger 20. Similarly, the tube-side inlet of the first indirect heat exchanger is connected to the tube-side outlet of the indirect liquid storage heat exchanger 20. The tube-side outlet of the first indirect heat exchanger is connected in series with the tubes of multiple indirect heat exchangers 30 and then connected to the tube-side inlet of the last indirect heat exchanger. The tube-side outlet of the last indirect heat exchanger is then connected to the inlet of the throttling device 40.

[0051] The diameter of the tube side of the indirect heat exchanger 30 gradually decreases from the tube side of the indirect liquid storage heat exchanger 20 to the throttling device 40.

[0052] This configuration reduces the impact of refrigerant density changes on the heat exchange performance of the indirect heat exchanger 30. It ensures that the refrigerant after phase change maintains sufficient contact with the heat exchange wall of the indirect heat exchanger 30, further improving its heat exchange efficiency.

[0053] Of course, the shell-side tube diameter of the wall-mounted heat exchanger 30 can be the same at this time, and there is no limitation here.

[0054] In some embodiments, such as Figure 1 As shown, the shell-side outlet of the indirect liquid heat exchanger 20 is connected to the inlet and first outlet of the liquid storage device 70, respectively, and a first valve 201 is provided on the first pipe between the shell-side outlet of the indirect liquid heat exchanger 20 and the first outlet of the liquid storage device 70.

[0055] It should be noted that the heat pump water heating system also includes a main control unit (not shown, the same throughout the text), which is electrically connected to the first valve 201.

[0056] When the water temperature in the indirect liquid heat exchanger 20 is higher than the water temperature in the liquid storage device 70, and the water temperature in the liquid storage device 70 is lower than the user's required temperature, the main control unit will open the first valve 201 to mix the water on the shell side of the indirect liquid heat exchanger 20 with the water on the first outlet side of the liquid storage device 70 before it is transmitted to the user, thereby increasing the outlet water temperature of the heat pump hot water system and achieving a reasonable hot water supply.

[0057] In some embodiments, such as Figure 1 As shown, the second outlet side of the liquid storage device 70 is connected to the shell side of the indirect liquid storage heat exchanger 20 through a second pipe. A second valve 202 is provided on the second pipe, and the second valve 202 is electrically connected to the main control unit.

[0058] When the water temperature in the indirect liquid storage heat exchanger 20 is higher than the water temperature in the liquid storage device 70, and the water temperature in the liquid storage device 70 is higher than the user's required temperature, the main control unit will close the first valve 201 and open the second valve 202, allowing water to be supplied from the second outlet side of the liquid storage device 70 to the shell side of the indirect liquid storage heat exchanger 20. This reduces the water temperature in the shell side of the indirect liquid storage heat exchanger 20, increases the heat exchange temperature difference (the lower the water temperature in the shell side of the indirect liquid storage heat exchanger 20, the better the heat exchange effect and the higher the energy efficiency), lowers the outlet water temperature of the heat pump hot water system, and prevents the high-temperature hot water in the shell side of the indirect liquid storage heat exchanger 20 from being directly supplied to the user, thus achieving a reasonable hot water supply.

[0059] The height of the shell-side inlet side of the indirect liquid storage heat exchanger 20 connected to the second outlet side of the liquid storage device 70 is lower than the height of the shell-side outlet side of the indirect liquid storage heat exchanger 20.

[0060] This design utilizes gravitational potential energy to create a continuous water pressure difference, enabling water circulation between the liquid storage device 70 and the shell side of the partitioned liquid storage heat exchanger 20 without additional power.

[0061] In some embodiments, to accurately detect the water temperature in the shell side of the indirect liquid heat exchanger 20 and within the liquid storage device 70, so that the main control unit can open and close the first valve 201 and / or the second valve 202 as needed, such as... Figure 1 As shown, a first temperature detection component 203 is provided in the shell side of the indirect liquid storage heat exchanger 20, and a second temperature detection component 701 is provided in the liquid storage device 70.

[0062] It should be noted that both the first temperature detection component 203 and the second temperature detection component 701 are electrically connected to the main control unit, and both the first temperature detection component 203 and the second temperature detection component 701 are preferably temperature sensors or temperature sensing bulbs; and the first temperature detection component 203 proposed in this embodiment is exemplified by being installed at the bottom of the shell side of the partition-type liquid storage heat exchanger 20, and the second temperature detection component 701 proposed in this embodiment is exemplified by being installed at the bottom of the liquid storage device 70.

[0063] To achieve a reasonable hot water supply, the opening and closing states of the first valve 201 and the second valve 202 are as follows:

[0064] Firstly, when the water temperature in the indirect liquid heat exchanger 20 is higher than the water temperature in the liquid storage device 70, and the water temperature in the liquid storage device 70 is lower than the user's required temperature, the main control unit will open the first valve 201 and close the second valve 202, so that the water on the shell side of the indirect liquid heat exchanger 20 is mixed with the water on the first outlet side of the liquid storage device 70 before being delivered to the user, thereby increasing the outlet water temperature of the heat pump hot water system.

[0065] Secondly, when the water temperature in the indirect liquid storage heat exchanger 20 is higher than the water temperature in the liquid storage device 70, and the water temperature in the liquid storage device 70 is higher than the user's required temperature, the main control unit will close the first valve 201 and open the second valve 202, so that water is delivered from the second outlet side of the liquid storage device 70 to the shell side of the indirect liquid storage heat exchanger 20, thereby reducing the water temperature in the shell side of the indirect liquid storage heat exchanger 20, increasing the heat exchange temperature difference, reducing the outlet water temperature of the heat pump hot water system, and preventing the high-temperature hot water in the shell side of the indirect liquid storage heat exchanger 20 from flowing directly to the user.

[0066] Third, when the water temperature in the indirect liquid heat exchanger 20 is lower than the water temperature in the liquid storage device 70, and the water temperature in the liquid storage device 70 is lower than the user's required temperature, the main control unit will close the first valve 201 and the second valve 202. At this time, only the liquid storage device 70 directly supplies water to the user.

[0067] Fourth, when the water temperature in the indirect liquid heat exchanger 20 is lower than the water temperature in the liquid storage device 70, and the water temperature in the liquid storage device 70 is higher than the user's required temperature, the main control unit will open the first valve 201 and the second valve 202. At this time, the shell side of the indirect liquid heat exchanger 20 and the liquid storage device 70 jointly supply water to the user.

[0068] The third and fourth scenarios typically occur when the heat pump water heating system is just started up or during defrosting, in order to prevent hot water loss from the storage device 70 and cold water from flowing to the user end.

[0069] In some embodiments, such as Figure 1 As shown, the first outlet side of the liquid storage device 70 is equipped with a check valve 702 and a first water pump 703.

[0070] It should be noted that both the check valve 702 and the first water pump 703 are electrically connected to the main control unit, and the check valve 702 and the first water pump 703 are sequentially installed on the pipeline located on the first water outlet side of the liquid storage device 70 along the water flow direction towards the user end.

[0071] In this way, the first water pump 703 can provide continuous power, overcome pipeline resistance and maintain stable water pressure, ensuring the water supply needs of users at long distances or high floors, and ensuring that the water in the storage device 70 can flow stably to the user end; while the check valve 702, through its unidirectional flow characteristics, prevents water backflow when the water pressure at the user end decreases, preventing the impeller of the first water pump 703 from reversing and being damaged; and the rapid closing of the check valve 702 can suppress water hammer impact caused by the sudden stop of the first water pump 703 or improper operation of the check valve 702, protecting the integrity of the pipeline system; and the combination of the pressurization of the first water pump 703 and the backflow prevention of the check valve 702 can reduce energy waste (such as preventing the water in the storage device 70 from being repeatedly pressurized due to backflow), and improve the system's energy efficiency ratio.

[0072] In some embodiments, such as Figure 1 As shown, a third valve 601 and a second water pump 602 are installed on the third pipe between the outlet side of the water replenishment device 60 and the shell-side inlet side of the partition heat exchanger 30.

[0073] It should be noted that the third valve 601 and the second water pump 602 are both electrically connected to the main control unit, and the pipe between the water supply device 60 and the shell-side water inlet side of the partition heat exchanger 30 is sequentially equipped with the second water pump 602 and the third valve 601 along the water flow direction.

[0074] Thus, the third valve 601 is used to precisely regulate the water flow rate entering the shell side of the indirect heat exchanger 30, avoiding the impact on the heat exchange efficiency of the indirect heat exchanger 30 due to excessive or insufficient flow rate; the second water pump 602 continuously provides power to maintain the circulating pressure of water in the shell side of the indirect heat exchanger 30, ensuring that the water can fully absorb the heat released by the refrigerant, thereby ensuring the efficient and stable operation of the indirect heat exchanger 30, and realizing the effective transfer and utilization of heat.

[0075] In other embodiments, such as Figure 5As shown, an exhaust pressure sensor 101 and an exhaust temperature sensor 102, electrically connected to the main control unit, are installed on the pipe between the exhaust side of the compressor 10 and the tube inlet of the indirect liquid heat exchanger 20. The exhaust pressure sensor 101 is used to detect the exhaust pressure on the exhaust side of the compressor 10 to prevent high-pressure failures caused by blockage of the indirect liquid heat exchanger 20 or the indirect heat exchanger 30 or excessive refrigerant in the heat pump water heating system, and to immediately cut off the power supply to the compressor 10 when the pressure is abnormal. The exhaust temperature sensor 102 is used to monitor the exhaust temperature on the exhaust side of the compressor 10 in real time to prevent the compressor 10 from carbonizing the lubricating oil or mechanical damage due to high temperature (such as refrigerant leakage or poor heat dissipation). When the exhaust temperature exceeds the threshold, the exhaust temperature sensor 102 will trigger a shutdown or reduce the speed of the compressor 10.

[0076] In some embodiments, the present invention also provides an air source heat pump unit, which includes the heat pump hot water system described above.

[0077] Thus, when the air source heat pump unit starts, the compressor 10 discharges superheated gaseous refrigerant. This superheated gaseous refrigerant passes sequentially through the tube side of the indirect heat exchanger 20, the tube side of the indirect heat exchanger 30, the throttling device 40, and the heat exchanger 50 before flowing back to the compressor 10. At this time, the water supply device 60 supplies room temperature water or water to the shell side of the indirect heat exchanger 30. This causes a phase change in the refrigerant within the tube side of the indirect heat exchanger 30, thereby transferring the heat of the refrigerant to the water within the shell side of the indirect heat exchanger 30, achieving a single heat exchange. However, the latent heat released during this single heat exchange is insufficient to heat the water above the critical temperature of the refrigerant; that is, the hot water formed during the single heat exchange can at most approach the critical temperature of the refrigerant.

[0078] After the hot water undergoes a primary heat exchange, it flows into the shell side of the indirect heat exchanger 20 for storage. Then, the superheated gaseous refrigerant discharged from the compressor 10 enters the tube side of the indirect heat exchanger 20 and undergoes a secondary heat exchange with the hot water in the shell side (because the temperature of the superheated gaseous refrigerant discharged from the compressor 10 is higher than the critical temperature of the refrigerant, the sensible heat carried by the superheated gaseous refrigerant can be used to further heat the water). That is, the sensible heat of the superheated gaseous refrigerant discharged from the compressor 10 is transferred to the hot water after the primary heat exchange, so that the water temperature is gradually increased. This makes the temperature of the hot water in the shell side of the indirect heat exchanger 20 close to the discharge temperature of the compressor 10, thereby increasing the maximum outlet water temperature of the heat pump water heating system and meeting the demand for higher water temperatures.

[0079] Obviously, the embodiments described above are only some embodiments of this utility model, not all embodiments. The accompanying drawings show preferred embodiments of this utility model, but do not limit the patent scope of this utility model. This utility model can be implemented in many different forms; rather, the purpose of providing these embodiments is to provide a more thorough and comprehensive understanding of the disclosure of this utility model. Although this utility model has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions described in the foregoing specific embodiments, or make equivalent substitutions for some of the technical features. Any equivalent structures made using the content of this utility model specification and drawings, directly or indirectly applied to other related technical fields, are similarly within the patent protection scope of this utility model.

Claims

1. A heat pump water heating system, characterized in that, include: A closed refrigerant circuit is formed by connecting the compressor (10), the tube side of the indirect liquid heat exchanger (20), the tube side of the indirect heat exchanger (30), the throttling device (40), and the heat exchanger (50) in series. The water supply device (60), the shell side of the partition heat exchanger (30), the shell side of the partition liquid storage heat exchanger (20), and the liquid storage device (70) are connected in series. The liquid storage device (70) is used to transport the fluid stored inside to the user end.

2. The heat pump water heating system according to claim 1, characterized in that, Multiple indirect heat exchangers (30) can be installed, and multiple indirect heat exchangers (30) can be connected in series.

3. The heat pump water heating system according to claim 1 or 2, characterized in that, The diameter of the tube side of the indirect heat exchanger (30) gradually decreases from the tube side of the indirect liquid storage heat exchanger (20) to the throttling device (40).

4. The heat pump water heating system according to claim 1 or 2, characterized in that, The shell-side outlet of the indirect liquid heat exchanger (20) is connected to the inlet and first outlet of the liquid storage device (70) respectively, and a first valve (201) is provided on the first pipe between the shell-side outlet of the indirect liquid heat exchanger (20) and the first outlet of the liquid storage device (70).

5. The heat pump water heating system according to claim 1 or 2, characterized in that, The second outlet side of the liquid storage device (70) is connected to the shell side of the indirect liquid storage heat exchanger (20) through a second pipe, and a second valve (202) is provided on the second pipe.

6. The heat pump water heating system according to claim 5, characterized in that, The height of the shell-side inlet side of the indirect liquid storage heat exchanger (20) connected to the second outlet side of the liquid storage device (70) is lower than the height of the shell-side outlet side of the indirect liquid storage heat exchanger (20).

7. The heat pump water heating system according to claim 1 or 2, characterized in that, The shell side of the indirect liquid heat exchanger (20) is provided with a first temperature detection component (203), and the liquid storage device (70) is provided with a second temperature detection component (701).

8. The heat pump water heating system according to claim 1 or 2, characterized in that, The first outlet side of the liquid storage device (70) is equipped with a check valve (702) and a first water pump (703).

9. The heat pump water heating system according to claim 1 or 2, characterized in that, A third valve (601) and a second water pump (602) are provided on the third pipe between the outlet side of the water replenishment device (60) and the shell-side inlet side of the partition wall heat exchanger (30).

10. An air source heat pump unit, characterized in that, The air source heat pump unit includes the heat pump hot water system according to any one of claims 1 to 9.

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