Air source cascade heat pump based on sleeve type phase change energy storage evaporative condenser

Abstract

The utility model discloses an air source cascade heat pump based on a sleeve type phase change energy storage evaporative condenser, which comprises a primary heat pump circulation system and a secondary heat pump circulation system which are coupled through a sleeve type phase change energy storage evaporative condenser. The sleeve type phase change energy storage condensation evaporator comprises a first refrigerant channel used for allowing a first refrigerant to flow, a second refrigerant channel used for allowing a second refrigerant to flow and a phase change energy storage material, the first refrigerant channel is sleeved with the second refrigerant channel, and the phase change energy storage material is arranged on the periphery of the second refrigerant channel. By means of the mode, the phase change energy storage material can effectively buffer and adjust mismatching of supply and demand of energy between the first-stage heat pump cycle and the second-stage heat pump cycle; when the air source heat pump is in the defrosting working condition, the phase change energy storage material can provide heat needed by defrosting of the first-stage heat pump without affecting normal operation of circulation of the second-stage heat pump, and the heating stability and the heating energy efficiency ratio are greatly improved.

Description

Technical Field

[0001] The utility model relates to the technical field of phase change energy storage and air source heat pumps, in particular to an air source cascade heat pump based on a shell-and-tube type phase change energy storage evaporative condenser. Background Art

[0002] Air source heat pump heating is the most universal heating energy-saving technology due to its high heating energy efficiency ratio and easy installation. However, due to the limitations of existing compressor and refrigerant manufacturing technology, the heating range of heat pumps is restricted.

[0003] In addition, air source heat pumps are greatly affected by ambient temperature. When the ambient temperature is lower than -12℃, the maximum outlet water temperature of the first-stage air source heat pump is 50℃, which greatly limits the use of air source heat pumps. At the same time, when the surface temperature of the outdoor tube-fin evaporator fins is lower than 0℃, frost forms on the fin surface, causing the heating performance of the air source heat pump to drop sharply, and defrosting technology becomes the key. At present, air source heat pump defrosting uses a four-way valve switch to convert the heating condition to the cooling condition, and the outdoor evaporator becomes a condenser to release heat for defrosting.

[0004] The mature technology to solve the problem of low ambient temperature and high temperature heating of air source heat pump is to adopt heat pump cycle two-stage cascade technology. Heat pump cycle two-stage cascade is divided into two forms: water system two-stage cascade and fluorine system two-stage cascade.

[0005] The two-stage cascade of water system is actually the cascade of the first-stage air source heat pump and the second-stage water source heat pump. The condenser of the first-stage air source heat pump (refrigerant one / water) and the evaporator of the second-stage water source heat pump (water / refrigerant two) are coupled for heat exchange through the water system. This type of system is complex to install and has a relatively low overall energy efficiency. Therefore, the two-stage cascade technology of fluorine system is generally used.

[0006] The two-stage cascade technology of the fluorine system combines the condenser of the air source heat pump and the evaporator of the secondary water source heat pump into one to form a condenser evaporator, forming a refrigerant one / refrigerant two heat exchange. In order to solve the problem of ambient temperature changes, the primary air source heat pump usually adopts frequency conversion technology to adapt to the secondary heat pump cycle through frequency conversion compressor adjustment. When the secondary heat pump user side has large environmental changes or frequent operations, the frequency conversion adjustment of the primary air source heat pump cannot meet the frequency changes when the heat load required by the secondary heat pump, which will bring about the problem of mismatch of the heat source adjustment of the two-stage cascade, causing drastic fluctuations in the temperature of the heated fluid.

[0007] Therefore, the fluorine system two-stage cascade air source heat pump unit has the advantages of compact system and high comprehensive energy efficiency ratio, but its disadvantage is that the control is complex, and in defrosting conditions, the two-stage heat pump has to switch to cooling conditions, which makes the heating unstable and the heating efficiency reduced. Utility Model Content

[0008] The main technical problem solved by the utility model is to provide an air source cascade heat pump based on a shell-and-tube phase change energy storage evaporative condenser, which can smooth the peaks and fill the valleys through phase change energy storage materials, so that the condensing temperature of the first-stage heat pump and the evaporating temperature of the second-stage heat pump are stabilized near the phase change point, and can effectively buffer and adjust the energy supply and demand mismatch between the first-stage heat pump cycle and the second-stage heat pump cycle. At the same time, when the first-stage air source heat pump cycle defrosts and changes to a refrigeration condition, the heat stored in the phase change energy storage material can provide a low-temperature heat source for the defrosting of the first-stage heat pump while ensuring the normal operation of the second-stage heat pump, and the system has a high comprehensive heating energy efficiency ratio.

[0009] In order to solve the above technical problems, a technical solution adopted by the utility model is: to provide an air source cascade heat pump based on a shell-and-tube phase-change energy storage evaporative condenser, comprising: a primary heat pump circulation system, a secondary heat pump circulation system and a shell-and-tube phase-change energy storage condensing evaporator, wherein the primary heat pump circulation system and the secondary heat pump circulation system are coupled through the shell-and-tube phase-change energy storage condensing evaporator.

[0010] The primary heat pump circulation system comprises an air-cooled tube-fin evaporator, a four-way valve, a primary compressor, a sleeve-type phase-change energy storage condenser evaporator and a primary throttle valve which are sequentially connected to form a heat exchange cycle.

[0011] The secondary heat pump circulation system comprises a shell-and-tube phase-change energy storage condenser evaporator, a secondary compressor, a condenser and a secondary throttle valve which are sequentially connected to form a secondary heat exchange cycle.

[0012] The shell-and-tube phase-change energy storage condenser evaporator includes a refrigerant channel 1 for passing refrigerant 1, a refrigerant channel 2 for passing refrigerant 2, and a phase-change energy storage material. The refrigerant channel 2 is sleeved on the periphery of the refrigerant channel 1, and the phase-change energy storage material is arranged on the periphery of the refrigerant channel 2.

[0013] In a preferred embodiment of the present invention, the four-way valve includes a first valve port, a second valve port, a third valve port and a fourth valve port along a clockwise direction.

[0014] The outlet of the air-cooled tube-fin evaporator is connected to the first valve port, the fourth valve port is connected to one end of the first-stage compressor, the second valve port is connected to the other end of the first-stage compressor, the third valve port is connected to the first input port of the sleeve-type phase change energy storage condenser evaporator, the first output port of the sleeve-type phase change energy storage condenser evaporator is connected to the inlet of the first-stage throttle valve, and the outlet of the first-stage throttle valve is connected to the inlet of the air-cooled tube-fin evaporator.

[0015] In a preferred embodiment of the utility model, the second output port of the sleeve-type phase change energy storage condenser evaporator is connected to one end of the secondary compressor, the other end of the secondary compressor is connected to the condenser inlet, the condenser outlet is connected to the secondary throttle valve inlet, and the secondary throttle valve outlet is connected to the second input port of the sleeve-type phase change energy storage condenser evaporator.

[0016] In a preferred embodiment of the present invention, the refrigerant channel 1 is adjacent to the refrigerant channel 2, and the two are isolated by the tube wall of the refrigerant channel 1.

[0017] In a preferred embodiment of the present invention, the first refrigerant channel is a heat exchange coil, and the second refrigerant channel is a twisted outer sleeve.

[0018] In a preferred embodiment of the utility model, the second refrigerant channel is wound around the outer periphery of the first refrigerant channel in a twisted spiral form, and the interlayer formed by the winding constitutes the second refrigerant channel. Each group of the second refrigerant channels is connected in series through a second refrigerant channel connecting pipe at the winding end.

[0019] In a preferred embodiment of the utility model, the refrigerant channel has a refrigerant inlet and a refrigerant outlet. After the refrigerant flows into the refrigerant inlet, it flows inside the heat exchange coil and flows out to the refrigerant outlet.

[0020] In a preferred embodiment of the utility model, the second refrigerant channel has a second refrigerant inlet and a second refrigerant outlet. After the second refrigerant flows in from the second refrigerant inlet, it flows inside the interlayer of the outer sleeve and the connecting tube and flows out toward the second refrigerant outlet.

[0021] In a preferred embodiment of the present invention, the phase change energy storage material is an organic phase change energy storage material, an inorganic phase change energy storage material, or a metal and alloy phase change energy storage material with a specific phase change point.

[0022] The beneficial effects of the utility model are:

[0023] The presence of phase change energy storage materials plays a role in shaving peaks and filling valleys, making the condensing temperature of the first-stage heat pump and the evaporating temperature of the second-stage heat pump stable near the phase change point, with simple control and stable system. When energy mismatch occurs between the condensation of the first-stage heat pump and the evaporation of the second-stage heat pump, the phase change energy storage materials can effectively buffer and adjust. When the defrosting of the first-stage air source heat pump changes to a refrigeration condition, the heat stored in the phase change energy storage material not only provides a low-temperature heat source for the defrosting of the first-stage heat pump, but also does not affect the normal heating of the second-stage heat pump, and the system has a high comprehensive energy efficiency ratio. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] In order to more clearly illustrate the technical solutions in the embodiments of the present utility model, the following briefly introduces the drawings required for use in the description of the embodiments. Obviously, the drawings described below are only some embodiments of the present utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative work, among which:

[0025] Figure 1 It is a structural schematic diagram of a preferred embodiment of an air source cascade heat pump based on a shell-and-tube phase-change energy storage evaporative condenser of the utility model;

[0026] Figure 2 It is a structural schematic diagram of a preferred embodiment of the shell-and-tube phase-change energy storage evaporative condenser of the utility model;

[0027] Figure 3 It is a side view of a preferred embodiment of the shell-and-tube phase-change energy storage evaporative condenser of the utility model;

[0028] The markings of the components in the accompanying drawings are as follows:

[0029] 1. Air-cooled tube-fin evaporator, 2. Four-way valve, 3. One-stage compressor, 4. Casing-tube phase-change energy storage condenser evaporator,

[0030] 41. Refrigerant 1, 42. Refrigerant 2, 43. Refrigerant 1 inlet, 44. Refrigerant 2 inlet, 45. Phase change energy storage material, 46. Refrigerant 2 channel, 47. Refrigerant 1 channel, 48. Refrigerant 2 channel connecting pipe, 49. Refrigerant 1 outlet, 410. Refrigerant 2 outlet,

[0031] 5. First-stage throttle valve, 6. Second-stage compressor, 7. Condenser, 8. Second-stage throttle valve. DETAILED DESCRIPTION

[0032] In order to make the purpose, technical scheme and advantages of the embodiments of the utility model clearer, the technical scheme in the embodiments of the utility model will be clearly and completely described below in conjunction with the drawings in the embodiments of the utility model. Obviously, the described embodiments are part of the embodiments of the utility model, not all of the embodiments. Generally, the components of the embodiments of the utility model described and shown in the drawings here can be arranged and designed in various different configurations.

[0033] Therefore, the following detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the present invention to be protected, but merely represents selected embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0034] The utility model relates to a preferred embodiment of an air source cascade heat pump based on a shell-and-tube type phase-change energy storage evaporative condenser.

[0035] See also Figure 1 An air source cascade heat pump based on a shell and tube phase change energy storage evaporative condenser includes a primary heat pump circulation system, a secondary heat pump circulation system and a shell and tube phase change energy storage condensing evaporator 4, wherein the primary heat pump circulation system and the secondary heat pump circulation system are coupled through the shell and tube phase change energy storage condensing evaporator 4.

[0036] In an exemplary embodiment, the primary heat pump circulation system includes an air-cooled tube-fin evaporator 1, a four-way valve 2, a primary compressor 3, a sleeve-type phase change energy storage condenser evaporator 4 and a primary throttle valve 5 which are sequentially connected to form a heat exchange cycle.

[0037] Furthermore, the four-way valve 2 includes a first valve port, a second valve port, a third valve port and a fourth valve port along a clockwise direction, the outlet of the air-cooled tube-fin evaporator 1 is connected to the first valve port, the fourth valve port is connected to one end of the first-stage compressor 3, the second valve port is connected to the other end of the first-stage compressor 3, the third valve port is connected to the first input port of the sleeve-type phase change energy storage condenser evaporator 4, the first output port of the sleeve-type phase change energy storage condenser evaporator 4 is connected to the inlet of the first-stage throttle valve 5, and the outlet of the first-stage throttle valve 5 is connected to the inlet of the air-cooled tube-fin evaporator.

[0038] In an exemplary embodiment, the two-stage heat pump circulation system includes a shell-and-tube phase-change energy storage condenser evaporator 4, a two-stage compressor 6, a condenser 7 and a two-stage throttle valve 8 which are sequentially connected to form a secondary heat exchange cycle.

[0039] The second output port of the sleeve-type phase-change energy storage condenser evaporator 4 is connected to one end of the secondary compressor 6, the other end of the secondary compressor 6 is connected to the inlet of the condenser 7, the outlet of the condenser 7 is connected to the inlet of the secondary throttle valve 8, and the outlet of the secondary throttle valve 8 is connected to the second input port of the sleeve-type phase-change energy storage condenser evaporator.

[0040] See also Figure 2-3 In an exemplary embodiment, the shell-and-tube phase change energy storage condenser evaporator 4 includes a refrigerant channel 1 47 for passing refrigerant 1 41, a refrigerant channel 2 46 for passing refrigerant 2 42, and a phase change energy storage material 45. The refrigerant channel 2 46 is sleeved on the periphery of the refrigerant channel 1 47, and the phase change energy storage material 45 is arranged on the periphery of the refrigerant channel 2.

[0041] Furthermore, the refrigerant channel 1 47 is adjacent to the refrigerant channel 2 46 , and the two are isolated by the tube wall of the refrigerant channel 1 47 .

[0042] Furthermore, the refrigerant channel 1 47 is a heat exchange coil, and the refrigerant channel 2 46 is a twisted outer sleeve: the refrigerant channel 2 46 is wound around the outer periphery of the refrigerant channel 1 47 in a twisted spiral form, and the interlayer formed by the winding constitutes the refrigerant channel 2 46, and each group of refrigerant channel 2 46 is connected in series through a refrigerant channel 2 connecting pipe 48 at the winding end.

[0043] Furthermore, the refrigerant channel 1 47 has a refrigerant inlet 43 and a refrigerant outlet 49. After the refrigerant 1 41 flows in from the refrigerant inlet 43, it flows inside the heat exchange coil and flows out toward the refrigerant outlet 49; the refrigerant channel 2 46 has a refrigerant inlet 44 and a refrigerant outlet 410. After the refrigerant 2 42 flows in from the refrigerant inlet 44, it flows inside the interlayer of the twisted outer sleeve and the connecting pipe and flows out toward the refrigerant outlet 410.

[0044] Furthermore, the phase change energy storage material 45 is an organic phase change energy storage material, an inorganic phase change energy storage material, or a metal and alloy phase change energy storage material with a specific phase change point, and the phase change temperature range of the phase change energy storage material is 5-50°C.

[0045] Preferably, the organic phase change energy storage material includes paraffin and non-paraffin organic phase change energy storage materials, and the inorganic phase change energy storage material includes hydrated salts, eutectic salts and molten salts.

[0046] The refrigerant 1 41 goes through the refrigerant 1 channel 47, and the refrigerant 2 42 goes through the refrigerant 2 channel 46. The refrigerant 1 41 and the refrigerant 2 42 are separated by the tube wall of the refrigerant 1 channel 47 and directly exchange heat. The phase change energy storage material is filled outside the refrigerant 2 channel 46. The refrigerant 2 42 and the phase change energy storage material 45 are separated by the tube wall of the refrigerant 2 channel 46 and directly exchange heat.

[0047] It can be understood that the refrigerant 1 41 is the condensation side (hot side) of the heat exchanger through the refrigerant 1 channel 47, the refrigerant 2 42 is the evaporation side (cold side) of the heat exchanger through the refrigerant 2 channel 46, and the phase change energy storage material 45 is filled outside the refrigerant 2 channel 46:

[0048] When the heat provided by refrigerant 1 41 is greater than the heat required by refrigerant 2 42, the temperature of refrigerant 2 42 rises. When the temperature rises above the phase change temperature point of the phase change energy storage material 45 outside the refrigerant 2 channel 46, the phase change energy storage material 45 exchanges heat through the wall of the refrigerant 2 channel 46 and quickly absorbs heat, reducing the temperature of the refrigerant 2 42 passing through to near the phase change point.

[0049] On the contrary, when the heat provided by refrigerant 1 41 is less than the heat required by refrigerant 2 42, the temperature of refrigerant 2 42 drops. When it drops to the phase change temperature point, the phase change energy storage material 45 quickly releases heat, raising the temperature of refrigerants 2 42 and 410 to near the phase change point. The phase change energy storage material effectively plays the role of peak shaving and valley filling and constant temperature regulation of heat flux density.

[0050] The working process of the air source cascade heat pump based on the shell-and-tube phase change energy storage evaporative condenser of the utility model is as follows:

[0051] Refrigerant 1 evaporates and absorbs heat in the air-cooled tube-fin evaporator 1 to form low-temperature and low-pressure refrigerant 1 vapor, passes through the four-way valve 2 and is compressed by the compressor 3 to form high-temperature and high-pressure refrigerant 1 vapor, then enters the shell-and-tube phase-change energy storage condensation evaporator 4 (the condenser of the first-stage heat pump) to condense and release heat to form high-temperature and high-pressure refrigerant 1 liquid, then passes through the first-stage throttle valve 5 to throttle to form a low-temperature and low-pressure vapor-liquid two-phase flow of refrigerant 1, and enters the air-cooled tube-fin evaporator 1 again to evaporate, completing a first-stage heat pump cycle;

[0052] At the same time, refrigerant 2 evaporates in the shell-and-tube phase-change energy storage condenser evaporator 4 (evaporator of the secondary heat pump), absorbs the primary heat pump cycle, condenses and releases heat, and forms low-temperature and low-pressure refrigerant 2 vapor, and then enters the secondary compressor 6 for compression to form high-temperature and high-pressure refrigerant 2 vapor, and then enters the condenser 7 to condense and release heat to form high-temperature and high-pressure refrigerant 2 liquid, and is throttled by the secondary throttle valve 8 to form a low-temperature and low-pressure refrigerant 2 vapor-liquid two-phase flow, and then enters the shell-and-tube phase-change energy storage condenser evaporator 4 again to evaporate and complete a secondary heat pump cycle.

[0053] The working process of the air source cascade heat pump based on the shell-and-tube phase change energy storage evaporative condenser of the utility model is as follows:

[0054] The four-way valve 2 is powered on and switched, and the primary heat pump circulation evaporator and condenser are interchanged. At this time, the air-cooled tube-fin evaporator 1 becomes the condenser, and the phase change energy storage condensing evaporator 4 becomes the primary heat pump circulation evaporator:

[0055] Refrigerant 1 evaporates in the shell-and-tube phase-change energy storage condenser evaporator 4 (the evaporator of the primary heat pump) and absorbs the heat of refrigerant 2. When the temperature of refrigerant 2 is lower than the phase change temperature point, the phase change energy storage material quickly raises the temperature of refrigerant 2 to ensure the normal operation of the secondary heat pump evaporation side. The excess heat of the phase change material is also exchanged through refrigerant 2 to raise the temperature of refrigerant 1 during defrosting.

[0056] At this time, the refrigerant after the temperature is raised forms a low-temperature and low-pressure refrigerant vapor, enters the four-way valve 2 and is compressed by the first-stage compressor 3 to form a high-temperature and high-pressure refrigerant vapor, then enters the air-cooled tube-fin evaporator 1 (condenser) to condense and release heat for defrosting, forming a high-temperature and high-pressure refrigerant liquid, then passes through the first-stage throttle valve 5 to throttle to form a low-temperature and low-pressure refrigerant vapor-liquid two-phase flow, and enters the shell-and-tube phase change energy storage condensation evaporator 4 (the evaporator of the first-stage heat pump) again to evaporate and complete a first-stage heat pump defrosting cycle;

[0057] At the same time, refrigerant 2 evaporates in the shell-and-tube phase change energy storage condenser evaporator 4 (evaporator of the secondary heat pump) and absorbs heat stored in the phase change energy storage material to form low-temperature and low-pressure refrigerant 2 vapor, which enters the secondary compressor 6 for compression to form high-temperature and high-pressure refrigerant 2 vapor, and then enters the condenser 7 for condensation and heat release to form high-temperature and high-pressure refrigerant 2 liquid, which is throttled by the secondary throttle valve 8 to form a low-temperature and low-pressure refrigerant 2 vapor-liquid two-phase flow, and then enters the shell-and-tube phase change energy storage condenser evaporator 4 again to evaporate and complete a secondary heat pump cycle.

[0058] In the utility model, the presence of the phase change energy storage material plays a role in peak shaving and valley filling, so that the condensation temperature of the first-stage heat pump and the evaporation temperature of the second-stage heat pump are stabilized near the phase change point, the control is simple, and the system is stable;

[0059] When there is an energy mismatch between the first-stage heat pump condensation and the second-stage heat pump evaporation, the phase change energy storage material can effectively buffer and regulate;

[0060] When the primary air source heat pump defrosts and changes to refrigeration mode, the heat stored in the phase change energy storage material not only provides a low-temperature heat source for the primary heat pump defrost, but also does not affect the normal heating of the secondary heat pump. The system has a high overall energy efficiency ratio.

[0061] The beneficial effects of the air source cascade heat pump based on the shell-and-tube phase change energy storage evaporative condenser of the utility model are:

[0062] The condenser-evaporator formed by combining the primary air source heat pump condenser and the secondary water source heat pump evaporator is made into a shell-and-tube phase change energy storage condenser-evaporator;

[0063] Phase change energy storage materials have the characteristics of absorbing and releasing a lot of heat at their phase change temperature points. The heat stored in them can effectively buffer and adjust the mismatch between the energy supply and demand between the primary and secondary heat pump cycles.

[0064] At the same time, when the air source heat pump is defrosting, the phase change energy storage material can provide the heat required for defrosting the first-stage heat pump without affecting the normal operation of the second-stage heat pump cycle, greatly improving the heating stability and heating energy efficiency of the fluorine system second-stage cascade air source heat pump.

[0065] The above description is only an embodiment of the present invention, and does not limit the patent scope of the present invention. Any equivalent structure or equivalent process transformation made using the contents of the present invention specification, or directly or indirectly applied in other related technical fields, are also included in the patent protection scope of the present invention.

Claims

1. An air source cascade heat pump based on a shell-and-tube phase change energy storage evaporative condenser, characterized in that: include: A primary heat pump circulation system, a secondary heat pump circulation system and a sleeve-type phase-change energy storage condenser evaporator, wherein the primary heat pump circulation system and the secondary heat pump circulation system are coupled via the sleeve-type phase-change energy storage condenser evaporator. The primary heat pump circulation system comprises an air-cooled tube-fin evaporator, a four-way valve, a primary compressor, a sleeve-type phase-change energy storage condenser evaporator and a primary throttle valve which are sequentially connected to form a heat exchange cycle. The secondary heat pump circulation system comprises a shell-and-tube phase-change energy storage condenser evaporator, a secondary compressor, a condenser and a secondary throttle valve which are sequentially connected to form a secondary heat exchange cycle. The shell-and-tube phase-change energy storage condenser evaporator includes a refrigerant channel 1 for passing refrigerant 1, a refrigerant channel 2 for passing refrigerant 2, and a phase-change energy storage material. The refrigerant channel 2 is sleeved on the periphery of the refrigerant channel 1, and the phase-change energy storage material is arranged on the periphery of the refrigerant channel 2.

2. The air source cascade heat pump based on the shell-and-tube phase change energy storage evaporative condenser according to claim 1 is characterized in that: The four-way valve includes a first valve port, a second valve port, a third valve port and a fourth valve port along a clockwise direction. The outlet of the air-cooled tube-fin evaporator is connected to the first valve port, the fourth valve port is connected to one end of the first-stage compressor, the second valve port is connected to the other end of the first-stage compressor, the third valve port is connected to the first input port of the sleeve-type phase change energy storage condenser evaporator, the first output port of the sleeve-type phase change energy storage condenser evaporator is connected to the inlet of the first-stage throttle valve, and the outlet of the first-stage throttle valve is connected to the inlet of the air-cooled tube-fin evaporator.

3. The air source cascade heat pump based on the shell-and-tube phase change energy storage evaporative condenser according to claim 1 is characterized in that: The second output port of the sleeve-type phase-change energy storage condenser evaporator is connected to one end of the secondary compressor, the other end of the secondary compressor is connected to the condenser inlet, the condenser outlet is connected to the secondary throttle valve inlet, and the secondary throttle valve outlet is connected to the second input port of the sleeve-type phase-change energy storage condenser evaporator.

4. The air source cascade heat pump based on the shell-and-tube phase change energy storage evaporative condenser according to claim 1 is characterized in that: The refrigerant channel 1 is adjacent to the refrigerant channel 2, and the two are isolated by the tube wall of the refrigerant channel 1.

5. The air source cascade heat pump based on the shell-and-tube phase change energy storage evaporative condenser according to claim 1, characterized in that: The first refrigerant channel is a heat exchange coil, and the second refrigerant channel is a twisted outer sleeve.

6. The air source cascade heat pump based on the shell-and-tube phase change energy storage evaporative condenser according to claim 5, characterized in that: The second refrigerant channel is wound around the outer periphery of the first refrigerant channel in a twisted spiral form, and the interlayer formed by the winding constitutes the second refrigerant channel. Each group of the second refrigerant channels is connected in series through a second refrigerant channel connecting pipe at the winding end.

7. The air source cascade heat pump based on the shell-and-tube phase change energy storage evaporative condenser according to claim 5, characterized in that: The refrigerant channel has a refrigerant inlet and a refrigerant outlet. After the refrigerant flows in from the refrigerant inlet, it flows inside the heat exchange coil and flows out toward the refrigerant outlet.

8. The air source cascade heat pump based on the shell-and-tube phase change energy storage evaporative condenser according to claim 6, characterized in that: The second refrigerant channel has a second refrigerant inlet and a second refrigerant outlet. After the second refrigerant flows in from the second refrigerant inlet, it flows inside the interlayer of the outer sleeve and the connecting pipe and flows out toward the second refrigerant outlet.

9. The air source cascade heat pump based on the shell-and-tube phase change energy storage evaporative condenser according to claim 1, characterized in that: The phase change energy storage material is an organic phase change energy storage material, an inorganic phase change energy storage material, and a metal and alloy phase change energy storage material with a specific phase change point.

Images