A closed heat source tower heat pump unit integrated equipment

Abstract

The present invention relates to an integrated equipment of a closed heat source tower heat pump unit, which comprises a heat source tower base and a heat pump unit arranged in the center of the heat source tower base, wherein a tower frame is arranged on the heat source tower base, and the heat pump unit comprises a heat pump main engine, and at least one unit of countercurrent serpentine tube heat exchanger is arranged on each side of the heat source tower base. A top cover, an axial flow fan mechanism and an inspection door are arranged on the tower frame, an antifreeze liquid volume tank is arranged below the heat source tower base, and also comprises related units for defrosting. A sound-absorbing or sound-insulating sound insulation layer is arranged on the periphery of the heat pump main engine, so that system integration can be realized, space can be saved, and an additional machine room does not need to be built. Defrosting does not require stopping the operation of the heat pump, the defrosting is fast and the defrosting effect is good, there is no problem of secondary frosting, and there is no need to consume 10% more electricity for defrosting, which can meet the needs of outdoor installation.

Description

Technical Field

[0001] The invention relates to the technical field of refrigeration and heating related equipment, and in particular to an integrated equipment of a closed heat source tower heat pump unit. Background Art

[0002] At present, the task of carbon neutrality and carbon peak is very arduous, especially the high energy consumption of buildings, which has exceeded 46.7% of the total social energy consumption, especially heating, which indirectly accounts for more than 20% of the total social energy consumption. Therefore, it is the most critical link in carbon reduction, and reducing building energy consumption will play a leading role in carbon peak. Today's heating is mainly based on energy conversion. Finding new energy to replace traditional mineral fossil energy will be a new trend in future economic development. It is particularly important to vigorously study new energy central air-conditioning, especially water vapor heat pumps that obtain low-temperature heat by energy transfer. It will save the country 1 trillion yuan in power construction investment costs and reduce the consumption of 335 million tons of standard coal each year.

[0003] Energy is the guarantee of social progress and the foundation of sustainable development. However, the over-exploitation and cumulative consumption of energy have caused increasingly serious environmental pollution problems, which restrict economic development and affect human living conditions. According to relevant literature, in the energy consumption of developed countries, building energy consumption accounts for nearly half of the total energy consumption and has been on an upward trend. Among them, the energy consumption for building air conditioning and heating accounts for the main part. The development of high-efficiency and energy-saving air conditioning cold and heat sources and air conditioning systems is of great significance to reducing energy consumption and adhering to the policy and strategy of sustainable development. Therefore, it is necessary to develop new energy-saving air conditioning systems. The existing various air source heat pumps use refrigerants as a way to dissipate heat for users or directly absorb heat from the air, which is difficult to achieve large-scale heating and long-distance transmission of heat or cold. Because the transmission distance of heat or cold is greatly limited by relying on the compressor to transmit heat or cold through the refrigerant, its power consumption is also quite amazing. This is because the compressor is only suitable for compressed short-distance transmission of gaseous fluids. If liquid fluids are transmitted, liquid hammer will cause liquid shock, which will destroy the compressor. The density of gaseous fluid is more than 100 times lower than that of liquid fluid. When the same mass of fluid is used to transfer heat or cold, the diameter of the gaseous fluid pipeline will be very large, and the pressure difference resistance will also be very large, which will consume a lot of electrical energy. However, it is different for circulating pumps to transport liquid fluids. It can transfer the mass of fluids over long distances on a large scale, so its heat or cold transmission is much more energy-efficient than that of compressors to transport gaseous media. The heat transfer coefficient of liquid media is also much greater than that of gaseous media. The energy savings of circulating pumps in long-distance heat or cold transmission far exceeds that of compressors. On the other hand, traditional air-to-air heat pumps basically treat frosting as a negative asset. Usually, the energy consumption of defrosting accounts for about 10% of the total energy consumption of the entire heat pump unit. When operating in a low-temperature environment with high relative humidity, it is likely to fall into the defrosting trap. Most of the time is spent on defrosting, and the heating time is relatively shortened, which seriously affects the user experience.

[0004] Frosting is both harmful and beneficial. We need to make rational use of defrosting and turn harm into benefit, so as to greatly improve the heat absorption capacity of the evaporator. Since the latent heat of condensation is the heat released during condensation, its value is equal to the latent heat of sublimation at the same temperature, that is, 283.5×104 joules / kilogram, or 677.28kcal / kg. If frosting occurs in the heat pump evaporator, it means that the fluid on the other side of the evaporator absorbs the latent heat of condensation of water vapor in the air. If defrosting is required, some heat needs to be consumed. It is reasonable to set the defrosting heat temperature at about 5°C, because if the temperature is too high, the heat loss will be large, and it will be taken away by the frost water, resulting in heat waste; if the defrosting heat is only about 1°C, the defrosting speed will be very slow. If the ambient temperature is very low, the outflowing frost water will frost again in the channel, making it difficult to drain the condensed water. Obviously, part of the 677.28kcal / kg condensation latent heat will be taken away by the frost water. The heat taken away is the water condensation latent heat and the sensible heat of 5℃ water. Because the water condensation latent heat is 79.6kcal / kg, plus the sensible heat of 5kcal / kg (because the temperature of the frost water flowing out is 5℃), a total of 84.6kcal / kg of heat cannot be absorbed and utilized by the refrigerant. This part of the water vapor condensation latent heat that cannot be absorbed and utilized accounts for only 12.49%. If a scientific and reasonable defrosting technology is adopted, the utilization rate of the water vapor condensation latent heat in the air can reach 87.51%, which is still very considerable.

[0005] Scientific and reasonable defrosting must first heat the inside of the frost layer to prevent the air from taking away most of the heat when heating the air outside the frost layer, thus avoiding waste of defrosting energy; secondly, the heat used for defrosting must be heat transferred from low-temperature air, rather than electric heat generated by energy conversion; furthermore, heat cannot be taken from the user's terminal room for defrosting; and the heating work cannot be stopped during the defrosting process; finally, the defrosting heat must be returned to heating, so that defrosting can be scientific and reasonable.

[0006] In order to turn harm into benefit, the biggest problem is that frosting cannot affect the normal operation of the heat pump unit, and the energy efficiency ratio of the heat pump cannot be turned into a downward trend during operation. After the relevant research team studied the frosting problem on the surface of the parallel flow evaporator of the automobile air conditioner, it was found that when the frosting area reaches 30% of the entire evaporator surface area, there will be an inflection point where the heat pump operation energy efficiency ratio decreases. Before the frosting area reaches 30% of the total area, its frosting rate is positively correlated with its operation energy efficiency ratio. That is to say, the frosting rate increases before 200 seconds at the beginning of frosting, and its energy efficiency ratio also increases rapidly. The frosting rate is relatively stable from 200 seconds to 300 seconds, and the energy efficiency ratio will decrease after 300 seconds. It is obviously incorrect to explain the phenomenon of the decrease in frosting rate by the low thermal conductivity of the frost layer. It is also impossible to explain the fundamental reason for the increase in the energy efficiency ratio of the heat pump unit at the beginning of frosting and the decrease in the energy efficiency ratio at the end of frosting by using the water vapor condensation mechanism. This phenomenon must be explained based on the amount of heat source affected by the air volume to be scientific and objectively true: when the frost layer area increases, it will inevitably affect the reduction of air volume, so the reduction of air volume will lead to a reduction in the heat of the heat source, which will lead to a decrease in the energy efficiency ratio. At the same time, the dynamic balance theory is considered to explain that when the speed of the heat source air volume reduction is far less than the increase rate of the latent heat released by water vapor condensation, the energy efficiency ratio of the heat pump unit will increase. When it reaches 200 seconds to 300 seconds, the speed of heat source reduction and the growth rate of water vapor condensation latent heat tend to be relatively balanced, so the energy efficiency ratio of the heat pump unit is in a relatively stable state. In addition, some researchers have used fin heat exchangers with adjustable fin width to conduct relevant research on the change of frosting rate, and found that when the fin width increases, the evaporator frosting rate rise period will be extended, and the fin width adjustment can be fully utilized to obtain more air energy. These two research results fully prove that the latent heat of water vapor condensation can indeed greatly improve the energy efficiency ratio of the heat pump unit and achieve a more accurate defrosting time control node. It is a very worthwhile research topic to use evaporator frosting to obtain more water vapor latent heat advantages in the air. However, what is the proportion of water vapor condensation latent heat in the air? We can give an example: when the relative humidity is 60%, how much latent heat is released by water vapor when the ambient temperature drops from -10℃ to -20℃ per cubic meter of air? From the absolute and relative humidity table, we can find that the absolute humidity at ambient temperature -10℃ and relative humidity 60% is 1.4g / m 3, and the absolute moisture content of saturated water vapor at -20℃ is 0.9g / m3. We also know that the dew point temperature of the air is -15℃ when the relative humidity is 60% and the ambient temperature is -10℃. Therefore, the air must be cooled below its corresponding dew point temperature to obtain the latent heat of water vapor condensation. Obviously, (1.4-0.9)×0.001×593=0.2965 kcal, which is more than 98 times higher than the sensible heat of 0.003 kcal when the air is cooled by 10℃. If the relative humidity of the environment is close to saturation, the latent heat of water vapor will be more than one thousand times the sensible heat of air of the same volume scale. Despite this, frosting must be controlled within 30% of the evaporator surface area to improve the energy efficiency ratio of the heat pump unit, otherwise frosting will become a negative asset for the operation of the heat pump unit, causing unstable operation of the heat pump and a sharp drop in energy efficiency. At present, many people in the industry believe that evaporator frosting is very harmful to the operation of heat pump units. Some technologies and methods are even used to avoid the occurrence of frosting on the evaporator fins, or to reduce the probability of frosting, so as to reduce the problem of more than 10% more electricity consumption during the defrosting process. For example: using a small temperature difference and a large flow rate to obtain air energy, but a small temperature difference and a large flow rate is not actually energy-saving. Instead, it will consume more power of the circulating pump and the axial fan motor. In order to obtain sufficient heat demand, the volume of the heat exchanger must be increased many times. There is also a technical solution for obtaining air energy using an open heat source tower heat pump. Although this technology does not have the risk of frosting, there is a problem of frozen pipes and antifreeze loss caused by the upward shift of the freezing point of the antifreeze, which pollutes the water and soil. Therefore, most of them still use a 5°C temperature difference with a relatively low probability of frosting to exchange heat with the air, and generally use a reverse operation method to defrost. The defrosting heat comes from the user's terminal room, which not only seriously affects the user experience, but also requires the heating work to be stopped. These technical methods for dealing with frosting problems have obviously become a negative asset for the operation of heat pumps. Using heat storage for defrosting not only requires additional heat storage equipment, but also causes heat loss during the heat storage and defrosting processes, and the heating needs to be stopped during the defrosting process. If an auxiliary heat pump is used for defrosting, there will be secondary frosting problems that are difficult to handle. Using electric heating for defrosting is even more energy-wasting. These defrosting methods will increase the energy consumption of the heat pump operation.

[0007] In addition, the heat exchanger for exchanging heat with air in the existing heat source tower is V-shaped, resulting in unconcentrated heat exchange and unreasonable space utilization. Summary of the invention

[0008] In view of the above problems, the present invention provides an integrated closed heat source tower heat pump unit that can realize system integration, save space, increase heat exchange area, improve heat exchange efficiency, defrost without stopping the heat pump operation, and has fast defrosting and good defrosting effect.

[0009] The technical solution adopted by the present invention to solve the above technical problems is: a closed heat source tower heat pump unit integrated equipment, including a heat source tower base and a heat pump unit arranged in the center of the heat source tower base, the heat source tower base is provided with a tower frame, the heat pump unit includes a heat pump main unit, at least one unit countercurrent serpentine heat exchanger is provided on each side of the heat source tower base, the heat source of the defrost heater comes from the heat of the condenser in the heat pump main unit in the heat source tower or the heat of the high-pressure refrigerant at the compressor outlet of the heat pump unit, an antifreeze liquid volume tank is provided under the heat source tower base, and each unit countercurrent serpentine heat exchanger is connected to the heat source tower through a plurality of sets of flat The serpentine tubes arranged in rows are overlapped in spacing and nested with a group of vertically arranged longitudinal corrugated fins. The medium inlet of each group of serpentine tubes is connected to the shunt main pipe, and the medium inlet of the shunt main pipe is connected to the defrost heater. The medium outlet of each group of serpentine tubes is connected to the confluence main pipe, and the medium outlet of the confluence main pipe is connected to the pipe inflow end of the heat pump host. The medium inlet of the shunt main pipe is connected to the antifreeze side inflow end of the defrost heater and the pipe outflow end of the heat pump host. Electric shutters are provided in the tower frame, and a top cover is provided on the top of the tower. An axial fan mechanism and an inspection door are provided on the top cover.

[0010] Preferably, there are several electric shutters, and the number of the electric shutters corresponds to the number of the counterflow serpentine tube heat exchangers, and each electric shutter is arranged at the air inlet of the counterflow serpentine tube heat exchanger at the corresponding position.

[0011] Preferably, the heat pump host comprises a first heat exchanger and a second heat exchanger, the heat pump unit further comprises a four-way electronic valve group, a refrigeration throttling device and a defrost throttling device, the pipeline inlet end and the pipeline outlet end are both arranged on the first heat exchanger, the medium outlet of each unit countercurrent serpentine heat exchanger is connected to the pipeline inlet end of the first heat exchanger, the medium inlet of each unit countercurrent serpentine heat exchanger is connected to the pipeline outflow end of the first heat exchanger, and an antifreeze circulation pump is connected in series on the pipeline whose pipeline outflow end is connected to the first heat exchanger, the outlet pipeline of the second heat exchanger is connected to the user terminal circulation pump, and the outlet end of the user terminal circulation pump is connected to the user terminal circulation pump. end, the inlet pipe of the second heat exchanger is connected to the user end return pipe, the first heat exchanger, the second heat exchanger, the compressor, the four-way electronic valve group and the refrigeration throttling device constitute a refrigerant circulation system, the second heat exchanger, the user end circulation pump and the user end constitute a refrigerant water or warm coal water circulation system, the first heat exchanger, the antifreeze circulation pump, the countercurrent serpentine tube heat exchanger, and the defrost heater constitute an antifreeze liquid absorbing air energy circulation system or a heat dissipation circulation system to the outside air, and a normally closed electric valve is provided on the circulation pipe at the outflow end of the hot fluid side of the defrost heater. When the normally closed electric valve is opened, the corresponding countercurrent serpentine tube heat exchanger is in a defrosting state.

[0012] Preferably, the first heat exchanger and the second heat exchanger are switched to an evaporator and a condenser via a four-way electronic valve group.

[0013] Preferably, the four-way electronic valve group is composed of several four-way electronic valves arranged in parallel.

[0014] Preferably, the electric shutters and the normally closed electric valve are arranged in linkage, and when the normally closed electric valve is opened, the electric shutters are in a closed state.

[0015] Preferably, a suction pipe and a discharge pipe are provided in the antifreeze liquid storage tank, the suction pipe is connected to the inflow pipe of the antifreeze liquid circulation pump, and the discharge pipe is connected to the vent pipe of the countercurrent serpentine tube heat exchanger.

[0016] Preferably, an axial flow fan is provided in the axial flow fan mechanism.

[0017] Preferably, a sound insulation layer is provided on the periphery of the heat pump main unit, and a main unit cushion layer is provided on the bottom of the heat pump main unit.

[0018] Preferably, a wind shield and support columns are provided on the base of the heat source tower.

[0019] Compared with the prior art, the present invention has the following beneficial effects:

[0020] 1. The heat pump unit of the present invention is arranged in the heat source tower, which can realize system integration, save space, and does not need to build an additional machine room. The heat pump does not need to be stopped for defrosting. The defrosting is fast and the defrosting effect is good. There is no problem of secondary frosting. There is no need to consume 10% more electricity for defrosting, and it can meet the needs of outdoor installation.

[0021] 2. Compared with the traditional heat source tower which has V-shaped fin tube heat exchangers on both sides, the counter-current serpentine tube heat exchanger structure arranged around the present invention increases the heat exchange area per unit volume space and air, and can save space at the same time;

[0022] 3. The defrosting heat of the traditional closed heat source tower comes from the warm medium water of the heat pump host condenser, which must be exchanged through the plate heat exchanger. The defrosting heat of the present invention directly utilizes the fluid heat branched from the high-pressure refrigerant of the heat pump host compressor to directly heat the antifreeze liquid;

[0023] 4. The present invention utilizes the common heat exchange medium circulating working fluid to exchange heat with the refrigerant inside the system and the outside air, and can collect cold sources or heat sources in the air on a large scale;

[0024] 5. The conventional finned tube air heat exchanger adopts a cross-flow heat exchange method, and the temperature difference between the medium in the finned tube and the outside air after the heat exchange is large. However, the outflow temperature difference between the medium in the serpentine finned tube and the outside air after the heat exchange is very close, because the average temperature difference of the counter-flow heat exchange is large, thereby improving the heat exchange efficiency;

[0025] 6. The air inlet shutters of the traditional heat source tower are manual or fixed, while the air inlet shutters of the present invention are electric and linked with the normally closed electric valve of the defrosting mechanism. When defrosting, the shutters can be automatically closed, and the operation is intelligent;

[0026] 7. When the traditional closed heat source tower heat pump is defrosted, the unit will stop heating, but the patented invention can achieve heating, frosting and defrosting at the same time, centralizing functions and improving work efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] Figure 1 It is a top view of the counter-flow serpentine tube heat exchanger arranged around the heat source tower base through the top cover in the present invention;

[0028] Figure 2 It is a schematic diagram of the side structure of the heat source tower of the present invention;

[0029] Figure 3 It is a schematic diagram of the internal flow structure of the heat source tower of the present invention;

[0030] Figure 4 It is an embodiment of the process structure diagram of the present invention;

[0031] Figure 5 It is another embodiment of the process structure diagram of the present invention. DETAILED DESCRIPTION

[0032] The following will be combined Figure 1-5 The present invention is described in detail. The exemplary embodiments and descriptions of the present invention are used to explain the present invention but are not intended to limit the present invention.

[0033] A closed heat source tower heat pump unit integrated equipment, which includes a heat source tower base 11 and a heat pump unit arranged in the center of the heat source tower base, a tower frame 1 is arranged on the heat source tower base, and the tower frame is a right-angle tower frame or a rounded-angle tower frame, and a windshield and a support column 4 are arranged on the heat source tower base, so that it can stably shield from wind and rain, and the heat pump unit includes a heat pump host, and a sound insulation layer 10 is arranged on the periphery of the heat pump host, and a host cushion layer 9 is arranged at the bottom of the heat pump host, so that it will not generate disturbing noise when installed in a public place, at least one unit of countercurrent serpentine tube heat exchanger 5 is arranged on each side of the heat source tower base, and an antifreeze liquid volume tank 8 is arranged under the heat source tower base, and each unit of the countercurrent serpentine tube heat exchanger is formed by overlapping the spacing of multiple groups of parallel arranged serpentine tubes and nesting with a group of vertically arranged longitudinal corrugated fins, and the medium inlet of each group of serpentine tubes is connected to the shunt main pipe, The medium inlet of the shunt main pipe is connected to the defrost heater 23, the heat source of the defrost heater comes from the heat of the condenser in the heat pump main unit in the heat source tower or the heat of the high-pressure refrigerant at the outlet of the compressor 17 in the heat pump unit. The medium outlet of each group of serpentine tubes is connected to the confluence main pipe, the medium outlet of the confluence main pipe is connected to the pipeline inflow end 12 of the heat pump main unit, the medium inlet of the shunt main pipe is connected to the antifreeze side inflow end of the defrost heater connected to the pipeline outflow end 13 of the heat pump main unit, and an electric shutter 6 is provided in the tower frame. Specifically, there are several electric shutters, and the number of electric shutters corresponds to the number of countercurrent serpentine heat exchangers. At the same time, each electric shutter is arranged at the air inlet of the countercurrent serpentine heat exchanger at the corresponding position. A top cover 7 is provided on the top of the tower, and an axial fan mechanism and an inspection door 3 are provided on the top cover, and an axial fan 2 is provided in the axial fan mechanism.

[0034] The heat pump host comprises a first heat exchanger 19 and a second heat exchanger 16, and the heat pump unit further comprises a four-way electronic valve group 18, a refrigeration throttling device 20 and a defrost throttling device 27, wherein the four-way electronic valve group is composed of a plurality of four-way electronic valves arranged in parallel, the pipeline inlet end and the pipeline outflow end are both arranged on the first heat exchanger, the medium outlet of each unit countercurrent serpentine heat exchanger is connected to the pipeline inflow end 12 of the first heat exchanger, the medium inlet of each unit countercurrent serpentine heat exchanger is connected to the pipeline outflow end 13 of the first heat exchanger, and the pipeline whose outflow end is connected to the first heat exchanger is connected in series with an antifreeze circulation pump 21, the outlet pipeline of the second heat exchanger is connected to the user terminal circulation pump 22, the outlet end 15 of the user terminal circulation pump is connected to the user terminal 25, and the second exchange The inlet pipe 14 of the heat exchanger is connected to the user end return pipe, the first heat exchanger, the second heat exchanger, the compressor 17, the four-way electronic valve group 18 and the refrigeration throttling device 20 constitute a refrigerant circulation system, the second heat exchanger, the user end circulation pump and the user end constitute a refrigerant water or warm coal water circulation system, the first heat exchanger, the antifreeze circulation pump, the countercurrent serpentine heat exchanger, and the defrost heater constitute an antifreeze absorption air energy circulation system or a heat dissipation circulation system to the outside air, and a normally closed electric valve 24 is provided on the circulation pipe at the outflow end of the hot fluid side of the defrost heater. When the normally closed electric valve is opened, the corresponding countercurrent serpentine heat exchanger is in a defrosting state, and the electric blinds and the normally closed electric valve are arranged in linkage. When the normally closed electric valve is opened, the electric blinds are in a closed state. The first heat exchanger and the second heat exchanger are switched to become an evaporator and a condenser through the four-way electronic valve group. Figure 3 As shown, the inlet and outlet of the hot fluid of the defrost heater are respectively connected to the branch pipe of the warm medium water of the heat pump main unit condenser or when the defrost heater 23 uses high-pressure refrigerant to heat the antifreeze liquid, its inlet is connected to the compressor outlet, and its outlet is connected to the branch pipe of the refrigerant side of the first heat exchanger (evaporator).

[0035] A suction pipe and a discharge pipe are arranged in the antifreeze volume tank. The suction pipe is connected with the inflow pipe of the antifreeze circulation pump, and the discharge pipe is connected with the discharge pipe of the countercurrent serpentine heat exchanger.

[0036] Depend on Figure 4It can be seen that except for the user terminal and the pipes connected to it, the entire heat pump unit system is set in the heat source tower, including the user terminal circulation pump and the antifreeze circulation pump to form an integrated equipment. When the normally closed electric valve is opened, it means that the corresponding countercurrent serpentine heat exchanger is defrosting. When the second heat exchanger 16 is operating as a condenser, the user terminal circulation pump 22 delivers heat to the user terminal 25. At this time, the first heat exchanger is an evaporator, and the antifreeze circulation pump 21 releases the latent heat of the antifreeze in the evaporator and then delivers it to the countercurrent serpentine heat exchanger 5, where it will exchange heat with the air drawn in by the axial flow fan 2 and passing over its fins, so that the temperature of the antifreeze rises again and enters the first heat exchanger 19 to release the latent heat to the refrigerant. The refrigerant obtains the latent heat and evaporates. The evaporated refrigerant is pressed into the second heat exchanger 16 (at this time a condenser) by the compressor 17 through the four-way electronic valve group 18, thereby transferring the latent heat of the refrigerant to the warm medium water on the other side. In this way, the process of transferring the low-temperature air energy from the outside to the high-temperature area for heating is completed over and over again. When the second heat exchanger 16 operates as an evaporator, the user end circulation pump 22 delivers cold air to the user end. At this time, the first heat exchanger 19 is operating as a condenser. Then, the water medium circulates inside the fin tube heat exchanger, and the antifreeze is discharged into the antifreeze volume tank 8. The circulation pump 21 delivers the cooling water with the latent heat of the refrigerant obtained from the condenser 19 to the countercurrent serpentine tube heat exchanger 5, thereby exchanging heat with the air brought by the axial flow fan 2. After the cooling water medium is cooled, it returns to the first heat exchanger (condenser at this time) 19 to condense the high-pressure refrigerant. After the high-pressure refrigerant is cooled, it is condensed into liquid refrigerant. The liquid refrigerant flows through the refrigeration throttling device 20 and enters the second heat exchanger (evaporator at this time) 16 to absorb the latent heat of the reflux refrigerant water on the other side and evaporate. After evaporation, the refrigerant is again pressed into the condenser 19 by the compressor 17 through the four-way electronic valve group 18 to complete the refrigerant circulation process. When the heat pump is running, its countercurrent serpentine heat exchanger needs to be defrosted, so the normally closed electric valve 24 will open, and a hot fluid will flow into the defrost heater 23 corresponding to the countercurrent serpentine heat exchanger that needs to be defrosted. The hot fluid flowing in in this embodiment is the high-pressure refrigerant of the compressor 17 that heats the antifreeze liquid. The refrigerant releases latent heat to the antifreeze liquid, which will cause the antifreeze liquid to heat up to about 5°C and melt the frost layer on the outside of the fin-tube heat exchanger. The refrigerant will then condense into liquid refrigerant and flow through the defrost throttling device 27 and flow back into the first heat exchanger 19 to absorb the latent heat of the antifreeze liquid. Then the refrigerant will evaporate and be pressed into the defrost heater 23 by the compressor 17 again to defrost.

[0037] Figure 5 Example and Figure 4The difference between the embodiments is that the defrosting method is different. This embodiment uses the warm medium water branched from the second heat exchanger (this is the condenser) 16 to defrost, and the warm medium water is transported by the user's end circulation pump 22. The warm medium water passes through the defrost electric valve 28 arranged on the branch pipeline and then passes through the normally closed electric valve 24 corresponding to the countercurrent serpentine tube heat exchanger that needs to be defrosted to complete the defrosting work. The defrosting heat actually returns to the warm medium water for heating.

[0038] The heat source tower of the present invention has a compact structure. The countercurrent serpentine heat exchanger uses a countercurrent method to exchange heat with the air. The heat exchange efficiency is stronger than that of the finned tubes of the traditional cross-flow heat exchange. Under the same ambient temperature, the heat or cooling effect obtained by achieving the same heat absorption or cooling effect has the advantage of energy saving, especially when the heat pump is running, it can absorb the latent heat of water vapor in the air without consuming an additional 10% of electricity, and the frost on the finned tube is used as a positive asset. It can realize the operation mode of defrosting during the heating process and frosting during the defrosting process. The invention does not waste water resources, nor does it have the problem of scale affecting the heat exchange effect. The whole system can form an integrated equipment that uses a common heat exchange medium circulating medium to exchange heat with the refrigerant inside the system and the outside air, and can collect cold sources or heat sources in the air on demand. There is no need to build a machine room, and the equipment is very convenient to install, and it can greatly reduce investment costs and operating costs.

[0039] The technical solutions provided by the embodiments of the present invention are introduced in detail above. Specific examples are used herein to illustrate the principles and implementation methods of the embodiments of the present invention. The description of the above embodiments is only applicable to help understand the principles of the embodiments of the present invention. At the same time, for those skilled in the art, according to the embodiments of the present invention, there will be changes in the specific implementation methods and application scopes. In summary, the content of this specification should not be understood as limiting the present invention.

Claims

1. A closed heat source tower heat pump unit integrated equipment, characterized by: The invention comprises a heat source tower base (11) and a heat pump unit arranged in the center of the heat source tower base, wherein the heat source tower base is provided with a tower frame (1), and the heat pump unit comprises a heat pump main unit, and at least one unit countercurrent serpentine heat exchanger (5) is arranged on each side of the heat source tower base, and an antifreeze liquid storage tank (8) is arranged below the heat source tower base, and each unit countercurrent serpentine heat exchanger is formed by overlapping a plurality of groups of parallel arranged serpentine tubes and nesting with a group of vertically arranged longitudinal corrugated fins, and the medium inlet of each group of serpentine tubes is connected to a shunt main pipe, and the medium inlet of the shunt main pipe is connected to a defrost heater (23), and the heat source of the defrost heater comes from the heat in the heat source tower. The heat of the condenser in the heat pump main unit or the heat of the high-pressure refrigerant at the outlet of the compressor (17) in the heat pump unit, the medium outlet of each group of serpentine tubes is connected to the confluence main pipe, the medium outlet of the confluence main pipe is connected to the pipeline inflow end (12) of the heat pump main unit, the medium inlet of the branch main pipe is connected to the antifreeze liquid side inflow end of the defrost heater and connected to the pipeline outflow end (13) of the heat pump main unit, the tower frame is provided with an electric shutter (6), the top of the tower is provided with a top cover (7), and the top cover is provided with an axial fan mechanism and an inspection door (3); the heat pump main unit includes a first heat exchanger (19) and a second heat exchanger (16), and the heat pump unit also includes a four-way electronic valve group ( 18), a refrigeration throttling device (20) and a defrosting throttling device (27), wherein the pipeline inlet end and the pipeline outlet end are both arranged on the first heat exchanger, the medium outlet of each unit countercurrent serpentine heat exchanger is connected to the pipeline inlet end (12) of the first heat exchanger, the medium inlet of each unit countercurrent serpentine heat exchanger is connected to the pipeline outlet end (13) of the first heat exchanger, and an antifreeze liquid circulation pump (21) is connected in series to the pipeline connecting the pipeline outlet end with the first heat exchanger, the outlet pipeline of the second heat exchanger is connected to the user terminal circulation pump (22), the outlet end (15) of the user terminal circulation pump is connected to the user terminal (25), and the inlet pipe of the second heat exchanger is connected to the user terminal (25). The channel (14) is connected to the user terminal return pipeline, the first heat exchanger, the second heat exchanger, the compressor (17), the four-way electronic valve group (18) and the refrigeration throttling device (20) constitute a refrigerant circulation system, the second heat exchanger, the user terminal circulation pump and the user terminal constitute a cold medium water or warm coal water circulation system, the first heat exchanger, the antifreeze circulation pump, the countercurrent serpentine tube heat exchanger, and the defrost heater constitute an antifreeze liquid absorbing air energy circulation system or a heat dissipation circulation system to the outside air, and a normally closed electric valve (24) is provided on the circulation pipeline at the outflow end of the hot fluid side of the defrost heater. When the normally closed electric valve is opened, the corresponding countercurrent serpentine tube heat exchanger is in a defrosting state.

2. According to claim 1, the closed heat source tower heat pump unit integrated equipment is characterized by: There are several electric shutters, and the number of the electric shutters corresponds to the number of the counter-flow serpentine tube heat exchangers. At the same time, each electric shutter is arranged at the air inlet of the counter-flow serpentine tube heat exchanger at the corresponding position.

3. According to claim 1, the closed heat source tower heat pump unit integrated equipment is characterized by: The first heat exchanger and the second heat exchanger are switched to an evaporator and a condenser via a four-way electronic valve group.

4. The closed heat source tower heat pump unit integrated equipment according to claim 1 is characterized in that: The four-way electronic valve group is composed of a plurality of four-way electronic valves arranged in parallel.

5. The closed heat source tower heat pump unit integrated equipment according to claim 1 is characterized in that: The electric shutter and the normally closed electric valve are arranged in linkage, and when the normally closed electric valve is opened, the electric shutter is in a closed state.

6. The closed heat source tower heat pump unit integrated equipment according to claim 1, characterized in that: The antifreeze volume tank is provided with a suction pipe and a discharge pipe, the suction pipe is connected with the inflow pipe of the antifreeze circulation pump, and the discharge pipe is connected with the vent pipe of the countercurrent serpentine tube heat exchanger.

7. The closed heat source tower heat pump unit integrated equipment according to claim 1, characterized in that: An axial flow fan (2) is arranged in the axial flow fan mechanism.

8. The closed heat source tower heat pump unit integrated equipment according to claim 1, characterized in that: A sound insulation layer (10) is provided on the periphery of the heat pump main unit, and a main unit cushion layer (9) is provided on the bottom of the heat pump main unit.

9. The closed heat source tower heat pump unit integrated equipment according to claim 1, characterized in that: A wind shield and a support column (4) are provided on the heat source tower base.

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