Integrated water-cooled and air-cooled heat pump modular unit

Abstract

The present invention discloses an integrated water-cooled and air-cooled heat pump modular unit, which includes a small cooling tower housing and a cooling system, a refrigerant circulation system, and functional modules assembled inside the small cooling tower housing; the cooling system includes a fan, a water distributor, a cooling circulation pump, a sprayer, a cooling filler layer, and a cooling water tank, and the refrigerant circulation system includes a small-power compressor, an air-cooled finned heat exchanger, an open-type spiral wound condenser, a four-way valve, an indoor heat exchanger, and a gas-liquid separator; the functional modules include a liquid storage tank, a drying filter, an electronic expansion valve, and a number of one-way valves that are connected to each other; after the small-power compressor is connected to the air-cooled finned heat exchanger and the open-type spiral wound condenser through the four-way valve, it is connected to the small-power compressor after passing through the functional modules, the indoor heat exchanger, the four-way valve, and the gas-liquid separator.

Description

Technical Field

[0001] The present invention relates to the field of air conditioning equipment, and particularly to a refrigeration and heating modular unit or a direct expansion (multi-connected) modular unit that highly integrates a cooling system and a refrigeration system, is installed in a small modular manner in parallel, and can combine air-cooled and water-cooled methods. Background Art

[0002] With the development of heat pump technology, low-temperature air-cooled heat pumps have been gradually popularized, and their cooling and heating functions provide users with more choices.

[0003] Since water-cooled units have significant energy-saving effects compared with air-cooled chillers, and most water-cooled chillers use screw compressors or centrifugal compressors, the refrigeration capacity of a single unit ranges from several hundred kilowatts to several thousand kilowatts, and the refrigeration capacity is powerful. And the boiler technology is mature, so it is widely used. For buildings in winter-cold and summer-hot regions with simultaneous refrigeration and heating requirements, using the method of water-cooled central air conditioning + boiler to meet the cooling and heating needs is a commonly adopted solution; in recent years, due to the development of heat pump technology, especially the low-temperature air-cooled heat pump can supply both cooling and heating, and one set of equipment can meet two needs, which is another good solution in summer-hot and winter-cold regions, so it is popular in the market. The above two cooling and heating methods are widely used in medium and large buildings or building clusters such as factories, office buildings, apartments, hotels, airports, hospitals, and schools. However, the existing technology still has the following problems:

[0004] First, although water-cooled units are about 30% more energy-efficient in refrigeration than air-cooled units, as the preferred machine type for summer refrigeration, the existing water-cooled chillers using high-power screw compressors and centrifugal compressors have the following problems in solving the refrigeration and heating in summer-hot and winter-wet-cold regions (-10°C - 10°C):

[0005] 1. Large volume, inconvenient installation and transportation, increased construction workload, and high professionalism. Water-cooled chillers generally use high-power screw compressors (single-unit power consumption above 100KW) or centrifugal compressors (single-unit power consumption above 200KW - 1000KW), and the weight of the unit is at least one or two tons and at most several tons, so the large volume makes installation and transportation inconvenient; the machine room of water-cooled refrigeration units is generally set in the underground part of the building main body, while the cooling tower is set on the roof of the building main body. The distance between the refrigeration host in the machine room and the cooling tower is at least dozens of meters and at most hundreds of meters, and the construction of the large-diameter cooling supply and return water network is difficult, requires strong construction professionalism, increases the construction difficulty, and the long cooling circulation pipe network construction workload leads to an increase in construction costs.

[0006] 2. Reduced building utilization due to the occupation of the main building space. The refrigeration main unit and water supply system, the circulation system composed of the chilled water pump, the circulation system composed of the cooling water pump, and the electronic control system require a specific machine room. The installation area ranges from hundreds of square meters to thousands of square meters, resulting in a waste of the effective utilization area of the main building and a reduction in the utilization rate of the main building. In today's world where land resources are in short supply and real estate regulation is becoming increasingly stringent, reducing land use area and improving building utilization are of great significance. In engineering practice, some newly built and renovated buildings cannot install refrigeration main units indoors due to indoor space limitations due to various reasons, and air-cooled units are used as an alternative, resulting in a significant increase in air-conditioning and refrigeration operating costs.

[0007] 3. Single units suffer from poor operational stability and difficult maintenance. Because water-cooled chillers offer high power and cooling capacity, yet are expensive, they often utilize dual-head compressors in a single unit to improve operational stability, rather than using a single standby unit or multiple units in parallel for combined cooling. This can lead to a lack of available units during refrigeration unit failure or maintenance, reducing refrigeration system stability. Furthermore, water-cooled chillers are difficult to maintain and expensive to repair.

[0008] 4. The separation of the unit's refrigeration system from the cooling system results in an overly long cooling pipe network, leading to high energy consumption in the circulating pump. The large height difference between the refrigeration unit and the cooling tower, coupled with an overly long cooling circulating water pipe network, increases the resistance along the cooling water path, increasing the head of the cooling circulating pump, which in turn increases the circulating pump's power and energy consumption. Furthermore, existing chillers mostly use shell-and-tube heat exchangers. The high flow rate creates a large pressure difference between the inlet and outlet of the fluid, increasing the fluid resistance in the shell. This increased friction increases the energy consumption of the circulating pump.

[0009] 5. The efficiency of traditional shell-and-tube condensers in chillers needs to be improved. Since the heat exchange between the refrigerant and the cooling medium takes place entirely within the closed heat exchanger shell, it is not conducive to the vaporization and evaporation of the cooling medium (water). This results in a decrease in the latent heat of vaporization of the water, thereby reducing the cooling effect of the water.

[0010] 6. Severe noise pollution. Chiller noise primarily comes from the compressor and circulating pump. When high-power compressors and refrigeration and cooling circulating pumps are concentrated in the same machine room, they generate significant noise and vibration. To reduce noise pollution, professional noise reduction treatment is necessary. This not only increases machine room construction costs but also reduces building comfort.

[0011] 7. A dual-supply cooling and heating solution with a chiller and boiler requires two sets of equipment per system, increasing initial investment and polluting the environment with coal- and gas-fired boilers. A water-cooled chiller combined with a heating boiler is the primary solution for meeting both cooling and heating needs in regions with cold winters and hot summers. In regions with cold, damp winters (-10°C to 10°C), heating only accounts for approximately one-third to one-quarter of the annual operating time. Consequently, boilers are often idle for extended periods, resulting in wasted investment and environmental pollution.

[0012] 2. Air-cooled heat pump (cold and hot water) units have two-way adjustment functions for cooling and heating, which can not only meet the cooling needs in summer, but also meet the heating needs in winter and are widely used in the market. However, for areas with hot summers and cold and wet winters, the cooling time is long and the heating time is very short. Although the use of air-cooled heat pump (cold and hot water) units in such areas can solve the winter heating problem, the air-cooling efficiency is 30% lower than that of the water-cooling form. The increase in cooling costs leads to increased energy consumption throughout the year, so better equipment selection is expected. Summary of the Invention

[0013] The technical problem to be solved by the present invention is to provide an integrated water-cooled and air-cooled heat pump module unit to solve the problems of large cooling water consumption and low heat exchange efficiency of the chiller, large area of the water-cooled chiller machine room occupying indoor space and resulting in waste of reduced building utilization rate, the separation of the cooling tower and the chiller causing the cooling pipe network to be too long and difficult to construct, increased construction cost, large chillers being difficult to transport, install and maintain, high energy consumption of the cooling pump resulting in reduced overall cooling efficiency of the unit, high noise of the chiller and easy noise pollution, and solving the problem of air-cooled heat pump heating but low cooling efficiency.

[0014] In order to solve the above technical problems, the technical solution adopted by the present invention is:

[0015] Integrated water-cooled and air-cooled heat pump modular unit, including a small cooling tower housing and a cooling system, a refrigerant circulation system (refrigeration system), and functional modules assembled inside the small cooling tower housing; the cooling system includes a fan, a water distributor, a cooling circulation pump, a sprayer, a cooling packing layer, and a cooling water tank, and the refrigerant circulation system includes a small-power compressor, an air-cooled finned heat exchanger, an open-type spiral-wound condenser, a four-way valve, an indoor-side heat exchanger, and a gas-liquid separator; the functional modules include a liquid storage tank, a drying filter, an electronic expansion valve, and several one-way valves connected to each other; the cooling water tank is arranged at the upper part inside the small cooling tower housing, and the small-power compressor, the liquid storage tank, the drying filter, the electronic expansion valve, several one-way valves, and the indoor-side heat exchanger are arranged outside the cooling water tank; the air-cooled finned heat exchanger is placed between the water baffle around the upper part of the cooling water tank and the inner wall of the small cooling tower housing for heat exchange between the refrigerant and the external air; the open-type spiral-wound condenser is immersed in the cooling water inside the cooling water tank; the water distributor is arranged at the bottom inside the cooling water tank; the sprayer is arranged above the cooling packing layer for spraying water onto the surface of the cooling packing layer to absorb heat; the fan is arranged on the top of the small cooling tower housing to discharge the refrigerant heat of the cooling packing layer and the open-type spiral-wound condenser to the outdoor atmosphere in the form of latent heat of vaporization; the small-power compressor is connected to the air-cooled finned heat exchanger and the open-type spiral-wound condenser through a four-way valve, and then is connected to the small-power compressor through the functional modules, the indoor-side heat exchanger, the four-way valve, and the gas-liquid separator.

[0016] Alternatively, the small-power compressor is connected to the air-cooled finned heat exchanger through a four-way valve, and then is connected to the small-power compressor through the functional modules, the indoor-side heat exchanger, the four-way valve, and the gas-liquid separator.

[0017] Alternatively, the small-power compressor is connected to the indoor-side heat exchanger through a four-way valve, and then is connected to the small-power compressor through the functional modules, the air-cooled finned heat exchanger, the four-way valve, and the gas-liquid separator.

[0018] Preferably, the small cooling tower housing includes a top plate, a base, a guard plate, and a water baffle installed around the upper part inside the guard plate; a sewage discharge valve and a sewage discharge port are arranged at the bottom of the cooling water tank, and the sewage discharge port is connected to the lower part of the guard plate; a water replenishment port and a float valve are arranged in the middle of the guard plate of the small cooling tower housing, and external cooling water enters through the water replenishment port and automatically replenishes the cooling water tank through the float valve switch when needed; a chilled water outlet and a chilled water inlet on the outside are arranged at the lower part of the guard plate of the small cooling tower housing, and are respectively communicated with the chilled water inlet and outlet of the indoor-side heat exchanger; a control cabinet is arranged at the lower part of the guard plate of the small cooling tower housing to control the electrical switches of the integrated water-cooled low-temperature air-cooled heat pump modular unit.

[0019] Further, the small power compressor is a compressor with a power consumption of 5-25KW, having an outlet and a reflux port; the indoor heat exchanger has P and Q interfaces; the several check valves include a first check valve, a second check valve, a third check valve, and a fourth check valve; the functional module has U and V interfaces; the air-cooled finned heat exchanger has X and Y interfaces, and the open-type spiral-wound condenser has a collecting box refrigerant inlet and a collecting box refrigerant outlet; the four-way valve includes a, b, c, and d ends.

[0020] Preferably, the outlet of the small power compressor enters through the a end and exits through the b end of the four-way valve, and is connected to the X interface of the air-cooled finned heat exchanger; the Y interface of the air-cooled finned heat exchanger passes through the first solenoid valve, enters through the collecting box refrigerant inlet of the open-type spiral-wound condenser, exits from the collecting box refrigerant outlet, passes through the first check valve, the U interface of the functional module, the liquid storage tank, the drying filter, and the V interface of the functional module, and is connected to the P interface of the indoor heat exchanger through the second check valve. The Q interface of the indoor heat exchanger enters through the d end and exits through the c end of the four-way valve, and is connected to the reflux port of the small power compressor through the gas-liquid separator.

[0021] Or, the outlet of the small power compressor enters through the a end and exits through the b end of the four-way valve, and is connected to the X interface of the air-cooled finned heat exchanger. The Y interface of the air-cooled finned heat exchanger passes through the second solenoid valve, the first check valve, the U interface of the functional module, the liquid storage tank, the drying filter, the electronic expansion valve, and the V interface of the functional module, and is connected to the P interface of the indoor heat exchanger through the second check valve. The Q interface of the indoor heat exchanger enters through the d end and exits through the c end of the four-way valve, and is connected to the reflux port of the small power compressor through the gas-liquid separator.

[0022] Or, the outlet of the small power compressor enters through the a end and exits through the d end of the four-way valve, and is connected to the Q interface of the indoor heat exchanger. After the P interface of the indoor heat exchanger is connected to the third check valve, it passes through the U interface of the functional module, the liquid storage tank, the drying filter, the electronic expansion valve, and the V interface of the functional module, passes through the fourth check valve and the second solenoid valve, and is connected to the Y interface of the air-cooled finned heat exchanger. The X interface of the air-cooled finned heat exchanger enters through the b end and exits through the c end of the four-way valve, and is connected to the reflux port of the small power compressor through the gas-liquid separator.

[0023] Further, an indoor-side chilled water circulation pump is externally connected to the indoor heat exchanger. At this time, the chilled water is transported to the refrigeration main unit - the indoor heat exchanger through the indoor-side chilled water circulation pump to produce chilled water, achieving the purpose of cooling the indoor environment.

[0024] Further, the indoor heat exchanger can be replaced by an indoor multi-connected unit. At this time, the indoor multi-connected unit includes a refrigerant fin heat exchanger and an indoor fan. The indoor fan makes air flow through the surface of the refrigerant fin heat exchanger, and the refrigerant directly vaporizes to absorb the heat of the indoor air and cool down.

[0025] Further, the connection modes between the small-power compressor, the open-type spiral-wound condenser, and the air-cooled fin heat exchanger can be adjusted adaptively in various ways according to actual needs. For example, the air-cooled fin heat exchanger and the open-type spiral-wound condenser are connected in parallel. After the high-temperature and high-pressure refrigerant vapor ejected from the small-power compressor exchanges heat with cooling water through the open-type spiral-wound condenser, the refrigerant becomes a high-temperature and high-pressure liquid and enters the liquid storage tank.

[0026] Preferably, the open-type spiral condenser includes a refrigerant collecting box, several turns of spiral refrigerant tube windings, several layers of anchor frames, a refrigerant inlet pipe, and a refrigerant outlet pipe. The refrigerant collecting box is composed of an end cover and a bottom plate. The length and width dimensions of the end cover and the bottom plate match each other and are both provided with flange plates of the same size on the outside. The flange plates are provided with several screw holes that match in size and position. Several tube holes are opened in the middle of the bottom plate. A box-shaped part protrudes from the middle of the end cover. The bottom plate and the end cover are screwed and fastened together by bolts passing through the screw holes on the flange plates to form a cavity for refrigerant collection. The refrigerant collecting box includes a steam-end collecting box and a liquid-end collecting box arranged oppositely. A collecting box refrigerant inlet and a collecting box refrigerant outlet are respectively provided above the side of the steam-end end cover and below the side of the liquid-end end cover. The refrigerant inlet pipe extends into the steam-end collecting box through the collecting box refrigerant inlet to form a steam distribution pipe. Small holes are evenly distributed along the lower edge of the steam distribution pipe, so that the refrigerant vapor is evenly sprayed into the entire steam-end collecting box, ensuring that each turn of the spiral refrigerant tube winding is evenly supplied with steam, facilitating the uniform distribution of the refrigerant in the tubes to achieve a full condensation and liquefaction effect. The refrigerant outlet pipe is connected to the collecting box refrigerant outlet. A deflector plate forming a certain angle with the bottom surface is arranged at the bottom of the liquid-end collecting box, so that the condensed refrigerant liquid flows into the refrigerant outlet pipe, facilitating the liquid outflow of the refrigerant and preventing the occurrence of liquid accumulation phenomena, and improving the utilization efficiency of the refrigerant.

[0027] Optionally, the open-type spiral-wound condenser can be replaced by a spiral immersion condenser or a tube immersion condenser.

[0028] Preferably, an H-shaped same-way multi-stage water distributor is adopted in the cooling water tank, which includes a main water distribution pipe, multi-stage sub-water pipes and a number of water distribution heads that are interconnected. Each lower-level sub-water pipe of each stage is vertically connected to the upper-level sub-water pipe above it to form a multi-stage H shape. A number of water distribution heads are distributed at both ends of the last-stage sub-water pipe, finally enabling each water distribution head to be on the same horizontal plane, and each adjacent water distribution head to be arranged at equal intervals, thus forming a uniform water distribution head array. The other end of the main water distribution pipe is connected to the cooling circulation pump. The cooling water heated through heat exchange in the cooling water tank enters the multi-stage sub-water pipes and the main water distribution pipe through the uniformly distributed water distribution heads, and finally enters the cooling circulation pump and the sprayer through the cooling pump guide pipe to enter the next cooling cycle. The use of the H-shaped same-way multi-stage water distributor can make the low-temperature cooling water cooled on the surface of the cooling water tank move downward vertically in the same horizontal plane, ensuring that the low-temperature cooling water exchanges heat layer by layer with the refrigerant tubes downward. As the refrigerant in the tubes is cooled, the temperature of the cooling water gradually rises. Through the setting of the H-shaped same-way multi-stage water distributor, the heated cooling water can effectively prevent the disordered heat exchange between the cooling water and the refrigerant tubes, ensuring that the low-temperature cooling water vertically flows through each layer of tubes in the same horizontal plane, thereby improving the cooling effect of the cooling water and the cooling efficiency of the refrigerant. According to Q absorption = V flow rate * S cross-sectional area * ρ density * △T temperature difference * C specific heat capacity; where V flow rate * S cross-sectional area is a fixed value, ρ density and C specific heat capacity are constants. Since the cross-sectional area of the open cooling water tank is hundreds of times that of the cooling circulation pipe, the cooling water flow rate V flow rate decreases, and then the residence time of the cooling water in the tank is prolonged.

[0029] Beneficial effects: The present invention integrates the refrigeration system into a small modular cooling tower to form an integrated unit with a highly integrated refrigeration system and cooling system; by using a scroll compressor or a small-power screw compressor, the unit is miniaturized. After miniaturization and modularization, the power consumption is 5KW - 40KW, and the single-unit weight is reduced to less than 0.5 tons, which facilitates the installation and transportation of the unit; after the highly integrated refrigeration system and cooling system, the refrigerant circulation system is built into the outdoor cooling tower, eliminating the traditional indoor machine room; the integrated unit eliminates the laying of cooling pipe networks in the traditional chiller project, reducing the construction volume and construction difficulty; the built-in cooling water circulation system has a lower head and a lower power of the cooling circulation pump, and the efficient open-type spiral-wound high-efficiency cooling system improves the evaporation rate of cooling water, reducing the cooling water circulation volume and further reducing the power consumption of the cooling circulation pump; the refined spray water distribution and the small-flow cooling water circulation reduce the fan speed, maximizing the avoidance of "water splashing" and "water drifting" phenomena and saving water; through the optimization of each component and system, the unit of the present invention has a higher integration degree, lower noise, and higher comprehensive efficiency; the present invention also adds an air-cooled finned heat exchanger inside the outer wall guard plate of the unit, solving the problem that the air-cooled heat pump (cold / hot water) unit has a high operating cost in summer due to its two-way regulation function of refrigeration and heating to meet the refrigeration demand in summer and heating demand in winter. The unit of the present invention can reduce the summer refrigeration operating cost by more than 30%. The present invention combines water-cooling technology and air-cooled heat pump technology to create a new type of air conditioner - an integrated water-cooled air-cooled heat pump modular unit, fundamentally solving the following problems of traditional chillers:

[0030] 1. It is inconvenient to install and transport units weighing several tons with a large volume. Since the present invention uses a scroll compressor or a small-power screw compressor to miniaturize and modularize large chillers, the power consumption is dozens of kilowatts at most, and the single-unit weight is reduced to less than 1 ton, which facilitates the installation and transportation of the unit.

[0031] 2. The reduction of building utilization rate and space waste caused by the refrigeration machine room occupying the main building space. The small modular unit can be installed on the roof of the building without a dedicated machine room, thus saving indoor space and improving the utilization rate of the main building.

[0032] 3. The small number of units equipped results in poor stability and difficult maintenance. The modular units operate simultaneously and are used as backups for each other. The repair and maintenance of individual units do not affect the overall operation and use, improving the operation stability of the entire air-conditioning system.

[0033] 4. High energy consumption of the cooling circulation pump. The large height difference between the cooling tower and the refrigeration host and the long length of the cooling pipe network result in an increase in the frictional resistance along the way, and a high-lift circulation pump is used, resulting in high power consumption. Placing the cooling tower and the refrigeration host on the same adjacent plane will obviously greatly reduce the lift and frictional resistance along the way, reducing the power consumption of the cooling circulation pump by 50%-70%. The shell-and-tube (double-pipe) heat exchanger has a large resistance, and the energy consumption of the circulation pump is high. Most existing water chillers use shell-and-tube heat exchangers. Since the shell side is short, a high flow rate is required, which results in a large pressure difference between the inlet and outlet of the fluid, greatly increasing the fluid resistance, increasing the power of the circulation pump and the energy consumption. The modular unit with an open-type spiral-wound high-efficiency cooling system uses an open-type spiral-wound condenser, and utilizes the self-gravity flow of the cooling water to overcome the resistance of the shell-and-tube heat exchanger in the traditional water chiller, thereby reducing the power consumption of the circulation pump.

[0034] 5. Increased construction volume of the pipe network, high construction cost, and high construction difficulty. The modular water chiller with an open-type spiral-wound high-efficiency cooling system combines the cooling tower and the host, although it will increase the total cost of the host, but the industrialized production and scale advantages can effectively reduce the manufacturing cost per unit. This transfer of downstream costs to upstream, namely "cost front-loading", reduces the construction cost, facilitates the construction of engineering companies, reduces the construction difficulty, and is conducive to the promotion of engineering contractors. And after the refrigeration unit is added with a heat pump function, the use function is increased and the cost performance of the unit is improved.

[0035] 6. In particular, an open-type spiral-wound high-efficiency cooling system is adopted, replacing the common shell-and-tube heat exchanger of the water-cooled unit with an open-type spiral-wound heat exchanger instead of a shell-and-tube (double-pipe) closed heat exchanger, so that a part of the latent heat of vaporization generated by the heat exchange of the refrigerant and the cooling water is released into the air through the water surface of the water tank. Utilizing the latent heat of vaporization of water increases the heat exchange amount per unit mass of water, achieving an effect that cannot be achieved by the shell-and-tube heat exchanger, improving the cooling efficiency, and making the entire unit operate more efficiently.

[0036] 7. The open-type heat exchanger has an open operating space, which is convenient for the cleaning and maintenance of the condenser.

[0037] 8. High noise. In civil buildings, the central air conditioner is the largest noise source. To solve the noise pollution, it is necessary to carry out professional and systematic anti-pollution treatment on the air-conditioning machine room, which increases the construction cost and requires round-the-clock professional personnel on duty, increasing the operating cost. The modular unit with an open-type spiral-wound high-efficiency cooling system (the unit of the present invention) only needs to be installed on the roof of a high-rise building in accordance with the specifications. The noise of the unit is below 65 dB(A) and does not require special noise reduction treatment, fully meeting the national standard, and fundamentally solving the noise pollution problem. And the host operates fully automatically without the need for special personnel on duty, thus reducing the construction and use costs.

[0038] 9. Serious waste of cooling water. The sources of cooling water consumption are three aspects: the evaporation consumption of cooling water, the sewage discharge consumption, and "flying water". Among them, "flying water" belongs to unbeneficial consumption. Since the heat transfer process of the refrigerant is directly or indirectly discharged into the atmosphere with the assistance of a fan, the larger the cooling water circulation volume, the larger the spraying volume, the higher the air circulation volume and wind speed, and the more water carried away by the fan from the spraying water, resulting in waste. The unit of the present invention adopting an open-type spiral-wound high-efficiency cooling system can realize the heat exchange process between the cooling water and the refrigerant through the latent heat of evaporation and the sensible heat of convective heat transfer, effectively reducing the cooling water circulation volume, lowering the wind speed, and thus reducing the "flying water" phenomenon.

[0039] 10. Particularly, an H-type parallel multi-stage water distributor is adopted in the unit of the present invention, which can make the low-temperature cooling water on the surface of the cooling water tank form a uniform flow, uniform pressure, and uniform speed gravitational force horizontally downward in the vertical direction, like a "piston" composed of the side wall of the water tank, forming a piston of water layers with the same temperature and different gradients flowing downward in the vertical direction, flowing through each layer of tube bundles, thereby improving the cooling efficiency of the cooling water. Through the setting of the H-type multi-stage water distributor, it can effectively prevent the disordered heat exchange between the cooling water and the refrigerant tube bundles, avoiding the incomplete backflow caused by the high flow rate in the inlet area of the circulation pump and the low flow rate in the far end area of the inlet of the circulation pump in the state without a water distributor; since the upper and lower tube bundles are wound in the reverse direction to form a group of "micro-channels" with an up-and-down structure. Since the surface of each tube bundle is arc-shaped, the micro-channel is a non-planar structure. When the cooling water flows from top to bottom under the traction of its own gravity flow and the cooling circulation pump, it continuously changes the local flow rate and flow direction, generating a flow deflection and disturbance, forming a turbulent and chaotic flow state, and can reach turbulence under the condition of a very low Reynolds number (Re < 100), improving the heat transfer coefficient K and obtaining more heat exchange quantity Qr = A * K(Tr - △t). The setting of the H-type parallel multi-stage water distributor is a necessary guarantee for realizing the function of the heat exchanger, achieving the efficient heat exchange of the heat exchanger.

[0040] 11. Solve the problem of low cooling efficiency of air-cooled heat pumps during heating. Since the unit of the present invention adds an air-cooled finned heat exchanger inside the outer wall guard plate of the unit, through the optimized refrigerant pipeline and system design, the heat pump heating function is realized on the premise of ensuring water-cooled refrigeration, fundamentally solving the defect of non-heating of traditional water-cooled chillers, and replacing the cold and warm dual-supply solution of chillers + boilers in hot summer and humid cold winter regions. It avoids the increase in initial investment of two sets of equipment for one system and the pollution to the environment caused by coal-fired and gas-fired boilers; secondly, in regions with humid cold winters (-10°C - 10°C), since the heating time only accounts for about 1 / 3 - 1 / 4 of the annual operating time, the short usage time and long idle time of boilers cause investment waste and environmental pollution. The use of air-cooled heat pump (cold and hot water) units in such regions greatly increases the summer cooling cost. The unit of the present invention solves the problem that the air-cooled heat pump (cold and hot water) unit has a high summer operating cost due to its two-way regulation function of refrigeration and heating, meeting the summer refrigeration and winter heating requirements. The unit of the present invention can reduce the summer refrigeration operating cost by more than 30%. BRIEF DESCRIPTION OF THE DRAWINGS

[0041] Figure 1 is a schematic diagram of the principle of the water-cooled refrigeration mode of the integrated water-cooled air-cooled heat pump module unit of the present invention.

[0042] Figure 2 is a schematic diagram of the principle of the air-cooled refrigeration mode of the integrated water-cooled air-cooled heat pump module unit of the present invention.

[0043] Figure 3 is a schematic diagram of the principle of the air-cooled heating mode of the integrated water-cooled air-cooled heat pump module unit of the present invention.

[0044] Figure 4 is an enlarged schematic diagram of the small-power compressor in the present invention.

[0045] Figure 5 is an enlarged schematic diagram of the four-way valve in the present invention.

[0046] Figure 6 is an enlarged schematic diagram of the indoor heat exchanger R9 in the present invention.

[0047] Figure 7 is a schematic diagram of the side sectional structure of the integrated water-cooled air-cooled heat pump module unit of the present invention.

[0048] Figure 8 is a schematic diagram of the front sectional structure of the integrated water-cooled air-cooled heat pump module unit of the present invention.

[0049] Figure 9 is a top view schematic diagram of the integrated water-cooled air-cooled heat pump module unit of the present invention.

[0050] Figure 10It is a schematic side sectional view of the integrated water-cooled air-cooled heat pump multi-connected (direct expansion) modular unit of the present invention.

[0051] Figure 11 It is a top view of the overall assembly of the open-type spiral-wound condenser in the present invention.

[0052] Figure 12 It is a front view of the steam end header of the open-type spiral-wound condenser in the present invention.

[0053] Figure 13 It is a front view of the liquid end header of the open-type spiral-wound condenser in the present invention.

[0054] Figure 14 It is a right side view of the end cover of the steam end header of the open-type spiral-wound condenser in the present invention.

[0055] Figure 15 It is a left side view of the end cover of the liquid end header of the open-type spiral-wound condenser in the present invention.

[0056] Figure 16 It is a side top view of the end cover of the steam end header in the present invention.

[0057] Figure 17 It is a side top view of the end cover of the liquid end header in the present invention.

[0058] Figure 18 It is a right side internal sectional view of the end cover of the steam end header in the present invention.

[0059] Figure 19 It is a right side internal sectional view of the end cover of the liquid end header in the present invention.

[0060] Figure 20 It is a schematic diagram of the layout of the projection of the anchor frame and the straight pipe section of the spiral refrigerant tube on the bottom plate (left view or right view) in the present invention.

[0061] Figure 21 It is a right side view schematic diagram of the position distribution of the straight pipe inlet section of the spiral refrigerant tube on the steam end bottom plate of the steam end header in the present invention (taking the first turn of the spiral refrigerant tube as an example).

[0062] Figure 22 It is a right side view schematic diagram of the position distribution of the straight pipe outlet section of the spiral refrigerant tube on the liquid end bottom plate of the liquid end header in the present invention (taking the first turn of the spiral refrigerant tube as an example).

[0063] Figure 23 It is a side view of the position distribution of the refrigerant header and the anchor frame in the present invention.

[0064] Figure 24It is a side top view of the position distribution of the refrigerant collecting box and the anchor frame in the present invention.

[0065] Figure 25 It is a schematic structural diagram of each anchor frame in the present invention.

[0066] Figure 26 It is a partially enlarged schematic view of the connection between the anchor frame and the bottom plate of the refrigerant collecting box in the present invention.

[0067] Figure 27 It is a side view of the first turn of the spiral refrigerant tube winding in the present invention.

[0068] Figure 28 It is a side top view of the first turn of the spiral refrigerant tube winding in the present invention.

[0069] Figure 29 It is Figure 19 A partially enlarged schematic view of one end of the steam end collecting box in

[0070] Figure 30 It is a side view of the second turn of the spiral refrigerant tube winding in the present invention.

[0071] Figure 31 It is a side top view of the second turn of the spiral refrigerant tube winding in the present invention.

[0072] Figure 32 It is a side view of the third turn of the spiral refrigerant tube winding in the present invention.

[0073] Figure 33 It is a side top view of the third turn of the spiral refrigerant tube winding in the present invention.

[0074] Figure 34 It is a side view of the fourth turn of the spiral refrigerant tube winding in the present invention.

[0075] Figure 35 It is a side top view of the fourth turn of the spiral refrigerant tube winding in the present invention.

[0076] Figure 36 It is a Y-axis point array diagram of the projection of the anchor frame and the spiral refrigerant tubes on the bottom plate in the present invention.

[0077] Figure 37 It is an X-axis point array diagram of the projection of the anchor frame and the spiral refrigerant tubes on the bottom plate in the present invention.

[0078] Figure 38 It is a schematic top view structure diagram of the H-type same-way multi-stage water distributor in the present invention.

[0079] Wherein: R1, a small power compressor; 11, an outlet; 12, a return port; R2, a four-way valve; R4, an air-cooled finned heat exchanger; R5, a liquid storage tank; R6, a drying filter; R8, an electronic expansion valve; R9, an indoor heat exchanger; R91, an indoor freezing circulation pump; R9a, an indoor multi-connected unit; R10, a gas-liquid separator; R121, a first one-way valve; R122, a second one-way valve; R123, a third one-way valve; R124, a fourth one-way valve; R131, a first solenoid valve; R132, a second solenoid valve;

[0080] R3, an open-type spiral wound condenser; 30, a refrigerant collecting box; 30a, an end cover; 30b, a bottom plate; 30-1, a steam end collecting box; 30-2, a liquid end collecting box; 30a-1, a steam end cover; 30a-2, a liquid end cover; 30b-1, a steam end bottom plate; 30b-2, a liquid end bottom plate; 31, a refrigerant inlet pipe; 32, a refrigerant outlet pipe; 31a, a gas distribution pipe; 32a, a deflector; 33, an anchor frame; 33-1, an anchor frame fixing section; 33-2, an anchor frame supporting section; 33.1, a first layer anchor frame; 33.2, a second layer anchor frame; 33.3, a third layer anchor frame; 33.4, a fourth layer anchor frame; 34, a spiral refrigerant tube; 34-1, a straight pipe inlet section; 34-2, a straight pipe outlet section; 34-3, a spiral section; 34.1, a first turn of spiral refrigerant tube winding; 34.2, a second turn of spiral refrigerant tube winding; 34.3, a third turn of spiral refrigerant tube winding; 34.4, a fourth turn of spiral refrigerant tube winding; 300, a flange plate; 301, a screw hole; 302, a tube hole; 303, a box-shaped part; 306, a collecting box refrigerant inlet; 307, a collecting box refrigerant outlet; 308, a bolt;

[0081] 330, an anchor frame rectangular structure; 340, a tube rectangular structure; O, the center point of the bottom plate; D, the diameter of the anchor frame; d, the diameter of the spiral refrigerant tube; H, the layer spacing in the y-axis direction between adjacent turns of tubes; L, the tube distance in the x-axis direction between adjacent straight pipe sections of the same turn of horizontal tubes; l, the distance in the x-axis direction between the flanks of different turns of tubes; S, the total height in the y-axis direction of the same turn of tubes; s, the distance in the y-axis direction of the center layer (the fourth layer) anchor frame; E, the distance in the y-axis direction between the flanks of the same turn of tubes; M, the total distance in the x-axis direction of the straight pipe sections of the same turn of horizontal tubes; m, the distance in the x-axis direction between the y-axis adjacent same turn of tubes; b, the adjacent winding spacing of the same turn of tubes; R, the diameter of the anchor frame supporting section; r, the diameter of the anchor frame fixing section;

[0082] C1, a cooling circulation pump; C2, a sprayer; C3, a water distributor; C4, a fan; C5, a small cooling tower housing; C6, a cooling water tank; C7, a cooling filler layer;

[0083] 51. Top plate; 52. Base; 53. Water baffle; 55. Control cabinet; 56. Drain valve; 57. Drain outlet; 541. Make-up water inlet; 542. Float valve; 543. Chilled water outlet; 544. Chilled water inlet;

[0084] C300. Main water distributor pipe; C301. First-stage sub-water pipe; C302. Second-stage sub-water pipe; C303. Third-stage sub-water pipe; C304. Fourth-stage sub-water pipe; C305. Fifth-stage sub-water pipe; C306. Sixth-stage sub-water pipe; C307. Water distribution head. Detailed implementation manners

[0085] The present invention will be further described in detail below in conjunction with the specific implementation manners.

[0086] As Figure 1 shown, the integrated water-cooled low-temperature air-cooled heat pump module unit includes a small cooling tower housing C5 and a cooling system, a refrigerant circulation system (refrigeration system), and functional modules assembled inside the small cooling tower housing C5; the cooling system includes a fan C4, a water distributor C3, a cooling circulation pump C1, a sprayer C2, a cooling packing layer C7, and a cooling water tank C6, and the refrigerant circulation system includes a low-power compressor R1, an air-cooled finned heat exchanger R4, an open-type spiral-wound condenser R3, a four-way valve R2, an indoor heat exchanger R9, and a gas-liquid separator R10; the functional modules include a liquid storage tank R5, a drying filter R6, an economizer R11, a plurality of electronic expansion valves, a plurality of check valves, and a three-way valve R13 that are connected to each other; the cooling water tank C6 is arranged at the upper part inside the small cooling tower housing C5, and the low-power compressor R1, the liquid storage tank R5, the drying filter R6, the plurality of electronic expansion valves, the plurality of check valves, the three-way valve R13, and the indoor heat exchanger R9 are arranged outside the cooling water tank C6; the air-cooled finned heat exchanger R4 is placed between the water baffle around the upper part of the cooling water tank C6 and the inner wall of the small cooling tower housing C5 for heat exchange between the refrigerant and the external air; the open-type spiral-wound condenser R3 is immersed in the cooling water of the cooling water tank C6; the water distributor C3 is arranged at the bottom inside the cooling water tank C6; the sprayer C3 is arranged above the cooling packing layer C7 for spraying water onto the surface of the cooling packing layer C7 to absorb heat; the fan C4 is arranged on the top of the small cooling tower housing C5 to discharge the refrigerant heat of the cooling packing layer C7 and the open-type spiral-wound condenser R3 to the outdoor atmosphere in the form of latent heat of vaporization; the low-power compressor R1 is connected to the open-type spiral-wound condenser R3, the three-way valve R13, and the air-cooled finned heat exchanger R4 through the four-way valve R2 and is divided into a main circuit and an auxiliary EVI circuit. The main circuit is connected to the low-power compressor R1 after passing through the functional modules, the indoor heat exchanger R9, and the gas-liquid separator R10, and the auxiliary EVI circuit is directly connected to the low-power compressor R1 through the functional modules.

[0087] Alternatively, as Figure 2 shown, after the small power compressor R1 is connected to the air-cooled finned heat exchanger R4 through the four-way valve R2 and the three-way valve R13, it is divided into a third main circuit and a third auxiliary EVI circuit. The third main circuit is connected to the small power compressor R1 after passing through the functional module, the indoor heat exchanger R9, and the gas-liquid separator R10. The third auxiliary EVI circuit is directly connected to the small power compressor R1 through the functional module.

[0088] Alternatively, as Figure 3 shown, after the small power compressor R1 is connected to the indoor heat exchanger R9 through the four-way valve R2, it is divided into a second main circuit and a second auxiliary EVI circuit. The second main circuit is connected to the small power compressor R1 after passing through the functional module, the air-cooled finned heat exchanger R4, the three-way valve R13, the four-way valve R2, and the gas-liquid separator R10. The second auxiliary EVI circuit is directly connected to the small power compressor R1 through the functional module.

[0089] As Figures 4 - 5 shown, the small power compressor R1 is a compressor with a power consumption of 5 - 25 KW, having an outlet 11 and a return port 12; the four-way valve R2 includes ports a, b, c, and d, and the indoor heat exchanger R9 has interfaces P and Q;

[0090] The several check valves include a first check valve R121, a second check valve R122, a third check valve R123, and a fourth check valve R124; the functional module has interfaces U and V; the air-cooled finned heat exchanger R4 has interfaces X and Y, and the open-type spiral wound condenser R3 has a header refrigerant inlet 306 and a header refrigerant outlet 307;

[0091] As Figures 7 - 9 shown, the small cooling tower housing C5 includes a top plate 51, a base 52, and a guard plate (i.e., the panels around the small cooling tower housing C5), and a water baffle 53 installed around the upper part inside the guard plate; a drain valve 56 and a drain port 57 are provided at the bottom of the cooling water tank C6, and the drain port 57 is connected to the lower part of the guard plate; a water replenishing port 541 and a float valve 542 are provided in the middle of the guard plate of the small cooling tower housing C5, and external cooling water enters through the water replenishing port 541 and automatically replenishes the cooling water tank C6 through the on-off of the float valve 542 when needed; an external chilled water outlet 543 and a chilled water inlet 544 are provided at the lower part of the guard plate of the small cooling tower housing C5, which are respectively communicated with the chilled water inlet and outlet of the indoor heat exchanger R9; a control cabinet 55 is provided at the lower part of the guard plate of the small cooling tower housing C5 to control the electrical switches of the integrated water-cooled air-cooled heat pump module unit.

[0092] The outlet 11 of the low-power compressor R1 enters through the a end and exits through the b end of the four-way valve R2, and is connected to the X interface of the air-cooled fin heat exchanger R4; the Y interface of the air-cooled fin heat exchanger R4 enters through the first solenoid valve R131, enters through the refrigerant inlet 306 of the collection box of the open spiral-wound condenser R3, and exits from the refrigerant outlet 307 of the collection box, passes through the first one-way valve R121, the U interface of the functional module, the liquid storage tank R5, the drying filter R6 and the V interface of the functional module, and is connected to the P interface of the indoor heat exchanger R9 through the second one-way valve R122. The Q interface of the indoor heat exchanger R9 enters through the d end and exits through the c end of the four-way valve R2, and is connected to the reflux port 12 of the low-power compressor R1 through the gas-liquid separator R10. The specific correspondence is as follows Figure 1 Water cooling mode shown:

[0093] In this mode, the R2a-b and cd ends of the four-way valve of the refrigerant circulation system are connected; the first solenoid valve R131 is open and the second solenoid valve R132 is closed; the compressor R1 is powered on, and the high-temperature, high-pressure gaseous refrigerant ejected from the outlet 11 of the compressor R1 enters through the a end and exits through the b end of the four-way valve R2, then enters the air-cooled fin heat exchanger R4. The high-temperature, high-pressure refrigerant vapor in the fin coil initially exchanges heat with the air flowing on its surface, and the temperature is reduced, and part of the refrigerant changes from the vapor phase to the liquid phase. At this time, the refrigerant becomes a medium-temperature, high-pressure liquid mixture, and enters the vapor manifold (collecting box refrigerant inlet 306) of the open spiral-wound condenser R3 through the first solenoid valve R131. The medium-temperature, high-pressure refrigerant flows through the surrounding tubes and further exchanges heat with the cooling water in the cooling water tank C6 for cooling and condensation, further reducing the temperature and pressure of the refrigerant, and the refrigerant is fully liquefied. After the phase change, the medium-temperature, medium-pressure liquid refrigerant flows out of the liquid manifold (refrigerant outlet 307) of the open spiral-wound condenser R3, passes through the first one-way valve R121, and then flows through the liquid storage tank R5, the drying filter R6, and the electronic expansion valve R8 for throttling and pressure reduction. The low-temperature, low-pressure refrigerant liquid passes through the second one-way valve R122 and enters the indoor heat exchanger R9. Inside the indoor heat exchanger R9, the low-temperature, low-pressure liquid refrigerant exchanges heat with the refrigerant water flowing through this heat exchanger. The hot water is cooled to chilled water for indoor use. After the liquid refrigerant heats up, it vaporizes into refrigerant vapor. The vapor refrigerant flows through the d-port and c-port of the four-way valve R2, passes through the gas-liquid separator R10, and returns to the reflux port 12 of the low-power compressor R1, completing a cycle. The entire refrigeration process is a reciprocating cycle of refrigerant vapor-liquid phase conversion.

[0094] In this refrigeration mode, the fan C4 in the cooling circulation system starts; the cooling circulation pump C1 starts; the sprayer C2 is in the spraying state. The high-temperature cooling water is evenly sprayed onto the top of the packing layer. The cooling water flows down along the surface of the cooling packing layer C7 under the action of its own gravity, forming a thin water film. Since the temperature of the cooling water is higher than the temperature of the air on the surface of the packing layer, the saturated steam formed on the surface of the water film is condensed and atomized. Under the action of the fan C4, the outdoor ambient air after heat exchange with the air-cooled finned heat exchanger R4 passes over the surface of the cooling packing layer C7 and discharges the water vapor into the ambient air. A large amount of heat is taken away when the cooling water vaporizes, and the circulating water is cooled to obtain low-temperature cooling water. The air takes away the heat, causing the refrigerant in the air-cooled finned heat exchanger R4 to be preliminarily condensed and liquefied and cooled down. The low-temperature cooling water is evenly sprayed onto the upper surface of the cooling water tank C6 along the bottom surface of the cooling packing layer C7, forming a cooling water layer with the same temperature. The cooling water in the same temperature layer moves downward along the microchannels of the open-type spiral-wound condenser R3 under the combined action of its own gravity flow, the cooling circulation pump C1, and the water distributor C3. The entire water layer convects and exchanges heat with the medium-temperature and high-pressure refrigerant mixture in the refrigerant tubes that has been preliminarily cooled in each refrigerant tube winding layer, and the refrigerant is completely condensed and liquefied. The temperature of the cooling water gradually rises as it moves downward. Since the rate of the cooling water layer moving downward is relatively low, the time of the cooling water in the cooling water tank C6 is extended. When the cooling water layer drops to the bottom tube layer, the temperature reaches the highest point. The higher-temperature cooling water can take away more heat when evaporating on the surface of the cooling water tank. The increase in the latent heat exchange amount can correspondingly reduce the cooling water circulation volume, reduce the power of the cooling circulation pump, and improve the overall efficiency of the unit. The evaporated water vapor is discharged into the air by the fan C4. The cooling water passes through each water distribution head of the water distributor C3 evenly distributed at the bottom of the cooling water tank C6, and the branches converge to the main pipe and enter the cooling circulation pump C1, then enter the sprayer C2 through the cooling circulation pipe to participate in the next cycle. The heat of the refrigerant is finally transferred to the atmosphere in the form of water vapor and hot air to achieve the purpose of condensation and cooling.

[0095] Alternatively, the outlet 11 of the small-power compressor R1 enters through the a end and exits through the b end of the four-way valve R2, and is connected to the X interface of the air-cooled finned heat exchanger R4. The Y interface of the air-cooled finned heat exchanger R4 passes through the second solenoid valve R132, the first check valve R121, the U interface of the functional module, the liquid storage tank R5, the dryer filter R6, the electronic expansion valve R8, and the V interface of the functional module, and is connected to the P interface of the indoor heat exchanger R9 through the second check valve R122. The Q interface of the indoor heat exchanger R9 enters through the d end and exits through the c end of the four-way valve R2, and is connected to the return port 12 of the small-power compressor R1 through the gas-liquid separator R10. Specifically corresponding to Figure 2 the air-cooled refrigeration mode shown as

[0096] In this mode, the a-b and c-d ends of the four-way valve R2 in the refrigerant circulation system are connected; the solenoid valve R132 is open and the solenoid valve R131 is closed; the compressor R1 is in operation. After the high-temperature and high-pressure gaseous refrigerant ejected from the jet port 11 of the compressor R1 enters through the a-end and exits through the b-end of the four-way valve R2, it enters the air-cooled fin heat exchanger R4 and exchanges heat with the cold air flowing through the surface of the air-cooled fin heat exchanger R4 to cool and condense. After the air is heated, it is discharged into the atmosphere by the fan C4, and the refrigerant is condensed and liquefied from the liquid phase to the vapor phase, with the pressure and temperature decreasing. At this time, the high-temperature and high-pressure refrigerant vapor is changed into a medium-temperature and medium-pressure liquid refrigerant. After passing through the liquid storage tank R5 and the dryer filter R6 in sequence, the pressure of the refrigerant further decreases after flowing through the electronic expansion valve R8. The low-temperature and low-pressure refrigerant liquid enters the indoor heat exchanger R9 after passing through the second check valve R122. The low-temperature and low-pressure liquid refrigerant exchanges heat with the coolant water flowing through this heat exchanger in the indoor heat exchanger R9. The hot water is cooled to chilled water for indoor use. After the liquid refrigerant is heated, it vaporizes into refrigerant vapor, flows into through the d-end and exits through the c-end of the four-way valve R2, and returns to the return port 12 of the small-power compressor R1 after passing through the gas-liquid separator R10, ending the main refrigerant cycle and entering the next cycle.

[0097] Alternatively, the outflow port 11 of the small-power compressor R1 enters through the a-end and exits through the d-end of the four-way valve R2 and is connected to the Q interface of the indoor heat exchanger R9. After the P interface of the indoor heat exchanger R9 is connected to the third check valve R123, it passes through the U interface of the functional module, the liquid storage tank R5, the dryer filter R6, the electronic expansion valve R8 and the V interface of the functional module, passes through the fourth check valve R124 and the second solenoid valve R132 and is connected to the Y interface of the air-cooled fin heat exchanger R4. The X interface of the air-cooled fin heat exchanger R4 enters through the b-end and exits through the c-end of the four-way valve, and is connected to the return port 12 of the small-power compressor R1 through the gas-liquid separator R10. Specifically, it corresponds to Figure 3 the air-cooled heating mode shown as

[0098] In this mode, the four-way valve of the refrigerant circulation system has its ports R2a-d and c-b connected; the first solenoid valve R131 is closed and the second solenoid valve R132 is open; the compressor R1 is in operation. The compressor R1 is energized and operates. The high-temperature and high-pressure gaseous refrigerant ejected from the outlet 11 of the compressor R1 enters through port a of the four-way valve R2 and exits through port d, and then enters the indoor heat exchanger R9. After the high-temperature and high-pressure refrigerant vapor exchanges heat with the indoor refrigerant (water) flowing through this heat exchanger, the refrigerant is condensed and liquefied at this time, and the temperature and pressure of the refrigerant vapor decrease. The high-temperature and high-pressure refrigerant vapor undergoes a phase change to become a medium-temperature and medium-pressure liquid refrigerant. It passes through the third check valve R123, successively through the liquid storage tank R5 and the dryer filter R6, and then the pressure further decreases after flowing through the electronic expansion valve R8. The low-temperature and low-pressure refrigerant liquid passes through the fourth check valve R124 and the second solenoid valve R132 and then enters the air-cooled finned heat exchanger R4. After the low-temperature and low-pressure liquid refrigerant exchanges heat with the air flowing through the surface of this heat exchanger, the liquid refrigerant is heated and vaporized into refrigerant vapor, flows in through port b of the four-way valve R2 and exits through port c, enters the gas-liquid separator R10, and then returns to the return port 12 of the small-power compressor R1, ending the main refrigerant cycle and entering the next cycle.

[0099] As Figure 6 shown, the indoor heat exchanger R9 is externally connected to the indoor freezing circulation pump R91. At this time, the chilled water is transported to the refrigeration main unit - the indoor heat exchanger R9 through the indoor freezing circulation pump R91 to produce low-temperature water, achieving the purpose of cooling the indoor environment.

[0100] As Figure 10 shown, the indoor heat exchanger R9 can be replaced by the indoor multi-connected unit R9a. At this time, the present invention is an integrated water-cooled air-cooled heat pump multi-connected (direct expansion) modular unit. The indoor multi-connected unit R9a includes a refrigerant fin heat exchanger and an indoor fan. The indoor fan makes the air flow through the surface of the refrigerant fin heat exchanger, and the indoor air is cooled by directly vaporizing the refrigerant to absorb heat.

[0101] Furthermore, the connection mode between the small-power compressor R1, the open-type spiral-wound condenser R3, and the air-cooled finned heat exchanger R4 can be adjusted adaptively in various ways according to actual needs. For example, the air-cooled finned heat exchanger R4 is connected in parallel with the open-type spiral-wound condenser R3. The high-temperature and high-pressure refrigerant vapor ejected from the small-power compressor R1 exchanges heat with the cooling water through the open-type spiral-wound condenser R3, and then the refrigerant becomes a high-temperature and high-pressure liquid and enters the liquid storage tank R5.

[0102] The open-type spiral condenser R3, as Figures 11 - 37As shown in the figure, it includes a refrigerant collection box 30, several turns of spiral refrigerant tube windings, several layers of anchor frames, a refrigerant inlet pipe 31, and a refrigerant outlet pipe 32. The refrigerant collection box 30 is composed of an end cover 30a and a bottom plate 30b. The length and width dimensions of the end cover 30a and the bottom plate 30b match each other, and flange plates 300 of the same size are provided on the outside. A number of screw holes 301 with matching sizes and positions are provided on the flange plates 300. A number of tube holes 302 are opened in the middle of the bottom plate 30b. A box-shaped part 303 protrudes in the middle of the end cover 30a. The bottom plate 30b and the end cover 30a are screwed and fastened together by bolts 308 passing through the screw holes 301 on the flange plates 300 to form a cavity for refrigerant collection. The refrigerant collection box 30 includes a steam-end collection box 30-1 and a liquid-end collection box 30-2 arranged oppositely. A collection box refrigerant inlet 306 and a collection box refrigerant outlet 307 are respectively provided above the side of the steam-end end cover 30a-2 and below the side of the liquid-end end cover 30a-2. The refrigerant inlet pipe 31 extends into the steam-end collection box 30-1 through the collection box refrigerant inlet 306 to form a steam distribution pipe 31a. Small holes are evenly distributed along the lower edge of the steam distribution pipe 31a, so that the refrigerant steam is evenly sprayed into the entire steam-end collection box 30-1, ensuring that each turn of the spiral refrigerant tube winding is evenly supplied with steam, facilitating the uniform distribution of the refrigerant in the tubes to achieve a full condensation and liquefaction effect. The refrigerant outlet pipe 32 is connected to the collection box refrigerant outlet 307. A deflector 32a forming a certain angle with the bottom surface is provided at the bottom of the liquid-end collection box 30-2, so that the condensed refrigerant liquid flows into the refrigerant outlet pipe, facilitating the liquid outflow of the refrigerant and preventing liquid accumulation, thereby improving the utilization efficiency of the refrigerant.

[0103] Among them, it should be particularly noted that:

[0104] Figure 20 It is a schematic diagram of the layout of the projection of the anchor frame and the straight pipe section of the spiral refrigerant tube on the bottom plate in the present invention. Since the projections of the anchor frame and the straight pipe section of the spiral refrigerant tube on the bottom plate are axially symmetrically distributed with the center point O of the bottom plate as the axis, therefore, whether it is a left view or a right view, it is Figure 22 the presented figure.

[0105] Figure 21This is a right view schematic diagram of the position distribution of the straight pipe inlet section of the spiral refrigerant tube in the present invention on the steam end bottom plate of the steam end collecting box (taking the first turn of the spiral refrigerant tube as an example), that is, the position distribution diagram of the straight pipe inlet section 34-1 of the spiral refrigerant tube on the steam end bottom plate 30b-1 seen from the external right side view of the steam end collecting box 30-1. For the convenience of narration and illustration, taking the first turn of the spiral refrigerant tube winding 34.1 as an example, only the position of the straight pipe inlet section 34-1 of the first turn of the spiral refrigerant tube on the steam end bottom plate 30b-1 is drawn, and the positions of the straight pipe inlet section 34-1 of the first turn of the spiral refrigerant tube winding 34.1 on the steam end bottom plate 30b-1 are numbered in the counterclockwise direction, from 1 to 26. Among them, the position of the straight pipe inlet section of the spiral refrigerant tube in the upper right corner is 1, the position of the straight pipe inlet section of the spiral refrigerant tube in the upper left corner is 9, the lower left corner is 14, and the lower right corner is 22; the positions of the straight pipe inlet sections of the above 26 first turn of the spiral refrigerant tube windings on the steam end bottom plate form a largest tube rectangle structure 340.

[0106] Similarly, Figure 22 This is a right view schematic diagram of the position distribution of the straight pipe outlet section of the spiral refrigerant tube in the present invention on the liquid end bottom plate 30b-2 of the liquid end collecting box 30-2 (taking the first turn of the spiral refrigerant tube winding 34.1 as an example), which is the position distribution diagram of the straight pipe outlet section 34-2 of the spiral refrigerant tube on the liquid end bottom plate 30b-2 seen from the right side view of the liquid end collecting box 30-2. We still take the first turn of the spiral refrigerant tube winding 34.1 as an example and only draw the position of the straight pipe outlet section 34-2 of the first turn of the spiral refrigerant tube on the liquid end bottom plate 30b-2. Since each spiral refrigerant tube 34 rotates and winds along the corresponding layer of the anchor 33, its straight pipe inlet section 34-1 must be connected to the corresponding straight pipe outlet section 34-2 after passing through the rotating section 34-3, and the position of the corresponding straight pipe outlet section 34-2 on the liquid end bottom plate 30b-2 (i.e., the position in Figure 24 ), and the position of its straight pipe inlet section 34-1 in Figure 23 are axisymmetric about the center point O of the bottom plate. Specifically, we also number the positions of the straight pipe outlet section 34-2 corresponding to the straight pipe inlet section 34-1. The position of the straight pipe outlet section 34-2 corresponding to the straight pipe inlet section 34-1 at position 1 is denoted as 1′, the position of the straight pipe outlet section 34-2 corresponding to the straight pipe inlet section 34-1 at position 2 is denoted as 2′, and so on, from 1′ to 26′. It forms another largest tube rectangle structure 340 in Figure 22 among them. The position of the straight pipe outlet section of the spiral refrigerant tube in the lower left corner is 1′, the position of the straight pipe outlet section of the spiral refrigerant tube in the lower right corner is 9′, the upper right corner is 14′, and the upper left corner is 22′. It can be seen that if Figure 21 andFigure 22 If the tube-in-tube rectangular structures 340 in Figure 22 are overlapped, then the position 1' of the straight tube inlet section 34-1 at position 1 and its corresponding straight tube outlet section 34-2 are axisymmetric with respect to the center point O of the bottom plate. The position 2' of the straight tube inlet section 34-1 at position 2 and its corresponding straight tube outlet section 34-2 are also axisymmetric. And so on, the positions of each straight tube inlet section 34-1 and its corresponding straight tube outlet section 34-2 in the tube-in-tube rectangular structure 340 are axisymmetric. Such a design can ensure that the distances between each spiral refrigerant tube 34 between the two bottom plates 30b are of the same path, further ensuring the uniformity of the cooling of the refrigerant in the tubes.

[0107] Figures 23 - 35 It is a side view, a side top view, and a partial enlarged schematic diagram of some positions of the refrigerant collecting box and the anchor frame position distribution, and the first to fourth turn spiral refrigerant tube windings of the present invention. It can be seen that the several layers of anchor frames are vertically fixedly connected between the bottom plates 30b of the steam end collecting box 30-1 and the liquid end collecting box 30-2. Each layer of the anchor frame is composed of four anchor frames 33, and the projections of each layer of the anchor frame on the two bottom plates form two symmetric anchor frame rectangular structures 330. The anchor frame rectangular structures formed by the projections of each layer of the anchor frame on the bottom plate are centered on the center point O of the bottom plate and their sizes decrease in sequence; the several turn spiral refrigerant tube windings are formed by several turns of spiral refrigerant tubes 34 rotating externally tangent around the corresponding layer of the anchor frame 33 at a certain angle. Each turn of the spiral refrigerant tube 34 is composed of several spiral refrigerant tubes 34. Each spiral refrigerant tube 34 is composed of a straight tube inlet section 34-1 and a straight tube outlet section 34-2 at both ends and a spiral section 34-3 in the middle, and a certain winding pitch b is maintained between each spiral refrigerant tube 34; the straight tube inlet section 34-1 or the straight tube outlet section 34-2 of the several spiral refrigerant tubes 34 in each turn is communicated with the tube holes 302 on the bottom plate 30b and is perpendicular to the bottom plate 30b, and is axisymmetrically arranged with respect to the center point O of the bottom plate in the length and width directions of the bottom plate 30b. The projections of the straight tube inlet section 34-1 or the straight tube outlet section 34-2 of the several spiral refrigerant tubes 34 in each turn on the corresponding bottom plate 30b (that is, the positions of the tube holes 302 corresponding to this turn of the spiral refrigerant tube 34 on the two bottom plates 30b) form two symmetric tube-in-tube rectangular structures 340. The positions of the straight tube inlet section 34-1 and the straight tube outlet section 34-2 of each spiral refrigerant tube 34 on the tube-in-tube rectangular structure 340 obtained by the projection on the bottom plate are also axisymmetric with respect to the center point O of the bottom plate, so as to ensure that the distances between each spiral refrigerant tube 34 between the two bottom plates 30b are of the same path, further ensuring the uniformity of the cooling of the refrigerant in the tubes; the rotation angles of the adjacent two turn spiral refrigerant tube windings and the corresponding layer of the anchor frame are opposite, forming a microchannel group.

[0108] Figures 36 - 37The following are the y-axis point array diagram and x-axis point array diagram of the anchor frame and the spiral refrigerant tube in the present invention projected on the bottom plate. N is the total number of turns of the tube; n is the number of turns to which a certain tube belongs; D is the diameter of the anchor frame; d is the diameter of the tube; H is the layer spacing in the y-axis direction between adjacent turns of the tube; L is the tube spacing in the x-axis direction between adjacent straight tube segments of the horizontal tubes in the same turn; l is the staggered layer spacing in the x-axis direction between different turns of the tube; S is the total height of the tubes in the y-axis direction in the same turn; s is the spacing of the anchor frame in the y-axis direction of the central layer (the fourth layer in this embodiment); E is the spacing of the side wings of the tubes in the y-axis direction in the same turn; M is the total distance of the straight tube segments of the horizontal tubes in the x-axis direction in the same turn; m is the distance in the x-axis direction between adjacent tubes in the same turn in the y-axis; b is the adjacent winding spacing of the tubes in the same turn; R is the diameter of the support section of the anchor frame; r is the diameter of the fixed section of the anchor frame; λ is the number of equal parts of the vertical side of the side wing; O is the origin (center point); β is the number of tubes in the X-axis direction; k is the number of equal parts of the tubes in the X-axis direction (except for adjacent tubes in the same turn in the y-axis).

[0109] Each point on the bottom plate, including the screw hole 301, the anchor frame point (the connection point of the fixed section of the anchor frame on the bottom plate), and the tube hole 302, presents a central symmetric layout with 0 as the origin. The center distance between adjacent anchor frame layers is equal to the layer spacing in the y-axis direction between adjacent turns of the tube, both being H, and the distance is the sum of the tube diameter d and the anchor frame diameter D, that is, H = D + d. The anchor frame should have sufficient strength to ensure that it does not deform when the tube is wound. The size of the diameter D of the winding section of the anchor frame determines the layer spacing. The diameter D of the anchor frame should be greater than the diameter d of the tube, that is, D > d; the lower side of the outer wall of the straight tube segment of the same turn of the tube is tangent to the upper side of the outer wall of the same layer of the anchor frame in the x-axis direction, and the inner side of the outer wall of the same turn of the tube is tangent to the outer side of the wall of the same layer of the anchor frame in the y-axis vertical direction; the outer walls of adjacent tubes are tangent to the outer wall of the anchor frame; the distance of the y-axis spacing Sn of the tubes in the same turn is the center anchor tube spacing s plus the sum of the diameters d of all tubes in the y-axis and the anchor frame diameter D minus the tube diameter d, that is, Sn = (s - d) + 2H(N - n + 1) = (s - d) + 2(D + d)(N - n + 1), where 0 ≤ s. When the anchor frame diameter D, the tube diameter d, and the number of turns N are determined, the s spacing determines the height of the total height S of the tubes in the y-axis direction in the same turn. In this case, the y-axis spacing S1 of the first turn of the tube = (s - d) + 8(D + d), the y-axis spacing S2 of the second turn of the tube = (s - d) + 6(D + d), the y-axis spacing S3 of the third turn of the tube = (s - d) + 4(D + d), the y-axis spacing S4 of the fourth turn of the tube = (s - d) + 2(D + d); the side wing spacing E of the tubes in the same turn is equally distributed, and adjacent winding layers are arranged in parallel. The tube spacing En of the same winding layer = Sn / λn. In this case, the side wing spacing E1 of the first turn of the tube = S1 / λ1, the side wing spacing E2 of the second turn of the tube = S2 / λ2, the side wing spacing E3 of the third turn of the tube = S3 / λ3, the side wing spacing E4 of the fourth turn of the tube = S4 / λ4, and En ≥ D + d / 2.

[0110] In the x-axis (horizontal) direction, the straight pipe segments of each turn and each column of tubes are arranged at equal distances between adjacent turns and columns (except for the adjacent columns at the central axis). L is the pipe distance in the x-axis direction between adjacent straight pipe segments of the horizontal columns in the same turn. The distance between adjacent columns at the central axis is mn, and mn = 2Ln = 2L[1 - (n - 1) / N]. In this example, for the first turn, m1 = 2L; for the second turn, m2 = 3 / 2L; for the third turn, m3 = L; for the fourth turn, m4 = 1 / 2L. The total distance between columns in the x-axis direction is Mn, and Mn = L*[k - 2(n - 1) / N]. In this case, for the first turn of columns, the total length M1 in the X-axis direction = kL; for the second turn of columns, the total length M2 in the X-axis direction = L(k - 1 / 2); for the third turn of columns, the total length M3 in the X-axis direction = L(k - 1); for the fourth turn of columns, the total length M4 in the X-axis direction = L(k - 3 / 2). The vertical columns on the side wings of each turn of columns are arranged in an equally divided staggered manner from the outside to the inside. The distance between the projections of adjacent straight pipe segments on the x-axis is equal, and the distance is l', which is the ratio of the pipe distance L in the x-axis direction between adjacent straight pipe segments of the horizontal columns in the same turn to the number of layers N. On the premise of ensuring winding, by maintaining the minimum staggered distance l', it can ensure that each layer has the largest horizontal cross-section and increase the heat exchange effect. In this case, l' =

[0111] L / 4; The distance ln between the side wings of different turns of columns in the x-axis direction = L[1 - (n - 1) / N], and L ≥ Nd. In this case, l1 = L; l2 = 3 / 4L; l3 = 1 / 2L; l4 = 1 / 4L.

[0112] The total distance M in the x-axis direction of the straight pipe segments of the horizontal columns in the same turn is greater than the total height S in the y-axis direction of the columns in the same turn, ensuring that the open-type spiral-wound condenser R3 has a relatively large evaporation surface A in the cross-section.

[0113] The heat exchange area of the open-type spiral-wound condenser R3 is calculated as follows:

[0114] The first step is to calculate the heat exchange quantity:

[0115] Given that the heat exchange quantity of the condenser is Qr, the heat consumed by the compressor is Qw, and the refrigerating capacity is Qc. According to the law of conservation of energy, we have:

[0116] Qr = Qw + Qc

[0117] The second step is to calculate the heat transfer area:

[0118] Given the thermal conductivity K, Tr is the average temperature of the hotter medium, and △t is the average temperature of the less hot medium. From the heat transfer formula, the heat exchange area is A. We get:

[0119] A = Qr / K(Tr - △t)

[0120] The third step is to calculate the length of the tubes:

[0121] Given the heat exchange area A and the tube diameter d, from the area formula, the total length L of each column winding; we get:

[0122] L = A / (dπ)

[0123] The number of tube bundles, the number of winding turns, and the winding pitch are adjusted according to the installation space, cross-sectional size, etc. The actual total length is not less than the designed length L.

[0124] This structure has a smaller volume, a higher winding density, and can obtain a longer extension length on the same axis compared with parallel tube in-line or spiral circular winding heat exchangers. It increases the tube pass, increases the heat transfer area A of a single tube bundle, and obtains more heat transfer quantity Qr = A * K(Tr - △t):

[0125] The axial spacing M in the x direction is greater than the spacing S in the y axis direction, which increases the cross-sectional area of the condenser, ensures that the cooling water tank has a larger evaporation area, and is convenient for the cooling water to vaporize and evaporate; the smaller staggered layer spacing l' between each turn of tube bundles not only ensures the uniform distribution of each layer of side wing columns, but also ensures that the cross-section of each winding layer is the largest, the winding amount increases, the total heat transfer area A increases, and more heat transfer quantity is obtained; Qr = A * K(Tr - △t);

[0126] While ensuring cleaning, maintaining the minimum tube bundle winding pitch b can increase the tube bundle density, make the microchannels formed by the upper and lower staggered layers smaller, and the heat transfer more sufficient;

[0127] Adjacent turns of tube bundles present a reverse winding structure, and the upper and lower layers of tube bundles form a baffling flow, increasing the disturbance of water, continuously changing the flow direction and flow velocity of the fluid, and can reach turbulence under a very low Reynolds number (Re < 100) condition, improving the heat transfer coefficient K and obtaining more heat transfer quantity; Qr = A * K(Tr - △t);

[0128] The anchor frame spacing between adjacent layers is designed at an equal distance H from the tube bundle layer spacing between adjacent layers. After each layer of tube bundles is wound, the adjacent windings and the anchor frame form a structure without spacing, making the entire condenser form a tight integrated structure and enhancing the overall strength of the condenser;

[0129] In summary: The open-type spiral winding condenser R3 has a compact structure, a small volume, a high heat transfer efficiency, and is easy to maintain.

[0130] Of course, the open-type spiral winding condenser R3 can be replaced by a spiral immersion condenser or a tube bundle immersion condenser.

[0131] The water distributor C3 adopts an H-type parallel multi-stage water distributor, which can be made of galvanized steel pipes, PUC pipes, PE and other metal pipes, plastic pipes, etc. It includes a water distributor main pipe C300, multi-stage branch pipes and several water heads C307 that are interconnected. Each lower-level branch pipe is perpendicularly connected to its upper-level branch pipe to form a multi-stage H-type structure. Several water heads are distributed at both ends of the last-stage branch pipe, finally enabling each water head C307 to be on the same horizontal plane, and each adjacent water head C307 to be equidistantly arranged, thus forming a uniform water head array. The other end of the water distributor main pipe C300 is connected to the cooling circulation pump C1. The cooling water that has been heated through heat exchange in the cooling water tank C6 passes through the uniformly distributed water heads C307, enters the multi-stage branch pipes and the water distributor main pipe C300, and finally enters the cooling circulation pump C1 and the sprayer C2 through the cooling pump guide pipe to enter the next cooling cycle. In this embodiment, as Figure 38 shown, the H-type multi-stage water distributor is a 6-stage water distributor, including a water distributor main pipe C300, a first-stage branch pipe C301, a second-stage branch pipe C302, a third-stage branch pipe C303, a fourth-stage branch pipe C304, a fifth-stage branch pipe C305, a sixth-stage branch pipe C306, and several water heads 307.

[0132] Using the H-type parallel multi-stage water distributor can make the low-temperature cooling water cooled on the surface of the cooling water tank move downward in the vertical direction on the same horizontal plane, ensuring that the low-temperature cooling water exchanges heat layer by layer with the refrigerant tubes downward. As the refrigerant in the tubes is cooled, the temperature of the cooling water gradually rises. Through the setting of the H-type parallel multi-stage water distributor, the disordered heat exchange between the cooling water and the refrigerant tubes can be effectively prevented, ensuring that the low-temperature cooling water vertically stratifies and flows through each layer of tubes on the same horizontal plane, thereby improving the cooling effect of the cooling water and the cooling efficiency of the refrigerant. According to Q absorption = V flow rate * S cross-sectional area * ρ density * △T temperature difference * C specific heat capacity; where V flow rate * S cross-sectional area is a constant value, ρ density and C specific heat capacity are constants. Since the cross-sectional area of the open cooling water tank is hundreds of times that of the cooling circulation pipe, the cooling water flow rate V flow rate decreases, and then the residence time of the cooling water in the tank is prolonged.

[0133] Although the embodiments of the present invention are described in the specification, these embodiments are only for reference and should not limit the protection scope of the present invention. All omissions, substitutions and changes made within the scope of the purpose of the present invention should be included in the protection scope of the present invention.

Claims

1. Integrated water-cooled and air-cooled heat pump modular unit, characterized in that, It includes a small cooling tower housing and a cooling system, a refrigerant circulation system, and functional modules assembled inside the small cooling tower housing; the cooling system includes a fan, a water distributor, a cooling circulation pump, a sprayer, a cooling filler layer, and a cooling water tank; the refrigerant circulation system includes a low-power compressor, an air-cooled finned heat exchanger, an open-type spiral-wound condenser, a four-way valve, an indoor-side heat exchanger, and a gas-liquid separator; the functional modules include a liquid storage tank, a dryer filter, and an electronic expansion valve connected by a number of one-way valves; the cooling water tank is arranged at the upper part inside the small cooling tower housing, and the low-power compressor, the liquid storage tank, the dryer filter, the electronic expansion valve, the number of one-way valves, and the indoor-side heat exchanger are arranged outside the cooling water tank; the small cooling tower housing includes a top plate, a base, a guard plate, and a water baffle installed around the upper part inside the guard plate, and the air-cooled finned heat exchanger is placed between the water baffle and the inner wall of the small cooling tower housing; the open-type spiral-wound condenser is immersed in the cooling water of the cooling water tank, the water distributor is arranged at the bottom inside the cooling water tank, the sprayer is arranged above the cooling filler layer, and the fan is arranged at the top of the small cooling tower housing; in the water-cooled refrigeration mode, the low-power compressor is connected to the air-cooled finned heat exchanger and the open-type spiral-wound condenser through the four-way valve, and then connected to the low-power compressor after passing through the functional modules, the indoor-side heat exchanger, the four-way valve, and the gas-liquid separator; in the air-cooled refrigeration mode, the low-power compressor is connected to the air-cooled finned heat exchanger through the four-way valve, and then connected to the low-power compressor after passing through the functional modules, the indoor-side heat exchanger, the four-way valve, and the gas-liquid separator; in the air-cooled heating mode, the low-power compressor is connected to the indoor-side heat exchanger through the four-way valve, and then connected to the low-power compressor after passing through the functional modules, the air-cooled finned heat exchanger, the four-way valve, and the gas-liquid separator; the open-type spiral-wound condenser includes a refrigerant collection box, a number of turns of spiral-shaped refrigerant tube windings, a number of layers of anchor frames, a refrigerant inlet pipe, and a refrigerant outlet pipe; the refrigerant collection box is composed of an end cover and a bottom plate, the length and width dimensions of the end cover and the bottom plate match each other and are both provided with flange plates of the same size on the outside, the flange plates are provided with a number of screw holes with matching sizes and positions, the middle of the bottom plate is provided with a number of tube holes, the middle of the end cover protrudes with a box-shaped part, and the bottom plate and the end cover are screwed and fastened together by bolts passing through the screw holes on the flange plates to form a cavity for refrigerant collection; the refrigerant collection box includes a steam-end collection box and a liquid-end collection box arranged oppositely, and a collection box refrigerant inlet and a collection box refrigerant outlet are respectively arranged above the side of the steam-end end cover and below the side of the liquid-end end cover; the refrigerant inlet pipe extends into the steam-end collection box through the collection box refrigerant inlet to form a steam distribution pipe, and small holes are evenly distributed along the lower edge of the steam distribution pipe so that the refrigerant steam is evenly sprayed into the entire steam-end collection box; the refrigerant outlet pipe is connected to the collection box refrigerant outlet, and a guide plate forming a certain angle with the bottom surface is arranged at the bottom of the liquid-end collection box so that the condensed refrigerant liquid flows into the refrigerant outlet pipe;The cooling water tank adopts an H-shaped parallel multi-stage water distributor, which includes a main water distribution pipe, multi-stage branch water pipes and several water distribution heads that are interconnected. Each lower-level branch water pipe of each stage is vertically connected to the upper-level branch water pipe above it to form a multi-stage H shape. Several water distribution heads are distributed at both ends of the last-stage branch water pipe, finally enabling each water distribution head to be on the same horizontal plane, and each adjacent water distribution head to be arranged at equal intervals, thereby forming a uniform water distribution head array. The other end of the main water distribution pipe is connected to the cooling circulation pump. The cooling water that has been heated through heat exchange in the cooling water tank passes through the uniformly distributed water distribution heads, enters the multi-stage branch water pipes and the main water distribution pipe, and finally enters the cooling circulation pump and the sprayer through the cooling pump diversion pipe to enter the next cooling cycle.

2. The integrated water-cooled and air-cooled heat pump modular unit according to claim 1, characterized in that, A drain valve and a drain port are provided at the bottom of the cooling water tank, and the drain port is connected to the lower part of the guard plate; a water replenishing port and a float valve are provided in the middle of the guard plate of the small cooling tower housing, and external cooling water enters through the water replenishing port, and the float valve switch automatically replenishes water into the cooling water tank when needed; a refrigerant water outlet and a refrigerant water inlet on the outside are provided at the lower part of the guard plate of the small cooling tower housing, which are respectively communicated with the refrigerant water inlet and outlet of the indoor heat exchanger; a control cabinet is provided at the lower part of the guard plate of the small cooling tower housing to control the electrical switch of the integrated water-cooled and air-cooled heat pump module unit.

3. The integrated water-cooled and air-cooled heat pump modular unit according to claim 1, characterized in that The small power compressor is a compressor with a power consumption of 5 - 25 KW, having an outlet and a return port; the indoor heat exchanger has P and Q interfaces; the several one-way valves include a first one-way valve, a second one-way valve, a third one-way valve, and a fourth one-way valve; the functional module has U and V interfaces; the air-cooled finned heat exchanger has X and Y interfaces, and the open-type spiral wound condenser has a header refrigerant inlet and a header refrigerant outlet; the four-way valve includes a, b, c, and d ports; in the water-cooled refrigeration mode, the outlet of the small power compressor enters through port a and exits through port b of the four-way valve, and is connected to the X interface of the air-cooled finned heat exchanger; the Y interface of the air-cooled finned heat exchanger passes through the first solenoid valve, enters through the header refrigerant inlet of the open-type spiral wound condenser and exits from the header refrigerant outlet, passes through the first one-way valve, the U interface of the functional module, the liquid storage tank, the dryer filter, and the V interface of the functional module, and is connected to the P interface of the indoor heat exchanger through the second one-way valve, and the Q interface of the indoor heat exchanger enters through port d and exits through port c of the four-way valve, and is connected to the return port of the small power compressor through the gas-liquid separator.

4. The integrated water-cooled and air-cooled heat pump modular unit according to claim 1, characterized in that The small power compressor is a compressor with a power consumption of 5 - 25 KW, having an outlet and a return port; the indoor heat exchanger has P and Q interfaces; the several one-way valves include a first one-way valve, a second one-way valve, a third one-way valve, and a fourth one-way valve; the functional module has U and V interfaces; the air-cooled finned heat exchanger has X and Y interfaces, and the open-type spiral wound condenser has a header refrigerant inlet and a header refrigerant outlet; the four-way valve includes a, b, c, and d ports; in the air-cooled refrigeration mode, the outlet of the small power compressor enters through port a and exits through port b of the four-way valve, and is connected to the X interface of the air-cooled finned heat exchanger, the Y interface of the air-cooled finned heat exchanger passes through the second solenoid valve, the first one-way valve, the U interface of the functional module, the liquid storage tank, the dryer filter, the electronic expansion valve, and the V interface of the functional module, and is connected to the P interface of the indoor heat exchanger through the second one-way valve, and the Q interface of the indoor heat exchanger enters through port d and exits through port c of the four-way valve, and is connected to the return port of the small power compressor through the gas-liquid separator.

5. The integrated water-cooled and air-cooled heat pump modular unit according to claim 1, wherein, The small-power compressor is a compressor with a power consumption of 5-25KW, having an outlet and a return port; the indoor heat exchanger has P and Q interfaces; the several check valves include a first check valve, a second check valve, a third check valve, and a fourth check valve; the function module has U and V interfaces; the air-cooled finned heat exchanger has X and Y interfaces, and the open-type spiral-wound condenser has a header refrigerant inlet and a header refrigerant outlet; the four-way valve includes a, b, c, and d ports; in the air-cooled heating mode, the outlet of the small-power compressor enters through port a and exits through port d of the four-way valve and is connected to the Q interface of the indoor heat exchanger. After the P interface of the indoor heat exchanger is connected to the third check valve, it passes through the U interface of the function module, the liquid receiver, the dryer filter, the electronic expansion valve, and the V interface of the function module, passes through the fourth check valve and the second solenoid valve, and is connected to the Y interface of the air-cooled finned heat exchanger. The X interface of the air-cooled finned heat exchanger enters through port b and exits through port c of the four-way valve, and is connected to the return port of the small-power compressor through the gas-liquid separator.

6. The integrated water-cooled and air-cooled heat pump modular unit according to claim 1, characterized in that, The indoor heat exchanger is replaced with an indoor multi-connected unit. At this time, the indoor multi-connected unit includes a refrigerant fin heat exchanger and an indoor fan. The indoor fan makes air flow through the surface of the refrigerant fin heat exchanger, and the refrigerant directly vaporizes to absorb the heat of the indoor air and cool down.

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