Integrated water-cooled low-temperature air-cooled heat pump modular unit

Abstract

The present invention discloses an integrated water-cooled low-temperature air-cooled heat pump modular unit, which includes a small cooling tower housing and a cooling system, a refrigerant circulation system, and a functional module 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, an indoor heat exchanger, and a gas-liquid separator; the functional module includes a liquid storage tank, a drying filter, an economizer, and a number of electronic expansion valves connected to each other; the small-power compressor is connected to the open-type spiral wound condenser, a three-way valve, and the air-cooled finned heat exchanger through a four-way valve and then divided into a main circuit and an auxiliary EVI circuit. The main circuit is connected to the small-power compressor after passing through the functional module, the indoor heat exchanger, and the gas-liquid separator, and the auxiliary EVI circuit is directly connected to the small-power compressor through the functional module.

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 mix air-cooled and water-cooled methods. Background Art

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

[0003] Since water-cooled units have significant energy-saving effects compared to air-cooled chillers, and most water-cooled chillers use screw compressors or centrifugal compressors, the refrigeration capacity of a single unit is at least several hundred kilowatts and at most several thousand kilowatts, with a powerful refrigeration capacity. 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 low-temperature air-cooled heat pumps that can supply both cooling and heating, 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 prior art still has the following problems:

[0004] First, although water-cooled units are about 30% more energy-saving 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 to solve the refrigeration and heating in summer-hot and winter-cold regions (below -15°C) have the following problems:

[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 of 200KW - 1000KW or more), and the unit weight is at least one or two tons and at most several tons, so the volume is large and the installation and transportation are inconvenient; the water-cooled refrigeration unit machine room 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 main unit 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 a strong construction professionalism, increases the construction difficulty, and the excessive length of the cooling circulation pipe network construction workload leads to an increase in construction costs.

[0006] 2. Reduction in building utilization rate due to occupation of the main building space. The refrigeration host, the circulating system composed of the make-up water system and the chilled water pump, the circulating system composed of the cooling water pump, and the electric control system require specific machine rooms. The installation floor area ranges from hundreds of square meters to thousands of square meters, resulting in a waste of the effective usable area of the main building and a reduction in the utilization rate of the main building. In today's situation where the supply of land resources is tight and real estate regulation is becoming increasingly strict, reducing the land use area and improving the utilization rate of buildings is of great significance. In engineering practice, due to indoor space limitations caused by various reasons in some newly built or renovated buildings, it is impossible to install the refrigeration host indoors, and an air-cooled unit alternative is adopted, which greatly increases the air-conditioning refrigeration operation cost.

[0007] 3. Poor operation stability and difficult maintenance of a single unit. Since water-cooled chillers have a large power, strong refrigeration capacity, and a high unit price, in order to improve operation stability, a single-unit dual-compressor head is used instead of a one-for-one standby unit or a multi-unit parallel combined refrigeration method. When the refrigeration host fails or needs maintenance, there is no available unit, resulting in a reduction in the stability of the refrigeration system. Moreover, water-cooled chillers are not easy to maintain and the maintenance cost is high.

[0008] 4. High energy consumption of the circulation pump due to the separation of the chiller's refrigeration system and cooling system, resulting in a long cooling pipe network. Due to the large height difference between the refrigeration host and the cooling tower and the long cooling circulation water pipe network, the frictional resistance along the cooling water increases, the head of the cooling circulation pump increases, and then the power of the circulation pump increases, resulting in a corresponding increase in energy consumption. In addition, most existing chillers use shell-and-tube heat exchangers, and the relatively high flow rate causes a large pressure difference between the fluid inlet and outlet, increasing the fluid resistance in the shell, and the increased frictional resistance increases the energy consumption of the circulation pump.

[0009] 5. The efficiency of the traditional shell-and-tube condenser in the chiller needs to be improved. Since the heat exchange between the refrigerant and the cooling medium is completely carried out inside the closed shell of the heat exchanger, it is not conducive to the vaporization and evaporation of the cooling medium (water). Therefore, the vaporization latent heat evaporation capacity of water is reduced, thereby reducing the cooling effect of water.

[0010] 6. Serious noise pollution. The noise of the chiller mainly comes from the compressor and the circulation pump. When high-power compressors and refrigeration and cooling circulation pumps operate in the same machine room, the noise and vibration generated are serious. In order to reduce noise pollution, professional noise reduction treatment must be carried out. This not only increases the construction cost of the machine room but also reduces the comfort of building use.

[0011] 7. The initial investment of the cold and heat dual-supply solution of chiller + boiler increases for a set of systems with two sets of equipment, and coal-fired and gas-fired boilers cause environmental pollution. The method of using a water-cooled chiller + heating boiler is the main solution to meet the refrigeration and heating needs in areas with hot summers and cold winters. In winter in cold regions (below -15°C), since the heating time accounts for about 1 / 2 of the annual operation time, the long use time of the boiler causes serious environmental pollution.

[0012] II. Air-cooled heat pump (cooling and heating) units have a two-way regulation function of refrigeration and heating. They can not only meet the refrigeration needs in summer, but also meet the heating requirements in winter and are widely used in the market. However, for areas with hot summers and cold winters, since the refrigeration time and heating time are each half, although the use of air-cooled heat pump (cooling and heating) units in such areas can solve the heating problem in winter, due to the fact that the air-cooled refrigeration efficiency is 30% lower than that of the water-cooled form, the increase in refrigeration cost leads to a higher annual energy consumption. Therefore, a 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 low-temperature air-cooled heat pump modular unit, which solves the problems of large cooling water consumption and low heat exchange efficiency of the chiller, the waste of large chiller plant area occupying indoor space resulting in reduced building utilization rate, the high construction difficulty and increased construction cost caused by the separation of the cooling tower and the chiller, the inconvenience of transportation, installation and maintenance of large chillers, the high energy consumption of the cooling pump leading to a reduction in the overall refrigeration efficiency of the unit, the high noise of the chiller and the easy generation of noise pollution, etc., and solves the problem of low refrigeration efficiency of the air-cooled heat pump for heating.

[0014] To solve the above technical problems, the technical solution adopted by the present invention is as follows:

[0015] Integrated water-cooled low-temperature 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 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 economizer, a number of electronic expansion valves, a number of check valves, and a three-way valve that are interconnected; the cooling water tank is provided at the upper part inside the small cooling tower housing, and the small-power compressor, the liquid storage tank, the drying filter, a number of electronic expansion valves, a number of check valves, the three-way valve, and the indoor heat exchanger are provided 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 provided at the bottom inside the cooling water tank; the sprayer is provided above the cooling filler layer for spraying water and absorbing heat on the surface of the cooling filler layer; the fan is provided at the top of the small cooling tower housing to discharge the refrigerant heat of the cooling filler 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 open-type spiral wound condenser, the three-way valve, and the air-cooled finned heat exchanger through a four-way valve and is divided into a main circuit and an auxiliary EVI circuit. The main circuit 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, and the auxiliary EVI circuit is directly connected to the small-power compressor through the functional modules.

[0016] Alternatively, the small-power compressor is connected to the indoor heat exchanger through a four-way valve and is divided into a second main circuit and a second auxiliary EVI circuit. The second main circuit is connected to the small-power compressor after passing through the functional modules, the air-cooled finned heat exchanger, the three-way valve, the four-way valve, and the gas-liquid separator, and the second auxiliary EVI circuit is directly connected to the small-power compressor through the functional modules.

[0017] Alternatively, the small-power compressor is connected to the air-cooled finned heat exchanger through a four-way valve and a three-way valve and is divided into a third main circuit and a third auxiliary EVI circuit. The third main circuit 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, and the third auxiliary EVI circuit is directly connected to the small-power compressor through the functional modules.

[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 valve and a sewage outlet are provided at the bottom of the cooling water tank, and the sewage outlet 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 automatically replenishes water into the cooling water tank through the float valve switch when needed; a chilled water outlet and a chilled water inlet outside are provided at the lower part of the guard plate of the small cooling tower housing, which are respectively communicated with the chilled water inlets and outlets 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 switches of the integrated water-cooled low-temperature air-cooled heat pump module unit.

[0019] Further, the small-power compressor is an injection-enhanced enthalpy compressor with a power consumption of 5-25KW, having an outlet, a return port, and an EVI 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, and the several electronic expansion valves include a first electronic expansion valve and a second electronic expansion valve; the functional module has U, V, and W 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 ends, and the three-way valve includes e, f, and g ends; the economizer R11 includes h, i, j, and k 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 header refrigerant inlet of the open-type spiral-wound condenser; the header refrigerant outlet of the open-type spiral-wound condenser enters through the f end and exits through the e end of the three-way valve and is connected to the X interface of the air-cooled finned heat exchanger; after the Y interface of the air-cooled finned heat exchanger is connected to the first one-way valve, it is divided into a main circuit and an auxiliary EVI circuit. The main circuit is through the U interface of the functional module, the liquid storage tank, the dryer filter, enters through the j end and exits through the k end of the economizer, passes through the second electronic expansion valve and the V interface, and then is connected to the P interface of the indoor heat exchanger through the second one-way 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, passes through the gas-liquid separator and is connected to the return port of the small-power compressor; the auxiliary EVI circuit is through the U interface, the liquid storage tank, the dryer filter, the first electronic expansion valve, enters through the h end and exits through the i end of the economizer, passes through the W interface, and then is connected to the EVI return port of the small-power compressor.

[0021] Alternatively, the outlet of the small-power compressor enters through the a end of the four-way valve and exits through the d end, 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 is divided into a second main circuit and a second auxiliary EVI circuit. The second main circuit is from the U interface of the functional module, through the liquid storage tank, the dryer filter, enters through the j end and exits through the k end of the economizer, passes through the second electronic expansion valve and the V interface, and is connected to the Y interface of the air-cooled finned heat exchanger through the fourth check valve. The X interface of the air-cooled finned heat exchanger enters through the e end and exits through the g end of the three-way valve, enters through the b end and exits through the c end of the four-way valve, and is connected to the return port of the small-power compressor through the gas-liquid separator. The second auxiliary EVI circuit is from the U interface, through the liquid storage tank, the dryer filter, the first electronic expansion valve, enters through the h end and exits through the i end of the economizer, passes through the W interface, and is then connected to the EVI return port of the small-power compressor.

[0022] Alternatively, the outlet of the small-power compressor enters through the a end of the four-way valve and exits through the b end, enters through the g end and exits through the e end of the three-way valve, and is connected to the X interface of the air-cooled finned heat exchanger. After the Y interface of the air-cooled finned heat exchanger is connected to the first check valve, it is divided into a third main circuit and a third auxiliary EVI circuit. The third main circuit is from the U interface of the functional module, through the liquid storage tank, the dryer filter, enters through the j end and exits through the k end of the economizer, passes through the second electronic expansion valve and the V interface, and is then 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 return port of the small-power compressor through the gas-liquid separator. The third auxiliary EVI circuit is from the U interface, through the liquid storage tank, the dryer filter, the first electronic expansion valve, enters through the h end and exits through the i end, passes through the W interface, and is then connected to the EVI return port of the small-power compressor.

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

[0025] Further, the connection modes between the small-power compressor, the open-type spiral-wound condenser, and the air-cooled finned heat exchanger can be adjusted adaptively in various ways according to actual needs. For example, an air-cooling priority mode can be adopted. The high-temperature and high-pressure refrigerant vapor ejected from the small-power compressor first enters the air-cooled finned heat exchanger to exchange heat with air and is preliminarily condensed into medium-temperature and high-pressure refrigerant liquid, which enters the open-type spiral-wound condenser through the e-end inlet and f-end outlet of the three-way valve to exchange heat with cooling water. After the refrigerant further cools down and reduces pressure, it flows out; or, the air-cooled finned heat exchanger and the open-type spiral-wound condenser are connected in parallel. 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, and then the refrigerant becomes high-temperature and high-pressure liquid and enters the liquid storage tank.

[0026] Preferably, the open-type spiral condenser includes a refrigerant collection box, several turns of spiral-shaped refrigerant tube windings, several 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 flange plates of the same size are provided on the outside. A number of screw holes with matching sizes and positions are provided on the flange plates. A number of tube holes are opened in the middle of the bottom plate, and 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 collection box includes a steam-end collection box and a liquid-end collection box arranged oppositely. A collection box refrigerant inlet and a collection 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 collection box through the collection 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 collection box, ensuring that each turn of the spiral-shaped 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 collection box refrigerant outlet. A deflector 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, facilitating the liquid outflow of the refrigerant and preventing the occurrence of liquid accumulation phenomenon, and improving the utilization efficiency of the refrigerant.

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

[0028] Preferably, an H-shaped parallel multi-stage water distributor is adopted in the cooling water tank, which includes a main water distribution pipe, multi-stage branch water pipes and a number of water heads that are interconnected. Each lower-level branch water pipe of each stage is vertically connected to its upper-level branch water pipe to form a multi-stage H shape. The number of water heads are distributed at both ends of the last-stage branch water pipe, finally realizing that each water head is on the same horizontal plane, and each adjacent water head is arranged at equal intervals, thereby forming a uniform water 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 passes through the uniformly distributed water 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 guide pipe to enter the next cooling cycle. The adoption of the H-shaped parallel 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 parallel 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 flows vertically and in layers 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 * ΔT 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 the 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; after 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 absorbs the technology of steam-injected enthalpy-increasing low-temperature air-cooled heat pump, and an air-cooled finned heat exchanger is added inside the outer wall guard plate of the unit, solving the problem that the air-cooled heat pump (cold and hot water) unit has a high summer operation cost due to its two-way regulation function of refrigeration and heating to meet the summer refrigeration and winter heating requirements. The unit of the present invention can reduce the summer refrigeration operation 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 low-temperature air-cooled heat pump modular unit, fundamentally solving the following problems of traditional chillers:

[0030] 1. The installation and transportation of a unit weighing several tons with a large volume are inconvenient. Since the present invention uses a scroll compressor or a small-power screw compressor to miniaturize and modularize a large chiller, 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 poor stability and difficult maintenance due to the small number of units equipped. The modular units operate simultaneously and are used as spares 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 high elevation 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. A high-lift circulation pump is used, leading to high power consumption. Placing the cooling tower and the refrigeration host on the same adjacent plane will obviously greatly reduce the lift and the 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 relatively 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. By using a modular unit with an open-type spiral-wound high-efficiency cooling system, since an open-type spiral-wound condenser is used, the self-gravity flow of the cooling water is utilized 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. By using a modular water chiller with an open-type spiral-wound high-efficiency cooling system, the cooling tower and the host are combined into one. Although it will increase the total cost of the host, industrialized production and scale advantages can effectively reduce the manufacturing cost per unit. This transfer of downstream costs to upstream, that is, "cost front-loading", reduces the construction cost, facilitates the construction of engineering companies, reduces the construction difficulty, and is conducive to the promotion by engineering contractors. Moreover, after adding a heat pump function to the refrigeration unit, the usage function is increased and the cost performance of the unit is improved.

[0035] 6. In particular, by using an open-type spiral-wound high-efficiency cooling system, the common shell-and-tube heat exchanger of the water-cooled unit is replaced with an open-type spiral-wound heat exchanger to replace the shell-and-tube (double-pipe) closed heat exchanger, enabling a part of the latent heat of vaporization generated by the heat exchange between the refrigerant and the cooling water to be released into the air through the water surface of the water tank. Utilizing the latent heat of vaporization of water increases the heat transfer 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 cleaning and maintaining the condenser.

[0037] 8. High noise. In civil buildings, the central air conditioner is the largest noise source. To solve the noise pollution, professional and systematic anti-pollution treatment must be carried out on the air-conditioning machine room, which increases the construction cost and requires round-the-clock professional personnel on duty, increasing the usage cost during operation. By using a modular unit with an open-type spiral-wound high-efficiency cooling system (the unit of the present invention), the unit only needs to be installed on the roof of the 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. Moreover, the host operates fully automatically without the need for special personnel on duty, thus reducing the construction and usage costs.

[0038] 9. Serious waste of cooling water. The sources of cooling water consumption include three aspects: evaporation consumption of cooling water, sewage discharge consumption, and "flying water". Among them, "flying water" is a non-beneficial 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, the more water is carried away by the fan from the spraying water, thus causing waste. The unit of the present invention adopting an open-type spiral-wound high-efficiency cooling system realizes 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, which can effectively reduce the cooling water circulation volume, lower the wind speed, and thus reduce 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, and avoid 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 "micro-channel" group with an upper and lower 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 due to its own gravity flow and the traction of the cooling circulation pump, it continuously changes the local flow rate and flow direction, generating a folding flow and disturbance, forming a turbulent flow and chaotic flow state. Turbulence can be achieved under 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 incorporates the steam-injected enthalpy-increasing low-temperature air-cooled heat pump technology, an air-cooled finned heat exchanger is added inside the outer wall guard plate of the unit. Through optimized refrigerant pipeline and system design, the heat pump heating function is achieved on the premise of ensuring water-cooled refrigeration, fundamentally solving the defect that traditional water-cooled chillers cannot provide heating, and replacing the solution of using chillers + boilers for both cooling and heating in summer-heat and winter-cold regions. This avoids the increase in initial investment for two sets of equipment in one system and the environmental pollution caused by coal-fired and gas-fired boilers. Secondly, in summer-heat and winter-cold regions, the refrigeration time and heating time are each half, and the use of air-cooled heat pump (cooling and heating) units in such regions greatly increases the summer refrigeration cost. The unit of the present invention solves the problem that air-cooled heat pump (cooling and heating) units have a two-way regulation function of refrigeration and heating to meet the summer refrigeration and winter heating requirements, but the summer operating cost is high. 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 It is a schematic diagram of the refrigeration mode principle of the integrated water-cooled low-temperature air-cooled heat pump module unit of the present invention.

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

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

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

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

[0046] Figure 6 It is an enlarged schematic diagram of the three-way valve in the present invention.

[0047] Figure 7 It is an enlarged schematic diagram of the economizer in the present invention.

[0048] Figure 8 It is an enlarged schematic diagram of the indoor heat exchanger R9 in the present invention.

[0049] Figure 9 It is a schematic diagram of the side sectional structure of the integrated water-cooled low-temperature air-cooled heat pump module unit of the present invention.

[0050] Figure 10 It is a schematic diagram of the front sectional structure of the integrated water-cooled low-temperature air-cooled heat pump module unit of the present invention.

[0051] Figure 11 It is a top view schematic diagram of the integrated water-cooled low-temperature air-cooled heat pump module unit of the present invention.

[0052] Figure 12 It is a side sectional structure schematic diagram of the integrated water-cooled low-temperature air-cooled heat pump multi-connected (direct expansion) module unit of the present invention.

[0053] Figure 13 It is a top view of the overall assembly of the open-type spiral-wound condenser in the present invention.

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

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

[0056] Figure 16 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.

[0057] Figure 17 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.

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

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

[0060] Figure 20 It is a right side internal view sectional drawing of the end cover of the steam end header in the present invention.

[0061] Figure 21 It is a right side internal view sectional drawing of the end cover of the liquid end header in the present invention.

[0062] Figure 22 It is a schematic diagram of the position layout of the anchor frame and the straight pipe section of the spiral refrigerant tube projected on the bottom plate (left view or right view) in the present invention.

[0063] Figure 23 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).

[0064] Figure 24 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).

[0065] Figure 25 It is a side view of the refrigerant collection box and the anchor frame position distribution in the present invention.

[0066] Figure 26 It is a top side view of the refrigerant collection box and the anchor frame position distribution in the present invention.

[0067] Figure 27 It is a schematic structural diagram of each anchor frame in the present invention.

[0068] Figure 28 It is a partially enlarged schematic view of the connection between the anchor frame and the bottom plate of the refrigerant collection box in the present invention.

[0069] Figure 29 It is a side view of the first turn of the spiral refrigerant tube winding in the present invention.

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

[0071] Figure 31 is Figure 19 A partially enlarged schematic view of one end of the steam end collection box in

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

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

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

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

[0076] Figure 36 It is a side view of the fourth turn of the spiral refrigerant tube winding in the present invention.

[0077] Figure 37 It is a top side view of the fourth turn of the spiral refrigerant tube winding in the present invention.

[0078] Figure 38 It is a Y-axis point array diagram of the projection of the anchor frame and the spiral refrigerant tube on the bottom plate in the present invention.

[0079] Figure 39 It is an X-axis point array diagram of the projection of the anchor frame and the spiral refrigerant tube on the bottom plate in the present invention.

[0080] Figure 40It is a schematic top view structure diagram of the H-type parallel multi-stage water distributor in the present invention.

[0081] Wherein: R1, small power compressor; 11, outlet; 12, return port; 13, EVI return port; R2, four-way valve; R4, air-cooled finned heat exchanger; R5, liquid storage tank; R6, dryer filter; R7, first electronic expansion valve; R8, second electronic expansion valve; R9, indoor heat exchanger; R91, indoor freezing circulation pump; R9a, indoor multi-connected unit; R10, gas-liquid separator; R11, economizer; R13, three-way valve; R121, first one-way valve; R122, second one-way valve; R123, third one-way valve; R124, fourth one-way valve;

[0082] R3, open-type spiral wound condenser; 30, refrigerant collecting box; 30a, end cover; 30b, bottom plate; 30-1, steam end collecting box; 30-2, liquid end collecting box; 30a-1, steam end cover; 30a-2, liquid end cover; 30b-1, steam end bottom plate; 30b-2, liquid end bottom plate; 31, refrigerant inlet pipe; 32, refrigerant outlet pipe; 31a, air distribution pipe; 32a, deflector; 33, anchor frame; 33-1, anchor frame fixing section; 33-2, anchor frame support section; 33.1, first layer anchor frame; 33.2, second layer anchor frame; 33.3, third layer anchor frame; 33.4, fourth layer anchor frame; 34, spiral refrigerant tube; 34-1, straight tube inlet section; 34-2, straight tube outlet section; 34-3, spiral section; 34.1, first turn of spiral refrigerant tube winding; 34.2, second turn of spiral refrigerant tube winding; 34.3, third turn of spiral refrigerant tube winding; 34.4, fourth turn of spiral refrigerant tube winding; 300, flange plate; 301, screw hole; 302, tube hole; 303, box-shaped part; 306, collecting box refrigerant inlet; 307, collecting box refrigerant outlet; 308, bolt;

[0083] 330, anchor frame rectangular structure; 340, tube rectangular structure; O, center point of the bottom plate; D, anchor frame diameter; d, spiral refrigerant tube diameter; H, layer spacing in the y-axis direction between adjacent turns of tubes; L, tube distance in the x-axis direction between adjacent straight tube sections of the same turn of horizontal tubes; l, distance in the x-axis direction between the side wings of different turns of tubes; S, total height in the y-axis direction of the same turn of tubes; s, distance in the y-axis direction of the center layer (fourth layer) anchor frame; E, distance in the y-axis direction between the side wings of the same turn of tubes; M, total distance in the x-axis direction of the straight tube sections of the same turn of horizontal tubes; m, distance in the x-axis direction between adjacent turns of tubes in the y-axis direction; b, adjacent winding spacing of the same turn of tubes; R, anchor frame support section diameter; r, anchor frame fixing section diameter;

[0084] C1, cooling circulation pump; C2, sprinkler; C3, water distributor; C4, fan; C5, small cooling tower shell; C6, cooling water tank; C7, cooling filler layer;

[0085] 51. Top plate; 52. Base; 53. Water baffle; 55. Control cabinet; 56. Drain valve; 57. Drain port; 541. Make-up water port; 542. Float valve; 543. Chilled water outlet; 544. Chilled water inlet;

[0086] 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. Specific embodiments

[0087] The present invention will be further described in detail below in conjunction with specific embodiments.

[0088] 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 small-power compressor R1, an air-cooled finned heat exchanger R4, an open-type spiral-wound condenser R3, a four-way valve R2, an indoor-side heat exchanger R9, and a gas-liquid separator R10; the functional modules include a liquid storage tank R5, a dryer filter R6, an economizer R11, a plurality of electronic expansion valves, a plurality of check valves, and a three-way valve R13 that are interconnected; the cooling water tank C6 is arranged at the upper part inside the small cooling tower housing C5, and the small-power compressor R1, the liquid storage tank R5, the dryer filter R6, the plurality of electronic expansion valves, the plurality of check valves, the three-way valve R13, and the indoor-side 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 at 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 small-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 small-power compressor R1 after passing through the functional modules, the indoor-side heat exchanger R9, the four-way valve R2, and the gas-liquid separator R10, and the auxiliary EVI circuit is directly connected to the small-power compressor R1 through the functional modules.

[0089] Or, as Figure 2 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.

[0090] Or, as Figure 3 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, the four-way valve R2, and the gas-liquid separator R10. The third auxiliary EVI circuit is directly connected to the small power compressor R1 through the functional module.

[0091] As Figures 4 - 7 shown, the small power compressor R1 is a liquid injection enhanced enthalpy compressor with a power consumption of 5-25KW, having an outlet 11, a return port 12, and an EVI return port 13; the four-way valve R2 includes ports a, b, c, and d; the three-way valve R13 includes ports e, f, and g; the economizer R11 includes ports h, i, j, and k; the indoor heat exchanger R9 has interfaces P and Q;

[0092] 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 several electronic expansion valves include a first electronic expansion valve R7 and a second electronic expansion valve R8; the functional module has interfaces U, V, and W; 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;

[0093] As Figures 9 - 11As 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 sewage valve 56 and a sewage outlet 57 are provided at the bottom of the cooling water tank C6, and the sewage outlet 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; a refrigerated water outlet 543 and a refrigerated water inlet 544 outside are provided at the lower part of the guard plate of the small cooling tower housing C5, which are respectively communicated with the refrigerated 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 low-temperature air-cooled heat pump module unit.

[0094] 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 refrigerant inlet 306 of the collecting box of the open-type spiral-wound condenser R3; the refrigerant outlet 307 of the collecting box of the open-type spiral-wound condenser R3 enters through the f end and exits through the e end of the three-way valve R13, and is connected to the X interface of the air-cooled finned heat exchanger R4; after the Y interface of the air-cooled finned heat exchanger R4 is connected to the first check valve R121, it is divided into a main circuit and an auxiliary EVI circuit. The main circuit is through the U interface of the functional module, the liquid storage tank R5, the dryer filter R6, enters through the j end and exits through the k end of the economizer R11, passes through the second electronic expansion valve R8 and the V interface, and then 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; the auxiliary EVI circuit is through the U interface, the liquid storage tank R5, the dryer filter R6, the first electronic expansion valve R7, enters through the h end and exits through the i end of the economizer R11, passes through the W interface, and then is connected to the EVI return port 13 of the small power compressor R1. The specific correspondence is as Figure 1 shown in the refrigeration mode:

[0095] In this mode, the four-way valve of the refrigerant circulation system has its R2a-b ends and c-d ends connected; the three-way valve R13 has its e-f ends connected; the compressor R1 is in operation; the small-power compressor R1 is energized and operates. The high-temperature and high-pressure gaseous refrigerant ejected from its outlet 11 enters through the a end of the four-way valve R2 and exits through the b end, and then enters the vapor collection port (collecting tank refrigerant inlet 306) of the open-type spiral-wound condenser R3. The high-temperature refrigerant flows through the surrounding tube bundles and exchanges heat with the cooling water in the cooling water tank C6 to be initially condensed and cooled, and then becomes a medium-temperature and high-pressure mixed liquid, which flows out from the liquid collection port (collecting tank refrigerant outlet 307) of the open-type spiral-wound condenser R3 and enters the air-cooled finned heat exchanger R4 to exchange heat with the circulating air again for cooling and condensation. At this time, the refrigerant is completely condensed and liquefied, and its pressure and temperature are further reduced. At this time, the high-temperature and high-pressure refrigerant steam is completely phase-changed into a medium-temperature and medium-pressure liquid refrigerant, and successively passes through the liquid storage tank R5 and the drying filter R6 and then is divided into two paths: the main-circuit refrigerant enters through the j end and exits through the k end of the economizer R11, exchanges heat with the refrigerant in the secondary circuit on the other side of the economizer R11 to be further condensed and cooled, and its pressure is further reduced after flowing through the second 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, and the liquid refrigerant is vaporized after heating up to become refrigerant steam, which flows through the d end of the three-way valve R2 and enters through the c end, passes through 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; in the auxiliary EVI circuit, the refrigerant is throttled and depressurized by the first electronic expansion valve R7, enters through the h end and exits through the i end of the economizer R11, exchanges heat with the refrigerant on one side of the main circuit to be vaporized and heated up to become a medium-temperature and low-pressure steam, returns to the EVI return port 13, and enters the small-power compressor R1 to complete one cycle.

[0096] In this refrigeration mode, the fan C4 in the cooling cycle 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 that has exchanged heat with the air-cooled 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 carried 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 heat exchanger R4 to be initially condensed, liquefied, and cooled. 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 that has been initially cooled in the refrigerant tubes through each refrigerant tube winding layer, and the refrigerant is completely condensed and liquefied. The temperature of the cooling water gradually increases as it moves downward. Since the rate of the cooling water layer moving downward is relatively low, the residence time of the cooling water in the cooling water tank C6 is extended. When the cooling water layer descends 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, lower 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. 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 each branch pipe converges to the main pipe and enters the cooling circulation pump C1. Then, it enters 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.

[0097] Alternatively, the outlet 11 of the low-power compressor R1 enters from the a end and exits from 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 is divided into a second main circuit and a second auxiliary EVI circuit. The second main circuit passes through the U interface of the functional module, the liquid storage tank R5, the dryer filter R6, enters from the j end and exits from the k end of the economizer R11, passes through the second electronic expansion valve R8 and the V interface, and passes through the fourth check valve R124 to be connected to the Y interface of the air-cooled finned heat exchanger R4. The X interface of the air-cooled finned heat exchanger R4 enters from the e end and exits from the g end of the three-way valve R13, enters from the b end and exits from the c end of the four-way valve, and is connected to the return port 12 of the low-power compressor R1 through the gas-liquid separator R10. The second auxiliary EVI circuit passes through the U interface, the liquid storage tank R5, the dryer filter R6, the first electronic expansion valve R7, enters from the h end and exits from the i end of the economizer R11, passes through the W interface, and then is connected to the EVI return port 13 of the low-power compressor R1. The specific correspondence is as Figure 2 shown in the air-cooled heating mode:

[0098] In this mode, the a-d end and c-b end of the four-way valve R2 of the refrigerant circulation system are connected; the e-g end of the three-way valve R13 is connected. The low-power compressor R1 is powered on and operates. The high-temperature and high-pressure gaseous refrigerant ejected from its outlet 11 enters the indoor heat exchanger R9 after entering from the a end and exiting from the d end of the four-way valve R2. After the high-temperature and high-pressure refrigerant vapor exchanges heat with the indoor refrigerant (water) flowing through this indoor heat exchanger R9, the refrigerant is condensed and liquefied at this time, the temperature and pressure of the refrigerant vapor decrease, and the high-temperature and high-pressure refrigerant vapor undergoes a phase change to become a medium-temperature and medium-pressure liquid refrigerant. Through the third check valve R123, it passes through the liquid storage tank 5 and the dryer filter 6 in sequence and is divided into two paths: the refrigerant in the second main circuit enters from the j end and exits from the k end of the economizer R11 and exchanges heat with the refrigerant in the secondary circuit on the other side of the economizer R11 to be further condensed and cooled. After flowing through the second electronic expansion valve R8, the pressure further decreases. The low-temperature and low-pressure refrigerant liquid enters the air-cooled finned heat exchanger R4 through the fourth check valve R124. After the low-temperature and low-pressure liquid refrigerant exchanges heat with the air flowing through the surface of this air-cooled finned heat exchanger R4, the liquid refrigerant is heated and vaporized into refrigerant vapor, flows through the e end and exits from the g end of the three-way valve R13, enters from the b end and exits from the c end of the four-way valve, enters the gas-liquid separator R10, and then returns to the return port 12 of the compressor R1 to end the main refrigerant cycle and enter the next cycle. In the second auxiliary EVI circuit, the refrigerant is throttled and depressurized by the first electronic expansion valve R7, enters from the h end and exits from the i end of the economizer R11, exchanges heat with the refrigerant on one side of the second main circuit, is vaporized and heated, and then becomes a medium-temperature and low-pressure steam and returns to the EVI return port 13 and enters the low-power compressor R1 to complete one cycle.

[0099] Alternatively, 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, enters through the g end and exits through the e end of the three-way valve R13, and is connected to the X interface of the air-cooled finned heat exchanger R4. After the Y interface of the air-cooled finned heat exchanger R4 is connected to the first one-way valve R121, it is divided into a third main circuit and a third auxiliary EVI circuit. The third main circuit enters through the U interface of the functional module, the liquid storage tank R5, the drying filter R6, and the j end and k end of the economizer R11, and is connected to the second electronic expansion valve R8. And V interface, and then 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 third auxiliary EVI loop enters through the h end and exits through the i end of the U interface, the liquid storage tank R5, the drying filter R6, the first electronic expansion valve R7, and the economizer R11, and is connected to the EVI reflux port 13 of the low-power compressor R1 through the W interface. The specific correspondence is as follows Figure 3 The air-cooled heat pump defrost mode shown:

[0100] In this mode, the ab and cd ends of the four-way valve R2 of the refrigerant circulation system are connected; the ef end of the three-way valve R13 is connected; the small-power compressor R1 is powered on and works, and the high-temperature and high-pressure gaseous refrigerant ejected from its outlet enters through the a end and exits through the b end of the four-way valve R2, then enters through the g end and exits through the e end of the three-way valve R13, and enters the air-cooled fin heat exchanger R4. Since the refrigerant vapor is around 90°C, the ice condensed on the surface of the air-cooled fin heat exchanger R4 is melted and discharged from the machine body through the drainage pipe to achieve the purpose of defrosting. At this time, the refrigerant is condensed and liquefied, and the pressure and temperature are further reduced. At this time, the high-temperature and high-pressure refrigerant vapor completely changes phase into a medium-temperature and medium-pressure liquid refrigerant, and is divided into two paths after passing through the liquid storage tank 5 and the drying filter 6 in turn: the refrigerant in the third main circuit enters through the k end and exits through the j end of the economizer R11, and is further condensed and cooled by heat exchange with the refrigerant in the secondary circuit on the other side of the economizer R11. After passing through the second electronic expansion valve R8, the pressure is further reduced. The low-temperature and low-pressure refrigerant liquid passes through the second one-way valve R122 and enters the indoor heat exchanger R9. The low-temperature and low-pressure liquid refrigerant is in the indoor heat exchanger R9. It exchanges heat with the refrigerant water flowing through this heat exchanger, and the hot water cools down. The liquid refrigerant is heated up and then vaporized to become refrigerant steam, flowing through the d end and c end of the three-way valve R2, and then returns to the reflux port 12 of the low-power compressor R1 after passing through the gas-liquid separator R10, ending the main refrigerant circulation and entering the next circulation; in the third auxiliary EVI circuit, the refrigerant is throttled and reduced in pressure by the first electronic expansion valve R7, and then enters the h end and exits the i end of the economizer R11, exchanges heat with the refrigerant on one side of the main circuit, vaporizes and heats up, and then becomes medium-temperature and low-pressure steam, returning to the EVI reflux port 13, and entering the low-power compressor R1, completing a circulation.

[0101] likeFigure 8 As shown, the indoor heat exchanger R9 is externally connected to the indoor chilled water circulation pump R91. At this time, the chilled water is transported to the refrigeration main unit, i.e., the indoor heat exchanger R9, by the indoor chilled water circulation pump R91 to produce low-temperature water, achieving the purpose of cooling the indoor environment.

[0102] As Figure 12 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 low-temperature 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 refrigerant directly vaporizes to absorb the heat of the indoor air and thus cools down.

[0103] Furthermore, the connection modes between the small-power compressor R1, the open-type spiral-wound condenser R3, and the air-cooled fin heat exchanger R4 can be adjusted adaptively in various ways according to actual needs. For example: an air-cooling priority mode can be adopted, where the high-temperature and high-pressure refrigerant vapor ejected from the small-power compressor R1 first enters the air-cooled fin heat exchanger R4 to exchange heat with air and is preliminarily condensed into a medium-temperature and high-pressure refrigerant liquid, enters through the e end and exits through the f end of the three-way valve R13, and then enters the open-type spiral-wound condenser R3 to exchange heat with the cooling water. After the refrigerant is further cooled and depressurized, it flows out; or, the air-cooled fin heat exchanger R4 and the open-type spiral-wound condenser R3 are connected in parallel. After the high-temperature and high-pressure refrigerant vapor ejected from the small-power compressor R1 exchanges heat with the cooling water in the open-type spiral-wound condenser R3, the refrigerant becomes a high-temperature and high-pressure liquid and enters the liquid storage tank R5.

[0104] The open-type spiral condenser R3, as Figures 13 - 39As shown in the figure, it includes a refrigerant collecting 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 collecting 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 with 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 collecting box 30 includes a steam-end collecting box 30-1 and a liquid-end collecting box 30-2 arranged oppositely. A collecting box refrigerant inlet 306 and a collecting 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 collecting box 30-1 through the collecting 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 collecting 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 collecting box refrigerant outlet 307. A deflector plate 32a is provided at the bottom of the liquid-end collecting box 30-2 at a certain angle to its bottom surface, 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, and improving the utilization efficiency of the refrigerant.

[0105] Among them, it should be particularly noted that:

[0106] Figure 22 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.

[0107] Figure 23This 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 perspective of the steam end collecting box 30-1. For the convenience of description 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 counterclockwise 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 rectangular structure 340.

[0108] Similarly, Figure 24 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 perspective 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 ), is axisymmetric with the position of its straight pipe inlet section 34-1 in Figure 23 with respect to the center point O of the bottom plate. Specifically, we also number the positions of the straight pipe outlet sections 34-2 corresponding to the straight pipe inlet sections 34-1. For the straight pipe inlet section 34-1 at position 1, the position of the corresponding straight pipe outlet section 34-2 is denoted as 1′, for the straight pipe inlet section 34-1 at position 2, the position of the corresponding straight pipe outlet section 34-2 is denoted as 2′, and so on, from 1′ to 26′, which forms another largest tube rectangular structure 340 in Figure 24 . 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 23 andFigure 24 If the rectangular structures 340 of the tube arrays in 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 rectangular structure 340 of the tube arrays 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.

[0109] Figures 25 - 37 It is a side view, a side top view, and a partial enlarged schematic diagram of the positions of the refrigerant collection box and the anchor frame of the present invention, as well as the first to fourth turns of the spiral refrigerant tube windings. It can be seen that the several layers of anchor frames are vertically and fixedly connected between the bottom plates 30b of the steam end collection box 30-1 and the liquid end collection box 30-2. Each layer of anchor frame is composed of four anchor frames 33, and the projections of each layer of 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 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 turns of spiral refrigerant tube windings are formed by several turns of spiral refrigerant tubes 34 rotating around the corresponding layer of anchor frames 33 with a certain angle of external tangency. 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 arranged axisymmetrically 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 array 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 array 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 spiral refrigerant tube windings of the adjacent two turns with respect to the corresponding layer of anchor frames are opposite, forming a microchannel group.

[0110] Figures 38 - 39The 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 tubes in different turns; 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 winding spacing between adjacent 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).

[0111] 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 centrosymmetric layout with 0 as the origin. The distance between the centers of 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 during tube winding, and 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 distance between the central anchor tubes s and the difference between the sum of the diameters d of all tubes in the y-axis and the anchor frame diameter D and 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 diameter D of the anchor frame, the diameter d of the tube, 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.

[0112] In the x-axis (horizontal) direction, the straight pipe sections 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 sections 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 of the 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 and staggered manner from the outside to the inside. The distance between the projections of adjacent straight pipe sections 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 sections of the horizontal columns in the same turn to the number of layers N. On the premise of ensuring winding, maintaining the minimum staggered distance l' can ensure that each layer has the largest horizontal cross-section and increase the heat exchange effect. In this case, l' = L / 4; the distance ln in the x-axis direction between the side wings of different turns of columns = L[1 - (n - 1) / N], and L ≥ Nd. In this case, l1 = L; l2 = 3 / 4L; l3 = 1 / 2L; l4 = 1 / 4L.

[0113] The total distance M in the x-axis direction of the straight pipe sections 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.

[0114] The heat exchange area of the open-type spiral-wound condenser R3 is calculated as follows:

[0115] The first step is to calculate the heat exchange quantity:

[0116] 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:

[0117] Qr = Qw + Qc

[0118] The second step is to calculate the heat transfer area:

[0119] 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:

[0120] A = Qr / K(Tr - △t)

[0121] The third step is to calculate the length of the tubes:

[0122] Given the heat exchange area A and the tube diameter d, from the area formula, the total length L of each tube winding is obtained:

[0123] L = A / dπ

[0124] The number of tube rows, 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.

[0125] This structure is smaller in volume, higher in winding density than the parallel tube in-line type or spiral circular winding type heat exchanger, and can obtain a longer extension length on the same axis, increasing the tube pass, increasing the heat transfer area A of a single tube row, and obtaining more heat transfer quantity Qr = A * K(Tr - △t):

[0126] The x-axis spacing M is greater than the y-axis direction spacing S, increasing the cross-sectional area of the condenser, ensuring that the cooling water tank has a larger evaporation area and facilitating the vaporization and evaporation of the cooling water; the smaller staggered layer spacing l' between each turn of tube rows not only ensures the uniform distribution of each layer of flank columns but also ensures that the cross-section of each winding layer is the largest, increasing the winding amount, increasing the total heat transfer area A, and obtaining more heat transfer quantity; Qr = A * K(Tr - △t);

[0127] While ensuring cleaning, maintaining the minimum tube row winding pitch b can increase the tube row density, making the microchannels formed by the upper and lower staggered layers smaller and the heat transfer more sufficient;

[0128] Adjacent turns of tube rows present a reverse winding structure, and the upper and lower layers of tube bundles form a baffle, increasing the disturbance of water, continuously changing the fluid flow direction and velocity, 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);

[0129] The anchor frame spacing between adjacent layers is designed at an equal distance H from the tube row layer spacing between adjacent layers. After each layer of tube rows 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;

[0130] In summary: The open-type spiral winding condenser R3 has a compact structure, small volume, high heat transfer efficiency, and is easy to maintain.

[0131] Of course, the open-type spiral winding condenser R3 can be replaced by a spiral immersion condenser or a tube row immersion condenser.

[0132] 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 vertically 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 evenly spaced, 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 heated through heat exchange in the cooling water tank C6 passes through the evenly 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 40 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.

[0133] 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 vertically 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 flows vertically and layer by layer 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 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 flow rate V flow rate of the cooling water decreases, and thus the residence time of the cooling water in the tank is prolonged.

[0134] 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 without departing from the spirit of the present invention should be included in the protection scope of the present invention.

Claims

1. An integrated water-cooled low-temperature 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, 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 dryer filter, an economizer, a number of electronic expansion valves, a number of check valves, and a three-way valve that are connected to each other; the cooling water tank is provided at the upper part inside the small cooling tower housing, and the small-power compressor, the liquid storage tank, the dryer filter, a number of electronic expansion valves, a number of check valves, the three-way valve, and the indoor-side heat exchanger are provided 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 of the cooling water tank; the water distributor is provided at the bottom inside the cooling water tank; the sprayer is provided above the cooling filler layer for spraying water onto the surface of the cooling filler layer to absorb heat; the fan is provided at the top of the small cooling tower housing to discharge the refrigerant heat of the cooling filler layer and the open-type spiral-wound condenser to the outdoor atmosphere in the form of latent heat of vaporization; in the refrigeration mode: the small-power compressor is connected to the open-type spiral-wound condenser, the three-way valve, and the air-cooled finned heat exchanger through the four-way valve and is divided into a main circuit and an auxiliary EVI circuit. The main circuit is connected to the small-power compressor after passing through the functional modules, the indoor-side heat exchanger, the four-way valve, and the gas-liquid separator, and the auxiliary EVI circuit is directly connected to the small-power compressor through the functional modules; in the air-cooled heating mode: the small-power compressor is connected to the indoor-side heat exchanger through the four-way valve and is divided into a second main circuit and a second auxiliary EVI circuit. The second main circuit is connected to the small-power compressor after passing through the functional modules, the air-cooled finned heat exchanger, the three-way valve, the four-way valve, and the gas-liquid separator, and the second auxiliary EVI circuit is directly connected to the small-power compressor through the functional modules; in the air-cooled heat pump defrosting mode: the small-power compressor is connected to the air-cooled finned heat exchanger through the four-way valve and the three-way valve and is divided into a third main circuit and a third auxiliary EVI circuit. The third main circuit is connected to the small-power compressor after passing through the functional modules, the indoor-side heat exchanger, the four-way valve, and the gas-liquid separator, and the third auxiliary EVI circuit is directly connected to the small-power compressor through the functional modules; The open spiral-wound condenser includes a refrigerant collection box, several turns of spiral refrigerant tube windings, several 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. A number of tube holes are opened in the middle of the bottom plate, and 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, forming a cavity for refrigerant collection. The refrigerant collection box includes a steam-end collection box and a liquid-end collection box arranged oppositely. A collection box refrigerant inlet and a collection 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 collection box through the collection 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 steam is evenly sprayed into the entire steam-end collection box. The refrigerant outlet pipe is connected to the collection box refrigerant outlet. A deflector plate forming a certain angle with the bottom surface is arranged at the bottom of the liquid-end confluence box, so that the condensed refrigerant liquid converges to the refrigerant outlet pipe. An H-shaped same-way multi-stage water distributor is adopted in the cooling water tank, which includes a water distributor main pipe, multi-stage branch pipes and a number of water heads that are interconnected. Each lower-level branch pipe of each stage is vertically connected to its upper-level branch pipe, forming a multi-stage H shape. A number of water heads are distributed at both ends of the last-stage branch pipe, finally realizing that each water head is on the same horizontal plane, and each adjacent water head is arranged at equal intervals, thereby forming a uniform water head array. The other end of the water distributor main pipe is connected to a cooling circulation pump. The cooling water heated through heat exchange in the cooling water tank enters the multi-stage branch pipes and the water distributor main pipe through the evenly distributed water heads, and finally enters the cooling circulation pump and the sprayer through the cooling pump guide pipe to enter the next cooling cycle.

2. The integrated water-cooled low-temperature air-cooled heat pump module unit according to claim 1, characterized in that, 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 valve and a sewage outlet are provided at the bottom of the cooling water tank, and the sewage outlet 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. External cooling water enters through the water replenishing 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 provided 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 provided 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 module unit.

3. The integrated water-cooled low-temperature air-cooled heat pump modular unit according to claim 1, characterized in that, The small-power compressor is a liquid-injected and enthalpy-increasing compressor with a power consumption of 5-25 KW, having an outlet, a reflux port, and an EVI reflux 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, and the several electronic expansion valves include a first electronic expansion valve and a second electronic expansion valve; the function module has U, V, and W 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, and the three-way valve includes e, f, and g ends; the economizer R11 includes h, i, j, and k ends; in the refrigeration mode: 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 collecting box refrigerant inlet of the open-type spiral-wound condenser; the collecting box refrigerant outlet of the open-type spiral-wound condenser enters through the f end and exits through the e end of the three-way valve, and is connected to the X interface of the air-cooled finned heat exchanger; after the Y interface of the air-cooled finned heat exchanger is connected to the first one-way valve, it is divided into a main circuit and an auxiliary EVI circuit. The main circuit is through the U interface of the function module, the liquid storage tank, the dryer filter, enters through the j end and exits through the k end of the economizer, passes through the second electronic expansion valve and the V interface, and then is connected to the P interface of the indoor heat exchanger through the second one-way 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; the auxiliary EVI circuit is through the U interface, the liquid storage tank, the dryer filter, the first electronic expansion valve, enters through the h end and exits through the i end of the economizer, passes through the W interface, and then is connected to the EVI reflux port of the small-power compressor.

4. The integrated water-cooled low-temperature air-cooled heat pump modular unit according to claim 1, characterized in that, The small-power compressor is a liquid-injected and enthalpy-increasing compressor with a power consumption of 5-25 KW, having an outlet, a reflux port, and an EVI reflux port; the indoor-side 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, and the several electronic expansion valves include a first electronic expansion valve and a second electronic expansion valve; the function module has U, V, and W interfaces; the air-cooled finned heat exchanger has X and Y interfaces, and the open-type spiral-wound condenser has a refrigerant inlet of the collecting box and a refrigerant outlet of the collecting box; the four-way valve includes a, b, c, and d ends, and the three-way valve includes e, f, and g ends; the economizer R11 includes h, i, j, and k ends; in the air-cooled heating mode: 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-side heat exchanger. After the P interface of the indoor-side heat exchanger is connected to the third one-way valve, it is divided into a second main circuit and a second auxiliary EVI circuit. The second main circuit is through the U interface of the function module, the liquid storage tank, the drying filter, enters through the j end and exits through the k end of the economizer, passes through the second electronic expansion valve and the V interface, passes through the fourth one-way 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 e end and exits through the g end of the three-way valve, 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; the second auxiliary EVI circuit is through the U interface, the liquid storage tank, the drying filter, the first electronic expansion valve, enters through the h end and exits through the i end of the economizer, passes through the W interface, and is then connected to the EVI reflux port of the small-power compressor.

5. The integrated water-cooled low-temperature air-cooled heat pump modular unit according to claim 1, characterized in that The small-power compressor is a liquid-injected and enthalpy-increasing compressor with a power consumption of 5-25 KW, having an outflow port, a reflux port, and an EVI reflux 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, and the several electronic expansion valves include a first electronic expansion valve and a second electronic expansion valve; the function module has U, V, and W interfaces; the air-cooled finned heat exchanger has X and Y interfaces, and the open-type spiral-wound condenser has a refrigerant inlet of the collecting box and a refrigerant outlet of the collecting box; the four-way valve includes a, b, c, and d ends, and the three-way valve includes e, f, and g ends; the economizer R11 includes h, i, j, and k ends; in the air-cooled heat pump defrosting mode: the outflow port of the small-power compressor enters through the a end of the four-way valve and exits through the b end, enters through the g end of the three-way valve and exits through the e end, and is connected to the X interface of the air-cooled finned heat exchanger. After the Y interface of the air-cooled finned heat exchanger is connected to the first one-way valve, it is divided into a third main circuit and a third auxiliary EVI circuit. The third main circuit is to enter through the U interface of the function module, the liquid storage tank, the drying filter, the j end of the economizer and exit through the k end, pass through the second electronic expansion valve and the V interface, and then be connected to the P interface of the indoor heat exchanger through the second one-way valve. The Q interface of the indoor heat exchanger enters through the d end of the four-way valve and exits through the c end, and is connected to the reflux port of the small-power compressor through the gas-liquid separator; the third auxiliary EVI circuit is to enter through the U interface, the liquid storage tank, the drying filter, the first electronic expansion valve, the h end and exit through the i end, pass through the W interface, and then be connected to the EVI reflux port of the small-power compressor.

6. The integrated water-cooled low-temperature air-cooled heat pump module unit according to claim 1, characterized in that, The indoor heat exchanger is 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 indoor air is cooled by directly vaporizing the refrigerant to absorb the heat of the indoor air.

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