CN211953314U

CN211953314U - Integrated water cooling air cooling heat pump module unit

Info

Publication number: CN211953314U
Application number: CN201922243848.8U
Authority: CN
Inventors: 李国斌
Original assignee: Hanrun United High Tech Development Beijing Co ltd
Current assignee: Hanrun United High Tech Development Beijing Co ltd
Priority date: 2019-12-13
Filing date: 2019-12-13
Publication date: 2020-11-17
Anticipated expiration: 2029-12-13

Abstract

The utility model discloses an integrated water cooling and air cooling heat pump module unit, which comprises a small cooling tower shell, a cooling system, a refrigerant circulating system and a functional module, wherein the cooling system, the refrigerant circulating system and the functional module are integrated in the small cooling tower shell; the cooling system comprises a fan, a water distributor, a cooling circulating pump, a sprayer, a cooling packing layer and a cooling water tank, and the refrigerant circulating system comprises a low-power compressor, an air-cooled finned heat exchanger, an open spiral wound condenser, a four-way valve, an indoor side heat exchanger and a gas-liquid separator; the functional module comprises a liquid storage tank, a drying filter, an electronic expansion valve and a plurality of one-way valves which are connected with each other; the low-power compressor is connected with the air-cooled finned heat exchanger and the open type spiral wound condenser through the four-way valve, and then is connected with the low-power compressor through the functional module, the indoor side heat exchanger, the four-way valve and the gas-liquid separator.

Description

Integrated water cooling air cooling heat pump module unit

Technical Field

The utility model relates to an air conditioning equipment field especially relates to a cooling system and refrigeration system height fit integration, many parallelly connected small-size modularization installations, can mix the refrigeration and the heating module unit of air-cooling and water-cooling mode or directly expand (ally oneself with) module unit.

Background

With the development of heat pump technology, the low-temperature air-cooled heat pump is gradually popularized, and the cold and warm functions of the heat pump provide more choices for users.

The water cooling unit has a remarkable energy-saving effect compared with an air cooling water cooling unit, and a screw compressor or a centrifugal compressor is adopted for the water cooling unit, so that the refrigerating capacity of a single unit is less, hundreds of kilowatts are more, thousands of kilowatts are more, and the refrigerating capacity is strong. And the boiler technology is mature, so the application is wide. For buildings with cooling and heating requirements in cold winter and hot summer areas, a solution scheme which is generally adopted is to adopt a water-cooling cold water central air conditioner and a boiler to meet the cooling and heating requirements; in recent years, due to the development of heat pump technology, particularly, a low-temperature air-cooled heat pump can supply cold and warm, one set of equipment can meet two requirements, and the low-temperature air-cooled heat pump is a better solution for summer heat and winter cold areas, so that the low-temperature air-cooled heat pump is popular in the market. The two cooling and heating modes are widely applied to middle and large buildings or building clusters in factories, office buildings, apartments, hotels, airports, hospitals, schools and the like. However, the prior art still has the following problems:

although the water cooling unit saves energy by about 30 percent compared with the refrigeration of an air cooling unit and is the preferred type of refrigeration in summer as the water cooling unit, the existing water cooling unit adopting a high-power screw compressor and a centrifugal compressor solves the problems of refrigeration and heating in hot summer and wet and cold areas (-10 ℃ to 10 ℃) in winter, and has the following problems:

1. large volume, inconvenient installation and transportation, increased construction amount and high professional degree. The water chilling unit generally adopts a high-power screw compressor (the single machine consumes more than 100 KW) or a centrifugal compressor (the single machine consumes more than 200KW-1000 KW), and the unit has less weight, more than one or two tons and several tons, so the water chilling unit has large volume and is inconvenient to install and transport; the water-cooled refrigerating unit machine room is generally arranged in the underground part of a building main body, and the cooling tower is arranged on the roof of the building main body. The cooling water supply and return network construction difficulty between the refrigeration main machine and the cooling tower in the machine room is low, the cooling water supply and return network construction difficulty is high, the requirement on the construction professional degree is high, the construction difficulty is increased, and the construction cost is increased due to the overlong construction amount of the cooling circulation network.

2. The building utilization rate is reduced due to the occupation of the main building space. A circulating system consisting of a refrigeration host machine, a water replenishing system, a freezing water pump, a circulating system consisting of a cooling water pump and an electric control system need a specific machine room, and waste of effective utilization area of the building main body and reduction of the utilization rate of the building main body are caused by more than hundreds of kilometers when the installation floor area is small. At present, the supply of land resources is tight, and real estate regulation is more and more strict, so that the method has important significance in reducing the land use area and improving the building utilization rate; in engineering practice, some newly-built and reconstructed buildings cannot install a refrigeration main machine indoors due to indoor space limitation caused by various reasons and adopt an air cooling unit substitution scheme, so that the refrigeration operation cost of an air conditioner is greatly increased.

3. The single unit has poor operation stability and is difficult to maintain. Because the water-cooling water chilling unit has large power, strong refrigerating capacity and high single-unit price, a single-unit double-machine-head compressor is adopted for improving the operation stability instead of a one-by-one unit or a multi-unit parallel combined refrigerating mode, and the refrigeration system has low stability because the refrigeration main machine is unavailable or is maintained. And the water-cooling water chilling unit is not easy to maintain and has high maintenance cost.

4. The energy consumption of the circulating pump is high due to the overlong cooling pipe network caused by the separation of the unit refrigeration system and the cooling system. Because of the large height difference between the refrigeration host and the cooling tower and the overlong cooling circulating water pipe network, the on-way resistance of cooling water is increased, the lift of the cooling circulating pump is increased, the power of the circulating pump is further improved, and the energy consumption is correspondingly increased; in addition, the existing water chilling unit mostly adopts a shell-and-tube heat exchanger, the pressure difference of a fluid inlet and a fluid outlet is large due to high flow, the fluid resistance in the shell is increased, and the energy consumption of the circulating pump is increased due to the increase of friction resistance.

5. The efficiency of a traditional shell and tube condenser in a water chiller needs to be improved. Because the heat exchange between the refrigerant and the cooling medium is completely carried out in the closed heat exchanger shell, the evaporation of the cooling medium (water) is not facilitated, the evaporation capacity of latent heat of vaporization of the water is reduced, and the cooling effect of the water is reduced.

6. The noise pollution is serious. The noise of the water chilling unit mainly comes from a compressor and a circulating pump, the noise and the vibration generated when a high-power compressor and a freezing and cooling circulating pump are concentrated in the same machine room during operation are serious, and professional noise reduction treatment is required for reducing noise pollution. Not only increases the construction cost of the machine room, but also reduces the use comfort of the building.

7. The cold water machine set and the boiler cold and warm supply solution have the advantages that the initial investment of two sets of equipment in one set of system is increased, and the environment is polluted by coal-fired and gas-fired boilers. The mode of water-cooling water chilling unit and heating boiler is the main solution for solving the requirements of refrigeration and heating in the areas with cold winter and hot summer. Since the heating time only occupies 1/3-1/4 of the annual operation time in the wet and cold (-10 ℃) areas in winter, the boiler has short service time and long idle time, thereby causing investment waste and environmental pollution.

The air-cooled heat pump (cold and hot water) unit has the bidirectional regulation functions of refrigeration and heating, can meet the requirements of refrigeration in summer and heating in winter, is wide in market application, but can solve the problem of heating in winter in hot summer and wet cold winter areas due to long refrigeration time and short heating time, but the annual energy consumption is increased due to the fact that the air-cooled heat pump (cold and hot water) unit is adopted in the areas, the air-cooled refrigeration efficiency is 30% lower than that of a water cooling mode, and the refrigeration cost is increased, so that better equipment selection is expected.

SUMMERY OF THE UTILITY MODEL

The to-be-solved technical problem of the utility model is to provide an integration water cooling air-cooled heat pump module unit, it is big to solve cooling water set cooling water consumption, heat exchange efficiency is low, water cooling water set computer lab area occupies the waste that the indoor space leads to building utilization to reduce greatly, the cooling tower is high with the cooling pipe network overlength construction degree of difficulty that cooling water set component separation was sent, construction cost increases, large-scale cooling water set is difficult to transport, the installation, maintain, the cooling pump energy consumption height leads to the whole refrigeration efficiency of unit to reduce, cooling water set noise is big, easily produce noise pollution scheduling problem and solve the air-cooled heat pump and heat but the low problem of refrigeration efficiency.

In order to solve the technical problem, the utility model discloses a technical scheme does:

the integrated water cooling air cooling heat pump module unit comprises a small cooling tower shell, a cooling system, a refrigerant circulating system (refrigerating system) and a functional module, wherein the cooling system, the refrigerant circulating system (refrigerating system) and the functional module are integrated in the small cooling tower shell; the cooling system comprises a fan, a water distributor, a cooling circulating pump, a sprayer, a cooling packing layer and a cooling water tank, and the refrigerant circulating system comprises a low-power compressor, an air-cooled finned heat exchanger, an open spiral wound condenser, a four-way valve, an indoor side heat exchanger and a gas-liquid separator; the functional module comprises a liquid storage tank, a drying filter, an electronic expansion valve and a plurality of one-way valves which are connected with each other; the cooling water tank is arranged at the upper part inside the small cooling tower shell, and the low-power compressor, the liquid storage tank, the drying filter, the electronic expansion valve, the plurality of one-way valves and the indoor side heat exchanger are arranged outside the cooling water tank; the air-cooled finned heat exchanger is arranged between the water baffle plates on the periphery above the cooling water tank and the inner wall of the small cooling tower shell and is used for exchanging heat between a refrigerant and external air; the open type spiral winding condenser is soaked in the cooling water of the cooling water tank; the water distributor is arranged at the bottom inside the cooling water tank; the sprayer is arranged above the cooling filler layer and used for spraying water and absorbing heat to the surface of the cooling filler layer; the fan is arranged at the top of the shell of the small cooling tower and discharges the heat of the refrigerant of the cooling filler layer and the open type spiral wound condenser to the outdoor atmosphere in a latent heat of vaporization mode; the low-power compressor is connected with the air-cooled finned heat exchanger and the open type spiral wound condenser through the four-way valve, and then is connected with the low-power compressor through the functional module, the indoor side heat exchanger, the four-way valve and the gas-liquid separator.

Or the low-power compressor is connected with the air-cooled finned heat exchanger through the four-way valve, and then is connected with the low-power compressor through the functional module, the indoor side heat exchanger, the four-way valve and the gas-liquid separator.

Or the low-power compressor is connected with the indoor side heat exchanger through the four-way valve and then connected with the low-power compressor through the functional module, the air-cooled finned heat exchanger, the four-way valve and the gas-liquid separator.

Preferably, the small cooling tower shell comprises a top plate, a base, a guard plate and water baffles arranged on the periphery above the inner part of the guard plate; a drain valve and a drain outlet are arranged at the bottom of the cooling water tank, and the drain outlet is connected to the lower part of the guard plate; a water replenishing port and a ball float valve are arranged in the middle of a protective plate of the small cooling tower shell, external cooling water enters from the water replenishing port, and the ball float valve is switched on and off to automatically replenish water into the cooling water tank when needed; the lower part of the guard plate of the small cooling tower shell is provided with an external chilled water outlet and a chilled water inlet which are respectively communicated with a chilled water inlet and a chilled water outlet of the indoor side heat exchanger; and a control cabinet is arranged on the lower part of the guard plate of the small cooling tower shell and used for controlling an electric switch of the integrated water cooling low-temperature type air-cooled heat pump module unit.

Further, the low-power compressor is a compressor consuming 5-25KW of power and is provided with a flow outlet and a return port; the indoor side heat exchanger is provided with an P, Q interface; the plurality of one-way valves comprise a first one-way valve, a second one-way valve, a third one-way valve and a fourth one-way valve; the function module is provided with an U, V interface; the air-cooled finned heat exchanger is provided with an X, Y interface, and the open type spiral winding condenser is provided with a collecting tank refrigerant inlet and a collecting tank refrigerant outlet; the four-way valve comprises a end a, a end b, a end c and a end d.

Preferably, the outflow port of the low-power compressor is connected with the X interface of the air-cooled finned heat exchanger through an end a and an end b of the four-way valve; the Y interface of the air-cooled finned heat exchanger enters and exits from a cold medium outlet of a collecting box through a first electromagnetic valve and a cold medium inlet of the collecting box of an open spiral wound condenser, passes through a U interface of a first one-way valve, a functional module, a liquid storage tank, a drying filter and a V interface of the functional module, and is connected with a P interface of an indoor side heat exchanger through a second one-way valve, and a Q interface of the indoor side heat exchanger enters and exits through a d end and a c end of a four-way valve and is connected with a backflow port of the low-power compressor through a gas-liquid separator.

Or the outflow port of the low-power compressor enters from the end a and exits from the end b of the four-way valve and is connected with the X interface of the air-cooled fin type heat exchanger, the Y interface of the air-cooled fin type heat exchanger is connected with the P interface of the indoor side heat exchanger through the second electromagnetic valve, the first one-way valve, the U interface of the functional module, the liquid storage tank, the drying filter, the electronic expansion valve and the V interface of the functional module, and the Q interface of the indoor side heat exchanger is connected with the backflow port of the low-power compressor through the end d and the end c of the four-way valve.

Or the outflow port of the low-power compressor enters from the end a of the four-way valve and exits from the end d of the four-way valve and is connected with the Q interface of the indoor side heat exchanger, after the P interface of the indoor side heat exchanger is connected with the third one-way valve, the P interface of the indoor side heat exchanger passes through the U interface of the functional module, the liquid storage tank, the drying filter, the electronic expansion valve and the V interface of the functional module and then passes through the fourth one-way valve and the second electromagnetic valve and is connected with the Y interface of the air-cooled fin type heat exchanger, and the X interface of the air-cooled fin type heat exchanger enters from the end b of the four-way valve and exits from the end c of the.

Furthermore, the outside of the indoor side heat exchanger is connected with an indoor side refrigerating circulating pump, and at the moment, the refrigerated water is conveyed to the refrigerating main machine, namely the indoor side heat exchanger, through the indoor side refrigerating circulating pump to prepare low-temperature water, so that the purpose of cooling the indoor space is achieved.

Further, the indoor side heat exchanger can be replaced by an indoor multi-connected unit, at the moment, the indoor multi-connected unit comprises a refrigerant fin heat exchanger and an indoor side fan, the indoor side fan enables air to flow through the surface of the refrigerant fin heat exchanger, and indoor air heat is directly evaporated and absorbed through a refrigerant to be cooled.

Furthermore, the connection mode between the low-power compressor and the open type spiral wound condenser and between the low-power compressor and the air-cooled fin type heat exchanger can be adjusted in various adaptability according to actual needs, such as: the air-cooled finned heat exchanger is connected with the open type spiral wound condenser in parallel, and after high-temperature and high-pressure refrigerant steam sprayed from the low-power compressor exchanges heat with cooling water through the open type spiral wound condenser, the refrigerant is changed into high-temperature and high-pressure liquid to enter the liquid storage tank.

Preferably, the open type spiral wound condenser comprises a refrigerant collecting box, a plurality of turns of spiral refrigerant tube array windings, a plurality of layers of anchor frames, a refrigerant inlet tube and a refrigerant outlet tube, wherein the refrigerant collecting box consists of an end cover and a bottom plate, the length and width of the end cover and the bottom plate are mutually matched, flange plates with the same size are arranged on the outer sides of the end cover and the bottom plate, a plurality of screw holes with matched size and position are arranged on the flange plates, a plurality of tube holes are arranged in the middle of the bottom plate, a box-shaped part protrudes from the middle of the end cover, and the bottom plate and the end cover penetrate through the screw holes in the flange plates through bolts to be screwed and buckled together to form a refrigerant collecting; the refrigerant collecting box comprises a steam end collecting box and a liquid end collecting box which are oppositely arranged, and a collecting box refrigerant inlet and a collecting box refrigerant outlet are respectively arranged above the side of the steam end cover and below the side of the liquid end cover; the refrigerant inlet pipe extends to the steam end collecting box through the refrigerant inlet of the collecting box to form a steam distribution pipe, small holes are uniformly distributed on the lower edge of the steam distribution pipe, so that the refrigerant steam is uniformly sprayed into the whole steam end collecting box, uniform steam admission of each spiral refrigerant tube winding is ensured, and the refrigerant is uniformly distributed in the tubes to realize the full condensation liquefaction effect; the refrigerant exit tube is connected with the refrigerant outlet of the collecting box, the bottom of the liquid-state end collecting box is provided with a guide plate which forms a certain included angle with the bottom surface of the liquid-state end collecting box, so that condensed refrigerant liquid is collected to the refrigerant exit tube, the liquid-state outflow of the refrigerant is facilitated, the occurrence of liquid accumulation is prevented, and the utilization efficiency of the refrigerant is improved.

Alternatively, the open spiral wound condenser may be replaced with a spiral submerged condenser or a shell and tube submerged condenser.

Preferably, an H-shaped same-pass multi-stage water distributor is adopted in the cooling water tank and comprises a water distributor header pipe, a multi-stage water distribution pipe and a plurality of water distribution heads which are communicated with each other, each stage of lower water distribution pipe is vertically connected with the upper stage of water distribution pipe to form a multi-stage H shape, the plurality of water distribution heads are distributed at two ends of the last stage of water distribution pipe, and finally, each water distribution head is arranged on the same horizontal plane and each adjacent water distribution head is arranged at equal intervals, so that a uniform water distribution head array is formed; the other end of the water distributor main pipe is communicated with a cooling circulating pump, cooling water heated by heat exchange in the cooling water tank enters the multistage water distribution pipe and the water distributor main pipe through the uniformly distributed water distribution heads, and finally enters the cooling circulating pump through the cooling pump guide pipe and enters the next cooling circulation through the sprayer. The H-shaped same-pass multistage water distributor can enable the low-temperature cooling water cooled on the surface of the cooling water tank to move downwards along the vertical direction on the same horizontal plane, ensure that the low-temperature cooling water exchanges heat with the refrigerant tubes layer by layer downwards, and gradually increase the temperature of the cooling water as the refrigerants in the tubes are cooled. The cooling water after temperature rise can effectively prevent disordered heat exchange between the cooling water and the refrigerant tubes through the arrangement of the H-shaped same-pass multistage water distributor, and ensures that the low-temperature cooling water vertically flows through each layer of tubes in a layered manner on the same horizontal plane, thereby improving the cooling effect of the cooling water and the cooling efficiency of the refrigerant. According to the specific heat capacity of the temperature difference C of the cross section area rho density delta T of the flow velocity VVx S; the cross-sectional area of V velocity of flow S is the definite value, and rho density, C specific heat capacity are the constants, because the cross-sectional area of open cooling water tank is hundreds of times of cooling circulation pipe, lead to cooling water velocity of flow V velocity of flow to reduce, and then cooling water detention water tank time extension.

Has the advantages that: the utility model embeds the refrigeration system into the small modular cooling tower to form an integrated unit with highly integrated refrigeration system and cooling system; the scroll compressor or the low-power screw compressor is adopted, so that the unit is miniaturized, after the unit is miniaturized and modularized, the power consumption is 5-40 KW, the weight of the unit is reduced to be below 0.5 ton, and the unit can be conveniently installed and transported; after the refrigeration system and the cooling system are highly integrated, the refrigerant circulating system is arranged in the outdoor cooling tower, so that the traditional indoor machine room is omitted; the integrated unit saves the laying of a cooling pipe network in the traditional water chilling unit engineering, reduces the construction amount and reduces the construction difficulty; the built-in cooling water circulation system has lower power of a lower-lift cooling circulation pump and is an efficient open spiral winding type efficient cooling system, so that the evaporation capacity of cooling water is improved, the circulation capacity of the cooling water is reduced, and the power consumption of the cooling circulation pump is further reduced; the refined spraying water distribution and the small-flow cooling water circulation reduce the wind speed of the fan, avoid the phenomena of water flying and water floating to the maximum extent and save water; after the optimization of each part and each system, the unit of the utility model has higher integration level, low noise and higher comprehensive efficiency; the utility model discloses still add air-cooled finned heat exchanger in unit outer wall backplate inboard, solved air-cooled heat pump (hot and cold water) unit because of having the refrigeration, heating two-way regulatory function, satisfy the demand that heats winter of refrigeration in summer, but the running cost high problem in summer, the utility model discloses the unit can make the refrigeration running cost in summer reduce more than 30%. The utility model discloses fuse water-cooling technique and air-cooled heat pump technique, created a brand-new air conditioner variety-integration water-cooling air-cooled heat pump module unit, fundamentally has solved the following problem of traditional cooling water set:

1. the unit of several tons of weight of the bulky volume is installed, transported inconveniently. Because the utility model discloses a power consumption is then dozens of kilowatts more after scroll compressor or miniwatt screw compressor will large-scale water chilling unit small-size modularization, and unit weight reduces to below 1 ton, installation, the transportation of the unit of can being convenient for.

2. The refrigeration machine room occupies the main building space, so that the building utilization rate is reduced, and the space is wasted. The small modular unit can be installed on a roof and does not need to be specially provided with a machine room, so that the indoor space is saved, and the utilization rate of a main building is improved.

3. The unit is small in equipment number, poor in stability and difficult to maintain. The modularized units run simultaneously to be mutually standby, the maintenance and the repair of individual units do not influence the overall operation and use, and the operation stability of the whole air conditioning system is improved.

4. The cooling circulation pump has high energy consumption. The height difference between the cooling tower and the refrigeration main machine and the on-way pipe resistance increase caused by overlong cooling pipe network, and the high-lift circulating pump is adopted to ensure that the electric energy consumption is high. Obviously, the lift and the on-way resistance can be greatly reduced by placing the cooling tower and the refrigeration main machine on the same plane, so that the power consumption of the cooling circulating pump is reduced by 50-70%; the heat exchanger adopting the shell-and-tube (sleeve) heat exchanger has larger resistance and high energy consumption of the circulating pump. The existing water chilling unit mostly adopts a shell-and-tube heat exchanger, and the shell pass is short, so that the required flow rate is high, the pressure difference of a fluid inlet and a fluid outlet is large, the fluid resistance is greatly increased, the power of a circulating pump is increased, and the energy consumption is increased. The modularized unit adopting the open spiral winding type efficient cooling system adopts the open spiral winding type condenser, and overcomes the resistance of a shell and tube heat exchanger in the traditional water chilling unit by utilizing the self gravity flow of cooling water, thereby reducing the power consumption of a circulating pump.

5. The construction amount of the pipe network is increased, the construction cost is high, and the construction difficulty is high. The modular water chilling unit adopting the open spiral winding type efficient cooling system integrates the cooling tower and the main machine into a whole, although the total cost of the main machine can be increased, the manufacturing cost of the single machine can be effectively reduced by the advantages of industrial production and scale, the downstream cost is transferred upstream, namely the cost is preposed, the construction cost is reduced, the construction of an engineering company can be facilitated, the construction difficulty is reduced, and the popularization of the engineering company is facilitated. And after the refrigerating unit is added with the function of the heat pump, the use function is added, and the cost performance of the unit is improved.

6. The open type spiral winding type efficient cooling system is particularly adopted, a shell-and-tube heat exchanger universal for the water cooling unit is changed into the open type spiral winding type heat exchanger to replace a shell-and-tube (sleeve-type) closed heat exchanger, so that a part of latent heat of vaporization generated by heat exchange of a refrigerant and cooling water is released to the air through the water surface of the water tank, the latent heat of vaporization of the water is utilized to improve the heat exchange quantity of unit mass water, the effect that the shell-and-tube heat exchanger cannot reach is achieved, the cooling efficiency is improved, and the operation efficiency of the whole unit is higher.

7. The open type heat exchanger has a wide operation space, and is convenient for cleaning and maintaining the condenser.

8. The noise is large. In civil buildings, a central air conditioner is the largest noise source, and professional and systematic antifouling treatment must be carried out on an air conditioner room to solve noise pollution, so that the construction cost is increased, all-weather professional personnel are required to watch, and the use cost in operation is increased. Adopt the high-efficient cooling system's of open spiral wound formula modularization unit (the utility model discloses the unit), only need with the unit standard install high-rise building roof roofing can, the unit noise need not special noise reduction treatment below 65Pb and reaches the national standard completely, can fundamentally solve the noise pollution problem. And the host computer runs automatically without the need of special person on duty, thus reducing the construction and use cost.

9. The cooling water is wasted seriously. Cooling water consumption source three links: cooling water evaporation consumption, pollution discharge consumption, "water run". Wherein the 'flying water' is of no benefit consumption. The heat transfer process of the refrigerant is directly or indirectly discharged into the atmosphere under the assistance of the fan, the larger the cooling water circulation is, the larger the spraying amount is, the higher the air circulation amount and the air speed are, and the more the spraying water is taken away by the fan, so that waste is caused. Adopt an open spiral wound high-efficient cooling system the utility model discloses the unit realizes cooling water and refrigerant heat transfer process through evaporation latent heat and heat convection sensible heat mode, can effectively reduce the cooling water circulation volume, reduced the wind speed, and then reduces "flying water" phenomenon.

10. Particularly, the utility model discloses adopt H type with journey multistage water-locator in the unit, can make the cryogenic cooling water on cooling water tank surface form the gravitation that flow equalizes, voltage-sharing, uniform velocity downwards along the vertical direction level, just like a "piston" that constitutes by the water tank lateral wall, formed by the piston that constitutes with the temperature, the water layer of different gradients flows downwards along the vertical direction, flow every layer of tubulation to the cooling efficiency of cooling water has been improved. By arranging the H-shaped multi-stage water distributors, disordered heat exchange between cooling water and refrigerant tubes can be effectively prevented, and the situation that backflow is not thorough due to high flow velocity in an inlet area of a circulating pump and low flow velocity in a distal area of the inlet area of the circulating pump in a water distributor-free state is avoided; the upper and lower layer tubes are reversely wound to form a micro-channel group of the upper and lower structures. Because the surface of each tube is arc-shaped, the interior of the microchannel is of a non-planar structure, when the cooling water flows from top to bottom due to self gravity flow and the traction of the cooling circulating pump, the local flow speed is continuously changed, the flow direction is baffled and disturbed, the states of turbulence and turbulent flow are formed, the turbulence can be achieved under the condition of very low Reynolds number (Re < 100), the heat transfer coefficient K is improved, and more heat exchange quantity Qr is A K (Tr-Deltat). The H-shaped same-pass multi-stage water distributor ensures the necessary guarantee of the function of the heat exchanger and realizes the high-efficiency heat exchange of the heat exchanger.

11. The problem that the air-cooled heat pump is low in heating efficiency is solved. Because the utility model discloses the unit has add air-cooled finned heat exchanger in unit outer wall backplate inboard, through the refrigerant pipeline and the system design of optimizing, has realized the heat pump heating function under the refrigerated prerequisite of ensureing the water-cooling, and fundamentally has solved traditional water-cooling water set and has not heated the defect, has replaced hot summer, wet cold area in winter adopts cooling water set + boiler cold, warm two solution that supply. The initial investment of two sets of equipment of one set of system is increased, and the pollution to the environment caused by coal-fired and gas-fired boilers is avoided; secondly, in the areas with wet and cold temperatures in winter (minus 10 ℃ to 10 ℃), the heat supply time only accounts for about 1/3 to 1/4 of the annual operation time, the boiler has short service time and long idle time, so that the investment is wasted and the environment is polluted, and the refrigeration cost of the air-cooled heat pump (cold and hot water) units adopted in the areas is greatly increased in summer. The utility model discloses the unit has solved air-cooled heat pump (hot and cold water) unit because of having the refrigeration, heating two-way regulatory function, satisfies the demand that heats winter of refrigeration in summer, but the running cost high problem in summer, the utility model discloses the unit can make the refrigeration running cost in summer reduce more than 30%.

Drawings

Fig. 1 is the principle schematic diagram of the water-cooling refrigeration mode of the integrated water-cooling air-cooling heat pump module unit.

Fig. 2 is the principle schematic diagram of the air-cooled refrigeration mode of the integrated water-cooled air-cooled heat pump module unit.

Fig. 3 is the principle schematic diagram of the air cooling and heating mode of the integrated water cooling and air cooling heat pump module unit.

Fig. 4 is an enlarged schematic view of a low power compressor according to the present invention.

Fig. 5 is an enlarged schematic view of the four-way valve of the present invention.

Fig. 6 is an enlarged schematic view of the indoor-side heat exchanger R9 according to the present invention.

Fig. 7 is a schematic side sectional view of the integrated water cooling and air cooling heat pump module unit.

Fig. 8 is a schematic diagram of the front sectional structure of the integrated water cooling and air cooling heat pump module unit.

Fig. 9 is a schematic top view of the integrated water cooling and air cooling heat pump module unit.

Fig. 10 is a schematic side sectional structure view of the integrated water-cooling air-cooling heat pump multi-connected (direct expansion) modular unit of the present invention.

Fig. 11 is a plan view of the entire assembly of the open type spiral wound condenser of the present invention.

Fig. 12 is a front view of a vapor end collection box of the open spiral wound condenser of the present invention.

Fig. 13 is a front view of a liquid end header of an open spiral wound condenser of the present invention.

Fig. 14 is a right side view of the end cap of the vapor end collection box of the open spiral wound condenser of the present invention.

Fig. 15 is a left side view of the end cap of the liquid end collection tank of the open spiral wound condenser of the present invention.

Fig. 16 is a side plan view of the end cap of the steam end header of the present invention.

Fig. 17 is a side plan view of an end cap of a liquid end manifold in accordance with the present invention.

Fig. 18 is a right side inner cross-sectional view of an end cap of a steam end header of the present invention.

Fig. 19 is a right side inner cross-sectional view of an end cap of a liquid end manifold in accordance with the present invention.

Fig. 20 is a schematic view (left view or right view) of the position layout of the projection of the anchor frame and the straight pipe section of the spiral refrigerant tube row on the bottom plate according to the present invention.

Fig. 21 is a right side view of the position distribution of the inlet section of the straight tube of the spiral refrigerant tube array on the steam end bottom plate of the steam end header of the present invention (taking the first spiral refrigerant tube array as an example).

Fig. 22 is a right side view of the position distribution of the outlet section of the straight spiral refrigerant tube array of the present invention on the liquid end bottom plate of the liquid end header (taking the first spiral refrigerant tube array as an example).

Fig. 23 is a side view showing the distribution of the refrigerant collecting box and the anchor frame according to the present invention.

Fig. 24 is a side plan view showing the distribution of the refrigerant header and the anchor frame according to the present invention.

Fig. 25 is a schematic structural view of each anchor frame in the present invention.

Fig. 26 is a partially enlarged view illustrating the connection between the anchor frame and the bottom plate of the refrigerant header according to the present invention.

Fig. 27 is a side view of the first spiral refrigerant tube winding of the present invention.

Fig. 28 is a side plan view of the first spiral refrigerant tube winding of the present invention.

Fig. 29 is an enlarged partial schematic view of one end of the vapor end header of fig. 19.

Fig. 30 is a side view of the second spiral refrigerant tube winding of the present invention.

Fig. 31 is a side plan view of the second spiral refrigerant tube winding of the present invention.

Fig. 32 is a side view of the third spiral refrigerant tube winding of the present invention.

Fig. 33 is a side plan view of the third spiral refrigerant tube winding of the present invention.

Fig. 34 is a side view of the fourth turn spiral refrigerant tube winding of the present invention.

Fig. 35 is a side plan view of the fourth turn spiral refrigerant tube winding of the present invention.

Fig. 36 is a Y-axis lattice diagram of the projection of the anchor frame and the spiral refrigerant tube on the bottom plate according to the present invention.

Fig. 37 is an X-axis lattice diagram of the projection of the anchor frame and the spiral refrigerant tube on the bottom plate according to the present invention.

Fig. 38 is a schematic top view of the H-shaped same-pass multi-stage water distributor of the present invention.

Wherein: r1, low power compressor; 11. an outflow port; 12. a return port; r2 and a four-way valve; r4, air-cooled finned heat exchanger; r5, a liquid storage tank; r6, dry filter; r8, electronic expansion valve; r9, indoor side heat exchanger; r91, indoor side refrigeration circulation pump; r9a, indoor multi-connected units; r10, a gas-liquid separator; r121 and a first check valve; r122, a second one-way valve; r123 and a third one-way valve; r124, fourth check valve; r131 and a first electromagnetic valve; r132 and a second electromagnetic valve;

r3, open spiral wound condenser; 30. a refrigerant collecting box; 30a, an end cover; 30b, a bottom plate; 30-1, a steam end collection box; 30-2, a liquid end collection box; 30a-1, a steam end cap; 30a-2, liquid end cap; 30b-1, a steam end bottom plate; 30b-2, a liquid end bottom plate; 31. a refrigerant inlet pipe; 32. A refrigerant outlet pipe; 31a, an air distribution pipe; 32a, a baffle; 33. an anchor frame; 33-1, an anchor frame fixing section; 33-2, an anchor frame supporting section; 33.1, a first layer of anchor racks; 33.2, a second layer of anchor racks; 33.3, a third layer of anchor frame; 33.4, a fourth layer of anchor frame; 34. a spiral refrigerant array pipe; 34-1, a straight pipe inlet section; 34-2, an outlet section of the straight pipe; 34-3, a spiral section; 34.1, a first turn of spiral refrigerant tube array winding; 34.2, a second turn of spiral refrigerant tube array winding; 34.3, a third turn of spiral refrigerant tube array winding; 34.4, a fourth turn of spiral refrigerant tube array winding; 300. a flange plate; 301. a screw hole; 302. tube arraying holes; 303. a box-shaped portion; 306. a collecting tank refrigerant inlet; 307. a collecting tank refrigerant outlet; 308. a bolt;

330. the anchor frame is of a rectangular structure; 340. a tubular rectangular structure; o, a central point of the bottom plate; D. anchor frame diameter; d. the diameter of the spiral refrigerant array pipe; H. the layer spacing of adjacent turn tubes in the y-axis direction; l, the tube spacing in the x-axis direction of the adjacent straight tube sections of the same-turn horizontal tube array; l, the distance between the side wings of the different turn tubes in the x-axis direction; s, the total layer height of the same-turn row tubes in the y-axis direction; s, the distance between the anchor frames of the central layer (the fourth layer) in the y-axis direction; E. the distance between the side wings of the same turn of tube array in the y-axis direction; m, the total distance of straight pipe sections of the same-turn horizontal tubes in the x-axis direction; the distance between adjacent column tubes of the same turn on the m and y axes in the x axis direction; b. the adjacent winding distance of the same turn of tube array; r, the diameter of the anchor frame supporting section; r, the diameter of the anchor frame fixing section;

c1, cooling circulation pump; c2, a sprayer; c3, a water distributor; c4, a fan; c5, small cooling tower shell; c6, a cooling water tank; c7, cooling the filler layer;

51. a top plate; 52. a base; 53. a water baffle; 55. a control cabinet; 56. a blowoff valve; 57. a sewage draining outlet; 541. a water replenishing port; 542. a float valve; 543. a chilled water outlet; 544. a chilled water inlet;

c300, a water distributor main pipe; c301, a first-stage water distribution pipe; c302, secondary water distribution pipes; c303, a three-level water distribution pipe; c304, a four-stage water diversion pipe; c305, a five-stage water distribution pipe; c306, a six-stage water pipe; c307, a water distribution head.

Detailed Description

The present invention will be described in further detail with reference to the following embodiments.

As shown in fig. 1, the integrated water-cooling low-temperature air-cooling heat pump module unit includes a small cooling tower casing C5, a cooling system, a refrigerant circulation system (refrigeration system) and a functional module, which are integrated in the small cooling tower casing C5; the cooling system comprises a fan C4, a water distributor C3, a cooling circulating pump C1, a sprayer C2, a cooling filler layer C7 and a cooling water tank C6, and the refrigerant circulating system comprises a low-power compressor R1, an air-cooled finned heat exchanger R4, an open spiral wound condenser R3, a four-way valve R2, an indoor side heat exchanger R9 and a gas-liquid separator R10; the function module comprises a liquid storage tank R5, a drying filter R6, an economizer R11, a plurality of electronic expansion valves, a plurality of one-way valves and a three-way valve R13 which are connected with one another; the cooling water tank C6 is arranged at the upper part inside the small cooling tower shell C5, and the small power compressor R1, the liquid storage tank R5, the drying filter R6, the electronic expansion valves, the one-way valves, the three-way valve R13 and the indoor heat exchanger R9 are arranged outside the cooling water tank C6; the air-cooled finned heat exchanger R4 is arranged between the water baffles on the periphery above the cooling water tank C6 and the inner wall of the small cooling tower shell C5 and is used for exchanging heat between a refrigerant and external air; the open type spiral wound condenser R3 is soaked in the cooling water of the cooling water tank C6; the water distributor C3 is arranged at the bottom of the cooling water tank C6; the sprayer C3 is arranged above the cooling filler layer C7 and is used for spraying water and absorbing heat to the surface of the cooling filler layer C7; the fan C4 is arranged at the top of the small cooling tower shell C5 and discharges the heat of the refrigerant of the cooling filler layer C7 and the open type spiral wound condenser R3 to the outdoor atmosphere in a latent heat of vaporization mode; the low-power compressor R1 is divided into a main loop and an auxiliary EVI loop after being connected with the open type spiral wound condenser R3, the three-way valve R13 and the air-cooled finned heat exchanger R4 through a four-way valve R2, the main loop is connected with the low-power compressor R1 after passing through a function module, an indoor side heat exchanger R9 and a gas-liquid separator R10, and the auxiliary EVI loop is directly connected with the low-power compressor R1 through the function module.

Or, as shown in fig. 2, the low-power compressor R1 is connected with the air-cooled finned heat exchanger R4 through the four-way valve R2 and the three-way valve R13, and then is divided into a third main circuit and a third auxiliary EVI circuit, the third main circuit is connected with the low-power compressor R1 through the functional module, the indoor-side heat exchanger R9 and the gas-liquid separator R10, and the third auxiliary EVI circuit is directly connected with the low-power compressor R1 through the functional module.

Or, as shown in fig. 3, the low power compressor R1 is connected to the indoor heat exchanger R9 through the four-way valve R2 and then divided into a second main circuit and a second auxiliary EVI circuit, the second main circuit is connected to the low power compressor R1 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, and the second auxiliary EVI circuit is directly connected to the low power compressor R1 through the functional module.

As shown in fig. 4-5, the low power compressor R1 is a compressor consuming 5-25KW of power and has a discharge port 11 and a return port 12; the four-way valve R2 comprises a terminal a, a terminal b, a terminal c and a terminal d, and the indoor side heat exchanger R9 is provided with a P, Q interface;

the check valves comprise a first check valve R121, a second check valve R122, a third check valve R123 and a fourth check valve R124; the function module is provided with an U, V interface; the air-cooled finned heat exchanger R4 has a X, Y interface, and the open spiral wound condenser R3 has a header tank refrigerant inlet 306 and a header tank refrigerant outlet 307;

as shown in fig. 7-9, the small cooling tower casing C5 includes a top plate 51, a base 52, a protective plate (i.e., a panel around the small cooling tower casing C5), and a water baffle 53 installed around the inner top of the protective plate; the bottom of the cooling water tank C6 is provided with a drain valve 56 and a drain outlet 57, and the drain outlet 57 is connected below the guard plate; a water replenishing port 541 and a ball float valve 542 are arranged in the middle of a guard plate of the small cooling tower shell C5, external cooling water enters from the water replenishing port 541, and the ball float valve 542 is switched on and off to automatically replenish water into the cooling water tank C6 when needed; the lower part of the guard plate of the small cooling tower shell C5 is provided with an external chilled water outlet 543 and a chilled water inlet 544 which are respectively communicated with the chilled water inlet and outlet of the indoor side heat exchanger R9; and a control cabinet 55 is arranged on the lower part of the guard plate of the small cooling tower shell C5 and is used for controlling an electric switch of the integrated water cooling and air cooling heat pump module unit.

An outflow port 11 of the low-power compressor R1 passes through an end a and an end b of a four-way valve R2 and is connected with an X interface of the air-cooled finned heat exchanger R4; the Y interface of the air-cooled finned heat exchanger R4 enters and exits from a collection tank refrigerant outlet 307 through a collection tank refrigerant inlet 306 of an open type spiral wound condenser R3 via a first electromagnetic valve R131, passes through a first check valve R121, a U interface of a functional module, a liquid storage tank R5, a drying filter R6 and a V interface of the functional module, and is connected with a P interface of an indoor side heat exchanger R9 via a second check valve R122, and a Q interface of the indoor side heat exchanger R9 enters and exits from a d end and a c end of a four-way valve R2 and is connected with a return port 12 of the low-power compressor R1 via a gas-liquid separator R10. The specific correspondence is as shown in fig. 1 for the water cooling refrigeration mode:

in the mode, the R2a-b end and the c-d end of a four-way valve of the refrigerant circulating system are communicated; the first solenoid valve R131 is open and the second solenoid valve R132 is closed; the compressor R1 is electrified to work, high-temperature and high-pressure gaseous refrigerant sprayed from the outlet 11 of the compressor R1 enters the air-cooled finned heat exchanger R4 after entering from the a end and exiting from the b end of the four-way valve R2, the temperature of high-temperature and high-pressure refrigerant steam in the finned coil is reduced after primary heat exchange with air flowing on the surface of the high-temperature and high-pressure refrigerant steam, and part of the refrigerant is changed into liquid phase from vapor phase. At the moment, the refrigerant is changed into a medium-temperature high-pressure liquid mixed liquid, the mixed liquid enters a vapor state collecting port (collecting tank refrigerant inlet 306) of the open type spiral wound condenser R3 through the first electromagnetic valve R131, the medium-temperature high-pressure refrigerant flows through the surrounding tubes to further exchange heat with cooling water in the cooling water tank C6 to be cooled and condensed, the temperature and the pressure of the refrigerant are further reduced, and the refrigerant is fully liquefied. The medium-temperature and medium-pressure liquid refrigerant after phase change flows out from a liquid collecting port (collecting box refrigerant outlet 307) of an open type spiral wound condenser R3, passes through a first one-way valve R121, then sequentially passes through a liquid storage tank R5 and a drying filter R6, then flows through an electronic expansion valve R8 for throttling and pressure reduction, the low-temperature and low-pressure refrigerant liquid passes through a second one-way valve R122 and then enters an indoor side heat exchanger R9, the low-temperature and low-pressure liquid refrigerant exchanges heat with secondary refrigerant water flowing through the heat exchanger in an indoor side heat exchanger R9, the hot water is cooled to be chilled water for indoor use, the liquid refrigerant is vaporized into refrigerant steam after being heated, the vapor refrigerant enters and exits from a d end and a c end of a four-way valve R2 and returns to a return port 12 of a low-power compressor R1 after passing through a gas-. The whole refrigeration process is the process of the vapor-liquid phase interactive transformation of the refrigerant reciprocating circulation.

In the cooling mode, the fan C4 in the cooling circulation system is started; cooling circulation pump C1 is started; sprayer C2 is in the spray position. High temperature cooling water sprays the packing layer top evenly, the cooling water flows down along cooling packing layer C7 surface under self action of gravity, a thin layer water film has been formed, because the temperature of cooling water is higher than packing layer surface air temperature, the saturated steam that the water film surface formed is atomized by the condensation, outdoor ambient air after the effect of fan C4 with air-cooled finned heat exchanger R4 heat transfer sweeps over cooling packing layer C7 surface and discharges steam to ambient air, a large amount of heats have been taken away after the cooling water vaporization, the circulating water has been cooled off and has obtained low temperature cooling water, the heat has been taken away to the air makes the interior refrigerant of air-cooled finned heat exchanger R4 by preliminary condensation liquefaction cooling. The low-temperature cooling water is evenly sprayed on the upper surface of a cooling water tank C6 along the bottom surface of a cooling filler layer C7 to form a cooling water layer with the same temperature, the cooling water on the same temperature layer moves downwards along a micro-channel of an open spiral winding type condenser R3 under the multiple actions of self gravity flow, a cooling circulating pump C1 and a water distributor C3, the whole water layer carries out heat convection with the medium-temperature high-pressure refrigerant mixed liquid after the preliminary cooling in each refrigerant tube winding layer, and the refrigerant is completely condensed and liquefied. The temperature of the downward movement of the cooling water is gradually increased, and the speed of the downward movement of the cooling water layer is lower, so that the time of the cooling water in the cooling water tank C6 is prolonged, and the temperature reaches the highest point when the cooling water layer descends to the bottom tube array layer. The cooling water of higher temperature evaporates on cooling water tank surface and can takes away more heats, and the increase of latent heat transfer volume can corresponding reduction cooling water circulation volume reduces cooling circulation pump power, improves the whole efficiency of unit. The evaporated water vapor is discharged to the air by the blower C4. Cooling water passes through the water distribution heads of the water distributor C3 which are uniformly distributed at the bottom of the cooling water tank C6, and each branch pipe converges to the main pipe to enter the cooling circulating pump C1, and then enters the sprayer C2 through the cooling circulating pipe to participate in the next circulation. The heat of the refrigerant is finally transferred to the atmosphere through the forms of water vapor and hot air, so that the purposes of condensation and temperature reduction are achieved.

Or, the outlet 11 of the low-power compressor R1 is connected to the X interface of the air-cooled finned heat exchanger R4 through the inlet and outlet of the a end and the b end of the four-way valve R2, the Y interface of the air-cooled finned heat exchanger R4 is connected to the P interface of the indoor-side heat exchanger R9 through the second solenoid valve R132, the first check valve R121, the U interface of the functional module, the liquid storage tank R5, the drying filter R6, the electronic expansion valve R8, and the V interface of the functional module, and the Q interface of the indoor-side heat exchanger R9 is connected to the return port 12 of the low-power compressor R1 through the inlet and the outlet of the d end and the c end of the four-way valve R2 and the gas-liquid separator R10. The specific correspondence is as shown in fig. 2 for the air-cooled refrigeration mode:

in the mode, the a-b end and the c-d end of a four-way valve R2 of the refrigerant circulating system are communicated; solenoid valve R132 is open and solenoid valve R131 is closed; the compressor R1 is in operation. High-temperature high-pressure gaseous refrigerant injected from a jet port 11 of a compressor R1 enters an air-cooled finned heat exchanger R4 after entering from an end a and exiting from an end b of a four-way valve R2, exchanges heat with cold air flowing through the surface of the air-cooled finned heat exchanger R4, cools and condenses, the air is discharged into the atmosphere by a fan C4 after being heated, the refrigerant is condensed and liquefied to change from a liquid phase to a vapor phase, the pressure and the temperature are reduced, at the moment, high-temperature high-pressure refrigerant steam is changed into medium-temperature and medium-pressure liquid refrigerant, the medium-temperature and medium-pressure liquid refrigerant passes through a liquid storage tank R5 and a drying filter R6 in sequence, the pressure of the refrigerant is further reduced after passing through an electronic expansion valve R8, low-temperature low-pressure refrigerant liquid passes through a second one-way valve R122 and then enters an indoor side heat exchanger R9, the low-temperature low-pressure liquid refrigerant exchanges, the refrigerant passes through the inlet end d and the outlet end c of the four-way valve R2, passes through the gas-liquid separator R10 and then returns to the return port 12 of the low-power compressor R1, and the refrigerant main cycle is finished and enters the next cycle.

Or, the outflow port 11 of the low-power compressor R1 is connected to the Q port of the indoor heat exchanger R9 through the a port and the d port of the four-way valve R2, the P port of the indoor heat exchanger R9 is connected to the third check valve R123, and then connected to the Y port of the air-cooled fin heat exchanger R4 through the U port of the function module, the liquid storage tank R5, the dry filter R6, the electronic expansion valve R8, and the V port of the function module, and then connected to the Y port of the air-cooled fin heat exchanger R4 through the fourth check valve R124 and the second solenoid valve R132, and the X port of the air-cooled fin heat exchanger R4 is connected to the return port 12 of the low-power compressor R1 through the gas-liquid separator R10. The specific correspondence is as shown in fig. 3 for the air cooling and heating mode:

in the mode, the R2a-d end and the c-b end of a four-way valve of the refrigerant circulating system are communicated; the first solenoid valve R131 is closed and the second solenoid valve R132 is opened; the compressor R1 is in operation. The compressor R1 is electrified to work, high-temperature and high-pressure gaseous refrigerant sprayed from the outlet 11 of the compressor R1 enters the indoor side heat exchanger R9 after entering the a end and exiting the d end of the four-way valve R2, the high-temperature and high-pressure gaseous refrigerant enters the indoor side heat exchanger R9 after heat exchange with indoor refrigerant (water) flowing through the heat exchanger, the refrigerant is condensed and liquefied at the moment, the temperature and the pressure of the refrigerant steam are reduced, the high-temperature and high-pressure refrigerant steam is changed into medium-temperature and medium-pressure liquid refrigerant after being subjected to phase change, the medium-temperature and medium-pressure liquid refrigerant passes through the third one-way valve R123 and sequentially passes through the liquid storage tank R5 and the drying filter 6, the pressure of the medium-temperature and low-pressure refrigerant after passing through the electronic expansion valve R8 is further reduced, low-temperature and low-pressure refrigerant liquid passes through the fourth one-way valve R124 and the second electromagnetic valve R132, c, the refrigerant enters a gas-liquid separator R10 from the end, returns to the return port 12 of the low-power compressor R1, and ends the main cycle of the refrigerant and enters the next cycle.

As shown in fig. 6, the outside of the indoor side heat exchanger R9 is connected to the indoor side refrigeration circulating pump R91, and at this time, the chilled water is delivered to the indoor side heat exchanger R9, which is the refrigeration main unit, through the indoor side refrigeration circulating pump R91, so as to produce low-temperature water, thereby achieving the purpose of cooling the indoor.

As shown in fig. 10, indoor side heat exchanger R9 can be replaced by indoor multiplex unit R9a, at this moment, the utility model discloses an integration water cooling air-cooled heat pump concatenates (directly expands) modular unit, indoor multiplex unit R9a includes refrigerant fin heat exchanger and indoor side fan, and indoor side fan makes the air current through refrigerant fin heat exchanger's surface, absorbs the indoor air heat and cools down through the direct vaporization of refrigerant.

Further, the connection mode between the low-power compressor R1 and the open spiral wound condenser R3 and the air-cooled finned heat exchanger R4 can be adjusted in various ways according to actual needs, such as: the air-cooled finned heat exchanger R4 is connected in parallel with the open type spiral wound condenser R3, and after high-temperature and high-pressure refrigerant steam sprayed from the low-power compressor R1 exchanges heat with cooling water through the open type spiral wound condenser R3, the refrigerant is changed into high-temperature and high-pressure liquid, and the high-temperature and high-pressure liquid enters the liquid storage tank R5.

The open spiral wound condenser R3, as shown in fig. 11-37: the refrigerant collecting box 30 is composed of an end cover 30a and a bottom plate 30b, the length and width of the end cover 30a and the bottom plate 30b are mutually matched, flange plates 300 with the same size are arranged on the outer sides of the end cover 30a and the bottom plate 30b, a plurality of screw holes 301 with matched size and position are formed in the flange plates 300, a plurality of rows of pipe holes 302 are formed in the middle of the bottom plate 30b, a box-shaped part 303 protrudes from the middle of the end cover 30a, and the bottom plate 30b and the end cover 30a penetrate through the screw holes 301 in the flange plates 300 through bolts 308 to be screwed and fastened together to form a refrigerant collecting cavity; the refrigerant collecting box 30 comprises a steam end collecting box 30-1 and a liquid end collecting box 30-2 which are oppositely arranged, and a collecting box refrigerant inlet 306 and a collecting box refrigerant outlet 307 are respectively arranged above the side of a steam end cover 30a-2 and below the side of a liquid end cover 30 a-2; the refrigerant inlet pipe 31 extends into the steam end collection box 30-1 through the collection box refrigerant inlet 306 to form a steam distribution pipe 31a, small holes are uniformly distributed on the lower edge of the steam distribution pipe 31a, refrigerant steam is uniformly sprayed into the whole steam end collection box 30-1, uniform steam admission of each spiral refrigerant array pipe winding is ensured, and the refrigerant is uniformly distributed in the array pipes to realize full condensation liquefaction effect; the refrigerant outlet pipe 32 is connected with the refrigerant outlet 307 of the collecting box, and the bottom of the liquid-state end collecting box 30-2 is provided with a guide plate 32a which forms a certain included angle with the bottom surface thereof, so that condensed refrigerant liquid is collected to the refrigerant outlet pipe, the liquid state of the refrigerant is convenient to flow out, the liquid accumulation phenomenon is prevented, and the utilization efficiency of the refrigerant is improved;

among them, what is particularly required to be mentioned are:

fig. 20 is a schematic view of the position layout of the projections of the anchor frame and the spiral refrigerant tubular column on the bottom plate according to the present invention, and the projections of the anchor frame and the spiral refrigerant tubular column on the bottom plate are axisymmetrically distributed with the center point O of the bottom plate as the axis, so that the projection is the figure shown in fig. 22 in both the left view and the right view.

Fig. 21 is a right-side view (taking the first turn of the spiral refrigerant array tube as an example) of the position distribution of the inlet section of the spiral refrigerant array tube straight tube on the steam end bottom plate of the steam end header of the present invention, that is, the position distribution of the inlet section 34-1 of the spiral refrigerant array tube straight tube on the steam end bottom plate 30b-1 from the outside right-side view of the steam end header 30-1, for convenience of description and illustration, we take the first turn of the spiral refrigerant array tube winding 34.1 as an example, and only draw the position of the inlet section 34-1 of the first turn of the spiral refrigerant array tube straight tube on the steam end bottom plate 30b-1, and sequence the position of the inlet section 34-1 of the straight tube 34.1 of the first turn of the spiral refrigerant array tube winding 34.1 on the steam end bottom plate 30b-1 according to the counterclockwise direction from 1 to 26, wherein the position of the inlet segment of the spiral refrigerant tube array straight tube at the upper right corner is 1, the position of the inlet segment of the spiral refrigerant tube array straight tube at the upper left corner is 9, the lower left corner is 14, and the lower right corner is 22; the inlet section of the straight tube of the above 26 first-turn spiral refrigerant tube array windings forms a largest tube array rectangular structure 340 at the position on the steam end bottom plate.

Similarly, fig. 22 is a schematic diagram of a right view of a position distribution of the outlet section of the spiral refrigerant tube array on the liquid end bottom plate 30b-2 of the liquid end collecting tank 30-2 (taking the first turn of spiral refrigerant tube array winding 34.1 as an example), which is a position distribution diagram of the outlet section 34-2 of the spiral refrigerant tube array on the liquid end bottom plate 30b-2 seen from the right side view of the liquid end collecting tank 30-2, and we still take the first turn of spiral refrigerant tube winding 34.1 as an example, and only show the position of the outlet section 34-2 of the first turn of spiral refrigerant tube array on the liquid end bottom plate 30 b-2. Since each spiral refrigerant array pipe 34 is wound along the anchor frame 33 of the corresponding layer in a rotating manner, the straight pipe inlet section 34-1 thereof is inevitably connected with the corresponding straight pipe outlet section 34-2 after passing through the rotating section 34-3, and the position (i.e. the position in fig. 24) of the corresponding straight pipe outlet section 34-2 on the liquid end bottom plate 30b-2 is axisymmetric with the position of the straight pipe inlet section 34-1 in fig. 23 based on the bottom plate center point O, specifically, we also number the position of the straight pipe outlet section 34-2 corresponding to the straight pipe inlet section 34-1, the position of the straight pipe inlet section 34-1 of the position 1, the position of the corresponding straight pipe outlet section 34-2 is referred to as 1 ', the position of the straight pipe inlet section 34-1 of the position 2 is referred to as 2', and so on, from 1 'to 26', another largest tube array rectangular structure 340 is formed in fig. 22, in which the position of the outlet section of the spiral refrigerant tube array at the lower left corner is 1 ', the position of the outlet section of the spiral refrigerant tube array at 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 the tube array rectangular structures 340 in fig. 21 and 22 are overlapped, the positions 1 'of the straight tube inlet section 34-1 at the position 1 and the straight tube outlet section 34-2 corresponding thereto are axisymmetric with the bottom plate center point O, the positions 2' of the straight tube inlet section 34-1 at the position 2 and the straight tube outlet section 34-2 corresponding thereto are axisymmetric, and so on, the positions of each straight tube inlet section 34-1 and the straight tube outlet section 34-2 corresponding thereto are axisymmetric in the tube array rectangular structure 340. By the design, the distance between each spiral refrigerant tube 34 and the two bottom plates 30b can be ensured to be the same, and the cooling uniformity of the refrigerant in the tubes is further ensured.

Fig. 23-35 are schematic diagrams showing the distribution of the refrigerant collecting box and the anchor frame, the side view, the side plan view and the partial position of the spiral refrigerant tube winding from the first turn to the fourth turn according to the present invention. It can be seen that the plurality of layers of anchor racks are vertically and fixedly connected between the steam end collection box 30-1 and the bottom plate 30b of the liquid end collection box 30-2, each layer of anchor rack consists of four anchor racks 33, the projections of the four anchor racks on the two bottom plates form two symmetrical anchor rack rectangular structures 330, and the anchor rack rectangular structures formed by the projections of the anchor racks on the bottom plates all take the center point O of the bottom plate as the axis and the sizes of the anchor rack rectangular structures are sequentially reduced; the plurality of turns of spiral refrigerant tube array windings are formed by a plurality of turns of spiral refrigerant tubes 34 which are externally tangent and rotated at a certain angle around the anchor frame 33 of the corresponding layer, each turn of spiral refrigerant tube array 34 consists of a plurality of spiral refrigerant tubes 34, each spiral refrigerant tube array 34 consists of a straight tube inlet section 34-1 at two ends, a straight tube outlet section 34-2 and a spiral section 34-3 in the middle, and a certain winding distance b is kept between every two spiral refrigerant tubes 34; the straight tube inlet sections 34-1 or the straight tube outlet sections 34-2 of the spiral refrigerant tubes 34 of each turn are communicated with the tube holes 302 on the bottom plate 30b, are perpendicular to the bottom plate 30b, and are arranged in the length and width directions of the bottom plate 30b in an axial symmetry manner by the center point O of the bottom plate, the projection of the straight tube inlet sections 34-1 or the straight tube outlet sections 34-2 of the spiral refrigerant tubes 34 of each turn on the corresponding bottom plate 30b (namely the positions of the spiral refrigerant tubes 34 corresponding to the tube holes 302 on the two bottom plates 30 b) forms two symmetrical tube array rectangular structures 340, the positions of the straight tube inlet sections 34-1 and the straight tube outlet sections 34-2 of each spiral refrigerant tube 34 on the tube array rectangular structures 340 obtained by the projection of the bottom plate are also in an axial symmetry manner by the center point O of the bottom plate, so as to ensure that the distance between the two bottom plates 30b of the spiral refrigerant tubes 34 is the same course, further ensuring the cooling uniformity of the refrigerant in the tubes; and the rotation angles of the spiral refrigerant tube array windings of the two adjacent turns and the anchor racks of the corresponding layers are opposite to each other, so that a micro-channel group is formed.

Fig. 36-37 are y-axis lattice diagrams and x-axis lattice diagrams of the projections of the anchor frame and the spiral refrigerant tube on the bottom plate according to the present invention. N is the total number of turns of the tube array; n is the number of turns to which a certain column of tubes belongs; d is the diameter of the anchor frame; d is the diameter of the tube array; h is the layer spacing of adjacent turn tubes in the y-axis direction; l is the tube pitch of the adjacent straight tube sections of the same turn of horizontal tube array in the x-axis direction; l is the staggered layer spacing of different turn tubes in the x-axis direction; s is the total layer height of the same turn of the row tube in the y-axis direction; s is the distance between the anchor frames of the central layer (the fourth layer in the embodiment) in the y-axis direction; e is the distance between the same-turn tube array side wings in the y-axis direction; m is the total distance of the straight pipe sections of the same turn of horizontal tubes in the x-axis direction; m is the distance between adjacent column tubes of the same turn on the y axis in the x axis direction; b is the adjacent winding distance of the same turn of tube array; r is the diameter of the anchor frame supporting section; r is the diameter of the anchor frame fixing section; lambda is the equal number of the vertical sides of the side wings; o is the origin (center point); beta is the number of X axial tubes; k is equal number of the tubes in the X-axis direction (except the y-axis of the tubes with the same turns).

Each point on the bottom plate comprises a screw hole 301, an anchor frame point (a connection point of an anchor frame fixing section on the bottom plate) and a tube array hole 302 which are in centrosymmetric arrangement with 0 as an origin. The distance between the adjacent anchor frame layer centers and the layer spacing in the y-axis direction of the adjacent turn tubes is equal to H, the distance between the adjacent anchor frame layers is equal to the sum of the diameter D of the tubes and the diameter D of the anchor frame, namely H + D, the anchor frame has enough strength to ensure that the tubes are not deformed when being wound, and the diameter D of the winding section of the anchor frame determines the layer spacing. The diameter D of the anchor frame is larger than the diameter D of the array pipe, namely D is larger than D; the lower sides of the outer walls of the straight pipe sections of the same turn of the array pipe are tangent to the upper side of the outer wall of the anchor frame on the same layer in the x-axis direction, and the inner sides of the outer walls of the same turn of the array pipe are tangent to the outer side of the anchor frame on the same layer in the y-axis vertical direction; the outer walls of the adjacent tubes are tangent to the outer wall of the anchor frame; the distance Sn between the same turns of the tube array on the y-axis is the difference between the central anchor tube distance s and the sum of the diameter D of each turn of the tube array on all the y-axes and the diameter D of the anchor frame, namely Sn is (s-D) +2H (N-N +1) ═ s-D) +2(D + D) (N-N +1), wherein 0 is less than or equal to s. When the diameter D of the anchor frame, the diameter D of the row tubes and the number N of turn layers are determined, the S-space determines the height of the total layer height S in the y-axis direction of the row tubes with the same turn. In the scheme, the y-axis distance S1 of a first turn of the array tube is (S-D) +8(D + D), the y-axis distance S2 of a second turn of the array tube is (S-D) +6(D + D), the y-axis distance S3 of a third turn of the array tube is (S-D) +4(D + D), and the y-axis distance S4 of a fourth turn of the array tube is (S-D) +2(D + D); the distance E between the same-turn tube array flanks is distributed in equal parts, adjacent winding layers are arranged in parallel, the distance En between the same-turn tube array flanks is Sn/lambda n, the distance E1 between the first-turn tube array flanks is S1/lambda 1, the distance E2 between the second-turn tube array flanks is S2/lambda 2, the distance E3 between the third-turn tube array flanks is S3/lambda 3, the distance E4 between the fourth-turn tube array flanks is S4/lambda 4, and En is more than or equal to D + D/2.

The straight pipe sections of the adjacent circles of the straight pipe sections in the x-axis (horizontal) direction are arranged at equal intervals (except for the adjacent circles at the central axis), and L is the pipe distance in the x-axis direction of the adjacent straight pipe sections of the same-circle horizontal circles; the distance between adjacent tubes at the central axis is mn, mn is 2Ln is 2L [1- (N-1)/N ]. The first turn m1 in this example is 2L; the second turn m2 ═ 3/2L; the third turn m3 is L, and the fourth turn m4 is 1/2L. The total distance of the tubes in the X-axis direction is Mn, Mn is L X [ k-2(N-1)/N ], in the case, the total axial length M1 of a first turn of tube is kL, the total axial length M2 of a second turn of tube is L (k-1/2), the total axial length M3 of a third turn of tube is L (k-1), and the total axial length M4 of a fourth turn of tube is L (k-3/2). The lateral wings of the turn tubes are arranged in equal staggered layers from the outer side to the inner side, the distance between the adjacent straight tube sections in the x-axis projection is equal, the distance is the ratio L ' of the tube distance L in the x-axis direction of the adjacent straight tube sections of the same turn horizontal tube array to the number N of the layers, and the minimum staggered layer distance L ' is kept on the premise of ensuring the winding, so that the maximum horizontal cross section of each layer can be ensured, and the heat exchange effect is improved, wherein L ' is L/4; the distance ln of the side wings of different coil arrays in the x-axis direction is equal to L [1- (N-1)/N ], L is more than or equal to Nd, and L1 is equal to L; l2 ═ 3/4L; l3 ═ 1/2L; l4 ═ 1/4L.

The total distance M of the straight pipe sections of the same-turn horizontal tube array in the x-axis direction is greater than the total layer height S of the same-turn tube array in the y-axis direction, and the cross section of the open type spiral wound condenser R3 is ensured to have a larger evaporation surface A.

The heat exchange area of the open spiral wound condenser R3 was accounted for as follows:

the first step of heat exchange quantity accounting:

the heat exchange quantity of the condenser is known as Qr, the heat consumption Qw and the refrigerating capacity Qc of the compressor are obtained by the law of energy conservation:

Qr＝Qw+Qc

and a second step of heat transfer area accounting:

the known heat conductivity coefficient K, Tr is the average temperature of the hotter medium, Δ t is the average temperature of the secondary heat medium, and the heat exchange area is A according to a heat transfer formula; obtaining:

A＝Qr/K(Tr-△t)

thirdly, calculating the length of the tube array:

knowing the heat exchange area A and the diameter d of the tube array, and calculating the total length L of each tube array winding according to an area formula; obtaining:

L＝A/dπ

the number of the tubes, the number of winding turns and the winding distance are adjusted according to the conditions of installation space, section size and the like, and the actual total length is not less than the designed length L.

Compared with a parallel tube in-line or spiral circle wound heat exchanger, the structure has the advantages of small volume and high winding density, longer extension length can be obtained on the same axis, tube pass is increased, heat exchange area A of a single tube array is increased, and more heat exchange quantity Qr is obtained as A x K (Tr-delta t):

the x-axis distance M is larger than the y-axis distance S, so that the cross section area of the condenser is increased, a larger evaporation area of the cooling water tank can be ensured, and the evaporation of cooling water is facilitated; the small staggered-layer spacing l' between the turn-row tubes not only ensures that the side wing rows of each layer are uniformly distributed, but also ensures that the cross section of each winding layer is maximum, the winding quantity is increased, the total heat exchange area A is increased, and more heat exchange quantity is obtained; qr ═ a × K (Tr- Δ t);

the minimum winding distance b of the tubes is kept under the condition of ensuring cleaning, so that the density of the tubes can be increased, the micro-channel formed by upper and lower staggered layers is smaller, and the heat exchange is more sufficient;

the adjacent turns of tube array are in a reverse winding structure, the tube bundles on the upper layer and the lower layer form baffling, the disturbance of water is increased, the flow direction and the flow speed of fluid are continuously changed, turbulence can be achieved under the condition of very low Reynolds number (Re < 100), the heat transfer coefficient K is improved, and more heat exchange quantity is obtained; qr ═ a × K (Tr- Δ t);

the distance between the anchor racks of the adjacent layers and the distance between the tube arrays of the adjacent layers are designed to be equal in distance H, and after the tube arrays of the adjacent layers are wound, the adjacent windings and the anchor racks form a non-distance structure, so that the whole condenser forms a compact integrated structure, and the overall strength of the condenser is enhanced;

to sum up: the open type spiral winding type condenser R3 has the advantages of compact structure, small volume, high heat exchange efficiency and easy maintenance.

Of course, the open spiral wound condenser R3 may be replaced with a spiral submerged condenser or a shell and tube submerged condenser.

The water distributor C3 adopts an H-shaped same-course multi-stage water distributor, can adopt galvanized steel pipes, PUC pipes, PE and other metal pipes, plastic pipes and the like, and comprises a water distributor header pipe C300, a multi-stage water distribution pipe and a plurality of water distribution heads C307 which are mutually communicated, wherein the lower-stage water distribution pipe of each stage is vertically connected with the upper-stage water distribution pipe to form a multi-stage H shape, the water distribution heads are distributed at two ends of the last-stage water distribution pipe, and finally, the water distribution heads C307 are displayed on the same horizontal plane, and each adjacent water distribution head C307 is arranged at equal intervals, thereby forming an even water distribution head array; the other end of the water distributor main pipe C300 is communicated with a cooling circulating pump C1, cooling water subjected to heat exchange and temperature rise in the cooling water tank C6 passes through the uniformly distributed water distribution heads C307, enters the multistage water distribution pipe and the water distributor main pipe C300, and finally enters the cooling circulating pump C1 and the sprayer C2 through the cooling pump guide pipe to enter the next cooling circulation. In this embodiment, as shown in fig. 38, the H-shaped multi-stage water distributor is a 6-stage water distributor, and includes a water distributor header pipe C300, a first-stage water distribution pipe C301, a second-stage water distribution pipe C302, a third-stage water distribution pipe C303, a fourth-stage water distribution pipe C304, a fifth-stage water distribution pipe C305, a sixth-stage water distribution pipe C306, and a plurality of water distribution heads 307.

The H-shaped same-pass multistage water distributor can enable the low-temperature cooling water cooled on the surface of the cooling water tank to move downwards along the vertical direction on the same horizontal plane, ensure that the low-temperature cooling water exchanges heat with the refrigerant tubes layer by layer downwards, and gradually increase the temperature of the cooling water as the refrigerants in the tubes are cooled. The cooling water after temperature rise can effectively prevent disordered heat exchange between the cooling water and the refrigerant tubes through the arrangement of the H-shaped same-pass multistage water distributor, and ensures that the low-temperature cooling water vertically flows through each layer of tubes in a layered manner on the same horizontal plane, thereby improving the cooling effect of the cooling water and the cooling efficiency of the refrigerant. According to the specific heat capacity of the temperature difference C of the cross section area rho density delta T of the flow velocity VVx S; the cross-sectional area of V velocity of flow S is the definite value, and rho density, C specific heat capacity are the constants, because the cross-sectional area of open cooling water tank is hundreds of times of cooling circulation pipe, lead to cooling water velocity of flow V velocity of flow to reduce, and then cooling water detention water tank time extension.

Although the embodiments of the present invention have been described in the specification, these embodiments are only for the purpose of presentation and should not be construed as limiting the scope of the present invention. Various omissions, substitutions, and changes may be made without departing from the spirit and scope of the invention.

Claims

1. The integrated water cooling and air cooling heat pump module unit is characterized by comprising a small cooling tower shell, a cooling system, a refrigerant circulating system and a functional module, wherein the cooling system, the refrigerant circulating system and the functional module are integrated in the small cooling tower shell; the cooling system comprises a fan, a water distributor, a cooling circulating pump, a sprayer, a cooling packing layer and a cooling water tank, and the refrigerant circulating system comprises a low-power compressor, an air-cooled finned heat exchanger, an open spiral wound condenser, a four-way valve, an indoor side heat exchanger and a gas-liquid separator; the functional module comprises a liquid storage tank, a drying filter, an electronic expansion valve and a plurality of one-way valves which are connected with each other; the cooling water tank is arranged at the upper part inside the small cooling tower shell, and the low-power compressor, the liquid storage tank, the drying filter, the electronic expansion valve, the plurality of one-way valves and the indoor side heat exchanger are arranged outside the cooling water tank; the air-cooled finned heat exchanger is arranged between the water baffles on the periphery above the cooling water tank and the inner wall of the small cooling tower shell; the open type spiral winding condenser is soaked in the cooling water of the cooling water tank; the water distributor is arranged at the bottom inside the cooling water tank; the sprayer is arranged above the cooling filler layer; the fan is arranged at the top of the small cooling tower shell; the low-power compressor is connected with the air-cooled finned heat exchanger and the open type spiral wound condenser through the four-way valve, and then is connected with the low-power compressor through the functional module, the indoor side heat exchanger, the four-way valve and the gas-liquid separator.

2. The integrated water cooling air cooling heat pump module unit according to claim 1, wherein the low-power compressor is connected with the air cooling finned heat exchanger through the four-way valve, and then connected with the low-power compressor through the functional module, the indoor side heat exchanger, the four-way valve and the gas-liquid separator.

3. The integrated water cooling air cooling heat pump module unit as set forth in claim 1, wherein the low power compressor is connected to the indoor side heat exchanger through the four-way valve, and then connected to the low power compressor through the functional module, the air cooling fin type heat exchanger, the four-way valve and the gas-liquid separator.

4. The integrated water cooling air-cooled heat pump module unit as set forth in any one of claims 1 to 3, wherein the small cooling tower shell comprises a top plate, a base, a guard plate, and a water baffle plate installed around the upper part inside the guard plate; a drain valve and a drain outlet are arranged at the bottom of the cooling water tank, and the drain outlet is connected to the lower part of the guard plate; a water replenishing port and a ball float valve are arranged in the middle of a protective plate of the small cooling tower shell, external cooling water enters from the water replenishing port, and the ball float valve is switched on and off to automatically replenish water into the cooling water tank when needed; the lower part of the guard plate of the small cooling tower shell is provided with an external chilled water outlet and a chilled water inlet which are respectively communicated with a chilled water inlet and a chilled water outlet of the indoor side heat exchanger; and a control cabinet is arranged on the lower part of the guard plate of the small cooling tower shell and used for controlling an electric switch of the integrated water cooling low-temperature type air-cooled heat pump module unit.

5. The integrated water cooling air cooling heat pump module unit as claimed in claim 1, wherein the low power compressor is a compressor consuming 5-25KW of power and having an outlet and a return; the indoor side heat exchanger is provided with an P, Q interface; the plurality of one-way valves comprise a first one-way valve, a second one-way valve, a third one-way valve and a fourth one-way valve; the function module is provided with an U, V interface; the air-cooled finned heat exchanger is provided with an X, Y interface, and the open type spiral winding condenser is provided with a collecting tank refrigerant inlet and a collecting tank refrigerant outlet; the four-way valve comprises a, b, c and d ends; an outlet of the low-power compressor is connected with an X interface of the air-cooled finned heat exchanger through an end a and an end b of the four-way valve; the Y interface of the air-cooled finned heat exchanger enters and exits from a cold medium outlet of a collecting box through a first electromagnetic valve and a cold medium inlet of the collecting box of an open spiral wound condenser, passes through a U interface of a first one-way valve, a functional module, a liquid storage tank, a drying filter and a V interface of the functional module, and is connected with a P interface of an indoor side heat exchanger through a second one-way valve, and a Q interface of the indoor side heat exchanger enters and exits through a d end and a c end of a four-way valve and is connected with a backflow port of the low-power compressor through a gas-liquid separator.

6. The integrated water cooling air cooling heat pump module unit as claimed in claim 2, wherein the low power compressor is a compressor consuming 5-25KW of power and having an outlet and a return; the indoor side heat exchanger is provided with an P, Q interface; the plurality of one-way valves comprise a first one-way valve, a second one-way valve, a third one-way valve and a fourth one-way valve; the function module is provided with an U, V interface; the air-cooled finned heat exchanger is provided with an X, Y interface, and the open type spiral winding condenser is provided with a collecting tank refrigerant inlet and a collecting tank refrigerant outlet; the four-way valve comprises a, b, c and d ends; the outflow port of the low-power compressor enters from the end a of the four-way valve and exits from the end b of the four-way valve and is connected with the X interface of the air-cooled finned heat exchanger, the Y interface of the air-cooled finned heat exchanger is connected with the P interface of the indoor side heat exchanger through the second electromagnetic valve, the first one-way valve, the U interface of the functional module, the liquid storage tank, the drying filter, the electronic expansion valve and the V interface of the functional module, and the Q interface of the indoor side heat exchanger enters from the end d of the four-way valve and exits from the end c of the four-way valve and is connected with the backflow port of the low-power compressor through the gas-liquid.

7. The integrated water cooling air cooling heat pump module unit according to claim 3, wherein the low power compressor is a compressor consuming 5-25KW power and having a flow outlet and a flow return outlet; the indoor side heat exchanger is provided with an P, Q interface; the plurality of one-way valves comprise a first one-way valve, a second one-way valve, a third one-way valve and a fourth one-way valve; the function module is provided with an U, V interface; the air-cooled finned heat exchanger is provided with an X, Y interface, and the open type spiral winding condenser is provided with a collecting tank refrigerant inlet and a collecting tank refrigerant outlet; the four-way valve comprises a, b, c and d ends; the outflow port of the low-power compressor enters from the end a of the four-way valve and exits from the end d of the four-way valve and is connected with the Q interface of the indoor side heat exchanger, after the P interface of the indoor side heat exchanger is connected with the third one-way valve, the P interface of the indoor side heat exchanger passes through the U interface of the functional module, the liquid storage tank, the drying filter, the electronic expansion valve and the V interface of the functional module and is connected with the Y interface of the air-cooled finned heat exchanger through the fourth one-way valve and the second electromagnetic valve, and the X interface of the air-cooled finned heat exchanger enters from the end b of the four-way valve and exits from the end c of the four-way valve.

8. The integrated water cooling air cooling heat pump module unit as set forth in claim 1, wherein the indoor side heat exchanger is replaced by an indoor multiple unit.

9. The integrated water cooling air cooling heat pump module unit according to claim 1, wherein the open type spiral wound condenser comprises a refrigerant collecting box, a plurality of turns of spiral refrigerant tube array windings, a plurality of layers of anchor racks, a refrigerant inlet tube and a refrigerant outlet tube, the refrigerant collecting box is composed of an end cover and a bottom plate, the length and width of the end cover and the bottom plate are matched with each other, flange plates with the same size are arranged on the outer sides of the end cover and the bottom plate, a plurality of screw holes with matched size and position are arranged on the flange plates, a plurality of tube holes are arranged in the middle of the bottom plate, a box part protrudes from the middle of the end cover, and the bottom plate and the end cover are screwed and fastened together by penetrating through the screw holes on the flange plates; the refrigerant collecting box comprises a steam end collecting box and a liquid end collecting box which are oppositely arranged, and a collecting box refrigerant inlet and a collecting box refrigerant outlet are respectively arranged above the side of the steam end cover and below the side of the liquid end cover; the refrigerant inlet pipe extends to the steam end collecting box through the refrigerant inlet of the collecting box to form a steam distribution pipe, and small holes are uniformly distributed on the lower edge of the steam distribution pipe; the liquid end collector box is provided with a liquid end collector box bottom which is provided with a guide plate forming a certain included angle with the bottom surface; the cooling water tank is internally provided with an H-shaped same-pass multi-stage water distributor which comprises a water distributor header pipe, a multi-stage water distribution pipe and a plurality of water distribution heads, wherein the water distributor header pipe, the multi-stage water distribution pipe and the plurality of water distribution heads are mutually communicated; the other end of the water distributor main pipe is communicated with a cooling circulating pump.