CN213237757U - Air-cooled air conditioner - Google Patents

Abstract

An air-cooled air conditioner comprises an air side heat exchanger, a user side heat exchanger and a compressor, wherein the air side heat exchanger comprises a plurality of fins and a plurality of heat exchange tubes penetrating through the fins respectively, the plurality of heat exchange tubes at the top of the air side heat exchanger are connected in series to form a heat exchange loop, the plurality of heat exchange tubes at the bottom of the air side heat exchanger are connected in series to form an ice suppression loop, one ends of the heat exchange loop and the ice suppression loop are connected through a distributor and a throttling mechanism, the other ends of the heat exchange loop and the ice suppression loop are connected with a refrigerant loop respectively, the throttling mechanism can increase the pressure of the refrigerant in the ice suppression loop, so that the temperature of the refrigerant in the ice suppression loop is higher than the temperature of inlet air, the pressure of the refrigerant in the heat exchange loop is reduced, the temperature of the refrigerant in the heat exchange loop is lower than the temperature of inlet air, the pressure of the refrigerant in the ice suppression loop and the heat exchange, the bottom of the air side heat exchanger is prevented from freezing.

Description

Air-cooled air conditioner

Technical Field

The utility model relates to an air conditioner field especially relates to an air-cooled air conditioner.

Background

Air-cooled air conditioning unit can acquire cold volume or heat through the mode of carrying out the heat exchange with the air, air-cooled air conditioning unit generally comprises parts such as air side heat exchanger, user side heat exchanger, fan, compressor, electric cabinet and water dish, when air conditioning unit heats the operation, if air side heat exchanger temperature is less than dew point temperature, the condensate water can appear on the surface on the air side heat exchanger, the condensate water can frost under low temperature environment and cover on air side heat exchanger, if the heat transfer effect of untimely defrosting can reduce air side heat exchanger surface and air.

In addition, the air-cooled air conditioning unit is generally placed outdoors and is in contact with the outdoor environment, so natural rainfall can enter the air-cooled air conditioning unit from the gap between fan blades, and condensed water and defrosting water on the air side heat exchanger can be accumulated on the water tray together when the air-cooled air conditioning unit heats. If ponding on the water tray can not in time discharge, crosses when low ponding at ambient temperature and freezes easily, and the ice sheet can increase and the bodiness along time, and up freezes gradually along air side heat exchanger fin, hinders air side heat exchanger circulation of air, and then reduces air side heat exchanger's heat exchange capacity, and ponding can soak or get into electric cabinet and other parts moreover, leads to the trouble and rusts, influences life.

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to overcome prior art's defect, provide an air-cooled air conditioner that can restrain and freeze. In order to achieve the above purpose, the utility model adopts the following technical scheme:

an air-cooled air conditioner comprises an air side heat exchanger, a user side heat exchanger and a compressor, wherein the air side heat exchanger comprises a plurality of fins and a plurality of heat exchange tubes penetrating through the fins respectively, the plurality of heat exchange tubes at the top of the air side heat exchanger are connected in series to form a heat exchange loop, the plurality of heat exchange tubes at the bottom of the air side heat exchanger are connected in series to form an ice suppression loop, one ends of the heat exchange loop and the ice suppression loop are connected through a distributor and a throttling mechanism, the other ends of the heat exchange loop and the ice suppression loop are connected with a refrigerant loop respectively, and the throttling mechanism can increase the pressure of a refrigerant in the ice suppression loop, so that the temperature of the refrigerant in the ice suppression loop is higher than the temperature of inlet air, and reduce the pressure of the refrigerant in the heat.

Preferably, the throttle mechanism comprises a throttle plate arranged in the distributor, and a throttle hole is arranged on the throttle plate.

Preferably, the throttle mechanism includes an expansion valve connected between the ice suppression circuit and the dispenser.

Preferably, the system further comprises a control system, an air temperature sensor for acquiring the ambient temperature T0, a fin temperature sensor for acquiring the fin temperature T1 of the air-side heat exchanger, and a post-valve temperature sensor for acquiring the post-throttling temperature T2 of the refrigerant in the heat exchange circuit, wherein the expansion valve, the air temperature sensor, the fin temperature sensor, and the post-valve temperature sensor are respectively connected with the control system, and the control system controls the opening degree of the expansion valve according to the difference between the post-throttling temperature T2 and the ambient temperature T0.

Preferably, the distributor includes branch liquid portion and hydrops portion, is equipped with a plurality of branch pipes in dividing the liquid portion, and the one end of a plurality of branch pipes is connected with the heat transfer circuit that corresponds through the capillary respectively, and the other end of a plurality of branch pipes communicates with the one end of hydrops portion respectively, and the other end of hydrops portion passes through hydrops pipe and presses down ice return circuit intercommunication to make the refrigerant intensive mixing of gas-liquid two-phase mixture.

Preferably, the throttling mechanism comprises an expansion valve arranged in the liquid accumulating pipe and/or a throttling plate arranged in the liquid accumulating part, a throttling hole is arranged in the middle of the throttling plate, and the inner diameter of the throttling hole is smaller than that of the liquid accumulating part.

Preferably, the throttle plate is mounted on or integrally formed with an inner wall of the liquid trap portion; or the throttle plate is integrally formed at the end part of the liquid accumulating pipe, and one end of the liquid accumulating pipe, which is provided with the throttle plate, is inserted into the inner wall of the liquid accumulating part.

Preferably, when the fin temperature T1 meets the frost point condition, if the difference between the throttled temperature T2 and the ambient temperature T0 is greater than the setting parameter a, the control system controls the expansion valve to increase the opening degree; if the difference value between the throttled temperature T2 and the ambient temperature T0 is less than the set parameter a and less than 0, the control system reduces the opening degree of the expansion valve by the amplitude of B1; and if the difference between the throttled temperature T2 and the ambient temperature T0 is less than the set parameter a and greater than 0, the control system reduces the opening degree of the expansion valve by the amplitude B2, wherein B2 is less than B1.

Preferably, one end of the liquid collecting part is connected with the periphery of the vertex angle of the liquid separating part, a distribution boss in a cone structure is arranged at the vertex angle of the liquid separating part, and the vertex angle of the distribution boss is opposite to the throttling hole.

Preferably, the refrigerant enters the heat exchange loop through the heat exchange header pipe, is collected by the distributor and then enters the ice suppression header pipe through the ice suppression loop, and the heat exchange header pipe and the ice suppression header pipe are respectively arranged at two ends of the air side heat exchanger.

The utility model discloses an air-cooled air conditioner, heat transfer circuit are the same with the structure in the return circuit that suppresses ice, establish ties by a plurality of heat exchange tubes in the air side heat exchanger respectively and constitute, but heat transfer circuit and the one end in the return circuit that suppresses ice pass through distributor and throttle mechanism and link to each other, change the refrigerant through throttle mechanism and press down the pressure in return circuit and heat transfer circuit respectively, make the refrigerant temperature in the return circuit that suppresses ice be higher than the air inlet temperature when heating, prevent that the bottom of air side heat exchanger from freezing.

Drawings

Fig. 1 is a schematic structural view of an air-cooled air conditioner according to an embodiment of the present invention;

fig. 2 is a schematic view of the internal structure of the air-cooled air conditioner according to the embodiment of the present invention;

fig. 3 is a schematic view of the internal structure of the air-cooled air conditioner according to the embodiment of the present invention after the fan is omitted;

fig. 4 is a front view of the embodiment of the present invention fig. 3;

FIG. 5 is a top view of a water tray according to an embodiment of the present invention;

FIG. 6 is a schematic diagram of the air-side heat exchanger and the water tray according to the embodiment of the present invention;

FIG. 7 is a schematic structural diagram of an air-side heat exchanger according to an embodiment of the present invention;

fig. 8 is a schematic view of the internal structure of an air-side heat exchanger according to an embodiment of the present invention;

fig. 9 is a schematic structural view of a distributor according to an embodiment of the present invention;

fig. 10 is a schematic structural view of a first embodiment of the throttle mechanism of the present invention;

fig. 11 is another schematic structural diagram of a first embodiment of a throttle mechanism according to an embodiment of the present invention;

fig. 12 is a pressure-enthalpy diagram of the heating process according to the embodiment of the throttle mechanism of the present invention;

fig. 13 is a pressure-enthalpy diagram of an embodiment of the throttle mechanism of the present invention during defrosting and cooling;

fig. 14 is a schematic structural view of a second embodiment of the throttle mechanism of the present invention;

fig. 15 is a pressure-enthalpy diagram of the second embodiment of the throttle mechanism of the present invention in the heating process.

Detailed Description

The following describes the air-cooled air conditioner according to the present invention with reference to the embodiments shown in fig. 1 to 15. The air-cooled air conditioner of the present invention is not limited to the description of the following embodiments.

The utility model discloses an air-cooled air conditioner includes casing 100 and installs air side heat exchanger 200, user side heat exchanger 310, electric cabinet 320, compressor 330 and the auxiliary component 340 in casing 100 respectively, is equipped with fan 440 at the top of casing 100, and compressor 330 can drive the refrigerant and carry out the heat exchange between air side heat exchanger 200 and user side heat exchanger 310.

As shown in fig. 2-4, the utility model discloses an air-cooled air conditioner has the characteristics of the drainage of being convenient for, the utility model discloses an air-cooled air conditioner is equipped with water tray 400 in the bottom of casing 100, and water tray 400 is including setting up at ring platform 410 all around and setting up at the mounting panel 420 at the middle part, and mounting panel 420 highly is less than ring platform 410, and is equipped with a plurality of wash ports 440 on mounting panel 420, and the side downward sloping of ring platform 410 is connected with mounting panel 420 and is formed flow guide surface 430, user side heat exchanger 310, compressor 330 and auxiliary component 340 install respectively on mounting panel 420, one side of air side heat exchanger 200 bottom corresponds the top at flow guide surface 430, electric cabinet 320 and air side heat exchanger 200 correspond the top at ring platform 410 respectively.

The utility model discloses an air-cooled air conditioner reduces highly forming at water tray center through the mounting panel and is used for guiding ponding exhaust recess to highly carrying out the overall arrangement with the part in the casing respectively corresponding ring platform and mounting panel, can guide the ponding discharge in the whole casing space, not only can guide condensation water and defrosting water on the air side heat exchanger, but also can guide the condensation water on natural precipitation and other parts, guarantee that the ponding that various forms arouse can not freeze and hinder the circulation of air, also can not soak the part in the casing.

Referring to fig. 6, the bottom of the air-side heat exchanger 200 is located above the connection between the annular table 410 and the flow guiding surface 430, the bottom of the air-side heat exchanger 200 is spaced from the annular table 410, and the distance from the air-side heat exchanger 200 to the annular table 410 is the distance d. The larger the distance d is, the more serious the air leakage is, the poorer the heat exchange effect is, and the better the drainage effect is; the smaller the distance d, the less the air leakage, the less the heat exchange effect and the poorer the drainage effect. When the distance d is within 5mm, accumulated water can be discharged, and influence on heat exchange caused by a large amount of air leakage at the distance d can be avoided.

Further, above the flow guide surface 430 on one side of the bottom of the air-side heat exchanger 200, the other side of the bottom of the air-side heat exchanger 200 is in contact with the annular table 410, that is, the distance d is equal to 0. When the distance d is zero, air can be completely prevented from being discharged from the gap d, the heat exchange effect of the air-side heat exchanger 200 is optimal, and meanwhile, accumulated water can be smoothly discharged because the part of the bottom of the air-side heat exchanger 200, which corresponds to the part above the flow guide surface 420, is suspended. Specifically, the width of the bottom of the air-side heat exchanger 200 is L, one side of the bottom of the air-side heat exchanger 200 is opposite to the annular table 410, and the other side of the bottom of the air-side heat exchanger 200 is opposite to the flow guide surface 420, wherein the width of the bottom of the air-side heat exchanger 200 opposite to the annular table 410 is L1, and the above parameters ensure that 0< L1< L makes the part of the bottom of the air-side heat exchanger 200 corresponding to the flow guide surface 420 suspended in the air

Further, a plurality of drain holes 440 are formed on the mounting plate 420 to correspond to the circumference of the bottoms of the user-side heat exchanger 310, the compressor 330, and the auxiliary unit 340. Although the water discharge hole 440 is formed on the mounting plate 420, it is difficult to completely level the surface of the mounting plate 420, and even if the surface of the mounting plate 420 is flat, the user-side heat exchanger 310, the compressor 330 and the auxiliary unit 340 are easily inclined and recessed when being mounted, so that the water discharge hole 440 is no longer located at the lowest position, and the accumulated water has viscosity, and it is still impossible to ensure that the accumulated water is completely discharged from the water discharge hole 440. When the user-side heat exchanger 310, the compressor 330 and the auxiliary component 340 of the embodiment are installed in the installation plate 420, the surfaces of the installation plate 420 at the periphery can be slightly recessed due to the self gravity of the user-side heat exchanger 310, the compressor 330 and the auxiliary component 340, and the drain holes 440 are correspondingly arranged at the slightly recessed positions of the surfaces of the installation plate 420, so that the height of the drain holes 440 can be further reduced, and the drainage effect can be improved. It will be appreciated that the location of the electrical cabinet 320 may also be reversed with respect to the air side heat exchanger 200. In addition, the bottom of the electric cabinet 320 may also correspond to the top of the joint between the ring platform 410 and the flow guiding surface 430, all belonging to the protection scope of the present invention.

As shown in fig. 3, the annular table 410 and the mounting plate 420 are respectively quadrilateral, and include four guiding surfaces 420, the four guiding surfaces 420 are respectively connected between four sides of the mounting plate 420 and the sides of the annular table 410, and the four guiding surfaces 420 are sequentially connected end to end.

Specifically, the ring platform 410 includes a front boss 411 and a rear boss 413 which are arranged oppositely, and a right boss 412 and a left boss 414 which are respectively connected to two ends of the front boss 411 and the rear boss 413, the electric cabinet 320 is installed on the left boss 414, the air-side heat exchanger 200 is in an L-shaped structure, and the right boss 412 and the rear boss 413 are correspondingly arranged below two side edges of the air-side heat exchanger 200. Of course, the air-side heat exchanger 200 may also be a U-shaped or other shaped structure, which falls within the protection scope of the present invention.

Further, the connection lines of the user side heat exchanger 310, the electric cabinet 320 and the auxiliary part 340 are arranged in a triangle, so that the stress of the mounting plate 420 can be balanced, and the side concentrated on the mounting plate 420 is avoided. Specifically, the electric cabinet 320 is arranged opposite to one side edge of the air-side heat exchanger 200, the user-side heat exchanger 310 is arranged at a position close to the side edge, the compressor 330 is arranged between the user-side heat exchanger 310 and the electric cabinet 320, the auxiliary part 340 is arranged at a position of the compressor 330 close to the other side edge of the air-side heat exchanger 200, and the auxiliary part 340 includes a gas-liquid separator, a liquid reservoir and the like.

As shown in fig. 7-8, the air-cooled air conditioner of the present invention can prevent the bottom of the air-side heat exchanger 200 from freezing, the air-side heat exchanger 200 of the air-cooled air conditioner of the present invention comprises a plurality of fins 201 and a plurality of heat exchange tubes 202 passing through the fins 201, the plurality of heat exchange tubes 202 at the top of the air-side heat exchanger 200 are connected in series to form a heat exchange loop 210, the plurality of heat exchange tubes 202 at the bottom of the air-side heat exchanger 200 are connected in series to form an ice suppressing loop 220, one end of the heat exchange loop 210 and one end of the ice suppressing loop 220 are connected through a distributor 230 and a throttling mechanism, the other end of the heat exchange loop 210 and the other end of the ice suppressing loop 220 are connected with a refrigerant loop respectively, the throttling mechanism can reduce the cross-sectional area when the refrigerant passes through, reduce the flow of the refrigerant and increase the pressure of, and reduces the pressure of the refrigeration in the heat exchange loop 210 so that the temperature of the refrigerant in the heat exchange loop 210 is lower than the temperature of the intake air.

The utility model discloses an air-cooled air conditioner, heat exchange loop 210 is the same with the structure of suppressing ice return circuit 220, establish ties by a plurality of heat exchange tubes 202 in the air side heat exchanger 200 respectively and constitute, but heat exchange loop 210 and the one end of suppressing ice return circuit 220 pass through distributor 230 and throttle mechanism and link to each other, change the refrigerant through throttle mechanism and be suppressing the pressure in ice return circuit 220 and heat exchange loop 210 respectively, make and suppress the refrigerant temperature in the ice return circuit 220 and be higher than the air inlet temperature when heating, prevent that the bottom of air side heat exchanger 200 from freezing.

When the heating mode works, the temperature of the refrigerant in the ice suppression loop 220 is higher than the temperature of the inlet air through the throttle mechanism, and the temperature of the refrigerant after entering the heat exchange loop 210 is lower than the temperature of the inlet air, because the temperature of the refrigerant in the ice suppression loop 220 is higher than the temperature of the inlet air, condensation occurs, heat is released, the bottom of the air side heat exchanger 200 is inhibited from being frozen, and meanwhile, the temperature of the refrigerant in the heat exchange loop 210 is lower than the temperature of the inlet air, evaporation occurs, heat is absorbed, and heating is achieved.

When the refrigeration mode and the defrosting mode work, the flow direction of the refrigerant is opposite to that of the heating mode, the high-temperature gas-liquid two-phase mixed refrigerant is condensed by the heat exchange loop 210 to release heat, so that the refrigerant is changed into a pure liquid state, but the throttling effect of the throttling mechanism on the pure liquid state refrigerant is small, the pressure of the pure liquid state refrigerant cannot be changed, and the temperature of the refrigerant in the whole air side heat exchanger 200 is obviously higher than the ambient temperature and 0 ℃, so the ice suppression loop 220 still can play a role in suppressing the bottom of the air side heat exchanger 200 from being frozen. In the cooling mode, the ice suppression circuit 220 is actually a supercooling section behind the condenser, and performs a supercooling (cooling) function on the refrigerant at the outlet of the condenser, so that the cooling performance is not affected.

As shown in fig. 9 to 11, in the first embodiment of the throttling mechanism, the throttling plate 241 is disposed in the distributor 230, the throttling hole 242 is disposed in the middle of the throttling plate 241, the inner diameter of the throttling hole 242 is smaller than the inner diameter of the liquid collecting part 232, and by disposing the throttling mechanism in the distributor 230, not only can the gas-liquid two-phase mixed refrigerant be throttled and the pressure of the refrigerant flowing to the heat exchange circuit 210 be reduced, but also the refrigerant, whether the gas-liquid two-phase mixed refrigerant or the pure liquid refrigerant, can be spontaneously and sufficiently mixed before being throttled by the throttling plate 241, and the refrigerant can more uniformly flow to the heat exchange circuit 210.

Specifically, the distributor 230 includes a liquid separating portion 231 and a liquid accumulating portion 232, a plurality of branch pipes 234 are arranged in the liquid separating portion 231, one ends of the plurality of branch pipes 234 are respectively connected with the corresponding heat exchange loops 210 through capillary tubes 235 with diameters far smaller than the branch pipes 234, the other ends of the plurality of branch pipes 234 are respectively communicated with one end of the liquid accumulating portion 232, and the other end of the liquid accumulating portion 232 is communicated with the ice suppressing loop 220 through the liquid accumulating pipe 233, so that refrigerant mixed by gas phase and liquid phase is fully mixed.

As shown in fig. 9, the throttle plate 241 is attached to the inner wall of the liquid accumulating portion 232, the inner wall of the liquid accumulating portion 232 is provided with a stepped surface 236 for attaching the throttle plate 241, the apex angle of the liquid separating portion 231 is provided with a distribution boss 237 having a tapered structure, the apex angle of the distribution boss 237 is disposed to face the throttle hole 242, and by disposing the apex angle of the distribution boss 237 to face the throttle hole 242, the refrigerant passing through the throttle hole 242 can flow more uniformly into the branch pipes 234 on the periphery. Of course, the throttle plate 241 may be integrally formed on the inner wall of the liquid accumulation portion 232.

Throttling in the distributor 230 enables part of liquid refrigerant to be flashed into gaseous refrigerant (volume expansion), the refrigerant is expanded in volume in a narrow space of the distributor 230, gas-liquid two-phase refrigerant can be fully mixed, and the uniform mixing can enable the flow uniformity of the distributor 230 to flow to all refrigerant loops, so that the performance of the air side heat exchanger 200 as an evaporator is improved.

The smaller the aperture of the orifice 242 is, or the thicker the throttle plate 241 is (the deeper the orifice 242 is), the larger the pressure difference and temperature difference before and after the refrigerant passes through the orifice 242 is, and in the heating operation, if the ambient temperature is lower, the surface temperature of the fin 201 is also lower, the icing difficulty of the ice suppression circuit 220 is smaller, the smaller the aperture of the required orifice 242 is, and the thicker the plate thickness of the throttle plate 241 is; the higher the ambient temperature is, the higher the surface temperature of the fin 201 is, the greater the icing difficulty is, the larger the aperture of the required throttle hole 242 is, and the thinner the plate thickness of the throttle plate 241 is; when the ambient temperature rises to a certain extent to the extent that the surface temperature of the fins 201 is higher than 0 ℃, the air-side heat exchanger 200 does not have the icing condition at this time.

In order to inhibit icing in an environment prone to icing, the orifice plate 241 and the orifice hole 242 need to be designed such that the aperture of the orifice hole 242 is small and the orifice plate 241 is thick, so that in an actual heating operation process, as the ambient temperature rises, the temperature of the refrigerant in the ice suppression circuit 220 is far higher than the ambient temperature and the difference value becomes larger and larger, and at this time, the ice suppression circuit 220 may cause a large amount of heat loss; when the surface temperature of the fin 201 is higher than 0 ℃, the throttle plate 241 and the throttle hole 242 still make the temperature of the refrigerant in the ice suppression circuit 220 higher than the ambient temperature, so that the ice suppression circuit 220 is condensed or cooled to dissipate heat to the environment, and a large amount of heat loss may also be caused.

As shown in fig. 12, which is a pressure-enthalpy diagram during heating operation of the air conditioning unit of the embodiment, T0 is an ambient temperature line, and process 1-2 is a compression process; the process 2-3 is a condensation process; the process 3-4 is a throttling process (primary throttling) of the air conditioning unit; process 4-5 is a condensation process for the ice suppression loop 220 of the air side heat exchanger 200; the process 5-6 is a throttling process (secondary throttling) of the throttling hole 242 in the throttling mechanism; process 6-1 is an evaporation process when the heat exchange loop 210 of the air side heat exchanger 200 is used as an evaporator.

The gas-liquid mixed refrigerant after primary throttling (process 3-4) of the air conditioning unit passes through the ice suppression loop 220 at the bottom of the air-side heat exchanger 200 (process 4-5), then passes through the throttling mechanism for secondary throttling (process 5-6) and then is uniformly distributed into the heat exchange loop 210 (process 6-1), because the throttling mechanism can reduce the temperature and pressure of the refrigerant, the temperature and pressure of the refrigerant in the heat exchange loop 210 (process 6-1) are lower than those of the refrigerant in the ice suppression loop 220 at the bottom (process 4-5), the throttling capacity of the throttling mechanism is adjusted, so that the temperature of the refrigerant in the ice suppression loop 220 is higher than that of inlet air (state points 4 and 5 are higher than T0), while the temperature of the refrigerant in the heat exchange loop 210 is lower than that of inlet air (state point 6 is lower than T0), at the moment, the refrigerant in the pipe of the ice suppression loop 220 dissipates heat to the air, condensation (process 4-5) occurs, heat is released, and icing outside the pipe is inhibited; and the refrigerant in the heat exchange loop 210 absorbs heat from the air and evaporates to realize heating (process 6-1).

As shown in fig. 13, the pressure-enthalpy diagrams for the cooling and defrosting operations of the air conditioning unit are substantially the same, and processes 1-2 are compression processes; process 2-3 is a condensation process when the heat exchange loop 210 is used as a condenser; the process 3-4 is a throttling process of the throttling mechanism, and at the moment, because the refrigerant entering the throttling mechanism is in a pure liquid state, the pressure drop of the refrigerant before and after passing through the throttling mechanism is not obvious, the throttling effect is very small, and the process can be ignored; the process 4-5 is a condensation or cooling process when the ice suppression loop 220 of the air side heat exchanger 200 is used as a supercooling section; the process 5-6 is a throttling process of the air conditioning unit; process 6-1 is an evaporation process when another heat exchanger in the air conditioning unit other than the air side heat exchanger 200 is used as an evaporator.

The high-temperature and high-pressure gaseous refrigerant firstly enters the heat exchange loop 210 through the heat exchange header pipe 211 (process 2-3), is condensed, releases heat, and changes the refrigerant into a pure liquid state, the refrigerant is gathered by the distributor 230 and then enters the ice suppression loop 220 at the bottom of the air side heat exchanger 200 (process 4-5), and finally enters the ice suppression header pipe 212 from the ice suppression loop 220, the ice suppression header pipe 212 and the heat exchange header pipe 211 are preferably arranged at two ends of the air side heat exchanger 200, the throttling effect of the throttling mechanism on the pure liquid refrigerant is small, the pressure of the pure liquid refrigerant cannot be changed, negligible, at this point, the temperatures of the internal refrigerants in the heat exchange circuit 210 and the ice suppression circuit 220 of the monolithic air side heat exchanger 200 are both significantly higher than ambient temperature, also higher than 0 c, the ice suppression circuit 220 can still function to suppress icing at the bottom of the heat exchanger 1. During refrigerating operation, the ice suppression loop 220 in the process 4-5 is equivalent to a supercooling section behind the heat exchange loop 210 (condenser), and at the moment, the ice suppression loop 220 performs a supercooling (cooling) function on a refrigerant at the outlet of the condenser, so that the refrigerating performance is not influenced. Preferably, a heat exchange manifold 211 and an ice suppression manifold 212 are provided at both ends of the air-side heat exchanger 200, respectively.

As shown in fig. 14 to 15, an embodiment of a throttle mechanism is a second throttle mechanism, the throttle mechanism is an expansion valve 244 disposed in the liquid accumulating tube 233, and the function of the expansion valve 244 of this embodiment is the same as that of the throttle orifice 242 of the first embodiment, but the difference is that the expansion valve 244 of this embodiment can be connected to a control system, and the expansion valve 244 can change the opening degree under the control of the control system, thereby changing the influence on the refrigerant throttling effect, which corresponds to the throttle orifice 242 with a variable inner diameter. If the temperature of the working environment changes greatly or in the extreme temperature working environment, the opening degree of the expansion valve 244 is changed, so that the pressure drop difference of the refrigerant before and after passing can meet the requirement, the ice suppression loop 220 can effectively release heat and suppress ice during heating, and the expansion valve 244 can be completely opened to avoid the influence on pure liquid refrigerant if the refrigerant is uniformly mixed at other positions during cooling and defrosting.

Of course, the expansion valve 244 of the second embodiment may or may not be shared with the expansion valve of the first embodiment. When the second embodiment and the first embodiment and the second embodiment are not used in common, the throttle mechanism comprises an expansion valve 244 or a throttle plate 241; in both embodiments, the throttle mechanism includes an expansion valve 244 and a throttle plate 241. After the expansion valve 244 is added between the distributor 230 and the ice suppression loop 220, if the throttle plate 241 in the distributor 23 is retained, the design of the throttle hole 242 should be such that the gas-liquid two-phase refrigerant is sufficiently mixed to improve the uniformity of the flow rate of the distributor 5 to each refrigerant loop, for example, the distribution boss 237 including the cone structure shown in fig. 10 and 11.

As shown in fig. 11, the throttle plate 241 is integrally formed at the end of the liquid collecting tube 233, the end of the liquid collecting tube 233 where the throttle plate 241 is disposed is inserted into the inner wall of the liquid collecting portion 232, the expansion valve 244 is located inside the liquid collecting tube 233, and the throttle plate 241 can be disposed in the distributor 230.

Fig. 15 shows a pressure-enthalpy diagram during heating operation of the air conditioning unit in this embodiment, which is basically the same as the first embodiment, except that the throttling capacity of the expansion valve 244 in this embodiment can be changed at any time, the size of the throttle hole 242 in the first embodiment is fixed, and the effect of heating operation in an extreme environment is affected, but the expansion valve 244 in this embodiment can be adjusted to the maximum opening degree in an environment without ice suppression, so as to avoid throttling of the refrigerant, prevent heat dissipation, and have the characteristics of ensuring heating effect, energy saving and environmental protection.

In fig. 15, if the temperature of the fin 201 is greater than 0 ℃, the process 5-6 corresponds to a state where the opening degree of the expansion valve 244 is the maximum, the throttling effect is very small when the opening degree of the expansion valve 244 is the maximum, and at this time, the ice suppression loop 220 and the heat exchange loop 210 have the same function and both function as an evaporator to condense, so as to improve the heating capacity of the air conditioning unit, which is a function that the throttling hole 242 does not have in the first embodiment; if the temperature of the fin 201 is less than 0 degrees, the process 5a1-6, the process 5a2-6, the process 5a4-6 and the process 5a3-6 correspond to a state in which the opening degree of the expansion valve 244 is gradually decreased, and the expansion valve 244 and the orifice 242 in the process 5a2-6, the process 5a4-6 and the process 5a3-6 function the same.

Further, the present embodiment further includes an air temperature sensor for acquiring an ambient temperature T0, a fin temperature sensor (not shown in the figure) for acquiring a fin temperature T1 on the fin 201, and a temperature sensor (not shown in the figure) after the valve for acquiring a temperature T2 after throttling of the refrigerant in the heat exchange circuit 210, wherein the expansion valve 244, the air temperature sensor, the fin temperature sensor, and the temperature sensor after the valve are respectively connected to the control system, and the temperature of the refrigerant in the ice suppression circuit 210 before the expansion valve 244 is determined by the throttling capacity of the air conditioning unit itself and can be defaulted as constant; when the fin temperature T1 satisfies the frost point temperature, which is usually 0 degrees or less, the control system controls the opening degree of the expansion valve 244 by comparing the difference between the throttled temperature T2 and the ambient temperature T0 with the setting parameter a.

When T1 is greater than 0, the temperature of the fins T1 does not meet the frost point temperature, the icing condition is avoided, the opening degree of the expansion valve is maximized, and the heat loss is avoided;

when T1 is less than or equal to 0 and T0-T2 is equal to a, the ambient temperature T0 is higher than the temperature T2 after throttling, the process 4a4-5a4 corresponds to the throttling process of the expansion valve 244, the expansion valve 244 does not need to be adjusted, the ice suppression loop 220 is in an optimal state at the moment, the ice suppression effect is achieved, and the heat released by condensation of the refrigerant in the tube of the ice suppression loop 220 just meets the set target;

when T1 is less than or equal to 0 and T0-T2> a, the process 4a3-5a3 corresponds to the throttling process of the expansion valve 244, at this time, although the ice suppression loop 220 has the effect of suppressing icing, the ice suppression loop 220 releases excessive heat, and the control system controls the expansion valve 244 to increase the opening degree;

when T1 is less than or equal to 0 and T0-T2< a, the opening degree of the expansion valve 244 is increased, in which case the magnitude of the opening degree change can be further controlled according to the magnitude of the temperature difference:

if T1 is less than or equal to 0 and T0-T2 is less than 0 and less than a, the ice suppression loop 220 cannot suppress icing, the process 4a1-5a1 corresponds to the throttling process of the expansion valve 244, and the control system reduces the opening degree of the expansion valve 244 by the amplitude of B1;

if T1 is less than or equal to 0 and < T0-T2< a, indicating that the ice suppression circuit 220 can suppress ice formation but has a weak effect, the process 4a2-5a2 corresponds to the throttling process of the expansion valve 244, and the control system decreases the opening degree of the expansion valve 244 by an amplitude B2, and then the opening degree of the expansion valve 244 by a small amplitude can be closer to the ideal state.

In actual work, the setting parameter a is generally 2-5 degrees, the larger the setting parameter a is, the better the ice suppression effect is, but the more serious the heat waste is, and vice versa. The difference between the ambient temperature T0 and the throttled temperature T2 of the refrigerant in the ice suppression circuit 200 does not appear to be equal to the ideal state of the set parameter a, and the control system is required to repeat the above comparison process in a circulating manner, and adjust the opening degree of the expansion valve 244 at different amplitudes for different situations, so that the difference is finally stabilized near the set parameter a, thereby ensuring that the ice suppression circuit 220 not only plays a role in suppressing icing, but also can control the heat loss of the ice suppression circuit 220. Further, the magnitude of the increase or decrease in the control system may be dynamic each time the opening degree of the expansion valve 244 is adjusted, that is, the greater the difference between the ambient temperature T0 and the post-throttle temperature T2 is from the setting parameter a, the greater the magnitude of the increase or decrease in the expansion valve 244 is so as to be closer to the ideal state. Preferably, B2< B1. The maximum opening state of the expansion valve 244 in this embodiment during defrosting and cooling is the same as that in fig. 13 of the first embodiment, and will not be described again here.

The foregoing is a more detailed description of the present invention, taken in conjunction with the specific preferred embodiments thereof, and it is not intended that the invention be limited to the specific embodiments shown and described. To the utility model belongs to the technical field of ordinary technical personnel, do not deviate from the utility model discloses under the prerequisite of design, can also make a plurality of simple deductions or replacement, all should regard as belonging to the utility model discloses a protection scope.

Claims (10)

1. An air-cooled air conditioner, characterized in that: the air side heat exchanger (200) comprises a plurality of fins (201) and a plurality of heat exchange tubes (202) penetrating the fins (201) respectively, the plurality of heat exchange tubes (202) at the top of the air side heat exchanger (200) are connected in series to form a heat exchange loop (210), the plurality of heat exchange tubes (202) at the bottom of the air side heat exchanger (200) are connected in series to form an ice suppression loop (220), one ends of the heat exchange loop (210) and the ice suppression loop (220) are connected through a distributor (230) and a throttling mechanism, the other ends of the heat exchange loop (210) and the ice suppression loop (220) are connected with a refrigerant loop respectively, the throttling mechanism can increase the pressure of the refrigerant in the ice suppression loop (220), the temperature of the refrigerant in the ice suppression loop (220) is higher than the temperature of inlet air, and the pressure of refrigeration in the heat exchange loop (210) is reduced, the temperature of the refrigerant in the heat exchange loop (210) is lower than the temperature of the inlet air.

2. The air-cooled air conditioner according to claim 1, wherein: the throttle mechanism comprises a throttle plate (241) arranged in the distributor (230), and a throttle hole (242) is arranged on the throttle plate (241).

3. The air-cooled air conditioner according to claim 1 or 2, wherein: the throttle mechanism includes an expansion valve (244) connected between the ice suppression circuit (220) and the dispenser (230).

4. An air-cooled air conditioner according to claim 3, wherein: the air-conditioning system further comprises a control system, an air temperature sensor for acquiring the ambient temperature T0, a fin temperature sensor for acquiring the fin temperature T1 of the air-side heat exchanger (200) and a post-valve temperature sensor for acquiring the post-throttling temperature T2 of the refrigerant in the heat exchange loop (210), wherein the expansion valve (244), the air temperature sensor, the fin temperature sensor and the post-valve temperature sensor are respectively connected with the control system, and the control system controls the opening degree of the expansion valve (244) according to the difference value between the post-throttling temperature T2 and the ambient temperature T0.

5. The air-cooled air conditioner according to claim 1, wherein: the distributor (230) comprises a liquid distribution part (231) and a liquid accumulation part (232), a plurality of branch pipes (234) are arranged in the liquid distribution part (231), one ends of the branch pipes (234) are connected with the corresponding heat exchange loops (210) through capillary tubes (235), the other ends of the branch pipes (234) are communicated with one ends of the liquid accumulation part (232), and the other ends of the liquid accumulation part (232) are communicated with the ice suppression loop (220) through liquid accumulation tubes (233) so that refrigerant mixed by gas and liquid phases can be fully mixed.

6. The air-cooled air conditioner according to claim 5, wherein: the throttling mechanism comprises an expansion valve (244) arranged in the liquid accumulating pipe (233) and/or a throttling plate (241) arranged in the liquid accumulating part (232), a throttling hole (242) is arranged in the middle of the throttling plate (241), and the inner diameter of the throttling hole (242) is smaller than that of the liquid accumulating part (232).

7. The air-cooled air conditioner according to claim 6, wherein: the throttle plate (241) is mounted on or integrally formed with the inner wall of the liquid accumulation part (232); or the throttle plate (241) is integrally formed at the end part of the liquid accumulating pipe (233), and one end of the liquid accumulating pipe (233) provided with the throttle plate (241) is inserted into the inner wall of the liquid accumulating part (232).

8. The air-cooled air conditioner according to claim 4, wherein: when the fin temperature T1 meets the frost point condition, if the difference between the throttled temperature T2 and the ambient temperature T0 is greater than a set parameter a, the control system controls the expansion valve (244) to increase the opening degree; if the difference between the throttled temperature T2 and the ambient temperature T0 is less than the set parameter a and less than 0, the control system decreases the opening degree of the expansion valve (244) by the amplitude of B1; if the difference between the throttled temperature T2 and the ambient temperature T0 is less than the set parameter a and greater than 0, the control system decreases the opening degree of the expansion valve (244) by a magnitude B2, wherein B2< B1.

9. The air-cooled air conditioner according to claim 5, wherein: one end of the liquid collecting part (232) is connected with the periphery of the vertex angle of the liquid separating part (231), a distribution boss (237) which is of a cone structure is arranged at the vertex angle of the liquid separating part (231), and the vertex angle of the distribution boss (237) is opposite to the throttling hole (242).

10. The air-cooled air conditioner according to claim 1, wherein: the refrigerant enters a heat exchange loop (210) through a heat exchange header pipe (211), is collected through a distributor (230) and then enters an ice suppression header pipe (212) through an ice suppression loop (220), and the heat exchange header pipe (211) and the ice suppression header pipe (212) are respectively arranged at two ends of the air side heat exchanger (200).

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