CN220017537U - Air conditioning equipment - Google Patents
Air conditioning equipment Download PDFInfo
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- CN220017537U CN220017537U CN202321095746.6U CN202321095746U CN220017537U CN 220017537 U CN220017537 U CN 220017537U CN 202321095746 U CN202321095746 U CN 202321095746U CN 220017537 U CN220017537 U CN 220017537U
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- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The present application discloses an air conditioning apparatus, comprising: the shell is provided with a first air channel, a second air channel and a liquid adding port; the heat exchange system comprises a compression device, a first heat exchange device, an expansion device and a second heat exchange device which are sequentially communicated through a refrigerant pipeline, the second heat exchange device comprises a refrigerant flow channel, a heat exchange liquid flow channel and a liquid distribution device, the heat exchange liquid in the heat exchange liquid flow channel can exchange heat with the refrigerant in at least part of the refrigerant flow channel, the liquid distribution device is communicated with an outlet of the heat exchange liquid flow channel and forms a heat exchange liquid flow channel, and the liquid distribution device can distribute the heat exchange liquid flowing out of the heat exchange liquid flow channel to the outer side of at least part of the refrigerant flow channel; the first heat exchange device is arranged in the first air duct, a part of refrigerant flow channels for distributing heat exchange liquid in the second heat exchange device are arranged in the second air duct, and the liquid adding port is communicated with the heat exchange liquid flow channels. The air quantity required by heat dissipation of the second heat exchange device of the air conditioning equipment is reduced, the heat load caused by air supplement is reduced, and the indoor cooling effect is improved.
Description
Technical Field
The application relates to the technical field of air conditioners, in particular to air conditioning equipment.
Background
The common split type air conditioning equipment, window type air conditioning equipment, double-air-pipe integral type air conditioning equipment and the like are respectively communicated with air inside and outside a room at cold and hot ends to realize independent air circulation, so that the cold quantity and the heat quantity are respectively released in different spaces. However, they all have the problems of high cost, complex installation, inconvenient movement and the like.
The single-duct integral air conditioning equipment only uses one duct, but both cold and hot ends of the air duct are communicated with indoor air, the indoor air is extracted, and cold and heat are respectively sent to the indoor and outdoor, so that the problems are avoided.
When the existing single-duct integral air conditioning equipment is used for refrigerating, the heat load brought by the outdoor air supply entering the room counteracts the refrigerating capacity due to large heat discharge air quantity, so that the overall cooling effect of the room is poor. Such as: refrigerating under the national standard working condition (35 ℃/24 ℃,27 ℃/19 ℃), and when the single-air-pipe integral air conditioning equipment outputs 3500W refrigerating capacity, the heat required to be sent outdoors is about 5000W at 55 DEG C The exhaust temperature is for example 600m for taking 5000W heat 3 /h, at this time, 600m from the outside 3 The air quantity per hour brings 3400W of heat load, the net cooling capacity actually obtained in the room is only 100W, and the actual refrigerating effect is poor.
Disclosure of Invention
The main purpose of the embodiment of the utility model is to provide air conditioning equipment, which adopts extremely low air quantity to dissipate heat and can greatly improve the cooling effect of the single-air-pipe integral air conditioning equipment on rooms.
In order to achieve the above object, the technical solution of the embodiment of the present utility model is as follows:
an air conditioning apparatus comprising:
the shell is provided with a first air channel, a second air channel and a liquid adding port; and
the heat exchange system comprises a compression device, a first heat exchange device, an expansion device and a second heat exchange device which are sequentially communicated through a refrigerant pipeline, wherein the second heat exchange device comprises a refrigerant flow channel, a heat exchange liquid flow channel and a liquid distribution device, the heat exchange liquid in the heat exchange liquid flow channel is arranged to exchange heat with at least part of the refrigerant in the refrigerant flow channel, the liquid distribution device is communicated with an outlet of the heat exchange liquid flow channel and forms a heat exchange liquid flow channel, and the liquid distribution device is arranged to distribute the heat exchange liquid flowing out of the heat exchange liquid flow channel to the outer side of at least part of the refrigerant flow channel;
The first heat exchange device is arranged in the first air duct, a part of refrigerant flow channels for distributing heat exchange liquid in the second heat exchange device are arranged in the second air duct, and the liquid adding port is communicated with the heat exchange liquid flow channels.
In the air conditioning equipment provided by the embodiment of the application, in the second heat exchange device, at least part of the refrigerant in the refrigerant flow channel can exchange heat with the heat exchange liquid and air distributed by the liquid distribution device, and the air can absorb the heat of the refrigerant to become high-temperature air; the heat exchange liquid can absorb the heat of the refrigerant and evaporate into the high-temperature air, and is discharged together with the air. The heat of the refrigerant is taken away by utilizing the evaporation latent heat of the heat exchange liquid, the temperature of the heat exchange liquid rises after the heat exchange liquid performs primary heat exchange with the refrigerant when flowing in the heat exchange liquid flow channel, the evaporation capacity of the high-temperature heat exchange liquid is increased when the high-temperature heat exchange liquid is distributed outside at least part of the refrigerant flow channel and exchanges heat with the refrigerant, and the heat of the refrigerant taken away by the evaporation latent heat is larger.
And meanwhile, the heat absorption of the air and the heat exchange liquid evaporation heat absorption are utilized to dissipate the heat of the refrigerant, so that the quantity of air required by the heat dissipation of the refrigerant can be greatly reduced, and the extremely small air quantity is realized. And at least part of the heat of the refrigerant in the refrigerant flow channel is simultaneously transferred to the air and the heat exchange liquid, so that the heat transfer is quick and efficient, the heat exchange can be performed with high efficiency, and the reduction of the overall size of the second heat exchange device is facilitated, so that the second heat exchange device has a compact structure, the used manufacturing materials are reduced, and the cost is reduced.
The liquid distribution device is communicated with the outlet of the heat exchange liquid flow channel to form a heat exchange liquid flow channel which can be communicated with the liquid adding port so as to provide enough heat exchange liquid for the heat exchange liquid flow channel and ensure the heat exchange liquid required by the normal operation of the air conditioning equipment.
Drawings
In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, and it is obvious that the drawings in the following description are only some embodiments of the present application, and other drawings may be obtained according to the structures shown in these drawings without inventive effort for a person skilled in the art.
Fig. 1 is a schematic structural view of an air conditioning apparatus according to an embodiment of the present application;
FIG. 2 is a schematic view showing a structure of a second heat exchanging device of an air conditioning apparatus according to an embodiment of the present application;
FIG. 3 is a schematic diagram of a second heat exchanger and a liquid distribution device of the second heat exchange device in FIG. 2;
FIG. 4 is an enlarged schematic view of the portion A in FIG. 3;
FIG. 5 is a schematic view of a portion of a liquid storage structure of the liquid distribution device in FIG. 3;
FIG. 6 is a schematic view of another partial structure of a liquid storage structure of the liquid distribution device in FIG. 3;
FIG. 7 is a schematic view of a part of the liquid distribution device in FIG. 3;
FIG. 8 is a schematic cross-sectional view of a second heat exchanging device of an air conditioning apparatus according to another embodiment of the present application;
FIG. 9 is another cross-sectional schematic view of the second heat exchange device shown in FIG. 8;
fig. 10 is a schematic cross-sectional structure view of a second heat exchanging device of an air conditioning apparatus according to still another embodiment of the present application;
fig. 11 is a schematic view showing a structure of a second heat exchanging device of an air conditioning apparatus according to still another embodiment of the present application;
fig. 12 is a schematic view showing a structure of a second heat exchanging device of the air conditioning apparatus according to still another embodiment of the present application;
fig. 13 is a partial schematic view of the structure of fig. 12.
Reference numerals illustrate:
100-second heat exchange device, 200-compression device, 300-expansion device, 400-first heat exchange device, 500-fan, 600-casing, 601-air inlet, 602-first air outlet, 603-second air outlet, 604-liquid filling port;
11-first heat exchanger, 111-first side, 112-second side, 113-first refrigerant flow channel, 114-heat exchange unit, 115-vertical interval, 116-heat exchange fluid flow channel, 12-liquid distribution device, 121-liquid storage structure, 1211-liquid storage space, 1212-liquid storage tank, 1213-partition, 1214-overflow surface, 1215-liquid input, 1216-liquid output, 122-water-beating piece, 123-driving piece, 1231-output shaft, 1232-motor, 124-spraying device, 20-second heat exchanger, 201-second refrigerant flow channel, 202-heat exchange liquid flow channel, 30-split flow pipeline, 40-confluence pipeline, 50-return flow pipeline, 60-fluid supplementing pipeline, 70-water pump.
The achievement of the objects, functional features and advantages of the present application will be further described with reference to the accompanying drawings, in conjunction with the embodiments.
Detailed Description
The following description of the embodiments of the present application will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all embodiments of the application. All other embodiments, which can be made by those skilled in the art based on the embodiments of the application without making any inventive effort, are intended to be within the scope of the application.
Embodiment one:
as shown in fig. 1 to 3, an embodiment of the present application provides an air conditioning apparatus, which may be an air conditioner. The air conditioning apparatus includes a cabinet 600 and a heat exchange system.
The casing 600 has a first air duct, a second air duct, and a filling port 604.
The heat exchange system is disposed in the casing 600, and includes the compression device 200, the first heat exchange device 400, the expansion device 300 and the second heat exchange device 100, which are sequentially communicated through a refrigerant pipeline, and the first heat exchange device 400 is disposed in the first air duct.
The second heat exchange device 100 comprises a refrigerant flow channel, a heat exchange liquid flow channel 202 and a liquid distribution device 12, wherein the heat exchange liquid in the heat exchange liquid flow channel 202 can exchange heat with at least part of the refrigerant in the refrigerant flow channel, the liquid distribution device 12 is communicated with an outlet of the heat exchange liquid flow channel 202 and forms a heat exchange liquid flow channel, and the liquid distribution device 12 can distribute the heat exchange liquid flowing out of the heat exchange liquid flow channel 202 to the outer side of at least part of the refrigerant flow channel.
A portion of the refrigerant flow channels in the second heat exchange device 100, in which the heat exchange liquid is disposed, are disposed in the second air duct, and the liquid filling port 604 is in communication with the heat exchange liquid flow channel.
In the air conditioning apparatus, the compression device 200, the first heat exchange device 400, the expansion device 300, and the second heat exchange device 100 may be sequentially connected through refrigerant lines to form a refrigerant circulation flow path. When the air conditioning apparatus is used for cooling, the first heat exchanging arrangement 400 may be used as an evaporator and the second heat exchanging arrangement 100 may be used as a cooler. The indoor air may flow through the first air duct, exchange heat with the refrigerant in the first heat exchange device 100, and the low temperature air after the heat exchange may flow back into the room.
In the second heat exchange device 100, the refrigerant flow path may be used for refrigerant to pass through, and the refrigerant may be gas, liquid or a gas-liquid mixture; the heat exchange liquid flow channel 202 may be used for passing heat exchange liquid, which may be water or an aqueous solution or other liquid. At least part of the refrigerant in the refrigerant flow channel can exchange heat with the heat exchange liquid in the heat exchange liquid flow channel 202, and the heat exchange liquid can absorb the heat of the refrigerant, so that the temperature of the refrigerant is reduced, the heat dissipation of the refrigerant is realized, and the temperature of the heat exchange liquid is increased.
The liquid distribution device 12 is communicated with the outlet of the heat exchange liquid flow channel 202, and can distribute high-temperature heat exchange liquid flowing out of the heat exchange liquid flow channel 202 to the outer side of at least part of the refrigerant flow channels, so that the refrigerant in at least part of the refrigerant flow channels can exchange heat with the high-temperature heat exchange liquid (the temperature of the high-temperature heat exchange liquid is lower than the temperature of the refrigerant in the refrigerant flow channels exchanging heat with the high-temperature heat exchange liquid); in addition, a part of the refrigerant flow channels in which the heat exchange liquid is distributed in the second heat exchange device 100 may be disposed in the second air duct, so that air is blown through the outside of the part of the refrigerant flow channels, and the air may exchange heat with the refrigerant in the part of the refrigerant flow channels.
In the second heat exchange device 200, at least part of the refrigerant in the refrigerant flow channel can exchange heat with the heat exchange liquid and air at the same time, and the air can absorb the heat of the refrigerant to become high-temperature air; the heat exchange liquid can absorb the heat of the refrigerant and evaporate into the high-temperature air, and is discharged together with the air. The heat of the refrigerant is taken away by utilizing the evaporation latent heat of the heat exchange liquid, the temperature of the heat exchange liquid rises after the heat exchange liquid has undergone primary heat exchange with the refrigerant when flowing in the heat exchange liquid flow channel 202, the evaporation capacity of the high-temperature heat exchange liquid is increased when the high-temperature heat exchange liquid is distributed outside at least part of the refrigerant flow channels and exchanges heat with the refrigerant, and the heat of the refrigerant taken away by the evaporation latent heat is larger.
And meanwhile, the heat absorption of the air and the heat exchange liquid evaporation heat absorption are utilized to dissipate the heat of the refrigerant, so that the quantity of air required by the heat dissipation of the refrigerant can be greatly reduced, and the extremely small air quantity is realized. And at least part of the heat of the refrigerant in the refrigerant flow channel is simultaneously transferred to the air and the heat exchange liquid, so that the heat transfer is quick and efficient, the heat exchange can be performed with high efficiency, and the reduction of the overall size of the second heat exchange device 100 is facilitated, so that the second heat exchange device 100 is compact in structure, the used manufacturing materials are reduced, and the cost is reduced.
The liquid distribution device 12 is in communication with the outlet of the heat exchange liquid flow channel 202, and may form a heat exchange liquid flow path, which may be in communication with the liquid filling port 604, so as to provide sufficient heat exchange liquid for the heat exchange liquid flow path, and ensure the heat exchange liquid required for the normal operation of the air conditioning apparatus. The air conditioning apparatus requires additional heat exchange fluid to be added through the fluid port 604 during operation. The filling port 604 may be connected to a heat exchange liquid supply device, such as a tap water pipe, outside the air conditioning apparatus.
Wherein the liquid distribution device 12 distributes the heat exchange liquid to the outside of at least part of the refrigerant flow channels, the heat exchange liquid may be distributed to the outside surface of at least part of the refrigerant flow channels, and/or the heat exchange liquid may be distributed to the environment outside of at least part of the refrigerant flow channels.
In some exemplary embodiments, the enclosure 600 further has an air inlet 601, a first air outlet 602, and a second air outlet 603, wherein the air inlet 601 is in communication with the first air outlet 602 through a first air duct, and the air inlet 601 is in communication with the second air outlet 603 through a second air duct. The air inlet 601 and the first air outlet 602 are both provided to communicate with the indoor space, and the second air outlet 603 is provided to communicate with the outdoor space. One or more of the air inlet 601, the first air outlet 602, and the second air outlet 603 may be provided.
The cabinet 600 of the air conditioning apparatus may be of a unitary structure such that the air conditioning apparatus may be a unitary mobile air conditioning apparatus, a window unit, or a single duct unitary air conditioning apparatus, and the air outlet of the cabinet 600 may communicate with the outside through an exhaust duct. The single duct does not represent a single duct in number, but means that only the exhaust duct is connected to the outside, and no suction duct is connected to the air inlet 601 of the casing 600, so as to suck air from the outside, or, in terms of circulation of cold and hot air, the return air of the cold and hot air is in the same space (i.e. the first air outlet 602 and the second air outlet 603 are both connected to the air inlet 601).
Air in the room (or in the semi-enclosed space) can enter the air conditioning equipment from the air inlet 601, a part of the air enters the first air duct and flows through the first heat exchange device 400 to exchange heat with the refrigerant in the first heat exchange device 400, the temperature of the air after heat exchange with the first heat exchange device 400 can be reduced, and the cooled air is discharged into the room (or in the semi-enclosed space) from the first air outlet (cold air inlet) 602, so that the room (or in the semi-enclosed space) can be refrigerated; the other part of the air enters the second air duct and flows through the second heat exchange device 100 to exchange heat with the refrigerant in the part of the refrigerant flow passage where the heat exchange liquid is arranged, the temperature of the air after heat exchange with the refrigerant is increased to become high-temperature gas, and the high-temperature gas can be discharged to the outside (or the outside of the semi-closed space) from the second air outlet (hot air port) 603 together with the steam of the heat exchange liquid.
The air conditioning apparatus of the embodiment of the present application requires additional heat exchange liquid to be added during operation. This is essentially different from the current air conditioning devices in which the evaporator is used to generate condensed water to enhance cooling, and the amount of air required for heat dissipation cannot be significantly reduced because the condensed water generated by the evaporator has different water production when the working conditions are different, and the effect cannot be ensured. In the air conditioning apparatus according to the embodiment of the present application, the heat exchange liquid evaporates while passing through the second heat exchange device 100, and becomes steam to be discharged to the outside from the second air outlet 603 together with the hot wind of the high temperature air. The heat exchange liquid evaporates and absorbs the heat of the refrigerant in the second heat exchange device 100, and the heat exchange liquid can take away most of the heat of the refrigerant in the second heat exchange device 100 due to the large vaporization latent heat. The heat transfer liquid evaporates to remove more than 50% of the total heat output of the second heat exchange device 100.
Because the mixture of the discharged air and the vapor of the heat exchange liquid has high temperature and high humidity, the air quantity required by the heat dissipation of the refrigerant in the second heat exchange device 100 is greatly reduced, so that only a small quantity of air is needed to be supplemented from the outside, the heat load caused by air supplement is reduced, and the refrigerating effect is greatly improved. For example, when refrigerating is performed under the national standard working condition (35 ℃/24 ℃ and 27 ℃/19 ℃), the air conditioning equipment of the embodiment of the application outputs 3500W refrigerating output, the heat required to be sent outdoors is about 5000W, and only the 5000W heat is required to be taken away by taking the 70 ℃ exhaust temperature and 60% relative humidity as an example To be 56m 3 The air quantity/h is supplemented by 56m from the outdoor 3 The air quantity per hour (which is equivalent to the fresh air quantity of the fresh air conditioner) only brings 320W of heat load, and the net cooling capacity actually obtained indoors reaches 3180W (30 times higher than that before improvement). The cooling effect of the split type fresh air conditioner is equivalent to that of a conventional split type fresh air conditioner.
In some exemplary embodiments, as shown in fig. 2, the second heat exchange device 100 further includes: a first heat exchanger 11 and a second heat exchanger 20.
The second heat exchanger 20 may include a second refrigerant flow path 201 and a heat exchange liquid flow path 202, the refrigerant in the second refrigerant flow path 201 being arranged to exchange heat with the heat exchange liquid in the heat exchange liquid flow path 202. The flow direction of the second refrigerant flow channel 201 may be opposite to the flow direction of the heat exchange liquid flow channel 202, that is, the flow direction of the refrigerant in the second refrigerant flow channel 201 may be opposite to the flow direction of the heat exchange liquid in the heat exchange liquid flow channel 202.
The first heat exchanger 11 may have a first refrigerant flow passage 113, and the first refrigerant flow passage 113 and the second refrigerant flow passage 201 may be connected in parallel. The refrigerant flow path of the second heat exchange device 100 may include the first refrigerant flow path 113 and the second refrigerant flow path 201.
The liquid distribution device 12 may be in communication with the outlet of the heat exchange liquid flow passage 202 and configured to distribute the heat exchange liquid flowing out of the heat exchange liquid flow passage 202 to the outside of the first refrigerant flow passage 113, i.e., to the outside of the first heat exchanger 11. The liquid distributing device 12 distributes the heat exchange liquid to the outside of the first heat exchanger 11, which may be to distribute the heat exchange liquid to the outer surface of the first heat exchanger 11 and/or to distribute the heat exchange liquid to the environment outside the first heat exchanger 11.
The first heat exchanger 11 may be disposed in the second air duct, so that the refrigerant in the first refrigerant flow channel 113 may exchange heat with the air flowing through the outside of the first heat exchanger 11, and further, the refrigerant in the first refrigerant flow channel 113 may exchange heat with the heat exchange liquid and the air disposed in the liquid distribution device 12 at the same time.
The second heat exchanger 20 may be disposed within the second air duct or may be disposed outside the second air duct.
In the second heat exchange device 100, the second refrigerant flow path 201 of the second heat exchanger 20 is used for refrigerant passage, and the heat exchange liquid flow path 202 of the second heat exchanger 20 is used for heat exchange liquid passage. The refrigerant in the second refrigerant flow channel 201 can exchange heat with the heat exchange liquid in the heat exchange liquid flow channel 202, and the heat exchange liquid can absorb the heat of the refrigerant, so that the temperature of the refrigerant is reduced, the heat dissipation of the refrigerant is realized, and the temperature of the heat exchange liquid is increased.
The first refrigerant flow channel 113 of the first heat exchanger 11 may be used for the refrigerant to pass therethrough, and the first refrigerant flow channel 113 may be connected in parallel with the second refrigerant flow channel 201 of the second heat exchanger 20, so that the refrigerant flowing into the second heat exchange device 100 may be branched and then respectively enter the second refrigerant flow channel 201 of the second heat exchanger 20 and the first refrigerant flow channel 113 of the first heat exchanger 11, flow out of the second refrigerant flow channel 201 and the first refrigerant flow channel 113 and then merge, and then flow out of the second heat exchange device 100.
The liquid distribution device 12 is communicated with the outlet of the heat exchange liquid flow passage 202, and can distribute high-temperature heat exchange liquid to the outer side of the first heat exchanger 11, so that the refrigerant in the first refrigerant flow passage 113 can exchange heat with the high-temperature heat exchange liquid (the temperature of the high-temperature heat exchange liquid is lower than that of the refrigerant in the first refrigerant flow passage 113); in addition, air is blown through the outside of the first heat exchanger 11, and the air can exchange heat with the refrigerant in the first refrigerant flow path 113.
The refrigerant in the first refrigerant flow channel 113 can exchange heat with the heat exchange liquid and the air, and the air can absorb the heat of the refrigerant and become high-temperature air; the heat exchange liquid can absorb the heat of the refrigerant and evaporate into the high-temperature air, and is discharged together with the air.
In the second heat exchange device 100 of the embodiment of the application, both the first heat exchanger 11 and the second heat exchanger 20 can be used for heat dissipation of the refrigerant, so as to reduce the temperature of the refrigerant; in the first heat exchanger 11, the heat of the refrigerant in the first refrigerant flow passage 113 is taken away by the latent heat of evaporation of the heat exchange liquid, and the temperature of the heat exchange liquid increases after the heat exchange has been performed once in the second heat exchanger 20, and the amount of evaporation of the high-temperature heat exchange liquid increases when the heat exchange with the refrigerant in the first refrigerant flow passage 113 is performed, and the heat of the refrigerant taken away by the latent heat of evaporation is larger. In the first heat exchanger 11, the refrigerant is radiated by both the heat absorption of air and the evaporation of the heat exchange liquid, and therefore, the amount of air required for the radiation of the refrigerant can be greatly reduced, and an extremely small air volume can be realized.
The heat of the refrigerant in the first heat exchanger 11 is transferred to the air and the heat exchange liquid at the same time, so that the heat transfer is quick and efficient, the heat exchange can be performed with high efficiency, and the reduction of the overall size of the first heat exchanger 11 is facilitated, so that the first heat exchanger 11 is compact in structure, the used manufacturing materials are reduced, and the cost is reduced.
In some exemplary embodiments, as shown in fig. 3, the liquid distribution device 12 includes a liquid storage structure 121 and a liquid distribution mechanism, where the liquid storage structure 121 has a liquid storage space 1211 that communicates with an outlet of the heat exchange liquid flow channel 202, and the liquid distribution mechanism is configured to distribute the heat exchange liquid in the liquid storage space 1211 to an outside of the first heat exchanger 11 (i.e., an outside of the first refrigerant flow channel 113).
In the liquid distribution device 12, a liquid storage space 1211 of the liquid storage mechanism is communicated with an outlet of the heat exchange liquid flow channel 202, high-temperature heat exchange liquid in the heat exchange liquid flow channel 202 after heat exchange with the refrigerant can flow out from the outlet of the heat exchange liquid flow channel 202 and enter the liquid storage space 1211, and the liquid storage space 1211 can be used for storing the heat exchange liquid, so that the heat exchange liquid has a certain reserve amount, and is favorable for taking away enough heat when the heat exchange liquid exchanges heat with the refrigerant in the first refrigerant flow channel 113 later, and further, the heat dissipation effect of the refrigerant is ensured.
The liquid distribution mechanism can distribute the high-temperature heat exchange liquid in the liquid storage space 1211 to the outer side of the first heat exchanger 11, so that the high-temperature heat exchange liquid can fall to the outer side of the first heat exchanger 11, the refrigerant in the first refrigerant flow channel 113 can exchange heat with the high-temperature heat exchange liquid and air outside the first refrigerant flow channel 113, and the high-temperature heat exchange liquid can absorb heat of the refrigerant and evaporate into high-temperature air to be discharged together with the air.
In some exemplary embodiments, as shown in fig. 3, the liquid distribution mechanism includes a water striking member 122 and a driving member 123, where the driving member 123 is connected to the water striking member 122 and configured to drive the water striking member 122 to move; the liquid storage structure 121 is disposed below the first heat exchanger 11, and a part of the water pumping member 122 is accommodated in the liquid storage space 1211 and is disposed so as to be capable of pumping up and splashing the heat exchange liquid in the liquid storage space 1211 to the outside of the first heat exchanger 11.
In the liquid distribution mechanism, a part of the water pumping member 122 (such as the lower part of the water pumping member 122) can be accommodated in the liquid storage space 1211 below the first heat exchanger 11; the driving member 123 may drive the water pumping member 122 to move, and when the water pumping member 122 moves, the heat exchange liquid in the liquid storage space 1211 may be beaten, so that the heat exchange liquid splashes upward onto the first heat exchanger 11.
The heat exchange liquid is changed into fine particles and splashed by the water beating piece 122, so that the heat exchange liquid falls onto the first heat exchanger 11 in a more dispersed state, the heat exchange area between the heat exchange liquid and the first refrigerant flow channel 113 is increased, the heat exchange between the heat exchange liquid and the refrigerant in the first refrigerant flow channel 113 is more uniform, and the evaporation capacity of the heat exchange liquid and the heat dissipation effect on the refrigerant are improved.
The heat exchange liquid which splashes on the first heat exchanger 11 but is not evaporated can slide down and drop into the liquid storage space 1211, so that the water pumping piece 122 pumps up the heat exchange liquid again, thereby realizing the recycling of the heat exchange liquid and improving the evaporation capacity of the heat exchange liquid and the heat dissipation effect of the refrigerant.
In some exemplary embodiments, as shown in fig. 3, the first heat exchanger 11 includes a plurality of rows of heat exchange units 114 vertically disposed and sequentially arranged in a transverse direction, each row of heat exchange units 114 may include heat exchange sub-pipes, the heat exchange sub-pipes of the plurality of rows of heat exchange units 114 are sequentially communicated to form a first refrigerant flow channel 113, a vertical interval 115 is provided between two adjacent rows of heat exchange units 114, and the vertical interval 115 may extend vertically.
Wherein, each row of heat exchange units 114 may include a heat exchange sub-pipeline, which may be a serpentine-distributed curved pipeline, and the heat exchange sub-pipelines of the plurality of rows of heat exchange units 114 are sequentially communicated to form a first refrigerant flow channel 113; alternatively, each row of heat exchange units 114 may include a plurality of parallel heat exchange sub-circuits, which may be straight-line pipes or curved pipes distributed in a serpentine shape, and the plurality of heat exchange sub-circuits of the plurality of rows of heat exchange units 114 are sequentially connected in a one-to-one correspondence manner, so as to form a plurality of parallel first refrigerant flow channels 113. Wherein, a heat exchange sub-pipeline can be formed by a plurality of pipelines (single-row pipes) which are arranged in a row and are communicated in sequence, and a plurality of parallel heat exchange sub-pipelines can be formed by a plurality of single-row pipes (multi-row pipes). Each row of heat exchange units 114 may include a single row of tubes, or a double row of tubes, although more rows of tubes are not preferred.
Corresponding to at least one vertical interval 115 of the first heat exchanger 11, the water pumping member 122 is provided with at least one, and is arranged in one-to-one correspondence with the vertical interval 115, and the other part of the water pumping member 122 is positioned in the corresponding vertical interval 115 and is arranged to enable heat exchange liquid in the liquid storage space 1211 to splash to the heat exchange units 114 at two sides of the corresponding vertical interval 115.
The number of the water beating members 122 is equal to that of the vertical intervals 115 of the first heat exchanger 11, and the water beating members 122 are in one-to-one correspondence, and the other part (such as the upper part of the water beating member 122) of the water beating members 122 can extend into the corresponding vertical intervals 115, so that when the driving member 123 drives the water beating members 122 to move, the water beating members 122 can beat the heat exchange liquid in the liquid storage space 1211, the heat exchange liquid can splash upwards, and the heat exchange liquid excited by the water beating members 122 can fall onto the heat exchange units 114 on two sides of the vertical intervals 115 corresponding to the water beating members 122, so that the refrigerant can be radiated by utilizing the evaporation of the heat exchange liquid.
In some exemplary embodiments, as shown in fig. 3, the first heat exchanger 11 includes at least three rows of heat exchange units 114 such that the first heat exchanger 11 has a plurality of vertical intervals 115; correspondingly, the plurality of water-beating members 122 are arranged, the liquid storage space 1211 is divided into a plurality of liquid storage tanks 1212, the plurality of liquid storage tanks 1212 are in one-to-one correspondence with the plurality of vertical intervals 115 and are positioned below the corresponding vertical intervals 115, the plurality of liquid storage tanks 1212 are in one-to-one correspondence with the plurality of water-beating members 122, and a part of the water-beating members 122 are accommodated in the corresponding liquid storage tanks 1212.
The vertical space 115, the water pumping member 122 and the liquid storage tank 1212 of the first heat exchanger 11 are all provided with a plurality of water pumping members 122, and the three are arranged in equal number and in one-to-one correspondence, one part of the water pumping member 122 (such as the lower part of the water pumping member 122) can be accommodated in the corresponding liquid storage tank 1212, and the other part of the water pumping member 122 (such as the upper part of the water pumping member 122) can extend into the corresponding vertical space 115. When the driving part 123 drives the water pumping part 122 to move, the heat exchange liquid in the corresponding liquid storage tank 1212 can be pumped up, and the heat exchange liquid in the liquid storage tank 1212 is splashed upwards to the heat exchange units 114 at two sides of the corresponding vertical interval 115, so that the heat exchange liquid is evaporated to dissipate heat of the refrigerant.
In some exemplary embodiments, as shown in fig. 3, the liquid storage space 1211 has a liquid input 1215, the liquid input 1215 being in communication with the outlet of the heat exchange liquid flow channel 202, and a plurality of liquid storage slots 1212 being arranged in sequence in a direction away from the liquid input 1215.
A partition 1213 is provided between adjacent reservoirs 1212, wherein: the top surface of the partition 1213 forms an overflow surface 1214, and the height of the overflow surface 1214 decreases in sequence along the direction away from the liquid input end 1215 (as shown in fig. 4, the height between the highest points of two adjacent overflow surfaces 1214 is h), so that the heat exchange liquid in one liquid storage tank 1212 can flow through the overflow surface 1214 into the adjacent liquid storage tank 1212 on the side away from the liquid input end 1215.
In the liquid storage structure 121, one end of the liquid storage space 1211 is a liquid input end 1215, and the liquid input end 1215 can be communicated with the outlet of the heat exchange liquid flow channel 202, so that the heat exchange liquid flowing out of the outlet of the heat exchange liquid flow channel 202 can enter the liquid input end 1215. The plurality of liquid storage tanks 1212 are arranged in sequence in a direction away from the liquid input end 1215, and the heat exchange liquid input from the liquid input end 1215 can enter the adjacent liquid storage tank 1212. Among the plurality of reservoirs 1212, a partition 1213 is provided between adjacent reservoirs 1212 to separate the adjacent reservoirs 1212. Wherein, the top surface of the partition 1213 may form the overflow surface 1214, and the height of the overflow surface 1214 sequentially decreases in a direction away from the liquid input end 1215, such that the plurality of liquid storage tanks 1212 form a stepped structure. Of the two adjacent reservoirs 1212, one reservoir 1212 near the liquid input end 1215 may be an advanced reservoir 1212, and one reservoir 1212 far from the liquid input end 1215 may be a low-level reservoir 1212, and after the heat exchange liquid in the advanced reservoir 1212 gathers to a height exceeding the overflow surface 1214, the heat exchange liquid can flow through the overflow surface 1214 and into the adjacent low-level reservoir 1212, i.e. the heat exchange liquid is realized to flow between the plurality of reservoirs 1212 step by step along the direction far from the liquid input end 1215.
The maximum liquid storage height of each liquid storage tank 1212 is determined by the overflow surface 1214 on the partition 1213 on the side of each liquid storage tank 1212 far from the liquid input end 1215, so that the maximum liquid storage height of each liquid storage tank 1212 is sequentially reduced along the direction far from the liquid input end 1215, thus a multi-stage liquid storage tank 1212 structure can be formed, and the heat exchange liquid can fill each liquid storage tank 1212 step by step, i.e. the heat exchange liquid in the advanced liquid storage tank 1212 overflows and then enters the next-stage liquid storage tank 1212. The heat exchange liquid can gather in the liquid storage tanks 1212 at all levels and can be pumped up by the pumping member 122 to ensure that enough heat exchange liquid can fall on the first heat exchanger 11, thereby ensuring the heat dissipation effect on the refrigerant.
Because of the height difference h between the overflow surfaces 1214, the heat exchange liquid can automatically flow from the high-level liquid storage tank 221 to the low-level liquid storage tank 1212 without external force driving, and the structure is simple and reliable and the cost is low.
It should be appreciated that, instead of sequentially decreasing in height in a direction away from the liquid input 1215 by providing an overflow surface 1214 atop the divider 1213, the flow of heat exchange liquid between the plurality of reservoirs 1212 in a direction away from the liquid input 1215 may be accomplished in other ways. Such as: in other exemplary embodiments, the divider 1213 is provided with overflow holes communicating with the reservoirs 1212 on either side of the divider 1213, and the height of the overflow holes decreases in sequence in a direction away from the liquid input 1215, so that heat exchange liquid in one reservoir 1212 can flow through the overflow holes into an adjacent reservoir 1212 on the side away from the liquid input 1215.
The maximum reservoir height of each reservoir 1212 is determined by the height of the overflow aperture in the divider 1213 on the side of each reservoir 1212 remote from the liquid input 1215. Since the height of the overflow holes in the partition 1213 decreases in sequence in the direction away from the liquid input end 1215, the maximum liquid storage height of each liquid storage tank 1212 decreases in sequence in the direction away from the liquid input end 1215, so that a multi-stage liquid storage tank 1212 structure can be formed, and the heat exchange liquid can fill each liquid storage tank 1212 step by step, i.e. the heat exchange liquid in the advanced liquid storage tank 1212 overflows and then enters the next liquid storage tank 1212. The heat exchange liquid can accumulate in the liquid storage tanks 1212 at each stage and can be pumped up by the pumping-up part 122 to ensure the heat dissipation effect on the refrigerant.
In some exemplary embodiments, as shown in fig. 5, the heights of the bottom surfaces of the plurality of reservoirs 1212 decrease in sequence in a direction away from the liquid input 1215 (i.e., to the left in fig. 5).
The height of the bottom surfaces of the plurality of liquid storage tanks 1212 decreases in sequence along a direction away from the liquid input end 1215, so that the bottom surfaces of the plurality of liquid storage tanks 1212 form a stepped structure, and further the groove depths of the plurality of liquid storage tanks 1212 may be set equal, so that the amounts of heat exchange liquid in the respective liquid storage tanks 1212 may be substantially the same, which is beneficial to ensuring a heat dissipation effect on the refrigerant flowing in the heat exchange unit 114.
Of course, the height of the bottom surfaces of the plurality of reservoirs 1212 is not limited to sequentially decreasing, such as: in other exemplary embodiments, as shown in fig. 6, the bottom surfaces of the plurality of reservoirs 1212 are disposed flush. The bottom surfaces of the plurality of liquid storage tanks 1212 are flush, and the maximum liquid storage height of the plurality of liquid storage tanks 1212 decreases in sequence in a direction away from the liquid input end 1215 (i.e., in a direction to the left in fig. 6), so that the groove depth of the plurality of liquid storage tanks 1212 decreases in sequence in a direction away from the liquid input end 1215, and thus the amount of heat exchange liquid in each liquid storage tank 1212 may gradually decrease.
In some exemplary embodiments, the inlet of the first refrigerant flow channel 113 and the outlet of the first refrigerant flow channel 113 are located at oppositely disposed first and second sides 111, 112 of the first heat exchanger 11, respectively. As shown in fig. 3, the position of the inlet of the first refrigerant flow channel 113 may also be higher than the position of the outlet of the first refrigerant flow channel 113, such as: the inlet of the first refrigerant flow channel 113 may be located at the upper right side of the first heat exchanger 11, and the outlet of the first refrigerant flow channel 113 may be located at the lower left side of the first heat exchanger 11. It should be understood that the inlet of the first refrigerant flow channel 113 and the outlet of the first refrigerant flow channel 113 may be located at the left and right sides or the front and rear sides of the first heat exchanger 11, respectively.
In the first heat exchanger 11, the refrigerant may flow into the first refrigerant flow passage 113 from an inlet of the first refrigerant flow passage 113, and may flow out from an outlet of the first refrigerant flow passage 113. Wherein the refrigerant flowing in from the inlet of the first refrigerant flow channel 113 may sequentially flow through the plurality of heat exchange units 114 in a direction from the first side 111 toward the second side 112 of the first heat exchanger 11, and exchange heat with the heat exchange liquid and air. The temperature of the refrigerant after heat exchange decreases, and thus, the temperature of the first side 111 of the first heat exchanger 11 may be lower than the temperature of the second side 112, such that the first side 111 may be a high temperature side of the first heat exchanger 11 and the second side 112 may be a low temperature side of the first heat exchanger 11.
In some exemplary embodiments, the liquid input 1215 is proximate to the first side 111 of the first heat exchanger 11. As shown in fig. 3, the liquid input end 1215 of the liquid storage space 1211 may be located at the lower side of the first heat exchanger 11 and near the right side of the first heat exchanger 11, i.e., the liquid input end 1215 may be located at the lower right side of the first heat exchanger 11.
The heat exchange liquid can flow in the liquid storage space 1211 in a direction away from the liquid input end 1215 generally from the liquid input end 1215, i.e., the heat exchange liquid can flow generally in a direction from the first side 111 toward the second side 112 of the first heat exchanger 11 such that the general flow direction of the heat exchange liquid is the same as the general flow direction of the refrigerant in the first heat exchanger 11.
In some exemplary embodiments, the flow direction of the air flowing outside the first heat exchanger 11 (the flow direction of the air) is set from the second side 112 toward the first side 111 of the first heat exchanger 11. As shown in fig. 3, the flow direction of the air may be set from the left side toward the right side of the first heat exchanger 11.
The air can flow from the second side 112 (low temperature side) to the first side 111 (high temperature side) of the first heat exchanger 11 under the action of the fan 500, and the refrigerant in the first heat exchanger 11 can flow from the first side 111 to the second side 112 as a whole, so that the overall flow direction of the air is opposite to that of the refrigerant in the first heat exchanger 11, and the overall flow direction of the air is opposite to that of the heat exchange liquid in the liquid storage space 1211, thereby forming a good countercurrent heat dissipation effect, maintaining a uniform temperature gradient at a lower level as a whole, having a lower average heat transfer temperature difference, and having a small energy loss. The air gradually absorbs heat and vapor of heat exchange liquid in the process of flowing from the second side 112 (low temperature side) to the first side 111 (high temperature side) of the first heat exchanger 11, the temperature rises, the absolute moisture content rises, the relative humidity is kept at a certain level, certain moisture absorption capacity is maintained, the air quantity is fully utilized, the required air quantity is smaller under the same heat dissipation capacity, and the structure of the first heat exchanger 11 is more compact.
Here, the general flow direction of the air is opposite to the general flow direction of the refrigerant in the first heat exchanger 11, and means the opposite of the flow direction of the fluid as a whole; the overall flow direction of the heat exchange liquid is the same as the overall flow direction of the refrigerant in the first heat exchanger 11, meaning the same flow direction of the fluid as a whole. For example, in some exemplary embodiments, the first refrigerant flow passage 113 of the first heat exchanger 11 is a serpentine distribution curved flow passage whose overall extending direction is opposite to the overall flow direction of the air, but there may be a case where the serpentine distribution curved flow passage is perpendicular to the overall flow direction of the air at a specific certain position. Likewise, a serpentine distribution of curved flow channels may exist at a particular location that is perpendicular to the general flow direction of the heat exchange liquid.
Of course, the liquid input end 1215 of the liquid storage space 1211 may also be proximate to the second side 112 of the first heat exchanger 11, at which time the heat exchange liquid may generally flow within the liquid storage space 1211 in a direction from the second side 112 of the first heat exchanger 11 toward the first side 111 such that the general flow direction of the heat exchange liquid is opposite to the general flow direction of the refrigerant in the first heat exchanger 11. In this case, the overall flow direction of the heat exchange liquid in the liquid storage space 1211 is opposite to the overall flow direction of the refrigerant in the first heat exchanger 11, the overall flow direction of the air is opposite to the overall flow direction of the refrigerant in the first heat exchanger 11, the overall flow direction of the heat exchange liquid in the liquid storage space 1211 is the same as the overall flow direction of the air, and the second heat exchange device 100 can have better condensate water consumption capability and improved energy efficiency when applied to the mobile air conditioning apparatus.
It should be understood that the position of the inlet of the first refrigerant flow channel 113 may be higher than the position of the outlet of the first refrigerant flow channel 113 so that the refrigerant in the first refrigerant flow channel 113 flows entirely from top to bottom, and thus, the flow direction of the air may also be set from bottom to top, i.e., from the lower side toward the upper side of the first heat exchanger 11, to be opposite to the overall flow direction of the refrigerant.
In some exemplary embodiments, as shown in fig. 2 and 3, the liquid storage space 1211 further has a liquid output 1216, the liquid output 1216 being located on a side of the liquid storage space 1211 remote from the liquid input 1215, the liquid output 1216 being in communication with the inlet of the heat exchange liquid flow passage 202 through the return line 50 such that the heat exchange liquid flow passage is a circulation flow passage.
The remaining non-evaporated heat exchange liquid in the liquid storage space 1211 may flow back to the inlet of the heat exchange liquid flow channel 202 of the second heat exchanger 20 through the return line 50 for recycling the heat exchange liquid. In the liquid storage space 1211, the remaining non-evaporated heat exchange liquid is reduced in temperature due to heat released by air cooling of air and/or evaporation of other heat exchange liquid, and the low-temperature heat exchange liquid is introduced into the heat exchange liquid flow passage 202 of the second heat exchanger 20 to continue circulation, so that the heat dissipation effect of the heat exchange liquid entering the second heat exchanger 20 on the refrigerant can be enhanced.
In some exemplary embodiments, the second heat exchange device 100 further includes a water pump 70 (see fig. 12), and the water pump 70 may be disposed in a line between the liquid output 1216 of the liquid storage space 1211 and the inlet of the heat exchange liquid flow channel 202.
The water pump 70 can pump the remaining unevaporated heat exchange liquid in the liquid storage space 1211 back into the heat exchange liquid flow channel 202 of the second heat exchanger 20 to realize the recycling of the heat exchange liquid.
In some exemplary embodiments, the beater 122 includes rotatable beater wheels, and the outer diameters of the beater wheels are arranged to be equal as shown in fig. 3, or the outer diameters of the beater wheels are arranged to increase in sequence in a direction away from the liquid input end 1215 (i.e., a direction to the left in fig. 7) as shown in fig. 7.
The water pumping member 122 may include a water pumping wheel, and the driving member 123 may drive the water pumping wheel to rotate, and the plurality of blades of the water pumping wheel may strike the heat exchange liquid in the liquid storage space 1211 during the rotation process, so that the heat exchange liquid splashes onto the first heat exchanger 11.
It should be appreciated that the beater 122 can be other reasonable and effective beater structures outside of the beater wheel, such as: the water pumping member 122 may include a water pumping plate, and the driving member 123 may drive the water pumping plate to move (e.g., swing up and down) and strike the heat exchange liquid in the liquid storage space 1211, so that the heat exchange liquid splashes onto the first heat exchanger 11.
In some exemplary embodiments, the driving member 123 and the water beating member 122 are provided in plurality, and the driving members 123 are connected to the water beating members 122 in a one-to-one correspondence.
The driving member 123 and the water beating member 122 are provided with a plurality of driving members 123 and 122, and the driving members 123 can respectively drive the water beating members 122 to move for beating water. The plurality of driving members 123 are arranged, so that the movement of the plurality of water spraying members 122 can be controlled respectively, different requirements can be met, and different heat dissipation effects can be achieved.
In other exemplary embodiments, as shown in fig. 3 and 7, the driving member 123 has an output shaft 1231, and the plurality of water-driving members 122 are mounted to the output shaft 1231, and the output shaft 1231 is disposed horizontally (as shown in fig. 7) or obliquely (as shown in fig. 3).
The driving member 123 may have an output shaft 1231, and the plurality of water-beating members 122 may be coaxially mounted on the output shaft 1231, so that one driving member 123 may simultaneously drive the plurality of water-beating members 122 to perform synchronous motion, thereby reducing the number of driving members 123 and being beneficial to reducing the cost.
In the case that the water pumping unit 122 includes water pumping wheels and the outer diameters of the water pumping wheels are equal, as shown in fig. 3, in order to adapt to the plurality of liquid storage tanks 1212 arranged in a stepped manner, the output shaft 1231 of the driving unit 123 may be obliquely disposed, so that the output shaft 1231 may be simultaneously connected with the plurality of water pumping wheels. Alternatively, as shown in fig. 7, in the case where the water pumping member 122 includes water pumping wheels, and the outer diameters of the water pumping wheels are sequentially increased, the water pumping wheels with sequentially increased outer diameters may be adapted to the plurality of liquid storage tanks 1212 arranged in a stepped manner, and thus the output shaft 1231 of the driving member 123 may be horizontally disposed, and the output shaft 1231 may be simultaneously connected to the water pumping wheels.
In some exemplary embodiments, as shown in fig. 3, the driving member 123 may include a motor 1232, and a motor shaft (output shaft 1231) of the motor 1232 may be connected to the water striking member 122 and directly drive the water striking member 122 to move; alternatively, the driving member 123 may include a transmission mechanism in addition to the motor 1232, and the motor 1232 may drive the driving member 122 to move through the transmission mechanism, which may be a gear transmission mechanism, a link mechanism, or the like.
In some exemplary embodiments, as shown in FIG. 2, the heat exchange liquid flow passage 202 is configured to also communicate with a source of heat exchange liquid (e.g., a fill port 604 or a drain pan for receiving condensate on the first heat exchange device 400) via a make-up line 60; alternatively, the liquid storage structure 121 is configured to be further connected to a liquid source of the heat exchange liquid (such as a liquid filling port 604 or a water receiving tray for receiving condensed water on the first heat exchange device 400) through the liquid supplementing pipeline 60.
The heat exchange liquid is lost due to evaporation during the circulation between the second heat exchanger 20 and the liquid distribution device 12, so that the heat exchange liquid of the liquid source can be supplemented into the circulation pipeline of the heat exchange liquid through the liquid supplementing pipeline 60. Wherein, the fluid replacement pipe 60 may be in communication with the heat exchange fluid flow channel 202, such as: can be communicated with the inlet of the heat exchange liquid flow channel 202 to directly send the supplementary heat exchange liquid into the heat exchange liquid flow channel 202; or the fluid replacement conduit 60 may be in communication with the fluid storage structure 121 to deliver the replacement heat exchange fluid directly to the fluid storage structure 121.
Wherein, in the case that the liquid storage structure 121 communicates with the liquid source of the heat exchange liquid through the liquid supplementing pipe 60, and the liquid storage structure 121 includes a plurality of liquid storage tanks 1212 with a stepped structure, the communicating position of the liquid storage structure 121 and the liquid supplementing pipe 60 (i.e. the liquid adding position of the liquid storage structure 121) may be set at any stage of liquid storage tank 1212 according to the temperature of the supplemented heat exchange liquid, for example: the temperature of the supplemental heat exchange liquid may be the same as or close to the temperature of the heat exchange liquid at the make-up location. So arranged, the complementary heat exchange liquid does not affect the overall temperature gradient of each level of liquid storage tank 1212, ensuring the original uniform temperature gradient in the liquid storage structure 121. Wherein the temperature of the supplementary heat exchange liquid may be the same as or close to the temperature of the heat exchange liquid at the liquid supplementing position, which means that the heat exchange liquid added into the liquid storage tank 1212 does not change the temperature sequence between the liquid storage tank 1212 provided with the liquid supplementing position and the upper and lower liquid storage tanks 1212.
It should be understood that the liquid distribution device 12 is not limited to the above, but may take other forms. Such as: in other exemplary embodiments, the liquid distribution device 12 includes: a liquid distribution mechanism and a liquid storage structure 121. The liquid distribution mechanism comprises a spraying device communicated with the outlet of the heat exchange liquid flow channel 202, and a spraying opening of the spraying device is arranged above the first heat exchanger 11; the liquid storage structure 121 comprises a liquid receiving disc arranged below the first heat exchanger 11, and the liquid receiving disc is arranged to receive heat exchange liquid sprayed by the spraying device.
In the liquid distribution device 12, a liquid inlet of the spray device can be communicated with an outlet of the heat exchange liquid flow channel 202, so that high-temperature heat exchange liquid in the heat exchange liquid flow channel 202 after heat exchange with the refrigerant can flow out from the outlet of the heat exchange liquid flow channel 202 and flow into the spray device. The spray opening of the spray device is arranged above the first heat exchanger 11, and the high-temperature heat exchange liquid entering the spray device can be sprayed downwards to the outer side of the first heat exchanger 11, so that the refrigerant in the first refrigerant flow channel 113 can exchange heat with the high-temperature heat exchange liquid and air outside the first refrigerant flow channel 113, and the high-temperature heat exchange liquid can absorb the heat of the refrigerant and evaporate into high-temperature air to be discharged together with the air. The air flowing outside the first heat exchanger 11 may flow in a direction from the second side 112 (the side where the outlet of the first refrigerant flow channel 113 is located) of the first heat exchanger 11 toward the first side 111 (the side where the inlet of the first refrigerant flow channel 113 is located), or may flow from the bottom up.
The liquid receiving disc is arranged below the first heat exchanger 11 and can be used for receiving unevaporated heat exchange liquid sprayed by the spraying device so as to collect the unevaporated heat exchange liquid and facilitate recycling.
The liquid receiving tray is communicated with the inlet of the heat exchange liquid flow channel 202 through the return pipeline 50, so that the heat exchange liquid flow channel is a circulation flow channel, and the unevaporated heat exchange liquid collected in the liquid receiving tray can flow back to the heat exchange liquid flow channel 202, and heat exchange between the heat exchange fluid and the refrigerant is performed in the second heat exchanger 20, so that the recycling of the heat exchange liquid is realized. In the liquid receiving tray, the remaining non-evaporated heat exchange liquid is cooled due to heat released by air cooling and/or evaporation of other heat exchange liquid, and the low-temperature heat exchange liquid is introduced into the heat exchange liquid flow channel 202 of the second heat exchanger 20 for continuous circulation, so that the heat dissipation effect of the heat exchange liquid entering the second heat exchanger 20 on the refrigerant can be enhanced.
In some exemplary embodiments, as shown in FIG. 2, the second heat exchange device 100 further includes a split flow line 30 and a merge flow line 40. The split line 30 has one inlet and two outlets, and the two outlets are respectively communicated with the inlet of the second refrigerant flow channel 201 and the inlet of the first refrigerant flow channel 113; the merging piping 40 has two inlets and one outlet, and the two inlets are respectively communicated with the outlet of the second refrigerant flow passage 201 and the outlet of the first refrigerant flow passage 113; the inlet of the tap line 30 and the outlet of the merge line 40 may be in communication with the refrigerant line.
In some exemplary embodiments, the second heat exchanger 20 also has a first total heat exchange flow path for the flow of refrigerant and a second total heat exchange flow path for the flow of heat exchange liquid, the refrigerant in the first total heat exchange flow path being arranged to exchange heat with the heat exchange liquid in the second total heat exchange flow path. Wherein: the outlet of the first total heat exchange flow channel is communicated with the inlet of the second refrigerant flow channel 201 and the inlet of the first refrigerant flow channel 113 which are connected in parallel, and the outlet of the second total heat exchange flow channel is communicated with the inlet of the heat exchange liquid flow channel 202; alternatively, the inlet of the first total heat exchange flow channel is arranged to be communicated with both the outlet of the second refrigerant flow channel 201 and the outlet of the first refrigerant flow channel 113 connected in parallel, and the outlet of the heat exchange liquid flow channel 202 is communicated to the liquid distribution device 12 through the second total heat exchange flow channel.
In the second heat exchanger 20, the outlet of the first heat exchange flow channel may be communicated with both the inlet of the second refrigerant flow channel 201 and the inlet of the first refrigerant flow channel 113, so that the refrigerant may flow through the first heat exchange flow channel first and then be split into the second refrigerant flow channel 201 and the first refrigerant flow channel 113; an outlet of the second total heat exchange flow channel can be communicated with an inlet of the heat exchange liquid flow channel 202, heat exchange liquid in the second total heat exchange flow channel can flow into the heat exchange liquid flow channel 202 after exchanging heat with the refrigerant in the first total heat exchange flow channel, and the heat exchange liquid in the heat exchange liquid flow channel 202 flows into the liquid distribution device 12 after exchanging heat with the refrigerant in the second refrigerant flow channel 201 and distributes liquid to the outer side of the first refrigerant flow channel 113.
Alternatively, the inlet of the first heat exchange flow channel may be communicated with both the outlet of the second refrigerant flow channel 201 and the outlet of the first refrigerant flow channel 113, so that the refrigerants split into the second refrigerant flow channel 201 and the first refrigerant flow channel 113 may merge and then flow into the first heat exchange flow channel; the outlet of the heat exchange liquid flow channel 202 is communicated to the liquid distribution device 12 through a second total heat exchange flow channel, namely, the inlet of the second total heat exchange flow channel is communicated with the outlet of the heat exchange liquid flow channel 202, and the outlet of the second total heat exchange flow channel is communicated with the liquid distribution device 12, so that the heat exchange liquid in the heat exchange liquid flow channel 202 flows into the second total heat exchange flow channel after exchanging heat with the refrigerant in the second refrigerant flow channel 201, and the heat exchange liquid in the second total heat exchange flow channel can enter the liquid distribution device 12 after exchanging heat with the refrigerant in the first total heat exchange flow channel and is distributed outside the first refrigerant flow channel 113.
In other exemplary embodiments, the first heat exchanger 11 also has a third total heat exchange flow path for the flow of refrigerant. Wherein the outlet of the third total heat exchange flow channel is arranged to be communicated with the inlet of the second refrigerant flow channel 201 and the inlet of the first refrigerant flow channel 113 which are connected in parallel, or the inlet of the third total heat exchange flow channel is arranged to be communicated with the outlet of the second refrigerant flow channel 201 and the outlet of the first refrigerant flow channel 113 which are connected in parallel, and the refrigerant in the third total heat exchange flow channel is arranged to exchange heat with the air and the heat exchange liquid flowing through the outer side of the first heat exchanger 11.
In the first heat exchanger 11, the outlet of the third total heat exchange flow channel may be communicated with both the inlet of the second refrigerant flow channel 201 and the inlet of the first refrigerant flow channel 113, so that the refrigerant may flow through the third total heat exchange flow channel first and then be split into the second refrigerant flow channel 201 and the first refrigerant flow channel 113; alternatively, the inlet of the third total heat exchange flow path may be communicated with both the outlet of the second refrigerant flow path 201 and the outlet of the first refrigerant flow path 113, so that the refrigerants split into the second refrigerant flow path 201 and the first refrigerant flow path 113 may merge and then flow into the third total heat exchange flow path. The refrigerant in the third total heat exchange flow channel can exchange heat with the air and heat exchange liquid flowing through the outer side of the first heat exchanger 11, so as to realize heat dissipation of the refrigerant.
It should be understood that the refrigerant may be split into the second refrigerant flow channel 201 and the first refrigerant flow channel 113 after flowing a certain distance through the first total heat exchange flow channel in the second heat exchanger 20 or the third total heat exchange flow channel in the first heat exchanger 11, or the refrigerant split into the second refrigerant flow channel 201 and the first refrigerant flow channel 113 may be merged and then enter the first total heat exchange flow channel in the second heat exchanger 20 or the third total heat exchange flow channel in the first heat exchanger 11. Therefore, the branching and joining positions of the refrigerant are not necessarily located outside the second heat exchanger 20 and the first heat exchanger 11, and may be located at a position in the second heat exchanger 20 or the first heat exchanger 11.
In some exemplary embodiments, the air conditioning apparatus further includes a water pan disposed below the first heat exchange device 400 and configured to receive condensate on the first heat exchange device 400, the heat exchange liquid flow path also communicating with the water pan through the fluid replacement conduit 60.
The drip tray may be used as a liquid source and the inlet of the fluid replacement conduit 60 may be in communication with the drip tray to provide heat exchange liquid to the heat exchange liquid flow path 202 or the liquid storage structure 121 via the drip tray. The condensed water of the water receiving tray has a low temperature, and the low-temperature condensed water is introduced into the heat exchange liquid flow passage 202 of the second heat exchanger 20, so that the heat radiation effect on the refrigerant in the second refrigerant flow passage 201 can be enhanced.
In some exemplary embodiments, the air conditioning apparatus further includes a liquid reservoir that may be provided in a communication line between the charging port 604 and the heat exchange liquid flow path.
The air conditioning apparatus may include a reservoir that may be in communication with the charging port 604 to add heat exchange liquid from the charging port 604 into the reservoir. The heat exchange liquid stored in the liquid storage container can provide heat exchange liquid for the heat exchange liquid flow path when the air conditioning equipment works.
In some exemplary embodiments, the refrigerant may include R290, R134a, R600, or R744 (carbon dioxide).
R290, R134a, R600 or R744 are used as refrigerants that are specific to ensure that the heat exchange liquid is heated to a higher temperature so that the heat exchange liquid is sufficiently vaporized into the air. When the air conditioning device is in refrigeration operation, the highest air outlet temperature of the second air outlet 603 can exceed 70 ℃, and the relative humidity can exceed 50%, so that high air outlet temperature and high air outlet humidity are realized.
In some exemplary embodiments, the heat exchange liquid may comprise water or an aqueous solution.
In the second heat exchange device 100, the second heat exchanger 20 may be a water-cooled heat exchanger, such as: the second heat exchanger 20 may be a shell and tube heat exchanger, a plate heat exchanger, a double pipe heat exchanger, or other forms of heat exchangers; the first heat exchanger 11 may be an air-cooled heat exchanger that mainly uses heat exchange liquid to evaporate and absorb heat, such as: the first heat exchanger 11 may be a tube and fin heat exchanger, a microchannel heat exchanger, or other forms of heat exchangers. The refrigerant in the second heat exchanger 20 may exchange heat with water, the temperature of the water increases to become high temperature water, and the high temperature water discharged from the second heat exchanger 20 may be disposed outside the first heat exchanger 11 by spraying or splashing. The refrigerant can exchange heat with air in the first heat exchanger 11, and the air temperature is increased to become high-temperature air; the high temperature water which is simultaneously distributed to the outer side of the first heat exchanger 11 can absorb the heat of the refrigerant in the first heat exchanger 11 and evaporate into the high temperature air.
It should be understood that the refrigerant, heat exchange liquid and air are not limited to the above, but may be provided as other fluids as desired.
Embodiment two:
the embodiment of the present application also provides an air conditioning apparatus, which is mainly different from the air conditioning apparatus of the first embodiment in that: and a second heat exchange device.
As shown in fig. 8 to 13, the second heat exchange device 100 includes a first heat exchanger 11, the first heat exchanger 11 includes a heat exchange liquid flow path 202 and a first refrigerant flow path 113, the first refrigerant flow path 113 is sleeved outside the heat exchange liquid flow path 202, and the refrigerant flow path of the second heat exchange device 100 includes the first refrigerant flow path 113. The refrigerant in the first refrigerant flow channel 113 (i.e., the refrigerant in the annular space between the flow channel wall of the first refrigerant flow channel 113 and the flow channel wall of the heat exchange liquid flow channel 202) is arranged to exchange heat with the heat exchange liquid (such as water) in the heat exchange liquid flow channel 202.
The first heat exchanger 11 is disposed in the second air duct, and the liquid distribution device 12 is communicated with the outlet of the heat exchange liquid flow channel 202, and is configured to distribute the heat exchange liquid flowing out of the heat exchange liquid flow channel 202 to the outer side of the first refrigerant flow channel 113, so that the refrigerant in the first refrigerant flow channel 113 can exchange heat with the heat exchange liquid distributed to the outer side of the first refrigerant flow channel 113 and the air flowing through the outer side of the first refrigerant flow channel 113.
In the second heat exchange device 100, the first refrigerant flow channel 113 of the first heat exchanger 11 may be used for passing a refrigerant, and the refrigerant may be a gas, a liquid or a gas-liquid mixture; the heat exchange liquid flow passage 202 of the first heat exchanger 11 may be used for passage of heat exchange liquid. The heat exchange liquid can exchange heat with the refrigerant in the first refrigerant flow channel 113 when flowing through the heat exchange liquid flow channel 202, and the heat exchange liquid in the heat exchange liquid flow channel 202 can absorb the heat of the refrigerant, so that the temperature of the refrigerant is reduced, the heat dissipation of the refrigerant is realized, and the temperature of the heat exchange liquid is increased.
The liquid distribution device 12 is communicated with the outlet of the heat exchange liquid flow channel 202, and can distribute high-temperature heat exchange liquid to the outer side of the first refrigerant flow channel 113, so that the refrigerant in the first refrigerant flow channel 113 can exchange heat with the high-temperature heat exchange liquid (the temperature of the high-temperature heat exchange liquid is lower than that of the refrigerant in the first refrigerant flow channel 113); in addition, the air in the second air duct may also flow through the first heat exchanger 11, and the air may also exchange heat with the refrigerant in the first refrigerant flow passage 113.
The refrigerant in the first refrigerant flow channel 113 can exchange heat with the heat exchange liquid and air flowing through the outside, and the air can absorb the heat of the refrigerant to become high-temperature air; the heat exchange liquid can absorb the heat of the refrigerant and evaporate into the high-temperature air, and is discharged together with the air.
In the second heat exchange device 100 according to the embodiment of the present application, in the first heat exchanger 11, the heat of the refrigerant in the first refrigerant flow channel 113 is taken away by utilizing the latent heat of evaporation of the heat exchange liquid, and the temperature of the heat exchange liquid is increased after the heat exchange liquid has undergone primary heat exchange with the refrigerant in the first refrigerant flow channel 113 when flowing through the heat exchange liquid flow channel 202, so that the heat exchange liquid is primarily heated by the refrigerant, which is beneficial to the evaporation of the heat exchange liquid after the heat exchange liquid is distributed outside the first refrigerant flow channel 113, and the heat exchange efficiency is improved. The high-temperature heat exchange liquid increases in evaporation amount when being distributed outside the first refrigerant flow channel 113 and exchanges heat with the refrigerant in the first refrigerant flow channel 113, and the heat of the refrigerant taken away by the latent heat of evaporation is larger. In the first heat exchanger 11, the refrigerant is radiated by both the heat absorption of air and the evaporation of the heat exchange liquid, and therefore, the amount of air required for the radiation of the refrigerant can be greatly reduced, and an extremely small air volume can be realized.
The heat of the refrigerant in the first heat exchanger 11 is transferred to the air and the heat exchange liquid at the same time, so that the heat transfer is quick and efficient, the heat exchange can be performed with high efficiency, and the reduction of the overall size of the first heat exchanger 11 is facilitated, so that the first heat exchanger 11 is compact in structure, the used manufacturing materials are reduced, and the cost is reduced.
The liquid distribution device 12 may distribute the heat exchange liquid to the outside of the first refrigerant flow channel 113, or may distribute the heat exchange liquid to the outside surface of the first refrigerant flow channel 113, and/or distribute the heat exchange liquid to the environment outside the first refrigerant flow channel 113.
In some exemplary embodiments, as shown in fig. 8-9, the first heat exchanger 11 further includes a heat exchange fluid flow passage 116 sleeved outside the first refrigerant flow passage 113. The liquid distribution device 12 is configured to distribute the heat exchange liquid flowing out of the heat exchange liquid flow channel 202 into the heat exchange fluid flow channel 116 (i.e., into an annular space between the flow channel wall of the heat exchange fluid flow channel 116 and the flow channel wall of the first refrigerant flow channel 113), and the heat exchange fluid flow channel 116 is in communication with the second air channel and configured to pass air of the second air channel.
The average temperature of the refrigerant in the first refrigerant flow channel 113 is higher than the temperature of the air in the heat exchange fluid flow channel 116 and the temperature of the heat exchange liquid laid into the heat exchange fluid flow channel 116, so that the heat of the refrigerant in the first refrigerant flow channel 113 is transferred to the air in the heat exchange fluid flow channel 116 and the heat exchange liquid laid into the heat exchange fluid flow channel 116 through the flow channel wall between the first refrigerant flow channel 113 and the heat exchange fluid flow channel 116.
The heat exchange liquid in the heat exchange liquid flow passage 202 is heated by the refrigerant and then is distributed into the heat exchange liquid flow passage 116, the heat exchange liquid evaporates in the heat exchange liquid flow passage 116 and absorbs heat of the air and heat transferred from the flow passage wall of the first refrigerant flow passage 113, the air absorbs heat transferred from the first refrigerant flow passage 113, and the heat absorbed air and steam formed by heat absorption and evaporation of the heat exchange liquid are discharged into the atmosphere in a high-temperature and high-humidity state.
The first heat exchanger 11 adopts a multi-channel structure, and heat of the refrigerant in the first refrigerant flow channel 113 can be transferred to heat exchange liquid in the heat exchange liquid flow channel 202, and can be transferred to air and heat exchange liquid in the third heat exchange flow channel, so that heat exchange of the first heat exchanger 11 is quick and efficient.
The heat exchange liquid in the heat exchange liquid flow channel 202 is heated before being distributed, and the evaporation process is heated by the refrigerant in the first refrigerant flow channel 113 again after being distributed, so that the evaporation of the heat exchange liquid is facilitated, the heat absorption capacity is increased, and the structure of the first heat exchanger 11 is more compact and the size is reduced under the same heat dissipation capacity.
In some exemplary embodiments, as shown in fig. 10, the heat exchange liquid flow channels 202 are provided in a plurality of and arranged in parallel, the first refrigerant flow channels 113 are provided in a plurality of and arranged in parallel, the plurality of first refrigerant flow channels 113 are sleeved outside the plurality of heat exchange liquid flow channels 202 in a one-to-one correspondence manner, and the flow directions of the plurality of heat exchange liquid flow channels 202 are the same, and the flow directions of the plurality of first refrigerant flow channels 113 are the same. The liquid distribution device 12 is connected to the outlets of the plurality of heat exchange liquid flow passages 202, and is configured to distribute heat exchange liquid to the outside of the plurality of first refrigerant flow passages 113.
The plurality of first refrigerant flow channels 113 are arranged at intervals, and channels through which air in the second air channel and heat exchange liquid distributed by the liquid distribution device 12 flow are formed at intervals, so that the refrigerant in the first refrigerant flow channels 113 can exchange heat with the air flowing through the outer side and the distributed heat exchange liquid sufficiently, and the heat exchange efficiency is improved.
This structural arrangement of the first heat exchanger 11 makes the first heat exchanger 11 compact, contributing to a reduction in the total volume of the first heat exchanger 11.
In some exemplary embodiments, as shown in fig. 10, the first heat exchanger 11 further includes a heat exchange fluid flow channel 116 sleeved outside the plurality of first refrigerant flow channels 113, a gap is provided between the heat exchange fluid flow channel 116 and each of the first refrigerant flow channels 113, the liquid distribution device 12 is configured to distribute heat exchange liquid into the heat exchange fluid flow channel 116, the heat exchange fluid flow channel 116 is in communication with the second air channel, and the heat exchange fluid flow channel 116 is configured to allow air in the second air channel and heat exchange liquid distributed by the liquid distribution device 12 to pass through, that is, a channel through which the air in the second air channel and the heat exchange liquid distributed by the liquid distribution device 12 flows is formed by a space inside the heat exchange fluid flow channel 116 and outside the first refrigerant flow channels 113.
Gaps are arranged between the heat exchange fluid flow channels 116 and each first refrigerant flow channel 113, so that air in the heat exchange fluid flow channels 116 is fully contacted with the outer sides of the plurality of first refrigerant flow channels 113, and the liquid distribution device 12 distributes heat exchange liquid flowing out of the plurality of heat exchange liquid flow channels 202 into the space between the heat exchange fluid flow channels 116 and the plurality of first refrigerant flow channels 113, so that heat exchange of the first heat exchanger 11 is more efficient, and the overall structure of the first heat exchanger 11 is more compact.
In the embodiment shown in fig. 8 to 10, the heat exchange fluid flow passage 116 is sleeved outside the first refrigerant flow passage 113; in the embodiment shown in fig. 11 to 13, the heat exchange fluid flow passage is not provided outside the first refrigerant flow passage 113.
In some exemplary embodiments, as shown in fig. 8-10, the flow direction of the first refrigerant flow channel 113 is opposite to the flow direction of the heat exchange liquid flow channel 202, i.e., the flow direction of the refrigerant in the first refrigerant flow channel 113 is opposite to the flow direction of the heat exchange liquid in the heat exchange liquid flow channel 202, so as to perform countercurrent heat exchange.
The flow direction of the first refrigerant flow passage 113 is opposite to the flow direction of the air in the heat exchange fluid flow passage 116, i.e., the flow direction of the refrigerant in the first refrigerant flow passage 113 is opposite to the flow direction of the air outside the first refrigerant flow passage 113, so that the countercurrent heat exchange is performed.
The flow direction of the heat exchange liquid in the heat exchange fluid flow passage 116 is set to be opposite to the flow direction of the air in the heat exchange fluid flow passage 116, i.e., the flow direction of the heat exchange liquid outside the first refrigerant flow passage 113 is opposite to the flow direction of the air outside the first refrigerant flow passage 113.
As shown in fig. 8, the heat exchange liquid in the heat exchange liquid flow passage 202 flows from bottom to top, the refrigerant in the first refrigerant flow passage 113 flows from top to bottom, and the air in the heat exchange fluid flow passage 116 flows from bottom to top, and the heat exchange liquid in the heat exchange fluid flow passage 116 flows from top to bottom.
The first refrigerant flow channel 113 is opposite to the fluid flow direction in the heat exchange liquid flow channel 202, and the fluid flow directions in the first refrigerant flow channel 113 and the heat exchange fluid flow channel 116 are opposite to each other, so as to form a good countercurrent heat exchange effect: the temperature of the refrigerant at the inlet of the first refrigerant flow channel 113 may be slightly higher than the temperature of the heat exchange liquid at the outlet of the heat exchange liquid flow channel 202 and the temperature of the air at the outlet of the heat exchange fluid flow channel 116, and the temperature of the refrigerant at the outlet of the first refrigerant flow channel 113 is slightly higher than the temperature of the heat exchange liquid at the inlet of the heat exchange liquid flow channel 202 and the temperature of the air at the inlet of the heat exchange fluid flow channel 116, so that a uniform temperature gradient with a lower level is maintained between the fluids as a whole, the average heat transfer temperature difference is lower, and the energy loss is small.
The heat exchange liquid in the heat exchange liquid flow channel 202 is distributed into the heat exchange fluid flow channel 116 from top to bottom through the liquid distribution device 12, and the air in the heat exchange fluid flow channel 116 flows from bottom to top, opposite to the flow direction of the heat exchange liquid in the heat exchange fluid flow channel 116, so that the countercurrent heat exchange effect is also achieved as described above. In addition, the air gradually absorbs heat and vapor formed by evaporation of heat exchange liquid in the upward flowing process, the temperature rises, the absolute moisture content rises, the relative humidity is kept at a certain level, certain moisture absorption capacity is maintained, and the air quantity is fully utilized, so that the required air quantity is smaller under the same heat dissipation capacity.
In some exemplary embodiments, as shown in fig. 11 and 12, the inlet of the first refrigerant flow channel 113 and the outlet of the heat exchange liquid flow channel 202 are located on the first side 111 of the first heat exchanger 11, the outlet of the first refrigerant flow channel 113 and the inlet of the heat exchange liquid flow channel 202 are located on the second side 112 of the first heat exchanger 11, and the first side 111 and the second side 112 of the first heat exchanger 11 are opposite sides.
Wherein, the flow direction of the first refrigerant flow channel 113 is opposite to the flow direction of the heat exchange liquid flow channel 202, that is, the flow direction of the refrigerant in the first refrigerant flow channel 113 is opposite to the flow direction of the heat exchange liquid in the heat exchange liquid flow channel 202; the flow direction of the air outside the first refrigerant flow passage 113 is set to flow from the second side 112 of the first heat exchanger 11 toward the first side 111 (as shown in fig. 12), or from bottom to top (as shown in fig. 11).
As shown in fig. 11, the flow direction of the heat exchange liquid disposed by the liquid distribution device 12 may be opposite to the flow direction of the air.
The second heat exchange device 100 shown in fig. 11 and 12 also has the countercurrent heat exchange effect as described above.
In some exemplary embodiments, as shown in fig. 12, the first heat exchanger 11 includes a plurality of rows of heat exchange units 114 vertically disposed and horizontally sequentially arranged, each row of heat exchange units 114 may include a first heat exchange sub-pipeline and a second heat exchange sub-pipeline sleeved outside the first heat exchange sub-pipeline, the first heat exchange sub-pipeline and the second heat exchange sub-pipeline may be serpentine distributed curved pipelines, the first heat exchange sub-pipelines of the plurality of rows of heat exchange units 114 are sequentially communicated to form a heat exchange liquid flow channel 202, and the second heat exchange sub-pipelines of the plurality of rows of heat exchange units 114 are sequentially communicated to form a first refrigerant flow channel 113, so that the first heat exchanger 11 adopts a double-layer pipe structure.
The water beating pieces 122 of the liquid distribution device 12 are arranged in one-to-one correspondence with the vertical intervals 115 of the first heat exchanger 11, the upper parts of the water beating pieces 122 can be located in the corresponding vertical intervals 115, and heat exchange liquid excited by the water beating pieces 122 can fall onto the heat exchange units 114 on two sides of the vertical intervals 115 corresponding to the water beating pieces 122 so as to dissipate heat of the refrigerant by utilizing evaporation of the heat exchange liquid.
In some exemplary embodiments, the inner side and/or the outer side of at least one of the first refrigerant flow channel 113, the heat exchange liquid flow channel 202, and the heat exchange fluid flow channel 116 of the first heat exchanger 11 is provided with a concave structure or a convex structure, and the concave structure may be a structure such as a screw thread, a groove, or the like, and the convex structure may be a structure such as a protrusion, a fin, or the like.
The concave structures or the convex structures can increase the heat exchange area between the refrigerant, the heat exchange liquid and the air so as to improve the heat exchange efficiency; and these concave structure or protruding structure can also provide the vortex effect for refrigerant, heat transfer liquid, the temperature of air in each runner are more even, are favorable to improving the heat transfer effect. Therefore, the concave structures or the convex structures integrally play a role in enhancing the heat exchange effect and improving the heat exchange efficiency.
In some exemplary embodiments, a gas-permeable porous adsorption material may be provided outside the first refrigerant flow channel 113. The porous adsorption materials can slow down the passing speed of the heat exchange liquid and the air, so that the contact time between the heat exchange liquid and the air is increased, the heat exchange liquid absorbs heat and then evaporates into the air, and the steam of the heat exchange liquid can flow away with the air.
In some exemplary embodiments, the second heat exchange device 100 further includes a third heat exchanger, which may be a conventional tube and fin heat exchanger. The third heat exchanger has a third refrigerant flow passage, which may be connected in series with the first refrigerant flow passage.
By connecting the first heat exchanger 11 and the third heat exchanger in series, the heat exchanging effect of the second heat exchanging device 100 as a whole is further improved.
In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present application and simplifying the description, and do not indicate or imply that the device or element being referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present application.
Furthermore, in the description of the present application, the meaning of "plurality" means at least two, for example, two, three, etc., unless specifically defined otherwise.
In the present application, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly, through intermediaries, or both, may be in communication with each other or in interaction with each other, unless expressly defined otherwise. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art according to the specific circumstances.
In the present application, unless expressly stated or limited otherwise, a first feature "up" or "down" a second feature may be the first and second features in direct contact, or the first and second features in indirect contact via an intervening medium. Moreover, a first feature being "above," "over" and "on" a second feature may be a first feature being directly above or obliquely above the second feature, or simply indicating that the first feature is level higher than the second feature. The first feature being "under", "below" and "beneath" the second feature may be the first feature being directly under or obliquely below the second feature, or simply indicating that the first feature is less level than the second feature.
In the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present application. In this specification, schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, the different embodiments or examples described in this specification and the features of the different embodiments or examples may be combined and combined by those skilled in the art without contradiction.
While embodiments of the present application have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the application, and that variations, modifications, alternatives and variations may be made to the above embodiments by one of ordinary skill in the art within the scope of the application.
Claims (24)
1. An air conditioning apparatus, comprising:
The shell is provided with a first air channel, a second air channel and a liquid adding port; and
the heat exchange system is arranged in the shell and comprises a compression device, a first heat exchange device, an expansion device and a second heat exchange device which are sequentially communicated through a refrigerant pipeline, wherein the second heat exchange device comprises a refrigerant flow channel, a heat exchange liquid flow channel and a liquid distribution device, heat exchange liquid in the heat exchange liquid flow channel is arranged to exchange heat with at least part of refrigerant in the refrigerant flow channel, the liquid distribution device is communicated with an outlet of the heat exchange liquid flow channel and forms a heat exchange liquid flow channel, and the liquid distribution device is arranged to distribute heat exchange liquid flowing out of the heat exchange liquid flow channel to the outer side of at least part of the refrigerant flow channel;
the first heat exchange device is arranged in the first air duct, a part of refrigerant flow channels for distributing heat exchange liquid in the second heat exchange device are arranged in the second air duct, and the liquid adding port is communicated with the heat exchange liquid flow channels.
2. The air conditioning apparatus of claim 1, wherein the housing further has an air inlet, a first air outlet, and a second air outlet, the air inlet is in communication with the first air outlet through the first air duct, the air inlet is in communication with the second air outlet through the second air duct, and the air inlet and the first air outlet are both disposed in communication with the room, and the second air outlet is disposed in communication with the outside.
3. An air conditioning apparatus according to claim 1, wherein the second heat exchanging arrangement further comprises:
a first heat exchanger including a first refrigerant flow path; and
the second heat exchanger comprises the heat exchange liquid flow channel and a second refrigerant flow channel, and the refrigerant in the second refrigerant flow channel is arranged to exchange heat with the heat exchange liquid in the heat exchange liquid flow channel;
the first refrigerant flow channel and the second refrigerant flow channel are connected in parallel, and the refrigerant flow channel comprises the first refrigerant flow channel and the second refrigerant flow channel;
the first heat exchanger is arranged in the second air duct, and the liquid distribution device is arranged to distribute the heat exchange liquid flowing out of the heat exchange liquid flow passage to the outer side of the first refrigerant flow passage.
4. An air conditioning apparatus as set forth in claim 3 wherein the flow direction of said second refrigerant flow path is opposite to the flow direction of said heat exchange liquid flow path;
the inlet and the outlet of the first refrigerant flow channel are respectively positioned on a first side and a second side which are opposite to each other of the first heat exchanger, and the air outside the first heat exchanger flows from the second side of the first heat exchanger to the first side or from bottom to top.
5. An air conditioning apparatus according to claim 1, wherein the second heat exchanging means includes:
the first heat exchanger comprises the heat exchange liquid flow passage and a first refrigerant flow passage, the first refrigerant flow passage is sleeved outside the heat exchange liquid flow passage, and the refrigerant flow passage comprises the first refrigerant flow passage;
the first heat exchanger is arranged in the second air duct, and the liquid distribution device is arranged to distribute the heat exchange liquid flowing out of the heat exchange liquid flow passage to the outer side of the first refrigerant flow passage.
6. The air conditioning apparatus of claim 5, wherein said first heat exchanger further comprises a heat exchange fluid flow path nested outside of said first refrigerant flow path, said liquid distribution means being configured to distribute heat exchange liquid into said heat exchange fluid flow path, said heat exchange fluid flow path being in communication with said second air duct and configured to pass air from said second air duct.
7. The air-conditioning apparatus according to claim 5, wherein a plurality of heat exchange liquid flow passages are provided and arranged in parallel, a plurality of first refrigerant flow passages are sleeved outside a plurality of heat exchange liquid flow passages in one-to-one correspondence, and the flow directions of a plurality of heat exchange liquid flow passages are the same, and the flow directions of a plurality of first refrigerant flow passages are the same;
The outlets of the heat exchange liquid flow channels are communicated with the liquid distribution device, and the liquid distribution device is arranged to distribute heat exchange liquid to the outer sides of the first refrigerant flow channels;
the plurality of first refrigerant flow channels are arranged at intervals, and channels through which air in the second air channel and heat exchange liquid distributed by the liquid distribution device flow are formed at intervals.
8. The air conditioning apparatus of claim 7, wherein said first heat exchanger further comprises a heat exchange fluid flow path that is sleeved outside of a plurality of said first refrigerant flow paths, a gap being provided between said heat exchange fluid flow path and each of said first refrigerant flow paths, said liquid distribution means being configured to distribute heat exchange liquid into said heat exchange fluid flow path, said heat exchange fluid flow path being in communication with said second air duct and configured to pass air from said second air duct.
9. An air conditioning apparatus as claimed in claim 6 or 8, wherein the flow direction of the first refrigerant flow passage is set opposite to the flow direction of the heat exchange liquid flow passage; and/or
The flow direction of the first refrigerant flow passage is set to be opposite to the flow direction of the air in the heat exchange fluid flow passage; and/or
The flow direction of the heat exchange liquid in the heat exchange fluid flow passage is set to be opposite to the flow direction of the air in the heat exchange fluid flow passage.
10. An air conditioning unit as claimed in claim 5 or 7, wherein the inlet of the first refrigerant flow path and the outlet of the heat exchange liquid flow path are located on a first side of the first heat exchanger, the outlet of the first refrigerant flow path and the inlet of the heat exchange liquid flow path are located on a second side of the first heat exchanger, the first and second sides of the heat exchanger being opposite sides;
wherein the flow direction of the first refrigerant flow channel is opposite to the flow direction of the heat exchange liquid flow channel; and/or the air outside the first refrigerant flow channel flows from the second side of the first heat exchanger towards the first side or from bottom to top.
11. An air conditioning apparatus as claimed in any one of claims 3 to 8, wherein the liquid distribution means comprises a liquid storage structure having a liquid storage space communicating with the outlet of the heat exchange liquid flow passage and a liquid distribution mechanism arranged to distribute the heat exchange liquid in the liquid storage space to the outside of the first refrigerant flow passage.
12. The air conditioning apparatus according to claim 11, wherein the liquid distribution mechanism includes a water-beating member and a driving member, the driving member being connected to the water-beating member and configured to drive the water-beating member to move, a portion of the water-beating member being accommodated in the liquid storage space and configured to excite and splash the heat exchange liquid in the liquid storage space to the outside of the first refrigerant flow passage.
13. The air conditioning apparatus of claim 12, wherein said first heat exchanger includes a plurality of rows of heat exchange units arranged vertically and arranged in sequence in a lateral direction, with a vertical spacing between adjacent rows of said heat exchange units;
the liquid storage structure set up in first heat exchanger below, the piece of fetching water is provided with at least one, and with vertical interval one-to-one sets up, another part of the piece of fetching water is located corresponding vertical interval is interior, and sets up to enable heat transfer liquid in the liquid storage space splashes to corresponding the heat transfer unit of vertical interval both sides.
14. The air conditioning apparatus of claim 13, wherein said first heat exchanger includes at least three rows of said heat exchange units such that said first heat exchanger has a plurality of said vertical intervals;
The water pumping pieces are arranged in a plurality, the liquid storage space is divided into a plurality of liquid storage tanks, the liquid storage tanks are in one-to-one correspondence with the vertical intervals and are positioned below the corresponding vertical intervals, the liquid storage tanks are in one-to-one correspondence with the water pumping pieces, and a part of the water pumping pieces are accommodated in the corresponding liquid storage tanks.
15. The air conditioning apparatus of claim 14, wherein said liquid storage space has a liquid input communicating with an outlet of said heat exchange liquid flow passage, a plurality of said liquid storage tanks being arranged in sequence in a direction away from said liquid input;
a separator is arranged between adjacent liquid storage tanks, wherein:
the top surface of the partition piece forms an overflow surface, and the height of the overflow surface is sequentially reduced along the direction away from the liquid input end, so that heat exchange liquid in one liquid storage tank can flow into the adjacent liquid storage tank away from one side of the liquid input end through the overflow surface; or,
the separating piece is provided with overflow holes communicated with the liquid storage tanks at two sides of the separating piece, and the height of the overflow holes is sequentially reduced along the direction away from the liquid input end, so that heat exchange liquid in one liquid storage tank can flow into the adjacent liquid storage tank away from one side of the liquid input end through the overflow holes.
16. The air conditioning apparatus of claim 15, wherein the bottom surfaces of the plurality of liquid reservoirs are flush or the heights of the bottom surfaces of the plurality of liquid reservoirs decrease in sequence in a direction away from the liquid input end.
17. The air conditioning unit of claim 15, wherein the inlet and outlet of the first refrigerant flow channel are located on opposite first and second sides of the first heat exchanger, respectively, and the liquid input is proximate either the first or second side of the first heat exchanger.
18. The air conditioning apparatus of claim 15, wherein the liquid storage space further has a liquid output end, the liquid output end being located on a side of the liquid storage space remote from the liquid input end, the liquid output end being in communication with the inlet of the heat exchange liquid flow passage through a return line such that the heat exchange liquid flow passage is a circulation flow passage.
19. The air conditioning apparatus according to claim 12, wherein a plurality of said driving members and said water-beating members are provided, and a plurality of said driving members are connected in one-to-one correspondence with a plurality of said water-beating members; or (b)
The driving piece is provided with an output shaft, the plurality of water-beating pieces are all installed on the output shaft, and the output shaft is horizontally arranged or obliquely arranged.
20. The air conditioning apparatus of claim 15, wherein said water-beating member includes a water-beating wheel, and the outer diameters of a plurality of said water-beating wheels are sequentially increased or equalized in a direction away from said liquid input end.
21. An air conditioning apparatus as claimed in any one of claims 3 to 8, wherein the liquid distribution means comprises:
the liquid distribution mechanism comprises a spraying device communicated with the outlet of the heat exchange liquid flow channel, and a spraying opening of the spraying device is arranged above the first heat exchanger; and
the liquid storage structure comprises a liquid receiving disc arranged below the first heat exchanger, and the liquid receiving disc is arranged to be capable of receiving heat exchange liquid sprayed by the spraying device.
22. The air conditioning apparatus of claim 21, wherein said liquid receiving tray communicates with an inlet of said heat exchange liquid flow path through a return line such that said heat exchange liquid flow path is a circulation flow path.
23. The air conditioning apparatus according to any one of claims 1 to 8, further comprising:
the water receiving disc is arranged below the first heat exchange device and is arranged to receive condensed water on the first heat exchange device, and the heat exchange liquid flow path is also communicated with the water receiving disc through a liquid supplementing pipeline; and/or
The liquid storage container is arranged on a communication pipeline between the liquid adding port and the heat exchange liquid flow path.
24. An air conditioning apparatus according to any one of claims 1 to 8, wherein the refrigerant is R290, R134a, R600 or R744; and/or
The heat exchange liquid comprises water or an aqueous solution.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202321095746.6U CN220017537U (en) | 2023-05-08 | 2023-05-08 | Air conditioning equipment |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202321095746.6U CN220017537U (en) | 2023-05-08 | 2023-05-08 | Air conditioning equipment |
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| CN220017537U true CN220017537U (en) | 2023-11-14 |
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| CN202321095746.6U Active CN220017537U (en) | 2023-05-08 | 2023-05-08 | Air conditioning equipment |
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| CN (1) | CN220017537U (en) |
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