Heat exchange system and application equipment equipped with the heat exchange system

Abstract

To provide a heat exchange system capable of obtaining good heat exchange efficiency over an extended period of time from an early stage of driving even when water content adheres to a fin of a heat exchanger during driving.SOLUTION: A heat exchange system comprises a heat exchanger including a plurality of fins coming into contact with air containing water content and cooling air by exchanging heat via the fins between a coolant circulating inside and the air, and a supply member supplying an additive agent for reducing a contact angle to the fins to the water content adhering to the fins due to cooling.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] The present disclosure relates to a heat exchange system and an application device including the heat exchange system, and particularly to a technique for improving the heat exchange efficiency of the heat exchange system.

Background Art

[0002] A heat exchange system mounted on an air conditioner or the like includes, for example, a heat exchanger having a plurality of fins, and heat exchange is performed between air and a heat medium flowing inside through the plurality of fins. When the fins are cooled by heat exchange during the operation of the heat exchange system, moisture in the air may aggregate when the air comes into contact with the fins, and moisture may adhere to the fins. When moisture adheres to the fins, the heat exchange efficiency of the heat exchanger may decrease due to the influence of the specific heat, thermal conductivity, latent heat, or sensible heat of the moisture. Further, when moisture adheres to a plurality of fins, the gaps between the fins may be blocked by the moisture. As a result, the flow of air in the heat exchanger is inhibited and the heat exchange efficiency decreases.

[0003] Therefore, for example, in Patent Document 1, a hydrophilic film containing a hydrophilic resin and a silicone resin is formed on the surface of the fins of a heat exchanger to quickly discharge the moisture adhering to the fins and impart antifouling properties to the fins.

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0005] However, in the method of Patent Document 1, the hydrophilicity of the hydrophilic film is likely to decrease due to the oil repellency of the silicone resin. Further, it is difficult to sufficiently obtain antifouling properties by this method, dirt adheres to the fins, and the hydrophilicity of the hydrophilic film decreases. As a result, the heat exchange efficiency of the heat exchanger decreases.

[0006] Therefore, an object of the present disclosure is to obtain excellent heat exchange efficiency over a long period from the initial stage of driving even when moisture adheres to the fins of a heat exchanger during operation in a heat exchange system.

Means for Solving the Problems

[0007] A heat exchange system according to one aspect of the present disclosure includes a plurality of fins that come into contact with air containing moisture, a refrigerant flowing inside, and a heat exchanger that cools the air by exchanging heat with the air through the fins. The heat exchange system also includes a supply member that supplies an additive that reduces the contact angle of the moisture adhering to the fins with respect to the fins.

[0008] According to the above configuration, when moisture adheres to the fins of the heat exchanger during heat exchange between air and the refrigerant for cooling, the contact angle of the moisture with respect to the fins decreases due to the additive supplied from the supply member. As a result, the wettability of the fin surface is improved, and the water film formed on the fin surface can be thinned. Also, since the surface tension of the moisture decreases, it becomes easier to discharge the moisture from the fin surface. As a result, it is possible to prevent the heat exchange efficiency from decreasing due to the moisture adhering to the fins or the air flow inside the heat exchanger from being obstructed by the moisture adhering to the fin surface, thereby reducing the heat exchange efficiency of the heat exchange system. Further, when impurities in the air adhere to the fins, the impurities can be quickly discharged together with the water film by forming a thin water film on the fin surface, and the fins can be maintained in a clean state.

[0009] In addition, these effects continue because the additive is supplied by the supply member to the moisture adhering to the fins. Also, since the additive can be supplied to the moisture adhering to the fins by the supply member, the labor of supplying the additive can be omitted. Therefore, excellent heat exchange efficiency can be obtained over a long period even when moisture or dirt adheres to the fins of the heat exchanger during operation in the heat exchange system.

[0010] The additive may be supplied by free fall from the supply member to the moisture adhering to the fins. Thereby, the additive can be automatically and efficiently added from the supply member to the fins by utilizing gravity, and the structure of the heat exchange system can be simplified.

[0011] The supply member may be arranged so as to be in contact with the fins. Thereby, it is possible to easily supply the additive from the supply member to the moisture adhering to the fins.

[0012] The plurality of fins extend in the vertical direction and are arranged side by side in an intersecting direction intersecting the vertical direction. The supply member may be elongated in the intersecting direction and arranged so as to be in contact with the end faces of the plurality of fins. Thereby, it is possible to easily supply the additive from the supply member along the surfaces extending in the vertical direction of each fin to the moisture adhering to the plurality of fins.

[0013] The supply member may be detachably arranged with respect to the heat exchanger. Thereby, the maintainability of the heat exchange system can be improved, and the supply member can be easily replaced as necessary. Therefore, stable heat exchange efficiency can be maintained over a long period.

[0014] The supply member may include a plurality of carriers that carry the additive, and a support that supports the plurality of carriers in a dispersed state so that the additive can be released from the carriers to the outside of the supply member.

[0015] According to the above configuration, by carrying the additive by the plurality of dispersed carriers, it is possible to easily supply the additive over a wide range to the moisture adhering to the fins from each carrier. Further, by the support, by supporting the plurality of carriers so that the additive can be released from the plurality of carriers to the outside of the supply member, the additive can be stably supplied from the supply member to the fins while supporting the carriers.

[0016] The carrier may be a porous granular material. Thereby, a rich additive can be retained in the pores of the carrier, and the additive can be slowly released from the supply member to the fins, so that the additive can be supplied to the moisture adhering to the fins over a long period from the initial stage of driving of the heat exchange system.

[0017] The additive may be a surfactant. Thereby, it can be easily made to favorably reduce the contact angle of the moisture adhering to the fins. Also, by using, for example, an existing surfactant as the additive, the degree of freedom in the design of the heat exchange system can be improved.

[0018] The additive may dissolve, disperse, or diffuse in the moisture adhering to the fins. Thereby, the additive can be quickly spread from the supply member to the moisture adhering to the fins.

[0019] An application device according to an aspect of the present disclosure includes any one of the above-described heat exchange systems. This application device is an air conditioner including an indoor unit, and the heat exchange system may be mounted on the indoor unit. Also, this application device is an air conditioner including an outdoor unit, includes a defrosting mechanism for removing frost adhering to the heat exchanger, and the heat exchange system may be mounted on the outdoor unit. Also, this application device may be a refrigeration device including a defrosting mechanism for removing frost adhering to the heat exchanger and refrigerating or freezing an object.

Effects of the Invention

[0020] According to each aspect of the present disclosure, in a heat exchange system, excellent heat exchange efficiency can be obtained over a long period from the initial stage of driving even when moisture adheres to the fins of the heat exchanger during driving.

Brief Description of the Drawings

[0021]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

Figure 9

Figure 10

Figure 11

Figure 12

Figure 13

Figure 14

Figure 15

Figure 16

Figure 17

DETAILED DESCRIPTION OF THE INVENTION

[0022] Hereinafter, each embodiment will be described with reference to the drawings. (First Embodiment) [Heat Exchange System and Application Equipment] FIG. 1 is a perspective view of an indoor unit of the application equipment 1 according to the first embodiment. FIG. 2 is an enlarged schematic view showing a state in which an additive is supplied to the moisture adhering to the fins 5 from the supply member 4 of FIG. 1. The application equipment 1 shown in FIG. 1 is, for example, an air conditioner including an indoor unit 10 and an outdoor unit (not shown). This air conditioner functions as a cooling device in this embodiment. The application equipment 1 includes a heat exchange system 2. This heat exchange system 2 is mounted on the indoor unit 10.

[0023] In the application equipment 1, the refrigerant circulates between the indoor unit 10 and the outdoor unit. The heat exchange system 2 exchanges heat between the indoor air and the refrigerant. The heat exchange system 2 has a plurality of fins 5 that come into contact with the air containing moisture, and includes a heat exchanger (evaporator) 3 through which the refrigerant flows inside, and a plurality of supply members 4 that supply an additive that reduces the contact angle with respect to the fins 5 to the moisture adhering to the fins 5.

[0024] When the air conditioner is driven as a cooling device, the heat exchanger 3 cools the indoor air by exchanging heat between the refrigerant flowing inside and the indoor air through the fins 5. The plurality of fins 5 extend in the vertical direction as an example, and are arranged so as to be spaced apart in the intersection direction (here, the horizontal direction) intersecting the vertical direction. The fins 5 contain, for example, a metal material (such as aluminum) with excellent thermal conductivity, but the material of the fins 5 is not limited to this. The plurality of fins 5 are in contact with the flow pipe 6 through which the refrigerant of the heat exchanger 3 flows.

[0025] The supply member 4 supplies an additive that reduces the contact angle with respect to the fins 5 to the moisture adhering to the fins 5 when the indoor air is cooled. As will be described later, the supply member 4 can thin the water film formed on the surface of the fins 5. In the present embodiment, the additive of the supply member 4 is supplied to the moisture adhering to the fins 5 by free fall. The supply member 4 gradually releases the additive so as to continuously supply the additive to the moisture adhering to the fins 5 over a predetermined period (for example, about several years). When the supply member 4 comes into contact with moisture, the supply member 4 releases the additive to the outside while dispersing the additive in the water.

[0026] As shown in FIGS. 1 and 2, as an example, the supply member 4 is elongated in the intersecting direction and is arranged so as to contact the end faces of the plurality of fins 5. The supply member 4 is formed in a strip shape and is arranged such that its longitudinal direction is along the arrangement direction of the plurality of fins 5. The supply member 4 is detachably arranged with respect to the heat exchanger 3. That is, the supply member 4 can be replaced with respect to the heat exchanger 3 at a predetermined timing.

[0027] The heat exchange system 2 of the present embodiment includes a plurality of supply members 4 arranged apart from each other. One supply member 4 extends in the thickness direction of the plurality of fins 5 of the heat exchanger 3 and contacts the end faces of the respective fins 5. As shown in FIG. 1, as an example, the heat exchanger 3 has a plurality of blocks 3a to 3c that are bent and arranged in the circumferential direction of the cylindrical fan 11 of the indoor unit 10. The plurality of supply members 4 are arranged so as to overlap with the respective blocks 3a to 3c. Thereby, each supply member 4 supplies an additive to the moisture adhering to the plurality of fins 5 of each block 3a to 3c. In the present embodiment, at least one supply member 4 is arranged between the filter 7 and the heat exchanger 3 of the indoor unit 10.

[0028] FIG. 3 is an enlarged view showing the internal structure of the supply member 4 in FIG. 1. As shown in FIG. 3, the supply member 4 includes a plurality of carriers 40 that carry an additive, and a support 41 that supports the plurality of carriers 40 in a dispersed state so that the additive can be released from the carriers 40 to the outside of the supply member 4.

[0029] The carrier 40 of this embodiment is a porous granular material. The outer diameter of this granular material can be set as appropriate, for example, it can be set to a value of several μm. As another example, this granular material can have a pore volume set to a value of several mL / g, a pore diameter set to a value of a dozen or so nm, and a specific surface area set to a value of several hundred m 2 / g, respectively. The particle size, specific surface area, and pore diameter of the granular material are set to values suitable for, for example, the sustained release of the additive required by the supply member 4. By configuring the carrier 40 with a porous granular material, for example, a rich additive can be carried inside the carrier 40. The carrier 40 of this embodiment contains an inorganic component. As an example, the carrier 40 is composed of porous glass containing glass such as amorphous silica. Examples of the material of the carrier 40 can include at least any one of porous glass, activated carbon, zeolite, and porous concrete.

[0030] The support 41 of this embodiment contains a water-insoluble component. This water-insoluble component is, as an example, a water-insoluble resin. Examples of this water-insoluble resin can include at least any one of polyethylene, polypropylene, polyamide, polyethylene terephthalate, polybutylene terephthalate, and acrylic-modified polyethylene (for example, "Acryft" manufactured by Sumitomo Chemical Co., Ltd.).

[0031] In the supply member 4, the support 41 is filled in the gaps between the plurality of carriers 40. As a result, the plurality of carriers 40 are supported by the support 41 in a state of being in contact with or separated from each other. When the supply member 4 comes into contact with water, for example, the additive is supplied from the carrier 40 located on the surface layer of the supply member 4 and elutes into the water. Thereby, the concentration of the additive in the carrier 40 on the surface layer decreases. Then, the additive moves from the carrier 40 located inside the supply member 4 toward the carrier 40 located on the surface layer of the supply member 4, and the concentration of the additive in the carrier 40 on the surface layer increases. The additive in the carrier 40 on this surface layer elutes into the water. By repeating this, the additive is supplied from the supply member 4 to the external water.

[0032] As this additive, any additive can be appropriately selected as long as it can reduce the contact angle with respect to the fins 5 against the moisture adhering to the fins 5. Examples of the additive include surfactants. The surfactant referred to here means a compound having a hydrophilic group and a hydrophobic group in its molecular structure. Examples of the surfactant include, for example, if it is an anionic surfactant, fatty acid salts, N-acyl sarcosine salts, N-acyl glutamate salts, alkylbenzene sulfonate salts, malic acid amides, alkane sulfonate salts, alkyl sulfate salts, polyoxyethylene alkyl ether sulfate salts, α-olefin sulfonate salts, N-acyl-N-methyl taurate salts, N-sulfo fatty acid esters, alkyl phosphates, etc. can be exemplified. Also, if it is a cationic surfactant, alkyl trimethyl ammonium salts, alkylbenzalkonium chlorides, fatty acid amide propyl cations, fatty acid amide butyl guanidines, dialkyldimethyl ammonium salts, etc. can be exemplified. Also, if it is an amphoteric surfactant, alkyl dimethyl acetic acid betaines, fatty acid amide propyl betaines, alkyl dimethyl hydroxy sulfobetaines, amide amino acid salts, alkyl amine oxides, alkyl imidazolinium betaines, etc. can be exemplified. Also, if it is a nonionic surfactant, fatty acid glycerin esters, fatty acid sorbitan esters, fatty acid sucrose esters, alkyl polyglucosides, polyoxyethylene propylene alkyl ethers, polyoxyethylene alkyl ethers, polyoxyethylene alkyl phenyl ethers, oxyalkylene alkyl ether-based surfactants such as polyoxyethylene polyoxypropylene glycol, etc. can be exemplified. The surfactant is not limited to this and can be suitably selected according to the use target and environment.

[0033] The supply member 4 contains, as an example, a support 41 of 20% by weight or more and 50% by weight or less, a carrier 40 of 10% by weight or more and 30% by weight or less, and a composition formed from the balance. The additive is contained in this balance. The composition ratio of the supply member 4 is not limited to this.

[0034] As shown in FIG. 2, when a surfactant is used as an additive and the additive is supplied to the moisture adhering to the plurality of fins 5, the contact angle can be favorably reduced and the additive can be diffused over a wide area of each fin 5. Examples of the additive include, in addition to surfactants, water-soluble organic solvents and the like. Examples of the organic solvent include alcohols, ketones, esters, ethers, and the like. Among these, for example, lower alcohols are suitable. Examples of the lower alcohol include ethanol, propanol, isopropyl alcohol, butanol, and the like.

[0035] The additive of the present embodiment dissolves, disperses, or diffuses in the moisture adhering to the fin 5. Thereby, for example, even in a direction intersecting the vertical direction, the additive can be quickly spread from the supply member 4 to the moisture adhering to the fin 5.

[0036] Next, a method for manufacturing the supply member 4 will be exemplified. As an example, the carrier 40, the support 41, and the additive are heated and kneaded to form a strand. After cutting this strand into a predetermined dimension, the supply member 4 having a desired shape can be obtained by injection molding the slice. If the supply member 4 is manufactured by injection molding, the shape of the supply member 4 can be easily set according to the shape of the heat exchanger 3, for example. Thus, when manufacturing the supply member 4 by heating and kneading the material and injection molding, as the material of the carrier 40, those having a strength capable of withstanding kneading and heat resistance in the temperature range during injection molding are suitable. Further, as the materials of the support 41 and the additive, those having heat resistance in the temperature range during the injection molding are suitable.

[0037] The shape of the supply member 4 is not limited to a long shape, and may be, for example, a spherical shape such as an ellipsoidal sphere or a rectangular parallelepiped. When arranging a single or a small amount of the supply member 4 in the indoor unit 10, for example, by arranging the columnar supply member 4 at the top of the heat exchanger 3 such that the longitudinal direction is along the arrangement direction of the plurality of fins 5, the additive can be efficiently diffused over a wide area of each fin 5.

[0038] The supply member 4 may contain other components. Examples of such components include, but are not limited to, at least one of a surfactant, an ester, salts, an antifoaming agent, a viscosity modifier, a fragrance, a coloring agent, a pH adjuster, an antioxidant, and inorganic substances such as talc and silica, which are different from the aforementioned additives. Also, the number of supply members 4 provided in the heat exchange system 2 is not limited.

[0039] When the application device 1 is driven as a refrigeration device, for example, the low-temperature refrigerant supplied from the compressor of the outdoor unit flows through the heat exchanger 3 in the indoor unit 10. The indoor air comes into contact with the plurality of fins 5 of the heat exchanger 3. As a result, the indoor air exchanges heat with the refrigerant flowing through the inside of the heat exchanger 3 via the plurality of fins 5 and is cooled. This cooled air is discharged from the indoor unit 10 into the room. Since the indoor air contains moisture, when the fins 5 cooled by the refrigerant come into contact with the indoor air, moisture adheres to the fins 5. The refrigerant used for heat exchange is sent from the indoor unit 10 to the outdoor unit. This refrigerant is heat-exchanged with the outside air by the condenser of the outdoor unit and condensed, then compressed by the compressor and supplied to the indoor unit 10 again.

[0040] Here, conventionally, the moisture adhering to the fins aggregates, for example, into water droplets. When water droplets adhere to the fins, the heat exchange efficiency of the heat exchanger decreases due to the influence of the specific heat, thermal conductivity, latent heat, or sensible heat of water. Also, when water droplets adhere to a plurality of fins, the gaps between the fins are blocked by the water droplets, inhibiting the flow of air in the heat exchanger and reducing the heat exchange efficiency. Moreover, the heat exchange efficiency also decreases when impurities in the air adhere to the fins and the fins become dirty.

[0041] In contrast, in this embodiment, when moisture adheres to the fins 5 of the heat exchanger 3 during heat exchange between air and the refrigerant for cooling, the contact angle of the moisture with respect to the fins 5 decreases from the additive supplied from the supply member 4. As a result, the wettability of the surface of the fins 5 is improved, and the water film formed on the surface of the fins 5 can be made thinner. Also, since the surface tension of the moisture decreases (in other words, the surface energy of the moisture decreases), it becomes easier to discharge the moisture from the surface of the fins 5. As a result, it is possible to prevent the heat exchange efficiency of the heat exchange system 2 from decreasing due to the moisture adhering to the fins 5, or the heat exchange efficiency from decreasing due to the air flow in the heat exchanger 3 being obstructed by the moisture adhering to the fins 5. Further, when a thin water film is formed on the fins 5, even when impurities in the air adhere to the fins 5, the impurities are quickly discharged together with the water film, and the fins 5 can be maintained in a clean state.

[0042] Moreover, these effects persist because the additive is supplied by the supply member 4 to the moisture adhering to the fins 5. Also, the additive can be supplied to the moisture adhering to the fins 5 by the supply member 4. Therefore, the labor of supplying the additive can be omitted. Accordingly, in the heat exchange system 2, even when moisture and dirt adhere to the fins 5 of the heat exchanger 3 during operation, excellent heat exchange efficiency can be obtained over a long period from the initial stage of driving of the heat exchange system 2.

[0043] Also, in this embodiment, the additive is supplied by free fall from the supply member 4 to the moisture adhering to the fins 5. Thereby, the additive can be automatically and efficiently added from the supply member 4 to the fins using gravity, and the structure of the heat exchange system 2 can be simplified.

[0044] Also, the supply member 4 is arranged so as to contact the fins 5. Thereby, it becomes easier to supply the additive from the supply member 4 to the moisture adhering to the fins 5.

[0045] Further, a plurality of fins 5 are arranged to extend in the vertical direction and line up in an intersecting direction intersecting the vertical direction, the supply member 4 is elongated in the intersecting direction, and is arranged to contact end faces of the plurality of fins 5. Thereby, with respect to moisture adhering to the plurality of fins 5, an additive can be easily diffused and supplied from the supply member 4 along the surface extending in the vertical direction of each fin 5.

[0046] Also, the supply member 4 is detachably arranged with respect to the heat exchanger 3. Thereby, the maintainability of the heat exchange system 2 can be improved, and the supply member 4 can be easily replaced as needed. Thus, stable heat exchange efficiency can be maintained over a long period.

[0047] Also, as an example, the supply member 4 includes a plurality of carriers 40 carrying an additive, and a support 41 that supports the plurality of carriers 40 in a dispersed state so that the additive can be released from the carriers 40 to the outside of the supply member 4.

[0048] According to the above configuration, by carrying the additive by the plurality of dispersed carriers 40, it is possible to easily supply the additive to a wide range with respect to the moisture adhering to the fins 5 from each carrier 40. Further, by the support 41 supporting the plurality of carriers 40 so that the additive can be released from the plurality of carriers 40 to the outside of the supply member 4, the additive can be stably supplied from the supply member 4 to the fins 5 while supporting the carriers 40.

[0049] Also, the carrier 40 is a porous granular material. Thereby, a rich additive can be held in the pores of the carrier 40, the additive can be slowly released from the supply member 4 to the fins 5, and the additive can be supplied to the moisture adhering to the fins 5 from the initial stage of driving of the heat exchange system 2 over a long period.

[0050] Also, the additive is a surfactant. Thereby, it is easy to favorably reduce the contact angle of the moisture adhering to the fins 5. Also, by using, for example, an existing surfactant as the additive, the design freedom of the heat exchange system 2 can be improved.

[0051] Also, as shown in FIG. 1, in this embodiment, the additive that has flowed through the surface of the fin 5 is received by the drain pans 8 and 9 provided in the indoor unit 10. Thereby, for example, it is possible to preferably prevent the additive from adhering to unnecessary portions of the application device 1.

[0052] In addition, when the application device 1 including the heat exchange system 2 is an air conditioner, the air conditioner may also serve as a heating device. When the air conditioner is driven as a heating device, the heat exchange system 2 may be mounted on the outdoor unit. Also, the air conditioner is not limited to a configuration including the indoor unit 10 and the outdoor unit. For example, it may be a spot air conditioner or a car air conditioner. Further, the application device 1 is not limited to an air conditioner, and may be, for example, a refrigeration device, a freezing device, a drying device, or the like. The use of the heat exchange system 2 may be any use that exchanges heat between the refrigerant flowing inside the heat exchanger 3 and air through the fins 5 of the heat exchanger 3 to cool the air. Hereinafter, the second embodiment will be described centering on the differences from the first embodiment.

[0053] (Second Embodiment) FIG. 4 is a schematic diagram of the application device 101 according to the second embodiment. FIG. 5 is a diagram schematically showing the state of the fins of the heat exchanger and its surroundings before and after defrosting in the conventional case. FIG. 6 is a diagram schematically showing the state of the fins 5 of the heat exchanger 3 and its surroundings before and after defrosting in the second embodiment. The application device 101 shown in FIG. 4 is a refrigeration device that refrigerates or freezes an object. The application device 101 includes a refrigerating chamber 102, a freezing chamber 103, a vegetable chamber 104, a heat exchanger 3, and a defrosting mechanism 105 for removing the frost adhering to the heat exchanger 3. As an example, the defrosting method of the defrosting mechanism 105 is a heater method. The defrosting method of the defrosting mechanism 105 is not limited to this, and may be any other known method such as a hot gas method, a water spray method, or an off-cycle method.

[0054] As shown in FIG. 5, in a conventional refrigeration apparatus, when the fins of a heat exchanger are cooled below the freezing point and pass through a supercooled state, and when the supercooled state is released, the moisture (condensed water) adhering to the fins freezes. As a result, frost adheres to the fins (FIG. 5(a)). When this frost adhesion to the fins is repeated, the frost accumulates. The accumulation of frost reduces the heat exchange efficiency. Therefore, by operating the defrosting mechanism in this state, the frost adhering to the fins melts and is removed. However, it is difficult to completely defrost by the normal defrosting operation of the defrosting mechanism, and some moisture (frost and water droplets) remains on the fins (FIG. 5(b)). When the refrigeration apparatus performs a re-cooling operation to re-cool the inside of the storage to the set temperature after the defrosting operation while moisture remains on the fins, the moisture is re-frozen and remains as ice on the surface of the fins. Since further frost adhesion occurs based on this residue, the frost accumulates cumulatively (FIG. 5(c)). As a result, the normal heat exchange of the heat exchanger is hindered, and the heat exchange rate of the refrigeration apparatus decreases.

[0055] On the other hand, as shown in FIG. 6, in the application device 101, when the defrosting operation of the defrosting mechanism 105 is performed, the frost melts and a plurality of water droplets are generated (FIG. 6(a)). The moisture of the water droplets is modified by an additive supplied by the supply member 4. A plurality of adjacent water droplets are combined by their hydrophilicity and slide down the surface of the fins 5 due to their own weight. As a result, the frost is removed from the fins 5 (FIG. 6(b)). As a result, most of the moisture is discharged from the fins 5. Thus, even when the defrosting operation and the re-cooling operation are repeated, the cumulative deposition of frost on the surface of the fins 5 is prevented (FIG. 6(c)). Therefore, an excellent heat exchange rate of the application device 101 can be obtained over a long period. For this reason, the power saving performance of the entire application device 1 can be improved. In addition, since the cumulative deposition of frost on the surface of the fins 5 is prevented, the amount of frost to be defrosted in one defrosting operation can be reduced. As a result, the defrosting time is shortened. In addition, since the amount of heat required for defrosting is suppressed, the rise in the temperature inside the storage during the defrosting operation is relatively suppressed. Therefore, the temperature rise of the object inside the refrigerated or frozen storage can also be suppressed. In addition, since the frequency of the defrosting operation can be reduced, the above-described effects can be further enhanced.

[0056] Next, a modified example of this embodiment will be described. The application device according to this modified example is an air conditioner including an outdoor unit. This application device is driven as a heating device. Examples of the application device driven as this heating device include, but are not limited to, a heat pump type water heater, a heat pump type warm water heating device, a warm water heating device by hot water supply, and a heat pump type heating device dedicated to an electric vehicle (EV). This application device includes, for example, a defrosting mechanism 105 that removes frost adhering to the heat exchanger 3. The heat exchange system 2 having the heat exchanger 3 is mounted on the outdoor unit. Even with the application device of this modified example having such a configuration, the same effects as those of the application device 101 can be obtained. Note that the frost adhering to the heat exchanger in the outdoor unit may be derived from snow.

[0057] (Confirmation test) [Test 1] An application device 1 including a commercially available dehumidifier (``AR-30HC'' manufactured by SUGGEST Co., Ltd.) in which the heat exchange system 2 and the capacitor are arranged in the same housing and the air that has passed through the heat exchanger 3 (evaporator) further passes through the capacitor and is discharged outside the housing, and a supply member 4 was prepared as Example 1.

[0058] In this Example 1, three strip-shaped supply members 4 whose lengths extend in the horizontal direction were arranged separately from each other so as to be in contact with the end faces of the respective fins 5 on the upper portions of the plurality of fins 5 arranged so as to extend in the vertical direction and line up in the intersecting direction intersecting the vertical direction. Also, in Example 1, a dumbbell-shaped supply member 4 in which the width dimensions of both ends are larger than the width dimension of the central portion in the longitudinal direction was used in plan view.

[0059] Also, as Comparative Example 1, a dehumidifier similar to Example 1 was prepared except that a dummy plate body was used instead of the supply member 4. Example 1 and Comparative Example 1 were driven under the conditions of a room temperature of 27°C and a relative humidity (RH) of 45%, and the performance difference between Example 1 and Comparative Example 1 before 100 minutes had elapsed after the start of driving was confirmed.

[0060] As a result, in Example 1, compared with Comparative Example 1, the temperature difference between the temperature T1 of the air near the air inlet for introducing air into the heat exchanger 3 and the temperature T2 of the air immediately after passing through the heat exchanger 3 was large, and it was confirmed that the air was appropriately heat-exchanged with the refrigerant by the heat exchanger 3.

[0061] [Test 2] An application device 1 including a commercially available spot air conditioner (manufactured by Haier Corporation, "JA-SPH25J") in which the heat exchange system 2 and the capacitor are arranged in the same housing and the air passing through the heat exchanger (evaporator) 3 and the air passing through the capacitor are individually discharged, and a supply member 4 was prepared as Example 2. In Example 2, four cylindrical supply members 4 with their longitudinal directions extending in the horizontal direction were arranged at intervals from each other at the air inlet arranged on the side of the device for introducing air into the heat exchanger 3. Further, as Comparative Example 2, a spot air conditioner similar to Example 2 except that the supply member 4 was not used was prepared. Example 2 and Comparative Example 2 were driven to confirm the performance difference between Example 2 and Comparative Example 2.

[0062] As a result, in Example 2, under the condition that the suction air velocity was set to 1 m / S, it was confirmed that the power consumption was reduced as the humidity increased in the range where the air temperature was 10°C or higher and 35°C or lower. Also, in Example 2, in the range where the suction air velocity was 4 m / s or less, it was confirmed that the power consumption was reduced as the suction air velocity became lower. Also, in Example 2, in the following range where the environmental absolute humidity was 30.0 g / m 3 It was confirmed that the dehumidification amount increased as the environmental absolute humidity increased compared with Comparative Example 2. Also, in an environment with an air temperature of 27 degrees and a humidity of 70%, it was confirmed that in Example 2, the relative humidity value at the air outlet was lower and the temperature of the air discharged from the air outlet was also lower than in Comparative Example 2. Thus, it was found that Example 2 had stable dehumidification performance and cooling function within this test range.

[0063] [Test 3] For the drain pan of the air conditioner, a mixture of the additive supplied from the supply member 4 and water was prepared as Example 3, and water was prepared as Comparative Example 3. As Example 3, Example 3A containing the additive at a concentration of 100 ppm and Example 3B containing the additive at a concentration of 1000 ppm were prepared. Example 3A, 3B and Comparative Example 3 were spread on the surface of the drain pan of the air conditioner, and the remaining water amount on the drain pan surface after a certain period of time was confirmed.

[0064] As a result, it was confirmed that in both Example 3A and 3B, the remaining water amount was suppressed to about half or less compared to Comparative Example 3. Also, it was confirmed that Example 3B had less remaining water amount than Example 3A. From this, it was found that when using the supply member 4, a thin water film can be formed by bringing the additive into contact with moisture, and the moisture can be removed early from the adhering surface. Therefore, when the supply member 4 is applied to the heat exchanger 3, it is considered that moisture remaining on the fins 5 can be prevented, and the generation of mold etc. on the surface of the fins 5 can be suppressed.

[0065] [Test 4] Next, a heat exchange system 2 provided in the indoor unit of a large air conditioner was prepared. A substantially rectangular parallelepiped-shaped section (including a plurality of fins 5 and the flow pipe 6) with a predetermined size (length 17.5 cm, width 9.5 cm, thickness 9 mm) was cut out from the heat exchanger 3 having a plurality of fins 5 of this heat exchange system 2. The initial weight of this section was measured with a scale in a state where the section was hung. Then, using a dropper, a mixed solution of a predetermined concentration of the additive mixed with water was supplied to the section. As the additive, "Emulgen LS-106" manufactured by Kao Corporation, a nonionic surfactant containing polyoxyalkylene alkyl ether, was used.

[0066] When the mixed solution began to drip from the slice and was left for an additional 3 minutes after the amount of the mixed solution supplied to the slice became saturated, the weight of the slice was measured, and the water retention amount of the slice was measured based on the difference between the measured weight and the initial weight. The test results are shown in Table 1. Table 1 shows the measured values of the water retention amount of the slices measured twice for the mixed solution at each additive concentration, the average value of the water retention amount which is the average value of the two measured values, and the water retention ratio B / A of the average value B of the water retention amount at each concentration of the additive to the average value A of the water retention amount when the additive concentration is 0.

[0067]

Table 1

[0068] As shown in Table 1, in this test range, it was confirmed that even when the additive concentration of the water (the above mixed solution) supplied with the additive is several tens of ppm, the water retention amount of Fin 5 can be reduced to almost 60% or less.

[0069] [Test 5] An application device driven as a heating device according to a modification of the second embodiment was prepared as Example 4. The outdoor unit of this application device has a plurality of heat exchangers 3 arranged in the vertical and horizontal directions. In this test, among the plurality of heat exchangers 3 arranged horizontally, a plurality of long supply members 4 were arranged with their longitudinal directions horizontal so as to surround a part of the side surface of the heat exchanger 3 located outside the outdoor unit. Also, a comparative example 4 was prepared with an application device similar to that of Example 4 except that the supply member 4 was not provided.

[0070] Regarding each of the application devices of Example 4 and Comparative Example 4, the relationship with the operating cycle time, which is a combination of the low-temperature heating capacity (kW) conforming to JIS C 9612:2013, the time required for the temperature to rise to the indoor target temperature (20°C) (heating time), and the time required for defrosting (defrosting time), was examined. At the time of the test, the outdoor dry-bulb temperature was 2°C, the outdoor wet-bulb temperature was 1°C, the indoor dry-bulb temperature was 20°C, and the indoor wet-bulb temperature was 14.5°C. Each of the application devices of Example 4 and Comparative Example 4 was set so that the defrosting mechanism would operate when the piping temperature of the heat exchanger became equal to or lower than the reference temperature.

[0071] Figure 7 is a graph showing the relationship between the operation cycle time and the heating capacity of the application device in the test results of Test 5. As shown in Figure 7, in Example 4, a slight (about 1%) improvement in heating capacity was observed compared to Comparative Example 4. Also, in Example 4, compared to Comparative Example 4, the time until frost adheres to the fins 5 of the heat exchanger 3 after the start of the heating operation is shorter, and as a result, the ability degradation gradient after the peak of the heating capacity is large. However, in Example 4, the defrosting time was shortened compared to Comparative Example 4. As a result, it was confirmed that the operation rate in the overall operation cycle time is higher in Example 4 than in Comparative Example 4. Specifically, in this test, it was confirmed that the operation efficiency of Example 4 is improved by about 3% or more compared to Comparative Example 4. Also, in Example 4, compared to Comparative Example 4, it was confirmed that the stop time of the heating operation during defrosting is reduced by 25%. Thus, it was found that in Example 4, the time during which heating stops and it feels cold during the defrosting operation can be reduced.

[0072] [Test 6] The application device 101, which is a refrigeration device according to the second embodiment, was prepared as Example 5. In Example 5, a plurality of columnar supply members 4 whose longitudinal direction extends in the horizontal direction were arranged. Also, an application device similar to Example 5 except that it does not include the supply member was prepared as Comparative Example 6. Further, a Comparative Example 7 similar to Comparative Example 6 except that a hydrophilic film was arranged on the fins of the heat exchanger was prepared. As the original configuration of each of the application devices of Example 5 and Comparative Examples 6 and 7, a Panasonic Corporation refrigerator "NR-F606WPX" was used. Then, each of the application devices of Example 5 and Comparative Examples 6 and 7 was placed in a test room with an air-conditioning temperature set to 25 and no humidity control (about 20 RH%).

[0073] A plurality of test articles were prepared, each containing one paper-made wipe (Kim Towel manufactured by Nippon Paper Crecia Co., Ltd.) and 200 mL of pure water in a metal tray. Using these test articles, a moisture load was applied to each of the application devices of Example 5 and Comparative Examples 6 and 7 so that frost adhered to the heat exchanger with the pure water in the metal tray. Also, a defrost operation was started every 13 hours, and each application device was set to end the defrost operation when the ambient temperature at a predetermined position of the heat exchanger reached 10°C during the defrost operation.

[0074] In addition, different load levels ("low level", "medium level 1", "high level", and "medium level 2") of load were applied to each of the application devices in the same order for each fixed period to drive them. The setting details of each load level are shown in Table 2 below. At "low level", a total of 3 sets of test articles were used, 2 sets of test articles were placed in the refrigerator compartment, and 1 set of test articles was placed in the vegetable compartment. At "medium level 1", "high level", and "medium level 2", a total of 5 sets of test articles were used, and 4 sets of test articles were placed in the refrigerator compartment, and 1 sets of test articles were placed in the vegetable compartment. As shown in Table 2, "medium level 2" has a greater load than "low level" in that the number of test articles is more than that of "low level", and has a smaller load than "medium level 1" in that there is no load for opening and closing the door.

[0075]

Table 2

[0076] Figure 8 is a graph showing the relationship between the number of defrosts and the defrost time in the test results of Test 6. Figure 9 is a graph showing the relationship between the number of defrosts and the cooling time in the test results of Test 6. "Medium No. 1" in the figure indicates "Medium Degree No. 1", and "Medium No. 2" indicates "Medium Degree No. 2". As shown in Figure 8, it was confirmed that in Example 5, the defrost time was shortened at all load levels compared to Comparative Examples 6 and 7. Also, it was confirmed that the defrost time became longer in the order of Example 5, Comparative Example 7, and Comparative Example 6. As shown in Figure 9, it was found that in Example 5, regardless of whether the load level was "low degree", "medium degree No. 1", or "medium degree No. 2", the re-cooling time after defrosting could be maintained almost at the initial value. As shown in Figures 8 and 9, in Comparative Examples 6 and 7, as the number of defrosts increased (with the passage of the operating time of the application device), the amount of frost deposited and remaining on the heat exchanger increased. As a result, both the defrost time and the re-cooling time after defrosting increased compared to Example 5.

[0077] According to another test, when the load level was "low degree", it was confirmed that Example 5 could reduce the power consumption during defrosting by 38.1% compared to Comparative Example 6. Also in this case, it was confirmed that Example 5 could reduce the total power consumption of the entire operation (the total power consumption during startup, stable operation, immediately before defrost operation, during defrost operation, and during the re-cooling period after defrost) by 12% compared to Comparative Example 6.

[0078] Here, Figure 10 is a photograph showing the state of the heat exchanger 3 of Example 5 before defrosting. Figure 11 is a photograph showing the state of the heat exchanger 3 of Example 5 after defrosting. Figure 12 is a photograph showing the state of the heat exchanger of Comparative Example 6 before defrosting. Figure 13 is a photograph showing the state of the heat exchanger of Comparative Example 6 after defrosting. Figure 14 is a photograph showing the state of the heat exchanger of Comparative Example 7 before defrosting. Figure 15 is a photograph showing the state of the heat exchanger of Comparative Example 7 after defrosting. Figures 11, 13, and 15 show the state of the heat exchanger immediately before the 17th defrost operation after the start of operation of the application device.

[0079] As shown in FIGS. 10 and 11, in Example 5, it was confirmed that almost all of the frost adhering to the heat exchanger 3 was defrosted by the defrosting operation, regardless of whether the load level was "low level", "medium level 1", or "medium level 2". Also, in Example 5, regardless of the load level, no frost bridge formed to connect adjacent fins 5 was confirmed. On the other hand, as shown in FIGS. 12 and 13, in Comparative Example 6, a considerable amount of water droplet-like frost remained on the fins even after the defrosting operation, and it was found that the frost accumulated. Also, in Comparative Example 6, it was confirmed that the bridge was formed below the heat exchanger. Further, as shown in FIGS. 14 and 15, in Comparative Example 7, although a certain amount of frost was defrosted by the defrosting operation, it was confirmed that lumps of water droplet-like frost locally remained on the ends and end faces of the fins of the heat exchanger where the hydrophilic film was not arranged, and on the surface of the flow pipe.

[0080] Thus, as a reason for the high defrosting effect of Example 5, it is considered that the moisture adhering to the fin 5 is modified by the additive supplied by the supply member 4. That is, in Example 5, the moisture adhering to the fin 5 is modified by contacting the additive, and the moisture slides off the fin 5 to promote drainage (liquid drainage). In contrast, in Comparative Example 7, although the action of the hydrophilic film arranged on the surface of the fin makes it somewhat easier to remove moisture, the moisture itself is not modified. Therefore, it is considered that moisture hardly slides off the fin in the part without the hydrophilic film on the fin. Also, in Comparative Example 6, since the moisture is not modified by the additive and no hydrophilic film is arranged on the surface of the fin, it is considered that the moisture was relatively likely to adhere to the surface of the fin before and after defrosting.

[0081] FIG. 16 is a graph showing the relationship between the operating time and the freezer temperature in the test results of Test 6. FIG. 16 shows the comparison results between Example 5 and Comparative Example 6 when the load level is "high". As shown in FIG. 16, even when the load level is "high", in Example 5, the temperature inside the cabinet is more stable compared to Comparative Example 6, and it was confirmed that the maximum temperature rise of the freezer during the defrost operation was only 4.4°C. On the other hand, under the same conditions, it was confirmed that the temperature rise of Comparative Example 6 reached a maximum of 11.1°C.

[0082] FIG. 17 is a graph showing the relationship between the number of defrosts and the freezer temperature in the test results of Test 6. As shown in FIG. 17, even when the load level is changed among "low", "medium level 1", "high", and "medium level 2", it was confirmed that Example 5 can suppress the temperature change inside the freezer during the defrost operation compared to Comparative Examples 6 and 7. According to Example 5, it is considered that the temperature inside the refrigerator can be kept stable, and the refrigeration quality and freezing quality can be improved.

[0083] The present disclosure is not limited to the above-described embodiments, and the configuration and method can be changed, added, or deleted without departing from the spirit of the present disclosure. The additive supplied by the supply member 4 may contain a plurality of components. When the additive contains a plurality of components, the additive may include, for example, a first component having a function of reducing the contact angle of moisture with respect to the fin 5, and a second component that activates the function of the first component so as to reduce the contact angle.

[0084] Also, the supply member 4 may be arranged so as to be able to supply the additive to the moisture adhering to the fin 5. For this reason, for example, the supply member 4 and the fin 5 may be arranged separately. In this case, the additive of the supply member 4 may be dropped onto the moisture adhering to the fin 5, or the additive may be supplied through a member separate from the supply member 4.

Explanation of Reference Numerals

[0085] 1, 101 Application Equipment 2 Heat Exchange System 3 Heat Exchanger 4 Supply member 5 Fin 10 Indoor unit 40 Carrier 41 Support 105 Defrosting mechanism

Claims

1. A heat exchanger having a plurality of fins that come into contact with moisture-containing air, and cooling the air by exchanging heat between the refrigerant flowing inside and the air through the fins; A supply member that supplies an additive that reduces the contact angle with respect to the fins to the moisture adhering to the fins by the cooling; and The supply member contains a plurality of carriers that carry the additive, and a support that supports the plurality of carriers in a dispersed state so that the additive can be released from the carriers to the outside of the supply member. A heat exchange system.

2. The heat exchange system according to claim 1, wherein the additive is supplied to the moisture adhering to the fins by free fall from the supply member.

3. The heat exchange system according to claim 1 or 2, wherein the supply member is arranged so as to be in contact with the fins.

4. The plurality of fins extend in the vertical direction and are arranged side by side in an intersecting direction intersecting the vertical direction, The heat exchange system according to claim 3, wherein the supply member is long in the intersecting direction and is arranged so as to be in contact with the end faces of the plurality of fins.

5. The heat exchange system according to any one of claims 1 to 4, wherein the supply member is detachably arranged with respect to the heat exchanger.

6. The material of the carrier is at least any one of porous glass, activated carbon, zeolite, and porous concrete. The heat exchange system according to any one of claims 1 to 5.

7. The heat exchange system according to any one of claims 1 to 6, wherein the carrier is a porous granular material.

8. The heat exchange system according to any one of claims 1 to 7, wherein the additive is a surfactant.

9. The heat exchange system according to any one of claims 1 to 8, wherein the additive dissolves, disperses, or diffuses in the moisture adhering to the fins.

10. An application device including the heat exchange system according to any one of claims 1 to 9.

11. An air conditioner including an indoor unit, The application device according to claim 10, wherein the heat exchange system is mounted on the indoor unit.

12. An air conditioner including an outdoor unit, An air conditioner including an outdoor unit, comprising a defrosting mechanism for removing frost adhering to the heat exchanger, The application device according to claim 10 or 11, wherein the heat exchange system is mounted on the outdoor unit.

13. The applied device according to claim 10, which is a refrigeration device that refrigerates or freezes an object and is provided with a defrosting mechanism for removing frost adhering to the heat exchanger.

Images