JP2007285673A - Drain structure for corrugated type heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve inducibility to a drain guide of condensate by improving adhesiveness of the drain guide and fins, to reduce a contact area of the induced condensate and the drain guide, and to reduce the number of contact fins by suppressing increase of draft resistance due to installation of the drain guide, in drain structure for a corrugated fin type heat exchanger. <P>SOLUTION: The corrugated fin type heat exchanger 1 comprises a flat tube 4 and the corrugated fins 5, and the drain guide 11 getting in touch with the corrugated fins 5 is provided in a concentrating side of the condensate. In a drain guide structure, the drain guide 11 is composed of linear members, the drain guide 11 is arranged obliquely to the flat tube 4, and at least one of both ends of the drain guide 11 is led to a lower end side or a side end side of the corrugated fin type heat exchanger 1. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a corrugated fin heat exchanger, and more particularly to a drainage construction technique for a corrugated fin heat exchanger in which slits or louvers are formed.

Conventionally, corrugated fin type heat exchangers are used as one of heat exchangers for air conditioners. The corrugated fin heat exchanger is a heat exchanger having a configuration in which a plurality of flat tubes are arranged in parallel and wave-shaped fins are brazed and joined between the tubes.
By the way, when an air-cooled heat exchanger is used on the evaporator side in the air conditioner, the refrigerant evaporation temperature in the evaporator is lower than the ambient air temperature. Therefore, moisture in the air is condensed on the surface of the heat exchanger. If this dew is left untreated, water accumulates between the fins and becomes the resistance of the air passing through the heat exchanger, so that the air volume decreases and sufficient heat exchange cannot be performed.
In the case of the corrugated fin type heat exchanger, the condensate generated by the dew condensation is not discharged but forms a water film as compared with the plate fin type heat exchanger, so that the ventilation resistance increases. In particular, those having corrugated fins with slits or louvers have a high water retention and a significant increase in ventilation resistance.
As a countermeasure against drainage of the heat exchanger, for example, Patent Document 1 discloses a configuration in which a drainage guide plate that contacts the corrugated fin is provided on the downstream side of the corrugated fin heat exchanger.
Japanese Patent Laid-Open No. 2001-263861

However, the plate-shaped drainage guide described in Patent Document 1 is difficult to attract condensed water to the drainage guide because the drainage guide has high rigidity and poor adhesion to the fins. Since the contact area is large, it is difficult for the condensed water to flow down.
Furthermore, if the drainage guide is provided vertically, the number of contact fins is small, so the drainage performance is poor, and the configuration in which the distance between the drainage guides is reduced to increase the number of contact fins increases the ventilation resistance.

  Therefore, the problem to be solved was to improve the attractiveness of the corrugated fin type heat exchanger to the drainage guide by improving the adhesion between the drainage guide and the fins, and was attracted. It is to reduce the contact area between the condensed water and the drainage guide, and to increase the number of contact fins by suppressing an increase in ventilation resistance due to the installation of the drainage guide.

  The problem to be solved by the present invention is as described above. Next, means for solving the problem will be described.

  That is, in claim 1, in the corrugated fin type heat exchanger, which is a heat exchanger composed of a flat tube and a corrugated fin, and provided with a drainage guide in contact with the corrugated fin on the condensate collecting side, the drainage guide is The drainage guide is inclined with respect to the flat tube, and at least one of both ends of the drainage guide is led to the lower end side or the side end side of the heat exchanger.

  According to a second aspect of the present invention, in the corrugated fin heat exchanger according to the first aspect, the wire diameter of the drainage guide is 50 to 300% of the fin pitch of the corrugated fin.

  In Claim 3, in the corrugated fin type heat exchanger according to claim 1, the flat tubes are arranged in a horizontal direction, and the heat exchanger is arranged vertically or inclined at the upper end side of the heat exchanger and downstream of the ventilation. The drainage guide is provided on the downstream side of the ventilation.

  The corrugated fin heat exchanger according to claim 1, wherein the flat tubes are arranged in a horizontal direction, and the upper end side of the heat exchanger is inclined to the upstream side of the air flow so that the drainage guide is ventilated. It is provided on the upstream side.

  According to a fifth aspect of the present invention, in the corrugated fin heat exchanger according to the first aspect, the adjacent drainage guides are alternately folded at the upper end side or the lower end side of the heat exchanger.

  According to a sixth aspect of the present invention, in the corrugated fin heat exchanger according to the first aspect, the adjacent drainage guides are alternately folded at the left end side or the right end side of the heat exchanger.

  The corrugated fin heat exchanger according to claim 1, wherein one end of the drainage guide is led to a lower end side of the heat exchanger and one end of the drainage guide is diagonally aligned with the heat exchanger. And an area led to the drainage guide.

  According to an eighth aspect of the present invention, in the corrugated fin heat exchanger according to the first aspect, the drainage guide is configured in a lattice shape.

  According to a ninth aspect of the present invention, in the corrugated fin heat exchanger according to the first aspect, one end of the drainage guide is collected on the lower end side of the heat exchanger.

  According to a tenth aspect of the present invention, in the corrugated fin heat exchanger according to the first aspect, the drainage guide is configured in a region limited to a portion where condensate condensate easily occurs.

  According to an eleventh aspect of the present invention, in the corrugated fin heat exchanger according to the first aspect, the drainage guide is made of resin.

  According to a twelfth aspect of the present invention, in the corrugated fin heat exchanger according to the first aspect, the drainage guide is made of metal.

  According to a thirteenth aspect of the present invention, in the corrugated fin heat exchanger according to the first aspect, the drainage guide is made of a fiber.

  In Claim 14, in the corrugated fin heat exchanger according to Claim 1, the drainage guide is movable.

  In claim 15, in the air conditioner equipped with the corrugated fin heat exchanger according to claim 1, the fan air volume is detected after a predetermined time has elapsed after the start of operation or when a decrease in the air volume of the fan for the heat exchanger is detected. Is instantaneously increased or water is injected to the condensed water condensing side of the heat exchanger.

  As effects of the present invention, the following effects can be obtained.

  In claim 1, since the drainage guide is a linear member, the flexibility of the drainage guide is increased and the adhesion to the fins is improved, so that the condensed water is easily attracted to the drainage guide, and the attracted condensed water is attracted. Since the contact area with the drainage guide is small, the condensed water tends to flow down. In addition, the number of contact cells (surfaces surrounded by fins and refrigerant pipes) can be increased by suppressing the increase in ventilation resistance due to the inclined arrangement with respect to the flat tube. Furthermore, since one end of the drainage guide is guided to the lower end side or the side end side of the heat exchanger, the condensed water that flows down can be easily drained from the heat exchanger.

  In the second aspect, in addition to the effect of the first aspect, the condensed water is more easily attracted to the drainage guide.

  In the third aspect, in addition to the effect of the first aspect, the drainage can be improved when the condensed water is concentrated on the downstream side of the ventilation.

  In the fourth aspect, in addition to the effect of the first aspect, drainage can be improved when condensed water is concentrated on the upstream side of the ventilation.

  In the fifth aspect, in addition to the effect of the first aspect, the condensed water can be easily guided to the lower end side, and drainage from the heat exchanger is facilitated.

  In the sixth aspect, in addition to the effect of the first aspect, the condensed water can be concentrated on the side end side, so that drainage from the heat exchanger becomes easy.

  In the seventh aspect, in addition to the effect of the first aspect, the condensed water can be guided to the lower end side.

  In the eighth aspect, in addition to the effect of the first aspect, the drainage guide can be easily manufactured by using a mesh net or the like.

  In the ninth aspect, in addition to the effect of the first aspect, drainage from the heat exchanger becomes easy.

  In the tenth aspect, in addition to the effect of the first aspect, efficient drainage is possible while suppressing an increase in ventilation resistance.

  In the eleventh aspect, in addition to the effect of the first aspect, the drainage guide can be easily manufactured by using the resin net.

  In the twelfth aspect, in addition to the effect of the first aspect, the heat exchanger can be easily attached by brazing or the like.

  According to the thirteenth aspect, in addition to the effect of the first aspect, since it can be wound around the heat exchanger, it can be easily installed on the field even after shipment in the market.

  In the fourteenth aspect, in addition to the effect of the first aspect, since the installation area of the drainage guide can be suppressed, an increase in ventilation resistance can be suppressed.

  In claim 15, in addition to the effect of claim 1, when the condensate is not sufficiently attracted to the drainage guide, the condensate is attracted to the drainage guide by performing forced drainage, and the function of the drainage guide is restored. Can be made.

Next, embodiments of the invention will be described.
FIG. 1 is a refrigerant circuit diagram showing the overall configuration of an engine-driven heat pump according to an embodiment of the present invention. FIG. 2A is a front view showing a corrugated fin heat exchanger. FIG. FIG. 3 and FIG. 3 are (a) a front view showing a drainage guide configuration of a corrugated fin heat exchanger showing an embodiment of the present invention, and (b) an enlarged front view.
4A is a side view of a corrugated fin heat exchanger showing an example of the arrangement of drainage guides. FIG. 4B is a side view of a corrugated fin type heat exchanger showing another example of arrangement of the drainage guides. FIG. Side view of corrugated fin type heat exchanger showing example (d) Side view of corrugated fin type heat exchanger showing another arrangement example of drainage guide, FIG. 5 is a front view showing a drainage guide configuration with an inclination of 45 degrees or more FIG. 6 is a front view showing a drain guide structure with an inclination of less than 45 degrees.
7 is a front view showing a drainage guide configuration folded at the upper end or lower end, FIG. 8 is a front view showing a drainage guide configuration folded at the right end or the left end, and FIG. 9 is a region divided by drainage guides arranged diagonally. It is a front view which shows the drainage guide structure which is a different inclination.
FIG. 10 is a front view showing a drainage guide configuration having a lattice shape, FIG. 11 is a front view showing another drainage guide configuration having a grid shape, and FIG. 12 is a front view showing another drainage guide configuration having a grid shape.
FIG. 13 is a front view showing another drainage guide configuration in which one lower end is concentrated, FIG. 14 is a front view showing another drainage guide configuration with symmetrical left and right inclinations, and FIG. 15 is a front view showing a wavy separate drainage guide configuration.
16 is a front view showing a partially drained drain guide configuration, FIG. 17 is a front view showing a movable drain guide configuration, and FIG. 18 is an overall configuration of an engine-driven heat pump according to another embodiment of the present invention. It is a refrigerant circuit figure shown.
FIG. 19 is a flowchart showing drainage attraction control of an engine-driven heat pump according to another embodiment of the present invention, and FIG. 20 is a flowchart showing the overall configuration of the engine-driven heat pump according to another embodiment of the present invention. 21 is a flowchart showing another drainage attraction control of an engine-driven heat pump according to another embodiment of the present invention.

The drainage guide 11 according to the present invention is provided on a surface perpendicular to the ventilation in the outdoor heat exchanger 211, and the condensed water condensed during the heating operation in which the outdoor heat exchanger 211 is used as an evaporator is supplied to a drain pan or the like. It is a member to attract. First, as an embodiment to which the drainage guide configuration 10 is applied, an engine-driven heat pump 200 in which the corrugated fin heat exchanger 1 is applied to the outdoor heat exchanger 211 will be described.
Further, the drainage guides 21 to 141 of different materials, the drainage guide mounting position examples 160 to 180 having different mounting positions by the installation of the corrugated fin heat exchanger 1, and the engine drive type that can forcibly return the function to the drainage guide 11. The heat pump 300 will be described.

First, the configuration of an engine-driven heat pump 200 according to an embodiment of the present invention will be briefly described with reference to FIG.
As shown in FIG. 1, an engine-driven heat pump 200 is connected to a compressor 203 that obtains power from an engine 201 as a drive source via an electromagnetic clutch 202 and compresses a refrigerant, and to a discharge side of the compressor 203. A four-way valve 221 that switches the flow of refrigerant during cooling and heating, an outdoor heat exchanger 211 that is supplied with refrigerant discharged from the compressor 203 via the four-way valve 221 during cooling, and outdoor air to the outdoor heat exchanger 211 The outdoor fan 215 that guides the heat exchange and promotes heat exchange, the indoor heat exchanger 212 to which the refrigerant discharged from the compressor 203 is supplied via the four-way valve 221 during heating, and the indoor air to the indoor heat exchanger 212 An indoor fan 216 that promotes heat exchange, and an outdoor heat exchanger 211 and an outdoor heat exchanger expansion valve 222 disposed between the indoor heat exchanger 212. It is to use a refrigerant cycle is made.

  The compressor 203 sucks and compresses the gas refrigerant from the suction side, and discharges the high-temperature and high-pressure gas refrigerant. The four-way valve 221 is connected to the discharge side of the compressor 203 via a discharge path 226, and refrigeration oil contained in the gas refrigerant is separated into the discharge path 226 to the suction side of the compressor 203. An oil separator 217 for returning is provided. That is, the gas refrigerant discharged from the compressor 203 flows into the four-way valve 221 through the oil separator 217 and is guided in a predetermined direction by the four-way valve 221. In addition, since the gas refrigerant sucked into the compressor 203 is also guided by the four-way valve 221, the refrigerant suction side of the compressor 203 and the four-way valve 221 are connected by a suction path 227.

The four-way valve 221 is connected to one end side of the outdoor heat exchanger 211, and a receiver 218 is connected to the other end side of the outdoor heat exchanger 211. On the other hand, one end of the indoor heat exchanger 212 is connected to the receiver 218 via a liquid side communication pipe, and the other end is connected to the four-way valve 221 via a gas side communication pipe.
The waste heat recovery unit 213 is provided in a path that branches from between the outdoor heat exchanger expansion valve 222 and the receiver 218 and is connected to the suction path 227. The waste heat recovery device expansion valve 224, the supercooling heat exchanger 214, and the waste heat recovery device 213 are connected in series to the passage toward the suction passage 227. As for the refrigerant passing through the path, the liquid refrigerant in the receiver 218 is supercooled by the supercooling heat exchanger 214 by latent heat of vaporization, and the waste heat of the engine 201 is recovered from the engine cooling water by the waste heat recovery unit 213. Evaporate.

Next, the corrugated fin heat exchanger 1 applied to the outdoor heat exchanger 211 of the engine-driven heat pump 200 will be described with reference to FIGS. 2 (a) and 2 (b). In this embodiment, the corrugated fin heat exchanger 1 is applied to the outdoor heat exchanger 211 of the engine-driven heat pump 200. However, the present invention is not limited to this embodiment and is applied to other air conditioners. The same effect can be obtained.
As shown in FIG. 2A, the corrugated fin heat exchanger 1 includes a flat tube 4, a plurality of flat tubes 4 arranged in parallel, and headers 2 and 3 that fix both ends thereof, and the flat tube 4. It is comprised from the corrugated fin 5 of the wave shape arrange | positioned in. With such a configuration, the refrigerant flows in from one header 2, passes through the parallel flat tubes 4, and flows out from the other header 3.
The above is the basic structure of the corrugated fin heat exchanger 100, but the path (hereinafter referred to as a path) through which the refrigerant flows can be freely designed, and the refrigerant resistance can be reduced as the number of paths increases. Further, the corrugated fin 5 may be provided with a cut-and-raised row (also called a slit or a louver) in a direction intersecting with the air flow (direction of passing air). This louver increases the flow rate of the staying air in the heat exchanger and increases the efficiency of heat exchange with the airflow. In addition, about the following Example, the corrugated fin type heat exchanger 1 is not particularly limited with respect to the number of passes and the presence or absence of louvers, and the same is true regardless of the configuration or shape of the number of passes or louvers. An effect is obtained.

Here, the drainage guide structure 10 of the corrugated fin-type heat exchanger 1 will be described with reference to FIGS.
As shown in FIG. 3 (a), the drainage guide structure 10 is provided on the upstream side or downstream side of the air passing through the corrugated fin heat exchanger 1, that is, on the front surface (primary side surface) or the rear surface (secondary side surface). A plurality of drain guides 11 are attached in parallel at predetermined intervals so as to be in contact with the outer surface surrounded by 5 and the flat tube 4 and the cell 7. The mounting angle of the drainage guide 11 is set so that the inclination A with respect to the flat tube 4 (horizontal direction or vertical direction) is 45 degrees. Moreover, the drainage guide 11 of the present invention has a linear shape. Furthermore, the wire diameter D of the drainage guide 11 is 50 to 300% of the fin pitch P of the corrugated fins 5. In this embodiment, the diameter is substantially the same (100%) as the fin pitch P of the corrugated fin heat exchanger 1. Here, the fin pitch P is a folding interval in the corrugated fin 5 formed in a wave shape.

By configuring the drainage guide 11 in a linear shape in this way, the flexibility of the drainage guide 11 can be increased, and the drainage guide 11 can be easily adhered even if the corrugated fins 5 are deformed.
Further, since the contact area between the condensed water attracted to the drainage guide 11 and the drainage guide 11 is also reduced, the weight of the condensed water becomes larger than the contact force to the drainage guide 11 of the condensed water due to the surface tension. Water easily flows down from the drain guide 11.
Furthermore, by disposing the drainage guide 11 at an inclination, one drainage guide 11 can be brought into contact with many cells 7 and the number of drainage guides 11 can be reduced, thereby suppressing an increase in ventilation resistance. it can.
Furthermore, since one end of the drainage guide is guided to the lower end side or the side end side of the heat exchanger, the condensed water can be easily drained from the corrugated fin heat exchanger 1.

When the drain guide 11 is made of resin, it can be easily formed by integral molding (for example, a resin net).
On the other hand, if the drainage guide 11 is made of metal, it can be attached to the corrugated fin heat exchanger 11 by brazing.
Furthermore, if the drainage guide 11 is made of fiber, it can be wound, so that it can be installed on site even after installation.

Moreover, the example 150 of the attachment position to the corrugated fin type heat exchanger 1 of the drainage guide 11 in a present Example is demonstrated using Fig.4 (a).
FIG. 4A illustrates the attachment position of the drainage guide 11 when the headers 2 and 3 are arranged vertically and dew condensation occurs on the leeward side. That is, it is attached to the surface of the leeward side (heat exchanger secondary side) 16 when the side on which the outdoor fan 215 is arranged is the windward side (heat exchanger primary side) 15.

Examples of different attachment positions 160 to 180 of the drainage guide 11 to the corrugated fin heat exchanger 1 will be described with reference to FIGS.
FIG. 4B illustrates the attachment position of the drainage guide 11 when the upper end side of the corrugated fin heat exchanger 1 is inclined toward the leeward side and condensation occurs on the leeward side. That is, it attaches to the heat exchanger secondary side 16 of the corrugated fin heat exchanger 1 as in the case of (a).
FIG. 4C illustrates the attachment position of the drainage guide 11 when the upper end side of the corrugated fin heat exchanger 1 is inclined to the windward side and dew condensation occurs on the windward side. That is, the drainage guide 11 is attached to the heat exchanger primary side 15 of the corrugated fin heat exchanger 1.
As shown in FIG.4 (d), when the corrugated fin type heat exchanger 1 is arrange | positioned in multiple rows, the drainage guide 11 is attached between the corrugated fin type heat exchangers 1 * 1.

  In general, in the corrugated fin heat exchanger 1, the dew tendency of the heat exchanger primary side 15 or the heat exchanger secondary side 16 depends on the evaporation temperature of the refrigerant, that is, the drift of the path of the corrugated fin heat exchanger 1 Or it depends on the route. Therefore, the mounting position of the drainage guide 11 depends on the installation conditions of the corrugated fin-type heat exchanger 1 (inclination angle, or a plurality of units are stacked and the like), the heat exchanger primary side 15 and the heat exchanger secondary side 16. It is desirable to select in consideration of the condensation tendency.

  Next, the example of arrangement | positioning to the corrugated fin type heat exchanger 1 of the drainage guide 11 mentioned above is demonstrated as another Example using FIGS. In addition, the wire diameters of the following drainage guides 21 to 141 are substantially the same as the fin pitch P as in the embodiment. Furthermore, the following drainage guides 21 to 141 are made of metal, resin, or fiber, and the same effect can be obtained regardless of the material.

As shown in FIG. 5, the drainage guide structure 20 is configured such that the inclination A of the drainage guide 21 with respect to the flat tube 4 in the corrugated fin heat exchanger 1 is greater than 45 degrees.
As shown in FIG. 6, the drainage guide configuration 30 is configured such that the inclination A of the drainage guide 31 with respect to the flat tube 4 in the corrugated fin heat exchanger 1 is less than 45 degrees.
The drainage guide structures 20 and 30 are another example in which only the inclination angle is changed, but the same effect as the embodiment of FIG. 3 can be obtained.
As shown in FIG. 7, the drainage guide configuration 40 is configured such that a drainage guide 41 arranged to be inclined with respect to the flat tube 4 is folded back at the upper end or the lower end of the corrugated fin heat exchanger 1. That is, it is set as the structure which couple | bonds the adjacent drainage guides 41 with an upper end or a lower end, and arrange | positions it in the left-right direction in zigzag form.
As shown in FIG. 8, the drainage guide structure 50 is configured such that a drainage guide 51 arranged to be inclined with respect to the flat tube 4 is folded back at the right end or the left end of the corrugated fin heat exchanger 1. That is, the drainage guides 41 adjacent to each other are coupled at the right end or the left end, and are arranged in a vertical direction in a zigzag manner.
Since the drainage guide structures 40 and 50 can concentrate the condensed water on the lower end side or the side end side of the corrugated fin heat exchanger 1, the drainage of the condensed water is facilitated.

As shown in FIG. 9, the drainage guide configuration 60 is provided with one drainage guide 61 a on the diagonal line of the corrugated fin heat exchanger 1, and the area below the drainage guide 61 a is the lower end side of the corrugated fin heat exchanger 1. A drainage guide 61b that guides condensed water is provided, and a drainage guide 61c that guides condensed water to the drainage guide 61a is provided in an area above the drainage guide 61a.
With such a configuration, the condensed water attracted by the drain guide 61c is collected in the drain guide 61a and drained at the lower end. On the other hand, the condensed water attracted by the drain guide 61b is drained to the lower end as it is.

  As shown in FIG. 10, FIG. 11 and FIG. 12, the drainage guide structures 70, 80, 90 are configured to have a lattice shape by combining drainage guides 71, 81, 91 arranged at two different angles. Yes. The drainage guide 71 is arranged at 45 degrees diagonally downward and leftward so that one mesh has a rhombus shape. The drainage guide 81 has a net shape in which one side (downward to the right) is wider than the other (downward to the left). One of the drainage guides 91 is arranged in parallel in the oblique direction, and the other is arranged in the up-down direction and in parallel in the left-right direction. In such a configuration, the drainage guides 71, 81, 91 can be easily manufactured using a resin net or the like.

As shown in FIG. 13, the drainage guide configuration 100 is configured to consolidate the drainage guide 101 at one point on the lower end side of the corrugated fin heat exchanger 1. That is, the drainage guide 101 is extended radially upward by connecting at one point at the lower end. Even in such a configuration, the condensed water can be concentrated on the lower end side of the corrugated fin-type heat exchanger 1, so that the condensed water can be easily drained.
FIG. 14 shows a drainage guide configuration 110 in which the drainage guide configuration 20 shown in FIG. 5 is symmetrically arranged, and the drainage guide 111 extends in parallel from the left or right center or lower side to the left and right diagonally upward. Therefore, the condensed water can be concentrated on the lower end side of the corrugated fin heat exchanger 1. A drainage guide configuration 120 shown in FIG. 15 is configured by forming the drainage guide 121 in a wave shape (sine curve shape) and extending in the vertical direction, and can easily drain the condensed water.

As shown in FIG. 16, the drainage guide configuration 130 is configured such that the drainage guide 131 is disposed only in a portion where condensation is likely to occur in the corrugated fin heat exchanger 1. In the drainage guide configuration 130, the corrugated fin heat exchanger 1 has a portion where the lower part of the corrugated fin heat exchanger 1 tends to condense from the center.
In general, the portion where condensation is likely to occur is not limited to the above-described drainage guide structure 130, but depends on the evaporation temperature of the refrigerant, that is, the drift of the bus of the corrugated fin heat exchanger 1 or its Varies depending on the airflow passing through the part. It is desirable to dispose the drainage guide 131 in a portion corresponding to the dew condensation tendency of the corrugated fin heat exchanger 1 to which the drainage guide 131 is attached.

As shown in FIG. 17, the drainage guide configuration 140 can make the drainage guide 141 movable. That is, rails are formed above and below the corrugated fin heat exchanger 1, and driving devices 142 and 142 (or either one) are arranged on the upper and lower rails so as to be movable left and right. A drainage guide 141 is stretched between the devices 142 and 142. Since the drive device 142 is an output that only moves the drainage guide 141 on the corrugated fin heat exchanger 1, it can be configured with an electric motor, a cylinder, or the like, but a configuration in which the drive unit is pulled with a wire is also possible. The drive configuration is not limited. The driving device 142 can translate the upper end portion and the lower end portion of the corrugated fin heat exchanger 1 along rails 143 provided at the upper end portion and the lower end portion of the corrugated fin heat exchanger 1 (FIG. 16). Arrow direction in the middle).
In the drainage guide configuration 140, the drainage guide 141 is movable, but must be in contact with the cell 7 of the corrugated fin heat exchanger 1. Further, the attracting property of the condensed water is enhanced by setting the speed of the driving device 142 to 1 reciprocation / 1 hr. Further, it is also possible to arrange the rails in the vertical direction on both the left and right sides and stretch the drainage guide 141 in the horizontal direction to move it up and down.
With such a configuration, even the single drainage guide 141 can easily drain the corrugated fin heat exchanger 1, and thus can be applied to a corrugated fin heat exchanger having a large area.

Next, the configuration of an engine-driven heat pump 300 according to another embodiment of the present invention will be described using FIG.
As shown in FIG. 18, the engine-driven heat pump 300 includes a second pressure sensor 352 and a first pressure sensor 351 upstream and downstream of the outdoor heat exchanger 311. Since these pressure sensors 351 and 352 are connected to an electronic control unit (hereinafter abbreviated as ECU) 350, the ECU 350 can detect the pressure values P1 and P2.
The outdoor fan electric motor 353 that drives the outdoor fan 315 of the engine-driven heat pump 300 is an outdoor fan electric motor 353 whose rotational speed can be varied. Since the outdoor fan motor 353 is connected to the ECU 350, the number of revolutions can be changed by the ECU 350. That is, the ECU 350 can adjust the air flow rate to the outdoor heat exchanger 311 by changing the rotational speed of the outdoor fan 315.
The engine-driven heat pump 300 is assumed to include the drainage guide 11. Since other refrigerant circuit configurations are the same as those of the engine-driven heat pump 200 described above, description thereof is omitted.

Here, the control of the engine-driven heat pump 300 according to another embodiment of the present invention will be described with reference to FIG. However, the following control is during heating operation in which the outdoor heat exchanger 311 acts as an evaporator.
The ECU 350 starts the engine 301 (S401), drives the compressor 303 with the electromagnetic clutch 302 ON (S402), and operates the engine-driven heat pump 300 (S403).
Next, when a predetermined time α has elapsed since the electromagnetic clutch 302 was turned ON (S402) (S405), the ECU 350 increases the rotational speed of the outdoor fan electric motor 353 only for the extremely short predetermined time β to increase the outdoor heat. Increase the air flow to the exchanger 311. Thereafter, the engine-driven heat pump 300 performs a normal operation (S406).
Furthermore, the ECU 350 determines that ΔP (ΔP = P2−P1), which is the difference between the first pressure sensor 351 and the second pressure sensor 352, is equal to or greater than a predetermined pressure value Pa while the engine-driven heat pump 300 continues to operate (S450). If it becomes (S451), it is determined that the air volume is reduced due to condensation, and the number of taps of the outdoor fan electric motor 353 is increased only for a predetermined time β to increase the air volume to the outdoor heat exchanger 311 (S452).

  In this way, the outdoor heat exchanger 311 can be installed even when the air volume drop due to condensation occurs immediately after the start of the operation of the engine-driven heat pump 300 in which attraction of the condensed water to the drain guide 11 is insufficient or during steady operation. The function of the drainage guide 11 can be restored by forcibly draining water by increasing the amount of air passing therethrough.

Moreover, the structure of the engine drive type heat pump 500 which concerns on another Example of this invention is demonstrated using FIG.
As shown in FIG. 17, the engine-driven heat pump 500 includes a second pressure sensor 552 and a first pressure sensor 551 upstream and downstream of the outdoor heat exchanger 511. Since these pressure sensors 551 and 552 are connected to the ECU 550, the ECU 550 can detect the respective pressure values P1 and P2.
The engine-driven heat pump 500 includes a water injection device 530 that enables water injection to the outdoor heat exchanger 511. This water injection device 530 can open and close a valve according to a command from the ECU 550 to inject a predetermined amount of water to the corrugated fin heat exchanger 1.
The engine-driven heat pump 300 is assumed to include the drainage guide 11. Since other refrigerant circuit configurations are the same as those of the engine-driven heat pump 200 described above, description thereof is omitted.

Next, the control of the engine-driven heat pump 500 according to another embodiment of the present invention will be described using FIG. However, the following control is during heating operation in which the outdoor heat exchanger 511 functions as an evaporator.
The ECU 550 starts the engine 501 (S601), drives the compressor 503 with the electromagnetic clutch 502 ON (S602), and operates the engine-driven heat pump 500 (S603).
Next, when a predetermined time α has elapsed since the electromagnetic clutch 502 was turned ON (S602) (S604), the ECU 550 operates the water injection device 530 to inject a predetermined amount of water into the outdoor heat exchanger 511 ( S605). Thereafter, the engine-driven heat pump 500 performs a normal operation (S606).
Further, the ECU 550 determines that ΔP (ΔP = P2−P1), which is a difference between the first pressure sensor 651 and the second pressure sensor 652, is equal to or greater than a predetermined pressure value Pa while the engine-driven heat pump 500 is continuously operated (S650). If it becomes (S651), it is determined that the air volume is reduced due to condensation, and the water injection device 330 is operated to inject a predetermined amount of water into the outdoor heat exchanger 311 (S652).

  In this way, even when the engine-driven heat pump 300, which is not sufficiently attracted to the drainage guide 11 of condensed water, immediately after the start of operation or during a steady operation, a decrease in the air volume due to condensation occurs, the outdoor heat exchanger 311 The function of the drainage guide 11 can be restored by forcibly draining water by jetting water.

The refrigerant circuit figure which shows the whole structure of the engine drive type heat pump which concerns on the Example of this invention. (A) Front view which shows a corrugated fin type heat exchanger. (A) Front view which shows the drainage guide structure of the corrugated fin type heat exchanger which shows the Example of this invention. (B) The same enlarged front view. (A) Side view of corrugated fin heat exchanger showing an example of arrangement of drainage guides (b) Side view of corrugated fin type heat exchanger showing another example of arrangement of drainage guides (c) Another example of arrangement of drainage guides Side view of corrugated fin type heat exchanger (d) Side view of corrugated fin type heat exchanger showing another arrangement example of drainage guide. The front view which shows the drainage guide structure which made the inclination 45 degree | times or more. The front view which shows the drainage guide structure which made the inclination less than 45 degree | times. The front view which shows the drainage guide structure turned up by an upper end or a lower end. The front view which shows the drainage guide structure turned up by the right end or the left end. The front view which shows the drainage guide structure which the area | region divided by the drainage guide arrange | positioned on a diagonal line is each different inclination. The front view which shows the drainage guide structure which is a grid | lattice form. The front view which shows another drainage guide structure which is a grid | lattice form. The front view which shows another drainage guide structure which is a grid | lattice form. The front view which shows another drainage guide structure which one bottom end concentrates. The front view which shows another drainage guide structure whose inclination is symmetrical. The front view which shows a wavy another drainage guide structure. The front view which shows the drainage guide structure partially stretched. The front view which shows the drainage guide structure made into the movable type. The refrigerant circuit figure which shows the whole structure of the engine drive type heat pump which concerns on another Example of this invention. The flowchart which shows the waste_water | drain attraction control of the engine drive type heat pump which concerns on another Example of this invention. The flowchart which shows the whole structure of the engine drive type heat pump which concerns on another Example of this invention. The flowchart which shows the separate drainage attraction control of the engine drive type heat pump which concerns on another Example of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Corrugated fin type heat exchanger 4 Flat tube 5 Corrugated fin 10 Drainage guide structure 10
11 Drainage guide 11

Claims (15)

In a corrugated fin type heat exchanger comprising a flat tube and a corrugated fin, wherein a drainage guide that contacts the corrugated fin is provided on the condensate condensing side,
The drainage guide is constituted by a linear member, the drainage guide is inclined with respect to the flat tube, and at least one of both ends of the drainage guide is guided to the lower end side or the side end side of the heat exchanger. Corrugated fin type heat exchanger. In the corrugated fin heat exchanger according to claim 1,
A corrugated fin heat exchanger characterized in that a wire diameter of the drainage guide is 50 to 300% of a fin pitch of the corrugated fin. In the corrugated fin heat exchanger according to claim 1,
The corrugated fin is characterized in that the flat tubes are arranged in a horizontal direction, and the heat exchanger is arranged vertically or inclined at the upper end side of the heat exchanger on the downstream side of the ventilation, and the drainage guide is provided on the downstream side of the ventilation. Type heat exchanger. In the corrugated fin heat exchanger according to claim 1,
A corrugated fin heat exchanger, wherein the flat tubes are disposed in a horizontal direction, are inclined to the upstream side of the heat exchanger, and are provided on the upstream side of the drainage guide. In the corrugated fin heat exchanger according to claim 1,
The corrugated fin heat exchanger, wherein the adjacent drainage guides are alternately turned back at the upper end side or the lower end side of the heat exchanger. In the corrugated fin heat exchanger according to claim 1,
The corrugated fin type heat exchanger, wherein the adjacent drainage guides are alternately folded at the left end side or the right end side of the heat exchanger. In the corrugated fin heat exchanger according to claim 1,
A corrugated structure comprising: a region where one end of the drainage guide is led to the lower end side of the heat exchanger; and a region where one end of the drainage guide is led to the drainage guide provided diagonally of the heat exchanger. Fin type heat exchanger. In the corrugated fin heat exchanger according to claim 1,
A corrugated fin heat exchanger, characterized in that the drainage guide has a lattice shape. In the corrugated fin heat exchanger according to claim 1,
One end of the drainage guide is concentrated on the lower end side of the heat exchanger, and the corrugated fin type heat exchanger is characterized. In the corrugated fin heat exchanger according to claim 1,
A corrugated fin heat exchanger characterized in that the drainage guide is configured in a region limited to a portion where condensate is likely to condense. In the corrugated fin heat exchanger according to claim 1,
A corrugated fin heat exchanger characterized in that the drainage guide is made of resin. In the corrugated fin heat exchanger according to claim 1,
A corrugated fin heat exchanger characterized in that the drainage guide is made of metal. In the corrugated fin heat exchanger according to claim 1,
A corrugated fin heat exchanger characterized in that the drainage guide is made of fiber. In the corrugated fin heat exchanger according to claim 1,
A corrugated fin heat exchanger, wherein the drainage guide is movable. In the air conditioner provided with the corrugated fin heat exchanger according to claim 1,
The fan air volume is instantaneously increased after a predetermined time has elapsed after the start of operation or when a decrease in the air volume of the fan for the heat exchanger is detected, or water injection is performed on the condensed water condensing side of the heat exchanger. Air conditioner.