Refrigeration cycle equipment

Abstract

This refrigeration cycle device comprises a condenser that has corrugated fins, and a water sprinkling device that sprinkles water onto the condenser, wherein the droplet diameter of the water sprinkled by the water sprinkling device is no more than 160 μm.

Description

[Technical Field]

[0001] This disclosure relates to a refrigeration cycle system that sprays water onto a condenser. [Background technology]

[0002] In refrigeration cycle systems, it is known that when the outside air temperature is high, water is sprayed onto the condenser of the outdoor unit, and the condenser is cooled by the heat of vaporization of the water, thereby improving the condensation capacity of the refrigerant. For example, Patent Document 1 discloses a spraying device equipped with multiple spray nozzles for spraying water onto a heat exchanger having plate fins. In Patent Document 1, multiple spray nozzles are arranged in front of the heat exchanger, and a mist of water is sprayed during cooling operation when the heat exchanger functions as a condenser. [Prior art documents] [Patent Documents]

[0003] [Patent Document 1] Patent No. 5880019 [Overview of the Initiative] [Problems that the invention aims to solve]

[0004] In the case of a heat exchanger with corrugated fins, water is collected in the valleys of the corrugated fins when water is sprayed, making it easier for water to be retained in the condenser compared to a heat exchanger with plate fins. However, if the amount of water retained in the condenser increases, it can create air resistance and potentially degrade the condenser's performance.

[0005] This disclosure solves the above-mentioned problems and provides a refrigeration cycle system that can suppress the deterioration of condenser performance due to water spraying. [Means for solving the problem]

[0006] The refrigeration cycle device according to this disclosure comprises a condenser having corrugated fins and a water spraying device that sprays water onto the condenser, wherein the droplet diameter of the water sprayed by the water spraying device is 160 μm or less. The watering device comprises a first pipe extending in a first direction and equipped with multiple first nozzles, a second pipe extending in the first direction and equipped with multiple second nozzles, and a third pipe extending in a second direction perpendicular to the first direction and equipped with multiple third nozzles. The first and second pipes are positioned opposite each other below the third pipe, one end of the third pipe is connected to the first pipe, and the other end is connected to the second pipe. The multiple third nozzles spray water upwards onto the condenser, while the multiple first and second nozzles spray water towards the center of the condenser. . [Effects of the Invention]

[0007] According to the refrigeration cycle device of this disclosure, by spraying water onto a condenser having corrugated fins with a droplet diameter of 160 μm or less, it is possible to suppress the increase in the amount of water held in the condenser and suppress the deterioration of the condenser's performance. [Brief explanation of the drawing]

[0008] [Figure 1] This is a schematic diagram of the refrigeration cycle device according to Embodiment 1. [Figure 2] This is a schematic diagram of the outdoor heat exchanger according to Embodiment 1. [Figure 3] This is a schematic diagram of the watering device for a refrigeration cycle system according to Embodiment 1. [Figure 4] This graph shows the relationship between the water discharge rate per unit area and the COP improvement rate for each droplet size in a heat exchanger with corrugated fins. [Figure 5] This is a side view of the heat source unit of the refrigeration cycle device according to Embodiment 2. [Figure 6] This figure shows the temperature distribution of the outdoor heat exchanger when the outdoor heat exchanger according to Embodiment 2 functions as a condenser. [Figure 7] This is a schematic diagram of the watering device for a refrigeration cycle system according to Embodiment 2. [Figure 8] This diagram illustrates the installation angle of the third nozzle of the third piping according to Embodiment 2. [Figure 9] This diagram illustrates the installation angles of the first nozzle and the second nozzle of the first and second pipes according to Embodiment 2. [Figure 10] This diagram illustrates the installation angles of the first nozzle and the second nozzle of the first and second pipes according to Embodiment 2. [Figure 11]This is a diagram for explaining the installation angles of the first nozzles and the second nozzles of the first pipe and the second pipe according to Embodiment 2. [Figure 12] This is a diagram showing an example of the connection arrangement of the heat source unit. [Figure 13] This is a schematic configuration diagram of the sprinkler device according to Embodiment 3.

Modes for Carrying Out the Invention

[0009] Hereinafter, embodiments will be described based on the drawings. In each figure, those denoted by the same reference numerals are the same or corresponding ones, which is common throughout the entire specification. Also, the forms of the constituent elements shown throughout the entire specification are merely examples and are not limited to these descriptions. Furthermore, in the following drawings, the relationship of the sizes of each constituent member may be different from the actual ones.

[0010] Embodiment 1. (Configuration of the Refrigeration Cycle Device) FIG. 1 is a schematic configuration diagram of a refrigeration cycle device 100 according to Embodiment 1. The refrigeration cycle device 100 of the present Embodiment 1 is a heat pump chiller that performs air conditioning using chilled and warm water. As shown in FIG. 1, the refrigeration cycle device 100 includes a heat source unit 1, an indoor unit 2, and a control device 3. The heat source unit 1 of the present embodiment has four refrigerant circuits. And two refrigerant circuits form a group and share one water heat exchanger 60. The heat source unit 1 of the present embodiment has two groups of two refrigerant circuits. And the two water heat exchangers 60 are connected in series by piping to cool or heat water, which is a heat medium, in two stages.

[0011] As shown in FIG. 1, the refrigerant circuit of each system of the heat source unit 1 of the present embodiment pipes and connects a compressor 11, a four-way valve 12, an outdoor heat exchanger 13, an expansion valve 14, a water heat exchanger 60, and an accumulator 15 to constitute the refrigerant circuit. As the refrigerant, for example, a single refrigerant such as R-22 or R-134a, a pseudo-azeotropic mixed refrigerant such as R-410A or R-404A, or a zeotropic mixed refrigerant such as R-407C can be used. Further, a refrigerant or a mixture thereof having a relatively small global warming potential, such as CF3CF=CH2, which contains a double bond in its chemical formula, or a natural refrigerant such as CO2 or propane can be used.

[0012] The compressor 11 compresses and discharges the inhaled refrigerant. The compressor 11 is driven via a compressor inverter drive device (not shown). The compressor 11 can change the capacity of the compressor 11, which is the amount of refrigerant sent out per unit time, by arbitrarily changing the driving frequency based on an instruction from the control device 3.

[0013] Also, the four-way valve 12, which is a flow path switching device, switches the flow of the refrigerant according to the operation to be performed based on an instruction from the control device 3. For example, during a cooling operation or the like, the four-way valve 12 allows the high-temperature and high-pressure refrigerant discharged from the compressor 11 to flow into the outdoor heat exchanger 13. Also, during a heating operation or the like, the high-temperature and high-pressure refrigerant discharged from the compressor 11 is allowed to flow into the water heat exchanger 60.

[0014] The outdoor heat exchanger 13 performs heat exchange between the refrigerant and the external air. The outdoor heat exchanger 13 functions as an evaporator in a heating operation for heating water, performs heat exchange between the low-pressure refrigerant flowing in from the expansion valve 14 side and the air, and evaporates and vaporizes the refrigerant. Also, in a cooling operation for cooling water, it functions as a condenser, performs heat exchange between the high-pressure refrigerant flowing in from the compressor 11 side and the air, and condenses and liquefies the refrigerant.

[0015] A watering device 5 is attached to the outdoor heat exchanger 13. The watering device 5 sprays water onto the outdoor heat exchanger 13 when it is functioning as a condenser. The outdoor heat exchanger 13 and the watering device 5 will be described in detail later.

[0016] Furthermore, the outdoor fan 16 supplies air to the outdoor heat exchanger 13, promoting heat exchange between the refrigerant and the air. Here, the outdoor fan 16 is driven via a fan inverter drive device (not shown) or the like. The airflow of the outdoor fan 16 can be changed by arbitrarily changing the drive frequency based on instructions from the control device 3. In Figure 1, the outdoor heat exchanger 13 and the outdoor fan 16 are shown in a one-to-one correspondence, but this is not particularly limited.

[0017] The water heat exchanger 60, which acts as a heat transfer medium heat exchanger, performs heat exchange between the water, which acts as the heat transfer medium, and the refrigerant. The water heat exchanger 60 is part of the flow path of the two refrigerant circuits and the flow path of the heat transfer medium circulation circuit. Therefore, it is a component of both the refrigerant circuit and the heat transfer medium circulation circuit. For example, during heating operation, the water heat exchanger 60 functions as a condenser, performing heat exchange between the refrigerant flowing in from the compressor 11 side and water, condensing the refrigerant into a liquefied or gas-liquid two-phase state, and heating the water. On the other hand, during cooling operation, it functions as an evaporator, performing heat exchange between the refrigerant flowing in from the expansion valve 14 side and water, evaporating the refrigerant into a vapor, and cooling the water.

[0018] The expansion valve 14, which acts as a throttling device, adjusts the pressure of the refrigerant passing through the water heat exchanger 60 by, for example, changing its opening degree. In this embodiment, the expansion valve 14 is configured as an electronic expansion valve that changes its opening degree based on instructions from the control device 3. However, it is not limited to this. For example, it may be a temperature-sensitive expansion valve that changes its opening degree based on the temperature of the refrigerant.

[0019] Each accumulator 15 is located on the suction side of the compressor 11 and stores excess refrigerant in the refrigerant circuit.

[0020] Pump 80 is one of the components that make up the heat transfer medium circulation circuit. In the heat transfer medium circulation circuit, pump 80 draws in water, applies pressure, and sends it out to circulate it. Furthermore, the pump inverter drive unit (not shown) can change the capacity of pump 80 by arbitrarily changing the drive frequency based on instructions from the control unit 3.

[0021] The indoor unit 2 is a unit that supplies conditioned air to the indoor space to be air-conditioned. As shown in Figure 1, each indoor unit 2 in this embodiment has an indoor heat exchanger 21, an indoor flow rate regulator 22, and an indoor fan 23. The indoor heat exchanger 21 and the indoor flow rate regulator 22 are components that constitute a heat transfer medium circulation circuit. Figure 1 shows a refrigeration cycle system 100 having two indoor units 2, but the number of indoor units 2 may be one or three or more.

[0022] The indoor flow rate control device 22 is composed of, for example, a two-way valve that can control the valve opening (opening area). By adjusting the opening, the indoor flow rate control device 22 controls the flow rate of water flowing into and out of the indoor heat exchanger 21. The indoor flow rate control device 22 adjusts the amount of water that passes through the indoor heat exchanger 21 based on the temperature of the water flowing into and out of the indoor unit 2, so that the indoor heat exchanger 21 can perform heat exchange with a heat amount corresponding to the heat load in the room. Here, the indoor flow rate control device 22 can completely close the valve and stop the supply of water so that it does not flow into or out of the indoor heat exchanger 21 when the indoor heat exchanger 21 does not need to exchange heat with the heat load, such as when the unit is stopped or the thermostat is turned off. In Figure 1, the indoor flow rate control device 22 is installed in the piping on the water outlet side of the indoor heat exchanger 21, but it is not limited to this. For example, the indoor flow rate control device 22 may be installed on the water inlet side of the indoor heat exchanger 21.

[0023] Furthermore, the indoor heat exchanger 21 is a fin-tube type heat exchanger that performs heat exchange between indoor air and water in the indoor space supplied by the indoor fan 23. During cooling operation, water that is colder than the air passes through the heat transfer tubes of the indoor heat exchanger 21, and the indoor space is cooled. On the other hand, during heating operation, water that is warmer than the air passes through the heat transfer tubes of the indoor heat exchanger 21, and the indoor space is heated. The indoor fan 23 generates an airflow that passes the air in the indoor space through the indoor heat exchanger 21 and returns it to the indoor space.

[0024] The control device 3 controls the operation of the entire refrigeration cycle system 100. The control device 3 consists of a computer equipped with a memory for storing data and programs necessary for control, and a CPU for executing programs, dedicated hardware such as an ASIC or FPGA, or both. The control device 3 controls each part of the refrigeration cycle system 100 based on detection information such as temperature sensors or pressure sensors equipped in the refrigeration cycle system 100, and instructions from a remote control (not shown). Specifically, the control device 3 controls the drive frequency of the compressor 11, the rotation speed of the outdoor fan 16 and indoor fan 23, the switching of the four-way valve 12, the opening degree of the expansion valve 14, the drive frequency of the pump 80, the opening degree of the indoor flow rate adjustment device 22, and the water spraying of the water spraying device 5.

[0025] In Figure 1, the control device 3 is provided separately from the heat source unit 1 and the indoor unit 2, but it may be mounted on either the heat source unit 1 or the indoor unit 2. Alternatively, the heat source unit 1 and the indoor unit 2 may each be equipped with a control device 3 and be connected to each other wirelessly or via wired communication to send and receive various data.

[0026] (Outdoor heat exchanger configuration) Next, the configuration of the outdoor heat exchanger 13 of this embodiment will be described. Figure 2 is a schematic diagram of the outdoor heat exchanger 13 according to Embodiment 1. The outdoor heat exchanger 13 of this embodiment is a parallel flow type heat exchanger (PFC heat exchanger). The outdoor heat exchanger 13 comprises a heat exchange section 130 consisting of a plurality of heat transfer tubes 131 and a plurality of fins 132, first headers 133a, 133b and 133c, second headers 134a and 134b, and connecting pipes 135a and 135b. In Figure 2, for the sake of simplifying the drawing, only a portion of the heat transfer tubes 131 and fins 132 are shown, and the overall illustration is omitted.

[0027] Each heat transfer tube 131 is a flattened tube with multiple flow channels formed inside. Each heat transfer tube 131 extends between the first headers 133a, 133b, and 133c and the second headers 134a and 134b. Each heat transfer tube 131 is spaced apart from each other in a direction perpendicular to the direction of extension. In the following description, the direction of extension of each heat transfer tube 131 may be referred to as the first direction or horizontal direction, and the direction perpendicular to the direction of extension of each heat transfer tube 131 may be referred to as the second direction or vertical direction. Furthermore, the direction perpendicular to both the horizontal and vertical directions may be referred to as the depth direction.

[0028] The fins 132 are corrugated fins bent into a wave shape. Each fin 132 extends between the first headers 133a, 133b, and 133c and the second headers 134a and 134b. Each fin 132 is also positioned between two adjacent heat transfer tubes 131 of a plurality of heat transfer tubes 131, and the two adjacent heat transfer tubes 131 are connected by the fins 132.

[0029] The first headers 133a, 133b, and 133c are connected to one end of the heat transfer tubes 131 in the direction of extension, and the second headers 134a and 134b are connected to the other end of the heat transfer tubes 131 in the direction of extension. The first headers 133a, 133b, and 133c, and the second headers 134a and 134b have the function of distributing the refrigerant flowing into the outdoor heat exchanger 13 to the heat transfer tubes 131, and the function of merging the refrigerant that has flowed through the heat transfer tubes 131.

[0030] One end of connecting pipe 135a is connected to the first header 133a, and the other end is connected to the four-way valve 12. One end of connecting pipe 135b is connected to the first header 133c, and the other end is connected to the expansion valve 14.

[0031] In the outdoor heat exchanger 13 of this embodiment, multiple flow paths P1, P2, P3, and P4 are formed in the heat exchange section 130 by the above configuration. Figure 2 shows the four flow paths P1 to P4 of the heat exchange section 130 when the outdoor heat exchanger 13 functions as a condenser. As shown in Figure 2, when the outdoor heat exchanger 13 functions as a condenser, the refrigerant discharged from the compressor 11 flows through the four-way valve 12 and into the first header 133a from the connecting pipe 135a. The refrigerant that has flowed into the first header 133a then flows into the second header 134a through the flow path P1 formed by multiple heat transfer tubes 131 connected to the first header 133a.

[0032] The refrigerant flowing into the second header 134a flows into the first header 133b through a flow path P2 formed by a plurality of heat transfer tubes 131 connected between the second header 134a and the first header 133b. The refrigerant flowing into the first header 133b flows into the second header 134b through a flow path P3 formed by a plurality of heat transfer tubes 131 connected between the first header 133b and the second header 134b. The refrigerant flowing into the second header 134b flows into the first header 133c through a flow path P4 formed by a plurality of heat transfer tubes 131 connected between the second header 134b and the first header 133c. The refrigerant flowing into the first header 133c flows out to the expansion valve 14 through the connecting pipe 135b.

[0033] (Configuration of the sprinkler system) Figure 3 is a schematic diagram of the sprinkler device 5 of the refrigeration cycle device 100 according to Embodiment 1. In Figure 3, the outdoor heat exchanger 13 is also shown for illustrative purposes. The sprinkler device 5 is attached to a housing or the like that holds the outdoor heat exchanger 13. In order to suppress a decrease in the heat exchange efficiency of the outdoor heat exchanger 13, the sprinkler device 5 and the outdoor heat exchanger 13 are arranged with a gap in the depth direction.

[0034] As shown in Figure 3, the sprinkler system 5 comprises a first pipe 50a, a second pipe 50b, and connecting pipes 52 connected to the first pipe 50a and the second pipe 50b, respectively. The first pipe 50a and the second pipe 50b are independent of each other, and one end of each is connected to the connecting pipe 52. The connecting pipe 52 is connected to a water pipe or the like, and water flowing in from the connecting pipe 52 is supplied to the first pipe 50a and the second pipe 50b, respectively. The connecting pipe 52 is provided with a valve to adjust the water flow rate, and the control device 3 controls the valve, thereby controlling the start and stop of sprinkling by the sprinkler system 5 and the amount of water sprinkled.

[0035] The first pipe 50a and the second pipe 50b are arranged facing each other. The first pipe 50a extends vertically outside one horizontal end of the heat exchange section 130. The second pipe 50b extends vertically outside the other horizontal end of the heat exchange section 130. In the following description, one horizontal end of the heat exchange section 130 will be referred to as the "first header side," and the other horizontal end of the heat exchange section 130 will be referred to as the "second header side."

[0036] Multiple first nozzles 51a are provided in the first pipe 50a. In the example shown in Figure 3, five first nozzles 51a are provided in the first pipe 50a, but the number of first nozzles 51a may be four or fewer, or six or more. Each first nozzle 51a is a hollow conical nozzle that sprays mist-like water at, for example, a spray angle of 60°. Each first nozzle 51a is arranged at a vertical interval and sprays water from the first header side to the second header side into the flow paths P1 to P4 of the heat exchange section 130. In other words, each first nozzle 51a sprays water from one horizontal end of the outdoor heat exchanger 13 toward the center of the outdoor heat exchanger 13.

[0037] Multiple second nozzles 51b are provided in the second pipe 50b. In the example shown in Figure 3, five second nozzles 51b are provided in the second pipe 50b, but the number of second nozzles 51b may be four or fewer, or six or more. Each second nozzle 51b is a hollow conical nozzle that sprays mist-like water at, for example, a spray angle of 60°. Each second nozzle 51b is arranged at vertical intervals and sprays water horizontally from the second header side toward the first header side toward the flow paths P1 to P4 of the heat exchange section 130. In other words, each second nozzle 51b sprays water from the other horizontal end of the outdoor heat exchanger 13 toward the center of the outdoor heat exchanger 13. Each second nozzle 51b is positioned opposite the first nozzle 51a, and the vertical position of each second nozzle 51b is the same as the vertical position of each first nozzle 51a.

[0038] Furthermore, the droplet diameter of the water sprayed from each first nozzle 51a and each second nozzle 51b in the watering device 5 of this embodiment is 160 μm or less, preferably 110 μm or less. In addition, the amount of water sprayed per unit area by each first nozzle 51a and each second nozzle 51b in the watering device 5 is 1.2 ± 0.2 L / (min·m). 2 ) which can be rephrased as 1.0L / (min·m 2 ) or more 1.4L / (min m 2 ) are as follows:

[0039] Figure 4 is a graph showing the relationship between the water spray rate per unit area and the COP improvement rate for each droplet size in a heat exchanger with corrugated fins. The graph in Figure 4 was obtained by conducting water spraying experiments on a heat exchanger with corrugated fins, varying the water spray rate for each droplet size. The COP improvement rate in Figure 4 is the improvement rate relative to the COP when no water is sprayed on the heat exchanger. In Figure 4, the solid line R1 is the graph for a droplet size of 110 μm, the dashed line R2 is the graph for a droplet size of 160 μm, and the dashed line R3 is the graph for a droplet size of 200 μm. The fin pitch of the heat exchanger used in the experiment was 1-2 mm.

[0040] As shown in Figure 4, the COP improvement rate when the droplet diameter is 160 μm or less is higher than the COP improvement rate when the droplet diameter is 200 μm or less. Furthermore, when the droplet diameter is 160 μm or less, the water distribution rate per unit area is 1.2 L / (min·m). 2 The COP improvement rate is higher when the droplet diameter is close to 160 μm or less and the water flow rate is 1.2 ± 0.2 L / (min·m). 2 By doing so, the COP improvement rate can be increased (for example, to 30% or more). In particular, if the droplet size is 110 μm and the water flow rate is 1.2 L / (min·m) 2 In this case, the COP improvement rate is highest, and can be 50% or more.

[0041] In the case of the watering device 5 shown in Figure 3, if the water flow rate of each first nozzle 51a and each second nozzle 51b is 0.2 L / min and the droplet diameter is 110 μm, the total flow rate is 2.00 L / min, and the water flow rate per unit area is 1.12 L / (min·m²). 2 ) The heat exchange section 130 is assumed to have a height of 1.22 m and a width of 1.47 m.

[0042] Furthermore, the lower limit of the droplet diameter of the water sprayed from each nozzle of the watering device 5 may be set to, for example, 60 μm. That is, the droplet diameter of the water sprayed from each nozzle of the watering device 5 may be 60 μm or more and 160 μm or less. If the droplet diameter of the water sprayed from each nozzle of the watering device 5 is less than 60 μm, many nozzles will be required to achieve the desired amount of water sprayed per unit area, which will lead to limitations in placement or increased costs. In addition, if the droplet diameter is less than 60 μm, it will be more susceptible to the effects of outside wind, and the droplets may not hit the outdoor heat exchanger 13.

[0043] As described above, in this embodiment, by setting the droplet diameter of the water sprayed from each nozzle of the water spraying device 5 that sprays water onto the outdoor heat exchanger 13, which functions as a condenser, to 160 μm or less, it is possible to suppress the increase in the amount of water held in the outdoor heat exchanger 13. As a result, it is possible to suppress the deterioration of the performance of the outdoor heat exchanger 13 and to improve the COP by water spraying. Furthermore, the amount of water sprayed per unit area of ​​the water spraying device 5 should be 1.2 ± 0.2 L / (min·m 2 By doing so, further improvement in COP can be achieved. The above effect is particularly effective when the fin pitch of fin 132 is 1 to 2 mm.

[0044] Embodiment 2. Embodiment 2 will now be described. Embodiment 2 differs from Embodiment 1 in the configuration of the sprinkler system 5A. The other configurations of the refrigeration cycle system 100 in Embodiment 2 are the same as in Embodiment 1.

[0045] Figure 5 is a side view of the heat source unit 1 of the refrigeration cycle device 100 according to Embodiment 2. As shown in Figure 5, the heat source unit 1 is a top-flow type outdoor unit in which an outdoor fan 16 is positioned above the outdoor heat exchanger 13. When the heat source unit 1 is a top-flow type, a wind velocity distribution is generated in the air flowing into the outdoor heat exchanger 13 as shown by the arrows in Figure 5. Specifically, the wind velocity is greater for air flowing above the outdoor heat exchanger 13 and lower for air flowing below. That is, the wind velocity of the air flowing into each flow path of the heat exchange section 130 of the outdoor heat exchanger 13 is P1 > P2 > P3 > P4. In the example of Figure 5, the outdoor heat exchanger 13 is positioned at an angle to the vertical, and the heat source unit 1 is Y-shaped in side view, but the outdoor heat exchanger 13 may be positioned without being tilted to the vertical.

[0046] Figure 6 shows the temperature distribution of the outdoor heat exchanger 13 when the outdoor heat exchanger 13 according to Embodiment 2 functions as a condenser. As shown in Figure 6, when the outdoor heat exchanger 13 functions as a condenser, the temperature is higher in the part of the heat exchange section 130 closer to the connecting pipe 135a, which is the refrigerant inlet, and lower in the part of the heat exchange section 130 closer to the connecting pipe 135b, which is the refrigerant outlet. In other words, the temperature decreases from upstream to downstream in the direction of refrigerant flow in the heat exchange section 130. For example, as shown in Figure 6, the flow path P1 is at a high temperature (e.g., 80°C to 100°C), the flow path P2 is at a medium temperature (e.g., 40°C to 50°C), and the flow paths P3 and P4 are at a low temperature (e.g., 30°C to 40°C).

[0047] As shown in Figures 5 and 6, the wind speed distribution and temperature distribution in the outdoor heat exchanger 13 are non-uniform. Therefore, if the watering device 5 uniformly sprays water onto the heat exchange section 130, variations in the cooling effect due to watering will occur, reducing the effect of improving condensation capacity and the watering efficiency. For this reason, the watering device 5A in this embodiment is configured to take into account the wind speed distribution and temperature distribution of the outdoor heat exchanger 13.

[0048] Figure 7 is a schematic diagram of the sprinkler device 5A of the refrigeration cycle device 100 according to Embodiment 2. In Figure 7, the outdoor heat exchanger 13 is also shown for illustrative purposes. The sprinkler device 5A is attached to a housing or the like that holds the outdoor heat exchanger 13. In order to suppress a decrease in the heat exchange efficiency of the outdoor heat exchanger 13, the sprinkler device 5A and the outdoor heat exchanger 13 are arranged with a gap in the depth direction.

[0049] As shown in Figure 7, the sprinkler system 5A includes a first pipe 50a, a second pipe 50b, a third pipe 50c, and a connecting pipe 52. The first pipe 50a and the second pipe 50b are positioned opposite each other below the third pipe 50c. One end of the third pipe 50c is connected to the first pipe 50a, and the other end is connected to the second pipe 50b.

[0050] The second pipe 50b and the third pipe 50c are connected to the connecting pipe 52. The connecting pipe 52 is connected to a water pipe or the like, and water flowing in from the connecting pipe 52 is supplied to the second pipe 50b, the third pipe 50c, and the first pipe 50a. The connecting pipe 52 is equipped with a valve to adjust the water flow rate, and the control device 3 controls the valve, thereby controlling the start and stop of watering by the watering device 5A, as well as the amount of water sprayed.

[0051] The first pipe 50a is positioned extending vertically beyond one horizontal end of the heat exchange section 130. The second pipe 50b is positioned extending vertically beyond the other horizontal end of the heat exchange section 130.

[0052] Multiple first nozzles are provided in the first pipe 50a. In the example shown in Figure 7, three first nozzles 51a1, 51a2, and 51a3 are provided in the first pipe 50a. Each of the first nozzles 51a1, 51a2, and 51a3 is a hollow conical nozzle that sprays mist-like water at, for example, a spray angle of 60°. Each of the first nozzles 51a1, 51a2, and 51a3 is arranged vertically spaced apart from each other. The first nozzle 51a1 mainly sprays water onto the flow path P2, the first nozzle 51a2 mainly sprays water onto the flow path P3, and the first nozzle 51a3 mainly sprays water onto the flow path P4. Each of the first nozzles 51a1, 51a2, and 51a3 sprays water from the first header side towards the second header side, that is, from one horizontal end of the outdoor heat exchanger 13 towards the center of the outdoor heat exchanger 13. As an example, the water discharge rate from each of the first nozzles 51a1, 51a2, and 51a3 is 0.24 L / min, and the droplet diameter is 160 μm or less, for example, 110 μm.

[0053] The second pipe 50b is provided with multiple second nozzles. In the example shown in Figure 4, the second pipe 50b is provided with three second nozzles 51b1, 51b2, and 51b3. Each second nozzle 51b1, 51b2, and 51b3 is a hollow conical nozzle that sprays mist-like water at, for example, a spray angle of 60°. Each second nozzle 51b1, 51b2, and 51b3 is positioned vertically apart from each other. Each second nozzle 51b1, 51b2, and 51b3 is positioned opposite each first nozzle 51a1, 51a2, and 51a3. The vertical position of each second nozzle 51b1, 51b2, and 51b3 is the same as the vertical position of each first nozzle 51a1, 51a2, and 51a3. The second nozzle 51b1 primarily sprays water onto the flow path P2, the second nozzle 51b2 primarily sprays water onto the flow path P3, and the second nozzle 51b3 primarily sprays water onto the flow path P4. Each of the second nozzles 51b1, 51b2, and 51b3 sprays water from the second header side toward the first header side, that is, from the other horizontal end of the outdoor heat exchanger 13 toward the center of the outdoor heat exchanger 13. As an example, the water spray rate of each second nozzle 51b is 0.24 L / min, and the droplet diameter is 160 μm or less, for example, 110 μm.

[0054] The third pipe 50c is arranged to extend horizontally along the lower end of the flow path P1 of the heat exchange section 130. The third pipe 50c is provided with a plurality of third nozzles 51c. In the example shown in Figure 7, the third pipe 50c is provided with four third nozzles 51c. Each third nozzle 51c is a hollow conical nozzle that sprays mist-like water at, for example, a spray angle of 60°. Each third nozzle 51c is arranged horizontally, spaced apart from each other. Each third nozzle 51c sprays water upward from below onto the flow path P1 at the top of the heat exchange section 130. In other words, the four third nozzles 51c of the third pipe 50c spray water onto the flow path P1 of the heat exchange section 130. As an example, the water spray rate from each third nozzle 51c is 0.13 L / min, and the droplet diameter is 160 μm or less, for example, 110 μm.

[0055] In this embodiment, when the height of the heat exchange unit 130 is 1.22 m and the width is 1.47 m, the total amount of water sprayed by the water spraying device 5A is 1.96 L / min, and the amount of water sprayed per unit area is 1.09 L / (min·m 2 ).

[0056] Next, the angles of the respective nozzles with respect to the outdoor heat exchanger 13 will be described. FIG. 8 is a diagram for explaining the installation angle of the third nozzle 51c of the third pipe 50c according to the second embodiment. FIG. 8 schematically shows the third nozzle 51c and the outdoor heat exchanger 13 when the outdoor heat exchanger 13 is viewed from the side (when viewed in the horizontal direction). The third nozzle 51c is a nozzle that sprays water into the flow path P1 where the wind speed is the highest. As shown in FIG. 8, the third nozzle 51c sprays water upward with respect to the heat exchange unit 130 of the outdoor heat exchanger 13. Further, the third nozzle 51c is installed at an angle α1 inclined toward the outdoor heat exchanger 13 with respect to the vertical direction. The angle α1 is an angle such that the water from the third nozzle 51c is sprayed over the entire flow path P1 of the heat exchange unit 130 without exceeding the upper end of the heat exchange unit 130, and is, for example, 45° to 70°. The plurality of third nozzles 51c provided in the third pipe 50c are all installed at the same angle.

[0057] FIG. 9 is a diagram for explaining the installation angles of the first nozzles 51a1 and the second nozzles 51b1 of the first pipe 50a and the second pipe 50b according to the second embodiment. FIG. 9 schematically shows the first nozzles 51a1 and the second nozzles 51b1 and the outdoor heat exchanger 13 when the outdoor heat exchanger 13 is viewed from above (when viewed in the vertical direction). The first nozzles 51a1 and the second nozzles 51b1 are nozzles that spray water into the flow path P2 where the wind speed is the second highest. As shown in FIG. 9, the first nozzles 51a1 and the second nozzles 51b1 are installed at an angle α2 inclined away from the outdoor heat exchanger 13 with respect to the horizontal direction. The angle α2 is an angle such that the water sprayed from the first nozzles 51a1 and the second nozzles 5Ibl arranged at both ends of the heat exchange unit 130 reaches the center of the heat exchange unit 130 with respect to the wind speed, and is, for example, 10° to 20°.

[0058] Figure 10 is a diagram illustrating the installation angles of the first nozzle 51a2 and the second nozzle 51b2 of the first pipe 50a and the second pipe 50b according to Embodiment 2. Figure 10 schematically shows the first nozzle 51a2 and the second nozzle 51b2 and the outdoor heat exchanger 13 when the outdoor heat exchanger 13 is viewed from above (viewed vertically). The first nozzle 51a2 and the second nozzle 51b2 are nozzles that spray water into the flow path P3, which has the third highest wind speed. As shown in Figure 10, the first nozzle 51a2 and the second nozzle 51b2 are installed at an angle α3 away from the outdoor heat exchanger 13 with respect to the horizontal direction. The angle α3 is such that the water sprayed from the first nozzle 51a2 and the second nozzle 51b2, which are located at both ends of the heat exchange section 130, reaches the center of the heat exchange section 130 with respect to the wind speed, and is, for example, 7° to 17°.

[0059] Figure 11 is a diagram illustrating the installation angles of the first nozzle 51a3 and the second nozzle 51b3 of the first piping 50a and the second piping 50b according to Embodiment 2. Figure 11 schematically shows the first nozzle 51a3 and the second nozzle 51b3 and the outdoor heat exchanger 13 when viewed from above (viewed vertically) of the outdoor heat exchanger 13. The first nozzle 51a3 and the second nozzle 51b3 are nozzles that spray water into the flow path P4 with the lowest wind speed. As shown in Figure 11, the first nozzle 51a3 and the second nozzle 51b3 are installed at an angle α4 away from the outdoor heat exchanger 13 with respect to the horizontal direction. The angle α4 is such that, with respect to the wind speed, the water sprayed from the first nozzle 51a3 and the second nozzle 51b3, which are located at both ends of the heat exchange section 130, reaches the center of the heat exchange section 130, for example, 0° to 10°.

[0060] As shown in Figures 9 to 11, the angles α2 to α4 at which the first nozzles 51a1 to 51a3 and the second nozzles 51b1 to 51b3 that spray water horizontally from both ends of the heat exchange section 130 are installed are set to differ according to the wind speed. Specifically, the inclination angle of the nozzles that spray water to areas with high wind speeds is set to be greater than the inclination angle of the nozzles that spray water to areas with high wind speeds, so that the sprayed water reaches the center.

[0061] As described above, by installing the third nozzle 51c on the third pipe 50c extending horizontally and tilting it upward at an angle α1, water can be sprayed over the entire flow path P1 where the airflow velocity is highest. Furthermore, by varying the angles α2 to α4 of the first nozzles 51a1 to 51a3 and the second nozzles 51b1 to 51b3 that spray water horizontally from both ends of the heat exchange section 130 according to the airflow velocity, water can be sprayed over the entire flow paths P2 to P4 of the heat exchange section 130.

[0062] Furthermore, in the sprinkler system 5A of this embodiment, the number of nozzles in the third pipe 50c, which sprinkles water onto the flow path P1, which is relatively hot in the heat exchange section 130, is greater than the number of nozzles in the first pipe 50a and greater than the number of nozzles in the second pipe 50b. As a result, the amount of water sprinkled per unit area onto the flow path P1, which is relatively hot in the heat exchange section 130, can be greater than the amount of water sprinkled per unit area onto the flow paths P2 to P4, which are relatively cold.

[0063] As described above, by spraying water over the entire outdoor heat exchanger 13, which functions as a condenser, and increasing the amount of water sprayed per unit area in the high-temperature portion, the condensation capacity of the outdoor heat exchanger 13 is improved, and the COP of the entire refrigeration cycle system 100 is improved. In addition, by spraying water over the entire outdoor heat exchanger 13, which functions as a condenser, and reducing the amount of water sprayed in the low-temperature portion of the outdoor heat exchanger 13, the waste of water used can be reduced, and the water spraying efficiency can be improved.

[0064] As described above, the same effects as in Embodiment 1 can be obtained in this embodiment. Furthermore, by arranging the nozzles in the watering device 5A as in this embodiment, the effect of improving the condensation capacity of the outdoor heat exchanger 13, which functions as a condenser, and suppressing the decrease in watering efficiency can be improved, thereby improving the COP.

[0065] Embodiment 3. Embodiment 3 will now be described. The heat source units 1 of the refrigeration cycle device 100 may be arranged in a connected configuration outdoors. Figure 12 shows an example of a connected configuration of the heat source units 1. As shown in Figure 12, the heat source units 1 of the refrigeration cycle device 100 may be arranged in a connected configuration in the depth direction. Figure 12 shows a state in which four heat source units 1 are connected in the depth direction.

[0066] As shown in Figure 12, when multiple heat source units 1 are connected, the portion of each heat source unit 1 located inside the outdoor heat exchanger 13, that is, the central portion in the horizontal direction of the heat source unit 1, is less affected by the outside wind, as indicated by the arrows in Figure 12, and the rate of water evaporation decreases. Therefore, the watering device 5B in this embodiment is configured to vary the droplet diameter and the amount of water sprayed in accordance with the influence of the outside wind.

[0067] Figure 13 is a schematic diagram of the sprinkler system 5B according to Embodiment 3. Figure 13 shows two sprinkler systems 5B that sprinkle water on two of the four outdoor heat exchangers 13 provided by the heat source unit 1, which are arranged horizontally. The two sprinkler systems 5B are connected by a connecting pipe 52a. The connecting pipe 52a is connected to a water pipe or the like, and water flowing in from the connecting pipe 52a is supplied to the second pipe 50b, the third pipe 50c, and the first pipe 50a of the two sprinkler systems 5B. The connecting pipe 52 is provided with a valve to adjust the water flow rate, and the control device 3 controls the valve to control the start and stop of sprinkling by the sprinkler system 5B, as well as the amount of water sprinkled.

[0068] As shown in Figure 13, the sprinkler system 5B includes a first pipe 50a, a second pipe 50b, and a third pipe 50c. The two sprinkler systems 5B are mounted on the housing 6 of the heat source unit 1 such that the second pipe 50b is located on the inside where it is less affected by external wind. The configuration of the first pipe 50a and the plurality of first nozzles 51a1, 51a2, and 51a3, as well as the configuration of the third pipe 50c and the plurality of third nozzles 51c in this embodiment, are the same as in Embodiment 2.

[0069] The second pipe 50b is positioned extending vertically beyond the other horizontal end of the heat exchange section 130. The second pipe 50b is provided with a plurality of second nozzles. In the example shown in Figure 13, the second pipe 50b is provided with three second nozzles 51b11, 51b12, and 51b13. Each of the second nozzles 51b11, 51b12, and 51b13 is a hollow conical nozzle that sprays mist-like water at, for example, a spray angle of 60°. Each of the second nozzles 51b11, 51b12, and 51b13 is positioned vertically apart from each other.

[0070] Each second nozzle 51b11, 51b12, and 51b13 is positioned opposite each first nozzle 51a1, 51a2, and 51a3. The vertical position of each second nozzle 51b11, 51b12, and 51b13 is the same as the vertical position of each first nozzle 51a1, 51a2, and 51a3. The second nozzle 51b1 mainly sprays water onto the flow path P2, the second nozzle 51b2 mainly sprays water onto the flow path P3, and the second nozzle 51b3 mainly sprays water onto the flow path P4. Each second nozzle 51b1, 51b2, and 51b3 sprays water from the other horizontal end of the outdoor heat exchanger 13 toward the center of the outdoor heat exchanger 13.

[0071] Furthermore, the water discharge rate of each second nozzle 51b11, 51b12, and 51b13 in this embodiment is 0.10 L / min, and the droplet diameter is 75 μm or less. That is, the droplet diameter of each second nozzle 51b11, 51b12, and 51b13 located on the inside is smaller than the droplet diameter of each first nozzle 51a1, 51a2, and 51a3 located on the outside, and the water discharge rate is also set to be lower. The angle α2 of the second nozzle 51b11 with respect to the horizontal direction is, for example, 10° to 20°, the angle α3 of the second nozzle 51b12 with respect to the horizontal direction is, for example, 7° to 17°, and the angle α4 of the second nozzle 51b13 with respect to the horizontal direction is, for example, 0° to 10°.

[0072] As described above, the same effects as in Embodiment 1 can be obtained in this embodiment as well. Furthermore, when multiple heat source units 1 are connected and arranged, the watering efficiency can be improved by reducing the droplet diameter of each nozzle located in a position where the influence of external wind is small, thereby facilitating evaporation.

[0073] Furthermore, in the case where the heat source units 1 are connected and arranged as in this embodiment, and the heat source units 1 are Y-shaped as shown in Figure 5, if piping for watering is provided on the upper part of the outdoor heat exchanger 13, it is necessary to provide a gap so that the pipes do not interfere with each other when connected in the depth direction. In this case, the installation area of ​​the connected heat source units 1 increases. In contrast, with the configuration of the watering device 5B in this embodiment, there is no piping between the upper end of the outdoor heat exchanger 13 and the third pipe 50c, so the upper ends of the outdoor heat exchangers 13 can be placed close together, and the increase in installation area can be suppressed.

[0074] The above describes the embodiments, but this disclosure is not limited to the above embodiments, and can be modified or combined in various ways without departing from the spirit of this disclosure. For example, in the above embodiments, the case in which the refrigeration cycle device 100 is a heat pump chiller was described, but the refrigeration cycle device 100 may be a cooling-only unit without a cooling / heating switch, a refrigerator for cooling a cold storage warehouse, or a direct expansion type air conditioner. When the refrigeration cycle device 100 is a cooling-only unit or a refrigerator, the four-way valve 12 is omitted, the outdoor heat exchanger 13 becomes a condenser, and the indoor heat exchanger 21 becomes an evaporator.

[0075] Furthermore, the number, arrangement, angle, water flow rate, and droplet diameter of the nozzles in Embodiments 1 to 3 are examples and can be changed as needed. For example, in the configuration of the watering device 5 of Embodiment 1, the angle of each nozzle may be varied according to the wind speed distribution, or the water flow rate may be varied according to the temperature distribution. Also, in the configurations of the watering devices 5A and 5B of Embodiments 2 and 3, the angle of any or all of the first to third nozzles may be set to 0°.

[0076] Furthermore, in embodiments 2 and 3, the third pipe 50c is configured to extend horizontally along the lower end of the flow path P1 of the heat exchange section 130, but the configuration is not limited to this. The third pipe 50c may be positioned above or below the lower end of the flow path P1 of the heat exchange section 130, as long as the third nozzle 51c is in a position to spray water onto the part of the heat exchange section 130 where the air velocity and temperature are high. However, when heat source units 1 are connected and arranged as in embodiment 3, it is preferable to set the distance from the upper end of the outdoor heat exchanger 13 to the third pipe 50c to a distance that does not interfere when the heat source units 1 are connected.

[0077] Furthermore, in the sprinkler device 5B of Embodiment 3, if reducing the amount of water sprayed from each of the second nozzles 51b11, 51b12, and 51b13 located on the inside prevents achieving the desired amount of water sprayed per unit area, the number of second nozzles may be increased.

[0078] Furthermore, although the above embodiment describes a configuration in which the heat source unit 1 has four refrigerant circuits, it is not limited to this and may have three or fewer refrigerant circuits, or five or more refrigerant circuits. In addition, although the above embodiment describes a case in which the outdoor heat exchanger 13 has four flow paths P1 to P4, the number of flow paths in the outdoor heat exchanger 13 may be three or fewer, or five or more. [Explanation of Symbols]

[0079] 1 Heat source unit, 2 Indoor unit, 3 Control device, 5, 5A, 5B Sprinkler system, 6 Housing, 11 Compressor, 12 Four-way valve, 13 Outdoor heat exchanger, 14 Expansion valve, 15 Accumulator, 16 Outdoor fan, 21 Indoor heat exchanger, 22 Indoor flow rate regulator, 23 Indoor fan, 50a First piping, 50b Second piping, 50c Third piping, 51a, 51a1, 51a2, 51a3 First nozzle, 51b, 51b1, 51b2, 51b3, 51b11, 51b12, 51b13 Second nozzle, 51c Third nozzle, 52, 52a Connecting piping, 60 Water heat exchanger, 80 Pump, 100 Refrigeration cycle system, 130 Heat exchange section, 131 Heat transfer tube, 132 Fins, 133a, 133b, 133c; first header, 134a, 134b; second header, 135a, 135b; connecting piping.

Claims

1. A condenser having corrugated fins, The system includes a sprinkler for sprinkling water onto the condenser, The droplet diameter of the water sprayed by the aforementioned watering device is 160 μm or less. The aforementioned sprinkler device is Multiple first nozzles are provided, and a first pipe extends in a first direction, Multiple second nozzles are provided, and a second pipe extends in the first direction, The device is provided with a plurality of third nozzles and a third pipe extending in a second direction perpendicular to the first direction, The first and second pipes are positioned opposite each other below the third pipe. One end of the third pipe is connected to the first pipe, and the other end is connected to the second pipe. The aforementioned plurality of third nozzles spray water upward onto the condenser. A refrigeration cycle device in which the plurality of first nozzles and the plurality of second nozzles spray water toward the center of the condenser.

2. The watering rate per unit area of ​​the aforementioned sprinkler system is 1.2 ± 0.2 L / (min·m). ２ The refrigeration cycle apparatus according to claim 1, wherein the refrigeration cycle apparatus is as described in claim 1.

3. The refrigeration cycle apparatus according to claim 1 or 2, wherein the plurality of first nozzles and the plurality of second nozzles are installed at different angles according to the wind speed distribution of the air flowing into the condenser.

4. The refrigeration cycle apparatus according to claim 3, wherein the angles of the first and second nozzles with respect to the second direction, which spray water onto the portion of the plurality of first nozzles and the plurality of second nozzles in which the air velocity of the air flowing into the condenser is relatively high, are greater than the angles of the first and second nozzles with respect to the second direction, which spray water onto the portion of the plurality of first nozzles and the plurality of second nozzles in which the air velocity is relatively low.

5. The refrigeration cycle apparatus according to any one of claims 1 to 4, wherein the number of the plurality of third nozzles is greater than the number of the plurality of first nozzles and greater than the number of the plurality of second nozzles.

6. The refrigeration cycle apparatus according to any one of claims 1 to 5, wherein the amount of water sprayed by the plurality of first nozzles and the amount of water sprayed by the plurality of second nozzles are different.

7. The refrigeration cycle apparatus according to any one of claims 1 to 6, wherein the third piping is located below the upper end of the condenser.

8. The refrigeration cycle apparatus according to any one of claims 1 to 7, wherein the amount of water sprayed per unit area of ​​the sprinkler device varies according to the temperature distribution of the condenser.

9. The refrigeration cycle apparatus according to claim 8, wherein the amount of water sprayed per unit area in the part of the condenser where the temperature is relatively high is greater than the amount of water sprayed per unit area in the part of the condenser where the temperature is relatively low.

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