JP4577188B2 - Cooling system - Google Patents

Description

  The present invention relates to a cooling device that cools a high-temperature fluid by exchanging heat without mixing the high-temperature fluid and a low-temperature fluid that is lower in temperature than the high-temperature fluid. It is suitable for use in a cooling device for controlling the air temperature in the station building.

  Conventionally, as such a cooling device, a refrigeration cycle type cooling device provided with a forced circulation refrigerant circuit, a boiling type cooling device provided with a natural circulation refrigerant circuit, or a refrigeration cycle method as widely used in air conditioners and the like And a cooling device having a configuration using both a cooling method and a boiling type cooling method.

  Among these cooling devices, as a boiling type cooling device, for example, the inside of one case is basically divided into two in the vertical direction, and a low temperature fluid side heat exchanger is provided in the upper region inside the case. There is a structure in which a high-temperature fluid side heat exchanger is disposed in a lower region inside the case (for example, see Patent Document 1).

  In this cooling device, a high-temperature fluid flows into the lower half side inside the case, and heat is exchanged between the high-temperature fluid and the refrigerant in the high-temperature fluid-side heat exchanger, thereby making it possible to boil and evaporate the refrigerant. Cooling the high-temperature fluid, flowing the low-temperature fluid into the upper half of the case, and exchanging heat between the refrigerant vaporized in the high-temperature fluid-side heat exchanger and the low-temperature fluid in the low-temperature fluid-side heat exchanger Thus, the heat of the refrigerant is radiated to the low-temperature fluid by utilizing the condensation of the refrigerant.

  In addition, as a cooling device configured to use both the refrigeration cycle method and the boiling type cooling method, for example, a cooling device for boiling type cooling and an evaporator for the refrigeration cycle are accommodated in one indoor unit, There is a structure in which a condenser for boiling cooling and a condenser for a refrigeration cycle are housed in separate outdoor units.

With a cooling system that uses both cooling systems, the cooling capacity of the boiling system is high when the outside air temperature is low, and the cooling of the refrigeration cycle system can be stopped or reduced. Compared with the device, power consumption can be reduced.
JP-A-10-190270 JP 2001-041503 A

  By the way, the cooling method of the cooling device is usually selected according to the temperature of the environment in which the cooling device is used.

  However, as described above, in the conventional cooling device, when the cooling method is different, the structure of the cooling device is greatly different. Therefore, the structure of the installation location of the cooling device is different depending on the cooling method. In other words, conventionally, cooling devices with different cooling methods have not been compatible.

  For this reason, the structure of the installation location of the cooling device has to be changed according to the environment in which the cooling device is used.

  An object of this invention is to provide the cooling device which can select a cooling system, without changing the structure of the installation place of a cooling device in view of the said point.

  In order to achieve the above object, the present invention provides a case (11, 70) in which a high temperature fluid side channel (31) and a low temperature fluid side channel (32) are provided, and a high temperature fluid side channel ( 31) first and second high temperature fluid side heat exchangers (12b, 12a) and first and second low temperature fluid side heat exchangers (32) arranged in the low temperature fluid side flow path (32). 13b, 13a), and the first refrigerant by the first high temperature fluid side heat exchanger (12b), the first low temperature fluid side heat exchanger (13b) and the first refrigerant pipe (44b, 45b). The circuit is configured, and the second refrigerant circuit is constituted by the second high-temperature fluid side heat exchanger (12a), the second low-temperature fluid side heat exchanger (13a), and the second refrigerant pipes (44a, 45a). It is characterized by comprising.

  In addition, as a 1st, 2nd refrigerant circuit, a refrigerant | coolant is boiled and vaporized with a high temperature fluid side heat exchanger, a refrigerant | coolant is condensed with a low temperature fluid side heat exchanger, and a refrigerant | coolant is naturally circulated using the density difference of a refrigerant | coolant. Uses a cooling-type refrigerant circuit that uses a boiling heat exchange cycle, or forcibly circulates the refrigerant using a compressor, dissipates high-temperature and high-pressure refrigerant in the low-temperature fluid side heat exchanger, and Cooling type refrigerant circuit using a refrigeration cycle that absorbs low-temperature and low-pressure refrigerant with a heat exchanger, cooling type refrigerant circuit using a boiling type heat exchange cycle, and cooling type using a refrigeration cycle Both refrigerant circuits can be used.

  Thus, in the present invention, the structure of the cooling device is a structure in which at least two refrigerant circuits are housed in one case.

  As a result, as described above, either the boiling cooling type or the refrigeration cycle can be selected as the type of the high temperature fluid side heat exchanger and the low temperature fluid side heat exchanger, or a decompression expansion valve or a compression can be used in the refrigerant circuit. By selecting whether or not to add a machine or the like, the cooling method of the cooling device can be arbitrarily selected without changing the structure of the case.

  As a result, according to the cooling device of the present invention, the case structure of the cooling devices of each cooling method can be shared, so that the cooling method can be selected without changing the structure of the installation location of the cooling device. It becomes possible.

Moreover, in this invention, the following structures are employ | adopted as a specific structure of a cooling device.
That is, the first refrigerant circuit is a natural circulation refrigerant circuit, and the second refrigerant circuit is a forced circulation refrigerant circuit that forcibly circulates the refrigerant using the compressor (47),
In the high temperature fluid side channel (31), the ventilation surfaces (12d, 12c) of the first and second high temperature fluid side heat exchangers (12b, 12a) face each other, and the first high temperature fluid side heat exchange is performed. The vessel (12b) is located upstream of the second hot fluid side heat exchanger (12a) in the hot fluid flow,
In the low temperature fluid side flow path (32), the ventilation surfaces (13d, 13c) of the first and second low temperature fluid side heat exchangers (13b, 13a) face each other, and the first low temperature fluid side heat exchange is performed. The vessel (13b) is arranged on the upstream side of the low temperature fluid flow with respect to the second low temperature fluid side heat exchanger (13a).
Further, as the case (11), for example, the shape of the cross section is a shape in which the length in the first direction is shorter than the length in the second direction orthogonal to the first direction, and the high temperature fluid It is possible to use the side flow path (31) and the low temperature fluid side flow path (32) provided in the case (11) side by side in the second direction.

  In addition, the code | symbol in the bracket | parenthesis of each means described in the claim and this column is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

(First embodiment)
In the present embodiment, a base station cooling device that cools the inside of a mobile phone base station in which communication equipment and the like are housed will be described as an example.

  1A to 1D show the overall configuration of the cooling device according to the first embodiment of the present invention. Moreover, in FIG. 2, the installation state to the station building of a cooling device is shown. FIG. 1A is a diagram showing an internal configuration when the cooling device is viewed from the front, and FIGS. 1B and 1C show the cooling device in FIG. FIG. 1D is a diagram showing an internal configuration when viewed in the B direction, and FIG. 1D is a diagram showing an arrangement of the inside air side heat exchanger 12 and the outside air side heat exchanger 13 when the cooling device is seen from above. It is. Moreover, in FIG. 1 (a)-(c) and FIG. 2, the up-down direction of a figure is a top-down direction of a cooling device.

  As shown in FIG. 2, the cooling device 1 of this embodiment is attached to the door 3 of the station 2 as a housing. When the door 2 is in a closed state, the inside of the station building 2 is sealed from the outside. In addition, a communication device 6 for communicating with a mobile phone 5 or the nearest exchange station via the antenna 4 is housed inside the station building 2, and when this communication device 6 is operated, The communication device 6 generates heat, and the temperature of the internal air (inside air) of the station building 2 rises. In this embodiment, this inside air corresponds to a high-temperature fluid, and the outside air (outside air) of the station 2 corresponds to a low-temperature fluid.

  The cooling device 1 of the present embodiment performs a boiling type cooling operation including a natural circulation refrigerant circuit and a vapor compression refrigeration cycle type cooling operation including a forced circulation refrigerant circuit simultaneously or by switching. Specifically, the boiling cooling method has no particular ON / OFF control, and the cooling performance is gradually reduced due to the temperature difference between the inside air and the outside air, and the refrigeration cycle method performs switching operation by controlling the decompression expansion valve and the compressor.

  Specifically, the cooling device 1 includes, as shown in FIGS. 1A to 1C, one case 11, two inside air heat exchangers 12 housed in the case 11, and two The outside air heat exchanger 13, one inside air fan 14, and one outside air fan 15 are mainly configured.

  The case 11 is a rectangular parallelepiped, and as shown in FIG. 1A, when the case 11 is viewed from the front, the front surface 21, the rear surface 22 positioned on the back side of the front surface 21, and the left side of the front surface 21. It has a left side surface 23, a right side surface 24 positioned on the right side of the front surface 21, an upper surface 25 positioned on the upper side of the front surface 21, and a lower surface 26 positioned on the lower side of the front surface 21.

  In addition, the width of the case 11 in the depth direction in FIG. 1A, that is, the width in the direction perpendicular to the front surface 21 and the back surface 22 is smaller than the other width of the case 11. A direction perpendicular to the front surface 21 and the back surface 22 is referred to as a thickness direction of the case 11. Further, the left-right direction toward the front surface 21 in FIG.

  In the present embodiment, as shown in FIG. 1 (d), the shape of the cross section of the case 11 is such that the length in the thickness direction of the case 11 is the right and left direction of the case 11 orthogonal to the thickness direction. The shape is shorter than the length. In addition, the cross section of case 11 means the cross section in the up-down direction of case 11, ie, a direction perpendicular | vertical to a top-and-bottom direction. Further, the thickness direction and the left-right direction of the case 11 in the present embodiment correspond to the first direction and the second direction described in the claims, respectively.

  Further, as shown in FIG. 2, the cooling device 1 is attached to the door 3 of the station 2 so that the back surface 22 of the case 11 faces the inside of the station building 2 and the front surface 21 faces the outside of the station building 2. It is supposed to be. That is, the thickness direction of the case 11 is the direction in which the cooling device 1 is attached to the station 2.

  Further, as shown in FIG. 1A, the inside of the case 11 is divided into two regions in the left-right direction of the case 11 by a partition wall 27. The partition wall 27 has a shape along the inside of the case 11 and is a substantially rectangular flat plate. The partition wall 27 is disposed perpendicular to the front surface 21, the back surface 22, the upper surface 25, and the lower surface 26 of the case 11 so as to be parallel to the vertical direction.

  Here, FIG. 3 shows a cross-sectional view of the case 11 when the case 11 is viewed from above. As shown in FIG. 3, the case 11 includes a left side 23, a left half of the front surface 21 in the drawing and a U-shaped metal plate that forms the partition wall 27, and a right half and right side surface 24 of the front surface 21 in the drawing. The L-shaped metal plate and the flat metal plate constituting the back surface 22 are fixed to each other using pins or the like.

  In addition, these metal plates are comprised, for example with iron. In addition, each metal plate has its end folded so that the metal plates are joined face to face, and a packing 28 is sandwiched between the metal plates. Yes. Furthermore, waterproofing is performed so that water does not enter from the joint between the metal plate and the metal plate by closing the gap between the metal plate with a sealant.

  Moreover, in this embodiment, the left side in FIG. 1A is the inside air side region 31 in the internal space of the case 11, which is an inside air flow path through which the inside air of the station building 2 circulates, and in FIG. The right side is an outside air side region 32, which is an outside air flow path through which the outside air of the station building 2 flows. In addition, the inside air side area | region 31 and the outside air side area | region 32 are respectively corresponded to the high temperature fluid side flow path and the low temperature fluid side flow path as described in a claim.

  As shown in FIG. 1A, in the inside air region 31, the inside air side heat exchanger 12 is arranged below the case 11, and the inside air fan 14 is arranged above the case 11. On the other hand, in the outside air region 32, the outside air heat exchanger 13 is disposed above the case 11, and the outside air fan 15 is disposed below the case 11.

  That is, in this embodiment, when the cooling device 1 is viewed from the front, the inside air-side heat exchanger 12 and the outside air-side heat exchanger 13 are respectively arranged diagonally in the lower left and upper right inside the case, The inside-air fan 14 and the outside-air fan 15 are arranged in diagonal directions, that is, upper left and lower right inside the case, respectively.

  One of the two room air side heat exchangers 12 is an inside air side heat exchanger (boiler) 12b for boiling cooling, and the other is an room air side heat exchanger (evaporator) 12a for a refrigeration cycle. In this embodiment, as shown in FIGS. 1B and 1D, the inside air side heat exchanger 12a for the refrigeration cycle is closer to the back surface 22 of the case 11 than the inside air side heat exchanger 12b for boiling cooling. Placed in position.

  Both of the two inside air heat exchangers 12a and 12b have substantially rectangular parallelepiped shapes and the same shape. The two inside air side heat exchangers 12a and 12b have widths in the direction perpendicular to their ventilation surfaces 12c and 12d (thickness of the inside air side heat exchanger 12) other than the inside air side heat exchanger 12. This is a thin plate shape that is thinner than the case 11 and thinner than the case 11. The ventilation surfaces 12c and 12d are surfaces through which the inside air passes, and face the flow of the inside air.

  The two inside air side heat exchangers 12a and 12b have the same shape and size of the ventilation surfaces 12c and 12d, and the ventilation surfaces 12c and 12d are aligned and substantially parallel to each other. It arrange | positions so that it may become substantially parallel to the back surface 22.

  Further, the total thickness of the two inside air heat exchangers 12 a and 12 b is not more than half the thickness of the case 11. The two inside air heat exchangers 12 a and 12 b are arranged on the back surface 22 side of the case 11 in the thickness direction of the case 11. In this embodiment, the space | interval of the back surface 22 and the internal air side heat exchanger 12a for refrigeration cycles is shorter than the thickness of the internal air side heat exchanger 12a for refrigeration cycles.

  The two inside air heat exchangers 12a and 12b are also arranged close to each other, and the distance between the two inside air heat exchangers 12a and 12b is the thickness of the two inside air heat exchangers 12a and 12b. Less than the sum of

  Further, as shown in FIGS. 1B and 2, the inside air intake is taken into the back surface 22 of the case 11 at a position facing the inside air fan 14 and a position facing the inside air heat exchanger 12, respectively. Openings 22a and 22b serving as mouths and inside air discharge ports are provided.

  Thereby, as shown in FIG. 1B and FIG. 2, the inside air is taken in from the inside air intake port 22 a located above the case 11, flows in the inside air side region 31 from the top to the bottom, The inside air discharge port 22b located below is discharged. For this reason, as shown in FIG. 2, the inside air of the station building 2 flows inside the station building 2 so as to make a U-turn inside the cooling device 1.

  One of the two outside air side heat exchangers 13 is an outside air side heat exchanger (condenser) 13b for boiling cooling, and the other is an outside air side heat exchanger (condenser) 13a for the refrigeration cycle. In this embodiment, as shown in FIGS. 1C and 1D, the outside air side heat exchanger 13a for the refrigeration cycle is closer to the front surface 21 of the case 11 than the outside air side heat exchanger 13b for boiling cooling. Placed in position.

  The two outdoor air side heat exchangers 13a and 13b have a rectangular parallelepiped shape and the same shape. The two outside air heat exchangers 13a and 13b have a width in the direction perpendicular to their ventilation surfaces 13c and 13d (thickness of the outside air heat exchanger 13) smaller than the width in the other direction. It is a thin plate shape thinner than the thickness of the case 11.

  The two outdoor air side heat exchangers 13a and 13b have the same shape and size of the ventilation surfaces 13c and 13d, the ventilation surfaces 13c and 13d are aligned, substantially parallel to each other, and the case 11 are arranged so as to be substantially parallel to the front surface 21 of the eleventh surface.

  Further, the total thickness of the two outdoor air side heat exchangers 13 a and 13 b is half or less than the thickness of the case 11. The two outside air side heat exchangers 13 a and 13 b are arranged closer to the front surface 21 than the center of the case 11 in the thickness direction of the case 11. In the present embodiment, the distance between the front surface 21 and the outside air side heat exchanger 13a for the refrigeration cycle is shorter than the thickness of the outside air side heat exchanger 13a for the refrigeration cycle.

  Further, the two outdoor air side heat exchangers 13a and 13b are also close to each other, and the interval between the two outdoor air side heat exchangers 13a and 13b is larger than the total thickness of the two outdoor air side heat exchangers 13a and 13b. It is getting smaller.

  Thus, in this embodiment, the inside air side heat exchanger 12 and the outside air side heat exchanger 13 are located on the front side of the case 11 when viewed from the upper surface side of the case 11 as shown in FIG. On the other hand, it is arranged in the diagonal direction inside the case on the back left side and the front right side.

  Moreover, as shown in FIG.1 (c), in the front surface 21 of case 11, the position which opposes the fan 15 for external air, and the position which opposes the external air side heat exchanger 13, respectively, an external air intake, Openings 21a and 21b serving as outside air discharge ports are provided.

  As a result, as shown in FIG. 1 (c), outside air is taken in from the outside air intake port 21 a located below the case 11, flows in the outside air side region 32 from below to above, and is located above the case 11. It is discharged from the outside air outlet 21b. As described above, the cooling device 1 of the present embodiment is a refrigerant circuit including the inside air-side heat exchanger 12 and the outside air-side heat exchanger 13 by flowing the inside air and the outside air facing each other inside the case 11. Counterflow heat exchange is performed.

  As described above, in the present embodiment, the inside air fan 14 is disposed on the upstream side of the inside air flow path (inside air flow), and the inside air heat exchanger 12 is disposed on the downstream side of the inside air flow path. . The outside air fan 15 is disposed upstream of the outside air flow path (outside air flow), and the outside air heat exchanger 13 is disposed downstream of the outside air flow path.

  Further, in the two inside air side heat exchangers 12a and 12b, the inside air side heat exchanger 12b for boiling cooling is disposed on the upstream side of the inside air flow path with respect to the inside air side heat exchanger 12a for the refrigeration cycle. . Similarly, also in the two outdoor air side heat exchangers 13a and 13b, the outdoor air side heat exchanger 13b for boiling cooling is disposed upstream of the outdoor air flow path with respect to the outdoor air side heat exchanger 13a for the refrigeration cycle. Yes.

  In this embodiment, a push-type centrifugal fan is used as the inside air fan 14 and the outside air fan 15.

  Thus, by using a push-in fan, the heat exchangers 12 and 13 can be arranged on the downstream side of the inside air and outside air flows in the inside air region 31 and the outside air region 32. By using a centrifugal fan, the suction and discharge flows of the fan can be bent to 90 degrees. Therefore, when flowing the inside air and the outside air in a U-turn with the cooling device 1, the bending pressure loss of the inside air and the outside air flow is reduced. Can be reduced. As a result, according to the present embodiment, compared to a case where no centrifugal fan is used, noise generated by the blowing of the inside air fan 14 and the outside air fan 15 can be reduced, and power consumption can be reduced.

  Further, in the present embodiment, as shown in FIG. 1B, the inside air region 31 is upstream of the inside air flow of the inside air side heat exchanger 12, and the inside air with respect to the inside air side heat exchanger 12. A heater 41 is disposed above the center of the side heat exchanger 12. The heater 41 is for making the inside air temperature of the station building 2 be equal to or higher than a lower limit temperature such as 0 ° C.

  Moreover, the temperature sensor 42 for inside air is arrange | positioned in the downstream of the inside air flow of the inside air side heat exchanger 12, and the vicinity of the inside air discharge port 11b.

  Further, as shown in FIG. 1C, the outside air region 32 has an outside air flow downstream of the outside air fan 15 and downstream of the outside air heat exchanger 13. A temperature sensor 43 is arranged.

  The temperature of the inside air and the outside air is detected by the inside and outside temperature sensors 42 and 43, and the operation of the inside air fan 14, the outside air fan 15 and the heater 41 is controlled by a control device (not shown) based on the detection result. To be controlled.

  In addition, as shown in FIGS. 1A and 1B, the inside air side region 31 is connected to an inside air side heat exchanger 12b for boiling cooling and an outside air side heat exchanger 13b for boiling cooling. A gas pipe 44b for boiling cooling that constitutes the flow path of the phase refrigerant is disposed.

  In addition, the inside air region 31 is connected to the inside air side heat exchanger 12a for the refrigeration cycle and the outside air side heat exchanger 13a for the refrigeration cycle, and the liquid piping for the refrigeration cycle constituting the flow path of the liquid phase refrigerant. 45a is arranged. A decompression expansion valve 46 is provided in the middle of the liquid pipe 45a.

  On the other hand, as shown in FIGS. 1A and 1C, the outside air region 32 is connected to an inside air side heat exchanger 12b for boiling cooling and an outside air side heat exchanger 13b for boiling cooling. The liquid piping 45b for boiling cooling which comprises the flow path of a phase refrigerant is arrange | positioned.

  In addition, the outside air region 32 is connected to the inside air side heat exchanger 12a for the refrigeration cycle and the outside air side heat exchanger 13a for the refrigeration cycle, and the gas piping for the refrigeration cycle constituting the flow path of the gas phase refrigerant. 44a is also arranged. A compressor 47 is provided in the middle of the gas pipe 44a.

  In the present embodiment, as shown in FIG. 1 (d), the inside air side heat exchanger 12 b and the outside air side heat exchanger 13 b for boiling cooling are disposed on the center side of the case 11 in the thickness direction of the case 11. The inside air side heat exchanger 12 a and the outside air side heat exchanger 13 a for the refrigeration cycle are arranged outside the case 11.

  For this reason, as shown in FIG. 1B, the gas pipe 44 b for boiling cooling and the liquid pipe 45 a for the refrigeration cycle are crossed and arranged in the inside air region 31. Further, as shown in FIG. 1C, the liquid piping 45b for boiling cooling and the gas piping 44a for the refrigeration cycle are also crossed and arranged in the outside air region 32.

  In addition, as gas piping 44a, 44b and liquid piping 45a, 45b, piping generally used in the heat exchanger which circulates a refrigerant | coolant can be used, for example, it is comprised with the metal material.

  In the present embodiment, the refrigerant circulates between the inside air side heat exchanger 12b and the outside air side heat exchanger 13b for boiling cooling via the gas pipe 44b and liquid pipe 45b for boiling cooling arranged in this way. It is supposed to be. Similarly, the refrigerant circulates between the inside air side heat exchanger 12a and the outside air side heat exchanger 13a for the refrigeration cycle via the gas pipe 44a and the liquid pipe 45a for the refrigeration cycle.

  Thus, as shown in FIG. 4, the cooling device 1 of the present embodiment includes an inside air side heat exchanger 12b and an outside air side heat exchanger 13b for boiling cooling, a gas pipe 44b for boiling cooling, and a liquid pipe 45b. A closed boiling cooling type refrigerant circuit is formed, and the inside air side heat exchanger 12a and the outside air side heat exchanger 13a for the refrigeration cycle, the gas pipe 44a and the liquid pipe 45a for the refrigeration cycle, the decompression expansion valve 46, the compression The machine 47 forms a sealed vapor compression refrigeration cycle type refrigerant circuit. FIG. 4 shows a schematic configuration of the refrigerant circuit provided in the cooling device of the present embodiment.

  In this embodiment, the refrigerant circuit of the boiling cooling system, the inside air side heat exchanger 12b for boiling cooling, the outside air side heat exchanger 13b for boiling cooling, the gas pipe 44b for boiling cooling, and the liquid pipe 45b are respectively provided. This corresponds to the first refrigerant circuit, the first high-temperature fluid side heat exchanger, the first low-temperature fluid side heat exchanger, and the first refrigerant pipe described in the claims.

  Further, a refrigerant circuit of a vapor compression refrigeration cycle system, an inside air side heat exchanger 12a for a refrigeration cycle, an outside air side heat exchanger 13a for a refrigeration cycle, a gas pipe 44a and a liquid pipe 45a for a refrigeration cycle, respectively, are patented. This corresponds to the second refrigerant circuit, the second high-temperature fluid side heat exchanger, the second low-temperature fluid side heat exchanger, and the second refrigerant pipe described in the claims.

  FIG. 5 shows a cross-sectional view of the inside air side heat exchanger 12b, the outside air side heat exchanger 13b, the gas pipe 44b, the liquid pipe 45b, and the partition wall 27 of the case 11 constituting a boiling cooling type refrigerant circuit. FIG. 5 is a longitudinal sectional view when the case 11 is cut in a plane direction parallel to the front surface 21. 6 is a cross-sectional view taken along line AA in FIG. 5, and FIG. 7 is an enlarged view of a region B surrounded by a broken line in FIG.

  As shown in FIG. 5, the inside air side heat exchanger 12b and the outside air side heat exchanger 13b for boiling cooling are both multi-flow path type heat exchangers, and include a plurality of multi-hole tubes 51 extending in the vertical direction. Both ends are connected to the upper communication portion 52 and the lower communication portion 53 extending in the left-right direction of the case 11, and the fins 54 are arranged between the multi-hole tubes 51.

  As shown in FIG. 6, the multi-hole tube 51 is a tube in which a large number of flow paths 55 are arranged in parallel in the direction perpendicular to the paper surface of FIG. 5. The size is equivalent to the width of bubbles generated from the refrigerant. For example, corrugated fins are used as the fins 54.

  In addition, the multi-hole tube 51, the upper side communication part 52, and the lower side communication part 53 are comprised with the metal material excellent in thermal conductivity, such as aluminum and copper.

  Further, as shown in FIG. 5, the length in the vertical direction of the inside air side heat exchanger 12b is equal to the length of the lower half of the case 11, and the length in the vertical direction of the outside air side heat exchanger 13b is 11 is longer than the upper half of 11. For this reason, a part of the outside air side heat exchanger 13 b overlaps with the inside air side heat exchanger 12 b in the vertical direction of the case 11.

  As shown in FIG. 5, the gas pipe 44 has one end connected to the upper surface of the upper communication portion 52 of the inside air side heat exchanger 12b and the other end connected to the side surface of the upper communication portion 52 of the outside air side heat exchanger 13b. It is connected. On the other hand, one end of the liquid pipe 45 is connected to the side surface of the lower communication portion 53 of the inside air heat exchanger 12b, and the other end is connected to the lower surface of the lower communication portion 53 of the outside air heat exchanger 13b.

  Further, as shown in FIG. 7, the gas pipe 44 passes through the partition wall 27 through a hole 27 a provided in the partition wall 27 through a connecting portion 61 as a waterproof means.

  The connecting part 61 is made of rubber, for example, and seals the gap between the partition wall 27 and the gas pipe 44. Further, in the present embodiment, the waterproof treatment is performed by applying the sealing agent 62 between the connecting portion 61 and the gas pipe 44. Note that the liquid pipe 45 also penetrates the partition wall 27 in the same manner as the gas pipe 44.

  In the boiling cooling type refrigerant circuit having the above-described configuration, in the inside air side heat exchanger 12b, the inside air having a temperature higher than the outside air via the fins 54, the liquid phase refrigerant sealed in the multi-hole tube 51, and Heat is exchanged between the two. As a result, the liquid-phase refrigerant boils and bubbles are generated in the multi-hole tube 51 as shown in FIG. 5, that is, a gas-phase refrigerant is formed, and the inside air is cooled.

  On the other hand, in the outside air side heat exchanger 13 b, heat exchange is performed between the outside air having a temperature lower than that of the inside air and the gas-phase refrigerant sealed in the multi-hole tube 51 through the fins 54. As a result, the gas-phase refrigerant is condensed into droplets, that is, a liquid-phase refrigerant, and the heat of the refrigerant is radiated to the outside air.

  At this time, since the outside air side heat exchanger 13b is disposed above the inside air side heat exchanger 12b, in the boiling cooling type refrigerant circuit, due to the density difference between the gas phase refrigerant and the liquid phase refrigerant, the refrigerant is Natural circulation in the order of inside air side heat exchanger 12b → gas pipe 44b → outside air side heat exchanger 13b → liquid pipe 45b → inside air side heat exchanger 12b (clockwise in FIG. 1 (a) and FIG. 5) To do.

  Further, in the present embodiment, the inside air side heat exchanger 12a and the outside air side heat exchanger 13a constituting the refrigerant circuit of the refrigeration cycle system are the same as the inside air side heat exchanger 12b and the outside air side heat exchanger 13b for boiling cooling. In addition, a multi-flow path type heat exchanger is used. Since these internal structures are the same as those of the above-described inside air side heat exchanger 12b and the outside air side heat exchanger 13b for boiling cooling, description thereof is omitted here.

  In the refrigerant circuit of the refrigeration cycle system, the refrigerant flows in the counterclockwise direction from the compressor 47 in FIG. That is, the compressor 47 → the gas pipe 44a → the outside air side heat exchanger 13a → the liquid pipe 45a → the pressure reducing expansion valve 46 → the inside air side heat exchanger 12a → the liquid pipe 45a → the inside air side heat exchanger 12a → the gas pipe 44a → the compressor. In the order of 47, the refrigerant is forcedly circulated by the compressor 47.

  At this time, the high-temperature and high-pressure refrigerant is discharged from the compressor 47, and the refrigerant compressed by the compressor 47 is condensed in the outside air side heat exchanger (condenser) 13a. Then, the condensed refrigerant is decompressed and expanded by the decompression expansion valve 46, and the interior air is cooled by evaporating the decompressed and expanded refrigerant by the interior air side heat exchanger (evaporator) 12a.

  In the cooling device 1 of the present embodiment, based on the temperature difference between the inside air and the outside air, a boiling type cooling operation including a natural circulation refrigerant circuit and a vapor compression refrigeration cycle type cooling operation including a forced circulation refrigerant circuit are performed. , To switch and do. For example, in summer and winter, night and daytime, when the temperature of the outside air may be high or low, cooling operation of the refrigeration cycle method is performed when the outside air is high, and boiling method is used when the temperature of the outside air is low Perform cooling operation.

  Thereby, since the operation of the compressor 47 can be stopped at the time of the boiling type cooling operation, it is possible to reduce the power consumption of the cooling device as compared with the cooling device that performs only the cooling operation of the refrigeration cycle method. it can. In addition, it can also be operated together.

  In the present embodiment, the partition wall 27 is made of a metal material, and the inside air and the outside air flow in the inside air side region 31 and the outside air side region 32, respectively. Direct heat exchange is also performed between the inside air and the outside air. The cooling device 1 of this embodiment cools the inside air of the station 2 by this heat exchange.

  Next, main effects of the cooling device of this embodiment will be described.

  (1) The cooling device of the present embodiment includes a case 11 in which an inside air side region 31 through which the inside air flows and an outside air side region 32 through which the outside air flows are arranged side by side in the left-right direction of the case 11; The two inside air side heat exchangers 12 arranged in 31 and the two outside air side heat exchangers 13 arranged in the outside air region 32 are provided.

  One of the two room air side heat exchangers 12 is an inside air side heat exchanger (boiler) 12b for boiling cooling, and the other is an room air side heat exchanger (evaporator) 12a for a refrigeration cycle. The two outside air heat exchangers 13 are an outside air heat exchanger (condenser) 13b for boiling cooling, and the other is an outside air heat exchanger (condenser) 13a for the refrigeration cycle. .

  The inside air side heat exchanger (boiler) 12b and the outside air side heat exchanger (condenser) 13b for boiling cooling are connected by a gas pipe 44b and a liquid pipe 45b, and thereby, a refrigerant circuit of a boiling cooling system. Is configured.

  The inside air side heat exchanger (evaporator) 12a and the outside air side heat exchanger (condenser) 13a for the refrigeration cycle are connected by a gas pipe 44a and a liquid pipe 45a, and are compressed in the middle of the gas pipe 44a. The pressure reduction expansion valve 46 is provided in the middle of the liquid piping 45a, and the refrigerant circuit of the refrigerating cycle system is comprised by these.

  Here, in the conventional cooling device for mobile phone base stations, as described in the above section, the refrigeration cycle cooling device, the boiling cooling device, and the combined cooling device using both are installed. There was no compatibility.

  For this reason, communication needs to provide a common service in countries around the world. In some countries, it is desirable to use the same base station from a hot area to a cold area. It was necessary to unify the method with the refrigeration cycle method or to develop a base station with a structure corresponding to the cooling method for each installation area. In the latter case, the maintenance method and supplies are completely different for each installation area even during the maintenance service, which is a heavy burden.

  On the other hand, in the cooling device of the present embodiment, as in the second and third embodiments described later, the gas pipe 44 and the liquid pipe 45 are replaced with each other in the refrigerant circuit of the present embodiment, or the reduced pressure expansion is performed. By adding or deleting the valve 46 and the compressor 47, the type of the two refrigerant circuits can be changed from the combined type to the refrigeration cycle type only or the boiling type.

  Thereby, the cooling system of the cooling device can be arbitrarily selected without changing the structure of the case 11. Therefore, according to the cooling device of this embodiment, since the case structure of the cooling device of each cooling method can be shared, the structure of the base station building 2 of the base station is made to be a common specification regardless of the type of the cooling method. can do.

  As a result, it is possible to select the cooling method of the cooling device according to the climate of each place without changing the structure of the base station station 2.

  (2) In the present embodiment, the decompression expansion valve 46 is disposed in the inside air region 31. In this way, by arranging the pressure reducing expansion valve 46, which is an important functional component in the refrigeration cycle, in the inside air side region 31 separated from the outside air, the pressure reducing expansion valve 46 is exposed to the outside air, and the pressure reducing expansion valve 46 becomes Dirty and corroded can be prevented.

  (3) In the present embodiment, in the two inside air heat exchangers 12a and 12b, the inside air side heat exchanger 12b for boiling cooling is positioned upstream of the inside air flow path from the inside air side heat exchanger 12a for the refrigeration cycle. Is arranged.

  By arranging in this way, after the inside air is cooled by the inside air side heat exchanger 12b for boiling cooling without using the compressor 47, the inside air after the cooling is used for the refrigeration cycle in which the compressor 47 is operated. It can cool with the inside air side heat exchanger 12a.

  Thereby, compared with the case where these heat exchangers are arrange | positioned in the opposite position, since the cooling operation rate by a refrigerating cycle system can be reduced, the power consumption of the compressor 47 can be reduced.

  Further, in the present embodiment, in the two outdoor air side heat exchangers 13a and 13b, the outside air side heat exchanger 13b for boiling cooling is disposed upstream of the outside air flow path from the outside air side heat exchanger 13a for the refrigeration cycle. Is arranged.

  In this case, the outside air side heat exchanger 13b for boiling cooling serves as a filter for capturing dust and the like in the outside air with respect to the outside air side heat exchanger 13a for the refrigeration cycle.

  Here, in the cooling device of the present embodiment, in the cooling operation of the boiling cooling method and the cooling operation of the refrigeration cycle method, the cooling operation of the refrigeration cycle method that can exhibit the capability is more important even when the outside air temperature is high. It is a function.

  Therefore, according to this embodiment, it is possible to protect the outside air side heat exchanger 13a that performs the refrigeration cycle from adhesion of contaminants in the outside air, corrosion due to the adhesion, and damage due to the entry of foreign matter contained in the outside air. It is possible to prevent the performance deterioration of the cycle type cooling operation.

  (4) In the present embodiment, the two inside air side heat exchangers 12a and 12b have the same shape and size of the ventilation surfaces 12c and 12d, the ventilation surfaces 12c and 12d are aligned, It arrange | positions so that it may become substantially parallel. Moreover, the space | interval of the two inside air side heat exchangers 12 is smaller than the sum total of the thickness of the two inside air side heat exchangers 12a and 12b.

  Similarly, the two outdoor air side heat exchangers 13a and 13b have the same shape and size of the ventilation surfaces 13c and 13d, and the ventilation surfaces 13c and 13d are aligned so as to be substantially parallel to each other. Is arranged. The interval between the two outside air heat exchangers 13a and 13b is smaller than the total thickness of the two outside air heat exchangers 13a and 13b.

  Thus, the ventilation resistance in the heat exchangers 12a and 13a of the refrigeration cycle system arranged on the downstream side is obtained by arranging the two heat exchangers in the same air passage with the ventilation surfaces aligned and close to each other. Can be reduced. Thereby, compared with the case where two heat exchangers are not arranged in this way, when the same amount of inside air or outside air flows in the case 11, the work of blowing air by the inside air and outside air fans 14 and 15 is reduced. Can be reduced. As a result, the power consumption of the inside air and outside air fans 14 and 15 can be reduced, and the noise caused by the blowing of the inside air and outside air fans 14 and 15 can be reduced.

  In addition, in this embodiment, the shape and magnitude | size of the ventilation surface 12c, 12d of the two inside air side heat exchangers 12a, 12b are the same, and arrange | positioning those ventilation surfaces 12c, 12d, and two inside air side heat exchangers Although the case where 12a and 12b are arrange | positioned was demonstrated as an example, the shape and magnitude | size of these ventilation surfaces 12c and 12d may be varied, or these ventilation surfaces 12c and 12d may be shifted in a parallel state. it can. In this case, if at least a part of these ventilation surfaces 12c and 12d are opposed to each other, the above-described effect can be obtained as compared with the case where they are not opposed. The same applies to the two outside air heat exchangers 13a and 13b.

  (5) In the present embodiment, the inside air side region 31 through which the inside air flows and the outside air side region 32 through which the outside air flows are provided in parallel in the left-right direction of the case 11 in one case 11.

  Here, in recent years, due to the relationship between installation properties, frequency bands, and communication capacity, there is an increasing need for small and medium-sized base stations instead of conventional large base stations. In the case of a small and medium-sized base station, an indoor unit, an outdoor unit for a refrigeration cycle, and an outdoor unit for a boiling type are separately provided as in the cooling device of Patent Document 2 described in the above-mentioned prior art section. Is difficult due to cost, maintainability, and mountability to a base station.

  On the other hand, in the present embodiment, the internal structure of the case 11 is a structure in which the inside air side region 31 and the outside air side region 32 are arranged in parallel in the left-right direction of the case 11, and one case 11 has a refrigeration cycle system. A refrigerant circuit and a boiling type refrigerant circuit are accommodated.

  Therefore, according to this embodiment, the mountability to the base station can be improved as compared with the cooling device of Patent Document 2 described above.

  Further, according to the cooling device 1 of the present embodiment, compared to the cooling device shown in FIG. 14 described in the fifth embodiment, the two flow paths are arranged inside the case 11 in the thickness direction of the case. Thus, for example, when the width in the case thickness direction of each flow path in both cooling apparatuses is the same, the thickness of the case 11 can be reduced. Therefore, it can be said that the cooling device 1 of this embodiment is a structure suitable for thickness reduction rather than the cooling device in which the two flow paths are arranged inside the case 11 in the thickness direction of the case.

  Further, when two flow paths are arranged in the left-right direction of the case 11 as in the present embodiment, the layout of the gas pipe 44 and the liquid pipe 45 can be freely compared with the case where the two flow paths are arranged vertically. The gas pipe 44 and the liquid pipe 45 can be arranged in a simple state.

  (6) In this embodiment, the inside air side heat exchanger 12b for boiling cooling is disposed below the inside air region 31 of the case 11, and the outside air side heat for boiling cooling is disposed above the outside air region 32 of the case 11. An exchanger 13b is arranged. That is, when the cooling device 1 is viewed from the front, the inside air-side heat exchanger 12b and the outside air-side heat exchanger 13b are arranged diagonally in the lower left and upper right inside the case, respectively.

  Thereby, the refrigerant is naturally circulated using the density difference of the refrigerant.

  In the present embodiment, the inside air fan 14 is disposed above the inside air region 31 of the case 11, and the outside air fan 15 is disposed below the outside air region 32 of the case 11. That is, when the cooling device 1 is viewed from the front, the inside air fan 14 and the outside air fan 15 are arranged diagonally in the upper left and lower right inside the case, respectively.

  Further, in the back surface 22 of the case 11, an inside air intake port 22 a is provided at a position facing the inside air fan 14, and an inside air discharge port 22 b is provided at a position facing the inside air side heat exchanger 12. In addition, an outside air inlet 21 a is provided at a position facing the outside air fan 15 on the front surface 21 of the case 11, and an outside air outlet 21 b is provided at a position facing the outside air heat exchanger 13.

  As a result, in the inside air region 31, the inside air flowing in from the inside air intake port 22a flows from top to bottom and is discharged from the inside air take-out port 22b. It is made to flow like a U-turn.

  On the other hand, in the outside air side region 32, the outside air flowing in from the outside region intake port 21a flows from the bottom to the top and is discharged from the outside air discharge port 21b. It makes it flow like it turns.

  As described above, since the outside air flows from the bottom to the top, the contaminants contained in the outside air can be prevented from adhering to the outside air side heat exchanger 13 due to the gravity. Also, since the outside air is made to flow in a U-turn, the contaminants that have entered from the outside air intake port 21a on the front surface 21 side of the case 11 are attached to the outside air heat exchanger 13 before the back surface 22 of the case 11. Can be attached to the upper surface 25 of the case 11, and the adhesion of contaminants to the outside air heat exchanger 13 can be suppressed.

  Moreover, in this embodiment, when the inside air side heat exchanger 12 and the outside air side heat exchanger 13 are viewed from the upper surface side of the case 11 as shown in FIG. It is arranged in the diagonal direction inside the case on the back left side and the front right side.

  That is, the total thickness of the two inside air heat exchangers 12 a and 12 b is less than half the thickness of the case 11. The two inside air heat exchangers 12a and 12b are arranged in the thickness direction of the case 11 on the back surface 22 side from the center of the case 11, and the ventilation surfaces 12c and 12d are substantially on the back surface 22 of the case 11. They are arranged in parallel.

  Further, the total thickness of the two outdoor air side heat exchangers 13 a and 13 b is also less than half the thickness of the case 11. The two outside air side heat exchangers 13 a and 13 b are arranged in the thickness direction of the case 11 on the front surface 21 side from the center of the case 11, and the ventilation surfaces 13 c and 13 d are substantially on the front surface 21 of the case 11. They are arranged in parallel.

  Thus, by arranging the inside air side heat exchangers 12a and 12b and the outside air side heat exchangers 13a and 13b, the inside air passage and the outside air passage inside the case 11 can be secured widely. Moreover, compared with the case where the inside air side heat exchanger 12 and the outside air side heat exchanger 13 are not parallel to the back surface 22 or the front surface 21 of the case 11 but are arranged obliquely, the heat exchangers 12, 14. The flow velocity and flow rate when the fluid passes through can be made uniform.

  In addition, from the viewpoint of ensuring a wider room for the inside air flow path and the outside air flow path, the distance between the back surface 22 and the inside air side heat exchanger 12a for the refrigeration cycle is set to the inside air side heat exchange for the refrigeration cycle as in this embodiment. It is preferable that the thickness is shorter than the thickness of the vessel 12a, and the distance between the front surface 21 and the outside air side heat exchanger 13a for the refrigeration cycle is shorter than the thickness of the outside air side heat exchanger 13a for the refrigeration cycle.

(Second Embodiment)
8A to 8D show the overall configuration of the cooling device according to the second embodiment of the present invention. 8A to 8D correspond to FIGS. 1A to 1D, respectively, and components similar to those in FIGS. 1A to 1D have the same reference numerals. Is attached.

  As shown in FIGS. 8A to 8D, the cooling device according to the present embodiment is an inside air side heat exchanger (evaporator) 12a for the refrigeration cycle in the cooling device shown in FIG. 1 described in the first embodiment. The outside air side heat exchanger (condenser) 13a is changed to an inside air side heat exchanger (boiler) 12b and an outside air side heat exchanger (condenser) 13b for boiling cooling, respectively.

  Moreover, in this embodiment, the liquid piping 45a arrange | positioned in the inside air area | region 31 in FIG. 1 is changed into the gas piping 44b, and the gas piping 44a arrange | positioned in the outside air area | region 32 in FIG. It is changed to 45b. In the present embodiment, two gas pipes 44 are arranged in parallel in the inside air region 31, and two liquid pipes 45 are arranged in parallel in the outside air region 32.

Here, in FIG. 9, schematic structure of the refrigerant circuit with which the cooling device of this embodiment is provided is shown.
In the cooling device of this embodiment, as shown in FIG. 9, the boiling is sealed by the inside air side heat exchanger 12b and the outside air side heat exchanger 13b for boiling cooling, the gas pipe 44b for boiling cooling, and the liquid pipe 45b. Two cooling-type refrigerant circuits are formed.

  In this embodiment, the refrigerant circuit of the boiling cooling system, the inside air side heat exchanger 12b for boiling cooling, the outside air side heat exchanger 13b for boiling cooling, the gas pipe 44b for boiling cooling, and the liquid pipe 45b are respectively provided. The first and second refrigerant circuits, the first and second high-temperature fluid side heat exchangers, the first and second low-temperature fluid side heat exchangers, and the first and second refrigerants according to claims Corresponds to piping.

  In this way, the cooling system of FIG. 1 is changed to the cooling device without changing the structure of the case 11 by changing the liquid piping 45a to the gas piping 44b and changing the gas piping 44a to the liquid piping 45b. The cooling method can be changed to the boiling type only.

  Moreover, since the cooling device 1 of this embodiment is provided with two refrigerant circuits of the same cooling system, even if a failure occurs in one refrigerant circuit, the remaining refrigerant circuit operates normally, so that the cooling device The cooling performance of 1 can be prevented from becoming 0.

(Third embodiment)
FIGS. 10A to 10D show the overall configuration of the cooling device according to the third embodiment of the present invention. 10A to 10D correspond to FIGS. 1A to 1D, respectively, and components similar to those in FIGS. 1A to 1D are denoted by the same reference numerals. Is attached.

  As shown in FIGS. 10A to 10D, the cooling device of the present embodiment is an inside air side heat exchanger (boiler) 12b for boiling cooling in the cooling device shown in FIG. 1 described in the first embodiment. The outside air side heat exchanger (condenser) 13b is changed to an inside air side heat exchanger (evaporator) 12a and an outside air side heat exchanger (condenser) 13a for the refrigeration cycle, respectively.

  Moreover, in this embodiment, the gas piping 44b arrange | positioned in the inside air area | region 31 in FIG. 1 is changed into the liquid piping 45a, and the liquid piping 45b arrange | positioned in the outside air area | region 32 in FIG. 44a has been changed. In the present embodiment, two liquid pipes 45 are arranged in parallel in the inside air region 31, and two gas pipes 44 are arranged in parallel in the outside air region 32. A decompression expansion valve 46 is provided in the middle of the liquid pipe 45, and a compressor 47 is provided in the middle of the gas pipe 44.

  Here, in FIG. 11, schematic structure of the refrigerant circuit with which the cooling device of this embodiment is provided is shown.

  In the cooling device of this embodiment, the inside air side heat exchanger 12a and the outside air side heat exchanger 13a for the refrigeration cycle, the gas pipe 44a and the liquid pipe 45a for the refrigeration cycle, the decompression expansion valve 46, and the compressor 47 are hermetically sealed. Two vapor compression refrigeration cycle refrigerant circuits are formed.

  In the present embodiment, the refrigerant circuit of the refrigeration cycle system, the inside air side heat exchanger 12a for the refrigeration cycle, the outside air side heat exchanger 13a for the refrigeration cycle, the gas pipe 44a and the liquid pipe 45a for the refrigeration cycle are respectively provided. The first and second refrigerant circuits, the first and second high-temperature fluid side heat exchangers, the first and second low-temperature fluid side heat exchangers, and the first and second refrigerants according to claims Corresponds to piping.

  As described above, the gas pipe 44b is changed to the liquid pipe 45a, the liquid pipe 45b is changed to the gas pipe 44a, and a decompression expansion valve 46 is added in the middle of the liquid pipe 45 in the cooling device of FIG. However, by adding the compressor 47 in the middle of the gas pipe 44, the cooling method of the cooling device can be changed only to the refrigeration cycle method without changing the structure of the case 11.

  Moreover, since the cooling device 1 of this embodiment is provided with two refrigerant circuits of the same cooling system, even if a failure occurs in one refrigerant circuit, the remaining refrigerant circuit operates normally, so that the cooling device The cooling performance of 1 can be prevented from becoming 0.

(Fourth embodiment)
In FIG. 12, the whole structure of the cooling device in the 1st example of 4th Embodiment is shown. FIG. 12 corresponds to FIG. 1A, and in FIG. 12, the same components as those in FIG.

  In the cooling device 1 of the first embodiment, as shown in FIG. 1A, a liquid pipe 45b for boiling cooling, a gas pipe 44a for a refrigeration cycle, and a compressor 47 are arranged in the outside air region 32. In contrast, in the present embodiment, as shown in FIG. 12, a liquid pipe 45 b for boiling cooling, a gas pipe 44 a for the refrigeration cycle, and a compressor 47 are arranged in the inside air region 31.

  In this way, not only the decompression expansion valve 46, which is an important functional component in the refrigeration cycle, but also the compressor 47 is disposed in the inside air region 31 separated from the outside air, so that the compressor 47 is exposed to the outside air. The compressor 47 can be prevented from being soiled or corroded.

  FIG. 13 shows the overall configuration of the cooling device in the second example of the fourth embodiment. 13 corresponds to FIG. 10A, and in FIG. 13, the same components as those in FIG. 1 are denoted by the same reference numerals.

  Similarly to the first example, in the cooling device 1 according to the third embodiment, as shown in FIG. 10A, two sets of gas pipes 44 and a compressor 47 for the refrigeration cycle are arranged in the outside air region 32. In contrast, in the second example of this embodiment, these are arranged in the inside air region 31 as shown in FIG.

  In the present embodiment, the case where both the decompression expansion valve 46 and the compressor 47 are arranged in the inside air region 31 has been described as an example, but the first and third implementations of the decompression expansion valve 46 and the compressor 47 are described. As in the embodiment, only the decompression expansion valve 46 may be arranged in the inside air region 31 or only the compressor 47 may be arranged in the inside air region 31.

(Fifth embodiment)
In FIG. 14, the whole structure of the cooling device in 5th Embodiment of this invention is shown. 14 is a diagram showing the internal structure when the cooling device attached to the station 2 is viewed from the side surface. In FIG. 14, the same reference numerals are given to the same components as in FIG. Is attached.

  In the first to fourth embodiments, the case 11 having a structure in which the inside air side region 31 and the outside air side region 32 are arranged in the left-right direction of the case 11 is used as the case. In the embodiment, basically, a case 70 having a structure in which an inside air side region 71 and an outside air side region 72 are arranged in the vertical direction of the case 70 is used.

  As shown in FIG. 14, the interior of the case 70 is divided into upper half side and lower half side regions mainly in the vertical direction of the case 70 by a partition wall 73, and the upper half side region is further divided into regions. The case 70 is divided into two regions in the thickness direction (left-right direction in the figure).

  In the inside of the case, the area on the lower half side and the area on the station 2 side in the upper half are the inside air area 71, and the area on the side far from the station 2 in the upper half is the outside air area 72. It is.

  In the inside air region 71, the inside air is taken in from the upper part of the case 70 by the inside air fan 14 as shown by the arrow in the figure, flows in the inside air region 71 from the top to the bottom, and from the lower part of the case 70 to the station building It is designed to flow toward 2. On the other hand, in the outside air region 72, the outside air flows from below to above by the outside air fan 15.

  Also in the present embodiment, similarly to the first embodiment, the inside air side region 71 is provided with the inside air side heat exchanger 12b for boiling cooling and the inside air side heat exchanger 12a for refrigeration cycle for boiling cooling. It arrange | positions so that the direction of the inside air side heat exchanger 12b may be located in the upstream of an inside air flow path.

  Further, in the outside air region 72, the outside air side heat exchanger 13b for boiling cooling and the outside air side heat exchanger 13a for refrigeration cycle are more upstream of the outside air flow path than the outside air side heat exchanger 13b for boiling cooling. It is arranged to be located on the side.

  In addition, the space | interval between the inside air side heat exchangers 12a and 12b and the space | interval between the outside air side heat exchangers 13a and 13b are the same as that of 1st Embodiment.

  In the present embodiment, similarly to the fourth embodiment, the compressor 47 provided in the inside air region 71 in the middle of the gas pipe 44a for the refrigeration cycle and the liquid pipe 45a for the refrigeration cycle are provided in the middle. A decompression expansion valve 46 is provided.

  As described above, the internal structure of the case can be changed with respect to the first embodiment. Moreover, the internal structure of a case can also be changed like this embodiment also with respect to the cooling device 1 shown in FIG. 8, FIG. 10 demonstrated in 2nd, 3rd embodiment.

  Thus, also in this embodiment, the structure of the cooling device is a structure in which two refrigerant circuits are housed in one case. Thereby, the kind of two refrigerant circuits can be made into only a refrigerating cycle system, only a boiling type, or a combined type.

  Therefore, according to the cooling device of this embodiment, since the case structure of the cooling device of each cooling method can be shared, the structure of the base station building 2 of the base station is made to be a common specification regardless of the type of the cooling method. can do. As a result, it is possible to select the cooling method of the cooling device according to the climate of each place without changing the structure of the base station station 2.

(Other embodiments)
(1) In the first embodiment, the refrigerant circuit of the boiling cooling system is configured by the inside air side heat exchanger 12b and the outside air side heat exchanger 13b for boiling cooling, the gas pipe 44b for boiling cooling, and the liquid pipe 45b. The case where the refrigerant circuit dedicated to the boiling cooling system is used has been described as an example.

  On the other hand, as a boiling cooling type refrigerant circuit, a bypass for avoiding the compressor 47 and a bypass for avoiding the decompression expansion valve 46 are provided for the refrigerant circuit of the refrigeration cycle type, and the compressor is provided by a switching valve or the like. 47 and the decompression expansion valve 46 can be avoided so that the refrigerant flows. That is, two refrigeration cycle system refrigerant circuits can be used, and one of them can be switched from the refrigeration cycle system to the boiling cooling system.

  However, in this case, the switching valve becomes a pressure loss of the refrigerant flow, the performance at the time of cooling operation of the boiling cooling method is deteriorated, and a sufficient energy saving effect cannot be obtained, or a large load is applied to the compressor 47 and the like when the valve is broken. There is a risk that the ability will be zero. Therefore, it is preferable to use a refrigerant circuit dedicated to the boiling cooling system as in the first embodiment.

  (2) In each of the above-described embodiments, the case where the gas pipe 44 and the liquid pipe 45 are arranged inside the case 11 has been described as an example. However, the gas pipe 44 and the liquid pipe 45 may be arranged outside the case 11.

  (3) In each of the above-described embodiments, the case where a multiflow path heat exchanger is used as the inside air heat exchanger 12b and the outside air side heat exchanger 13b for boiling cooling has been described as an example. Other heat exchangers applicable to boiling cooling devices can be used.

  Moreover, although the case where a multiflow path type heat exchanger is used as an example of the inside air side heat exchanger 12a and the outside air side heat exchanger 13a for the refrigeration cycle has been described as an example, the present invention is not limited to this and is applied to a refrigeration cycle cooling device Other possible heat exchangers can be used. For example, a single flow path type heat exchanger composed of one tube and plate fins or spine fins can be used.

  (4) In each of the above-described embodiments, the case where the inside air fan 14 and the outside air fan 15 are arranged one by one in the inside air region 31 and the outside air region 32 of the case 11 has been described as an example. The number of inside air fans 14 and outside air fans 15 may be two or more, that is, a plurality of fans.

  As a result, the number of the inside air fans 14 and the number of outside air fans 15 can be improved as compared with the case where the number of inside air fans 14 and outside air fans 15 is one, or the remaining fans can function even if one fan fails. Thus, it is possible to suppress the stop of the blowing by the inside air fan 14 and the outside air fan 15.

  (5) In each of the above-described embodiments, the case where the centrifugal fan is used as the inside air fan 14 and the outside air fan 15 has been described as an example. However, other fans can be used, for example, an axial fan is used. You can also.

  In each of the above-described embodiments, the inside air of the station building 2 is a circulatory system, and the air blowing work is lower than that of the open system outside air. Although the axial fan has a disadvantage that the blowing pressure is lower than that of the centrifugal fan, it has a merit of low cost from the viewpoint of the structure. Therefore, it is preferable to use the axial fan as the internal air fan 14.

  (6) In each of the above-described embodiments, the case where the inside air fan 14 and the outside air fan 15 are arranged inside the case 11 has been described as an example. However, the inside air region 31 and the outside air region 32 of the case 11 are respectively provided. If the inside air and the outside air can flow, the inside air fan 14 and the outside air fan 15 inside the case 11 can be omitted. For example, separately from the case 11, a fan can be disposed outside the case 11.

  (6) In each of the above-described embodiments, the case where two refrigerant circuits are accommodated in the case 11 has been described as an example. However, a refrigerant circuit can be further added.

  (7) In the first embodiment, the case 11 has been described as an example of the case 11 adopting a method of interposing packing and fixing the case 11 and the metal plates constituting the partition wall 27 with pins or the like. Other methods can also be adopted.

  For example, a method of forming the case 11 can be employed by integrally joining the case 11 and the metal plates constituting the partition wall 27 by brazing.

  Note that the case 11 can be used regardless of the type as long as the case 11 has a single case in the state of a finished product and the inside of the case 11 is divided into two spaces in the left-right direction. .

  (8) In each of the above-described embodiments, the case where the inside air and the outside air are caused to flow in the case 11 while facing each other has been described as an example. However, the inside air and the outside air can be caused to flow in the same direction.

  (9) In each of the above-described embodiments, the case where the refrigerant is naturally circulated in the boiling cooling refrigerant circuit has been described as an example, but the refrigerant can be forcedly circulated. In this case, for example, a pump is connected to the gas pipe 44b or the liquid pipe 45b so as to forcibly circulate the refrigerant.

  (10) In the first to fourth embodiments, the case 11 has been described as an example in which the shape of the case 11 is a rectangular parallelepiped, but may be changed to other shapes.

  For example, the shape of the case 11 is changed to an elliptical shape by changing the upper surface 25 and the lower surface 26 in FIG. 1 and the front surface 21, the rear surface 22, the left side surface 23, and the right side surface 24 are changed to one cylindrical surface. You can also. In this case, the shape of the partition wall 27 is a rectangle as in FIG.

  Further, the shape of the partition wall 27 can be changed from a rectangular shape to another shape according to the shape of the case 11.

  In each of the above-described embodiments, the case where the partition wall 27 has a flat plate shape has been described as an example. However, if the inside of the case 11 can be divided into left and right parts, the partition wall 27 can be bent. However, from the viewpoint of simplifying the case and obtaining high waterproof properties, the partition walls are preferably flat.

  (11) In the first to fourth embodiments, the case where the partition wall 27 is arranged perpendicular to the front surface 21, the back surface 22, the upper surface 25, and the lower surface 26 of the case 11 has been described as an example. If it can be divided into two parts, the partition wall 27 can be disposed obliquely with respect to the front surface 21 and the back surface 22 of the case 11, or disposed obliquely with respect to the upper surface 25 and the lower surface 26.

  (12) In each of the above-described embodiments, the case where a vapor compression refrigeration cycle refrigerant circuit is used as an example of the refrigeration cycle refrigerant circuit has been described as an example. A cycle-type refrigerant circuit can be used.

  Further, although the refrigeration cycle method for evaporating and condensing the refrigerant has been described as an example, a refrigeration cycle method in which the refrigerant does not evaporate and condense like a so-called supercritical cycle can also be adopted.

  (13) In each of the above-described embodiments, the base station cooling device that cools the inside of the mobile phone base station is described as an example. However, the high-temperature fluid inside the housing and the low-temperature fluid outside the housing are mixed. The present invention can be applied to other boiling type cooling devices that cool the high-temperature fluid inside the casing by exchanging heat. The subject of cooling is not limited to the high-temperature fluid inside the housing, and the present invention can also be applied to a cooling device that cools a high-temperature fluid using a low-temperature fluid that is lower in temperature than the high-temperature fluid.

  For example, the present invention can be applied to a cooling device that cools a high-temperature liquid such as cooling water or oil for cooling a heating element by using a low-temperature liquid such as water or oil whose temperature is lower than that of the liquid. .

BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows the whole structure of the cooling device in 1st Embodiment of this invention, (a) is front perspective drawing of a cooling device, (b), (c) is side perspective of the cooling device in (a). It is a figure and (d) is an upper surface perspective view of the cooling device in (a). It is a figure which shows the installation state to the station building of the cooling device in FIG. It is sectional drawing of the case 11 when the case 11 in Fig.1 (a) is seen from upper direction. It is a figure which shows schematic structure of the refrigerant circuit with which the cooling device of FIG. 1 is provided. 2 is a cross-sectional view of an inside air side heat exchanger 12b, an outside air side heat exchanger 13b, a gas pipe 44b, a liquid pipe 45b, and a partition wall 27 of a case 11 for boiling cooling included in the cooling device in FIG. It is the sectional view on the AA line in FIG. It is an enlarged view of the area | region B enclosed with the broken line in FIG. It is a figure which shows the whole structure of the cooling device in 2nd Embodiment of this invention, (a) is front perspective drawing of a cooling device, (b), (c) is side perspective drawing of the cooling device in (a). It is a figure and (d) is an upper surface perspective view of the cooling device in (a). It is a figure which shows schematic structure of the refrigerant circuit with which the cooling device of FIG. 8 is provided. It is a figure which shows the whole structure of the cooling device in 3rd Embodiment of this invention, (a) is front perspective drawing of a cooling device, (b), (c) is side surface perspective view of the cooling device in (a). It is a figure and (d) is an upper surface perspective view of the cooling device in (a). It is a figure which shows schematic structure of the refrigerant circuit with which the cooling device of FIG. 10 is provided. It is a figure which shows the whole structure of the cooling device in the 1st example of 4th Embodiment of this invention. It is a figure which shows the whole structure of the cooling device in the 2nd example of 4th Embodiment of this invention. It is a figure which shows the whole structure of the cooling device in 5th Embodiment of this invention.

Explanation of symbols

1 ... cooling device, 11 ... case,
12a ... Inside air side heat exchanger for refrigeration cycle, 13a ... Outside air side heat exchanger for refrigeration cycle,
12b ... Inside air side heat exchanger for boiling cooling, 13b ... Outside air side heat exchanger for boiling cooling,
14 ... Inside air fan, 15 ... Outside air fan, 27 ... Bulkhead,
31 ... Inside air side region, 32 ... Outside air side region,
44a, 44b ... gas piping, 45a, 45b ... liquid piping,
46: decompression expansion valve, 47: compressor.

Claims (7)

A case (11, 70) in which a high temperature fluid side channel (31) through which a high temperature fluid flows and a low temperature fluid side channel (32) through which a low temperature fluid flows are provided;
First and second high-temperature fluid side heat exchangers (12b) that cool the high-temperature fluid by heat exchange between the high-temperature fluid-side flow path (31) and the refrigerant enclosed in the high-temperature fluid. 12a)
First and second low-temperature fluid side heat exchangers that dissipate heat from the refrigerant to the low-temperature fluid by heat exchange between the low-temperature fluid side flow path (32) and the refrigerant enclosed in the low-temperature fluid. (13b, 13a),
A first refrigerant pipe (44b, 45b) for circulating a refrigerant between the first high temperature fluid side heat exchanger (12b) and the first low temperature fluid side heat exchanger (13b);
A second refrigerant pipe (44a, 45a) for circulating the refrigerant between the second high temperature fluid side heat exchanger (12a) and the second low temperature fluid side heat exchanger (13a). ,
The first high-temperature fluid side heat exchanger (12b), the first low-temperature fluid side heat exchanger (13b), and the first refrigerant pipe (44b, 45b) constitute a first refrigerant circuit,
The first refrigerant circuit causes the refrigerant to evaporate in the first high-temperature fluid-side heat exchanger (12b), condenses the refrigerant in the first low-temperature fluid-side heat exchanger (13b), and the density of the refrigerant It is a natural circulation refrigerant circuit that naturally circulates refrigerant using the difference,
The second high-temperature fluid side heat exchanger (12a), the second low-temperature fluid side heat exchanger (13a), and the second refrigerant pipe (44a, 45a) constitute a second refrigerant circuit,
The second refrigerant circuit is provided in the middle of the second refrigerant pipe (44a, 45a), and in the middle of the compressor (47) for compressing the refrigerant and the second refrigerant pipe (44a, 45a). And a decompression / expansion means (46) for decompressing and expanding the refrigerant. The refrigerant compressed by the compressor (47) is radiated by the second low-temperature fluid-side heat exchanger (13a) , The refrigerant is decompressed and expanded by the decompression / expansion means (46), the decompressed and expanded refrigerant is absorbed by the second high-temperature fluid-side heat exchanger (12a), and the refrigerant is utilized by using the compressor (47). Is a forced circulation refrigerant circuit that forcibly circulates
In the high temperature fluid side flow path (31), the ventilation surfaces (12d, 12c) of the first and second high temperature fluid side heat exchangers (12b, 12a) face each other, and the first high temperature fluid A side heat exchanger (12b) is disposed upstream of the second hot fluid side heat exchanger (12a) in the hot fluid flow;
In the low temperature fluid side channel (32), the ventilation surfaces (13d, 13c) of the first and second low temperature fluid side heat exchangers (13b, 13a) face each other, and the first low temperature fluid The cooling device, wherein the side heat exchanger (13b) is disposed upstream of the second low temperature fluid side heat exchanger (13a) in the low temperature fluid flow.
At least one of the cooling apparatus according to claim 1, characterized in that it is arranged in the hot fluid flow path (31) of the compressor (47) and the pressure reducing expansion means (46). Said first temperature fluid side heat exchanger (12b) and said second temperature fluid side heat exchanger (12a), the ventilation surface (12d, 12c) are each other row flat, the spacing of each other the 1. It is arranged so as to be smaller than the total width in the direction perpendicular to the ventilation surfaces (12d, 12c) of the second high-temperature fluid side heat exchanger (12b, 12a),
Said first cryogenic fluid heat exchanger (13b) and said second cryogenic fluid heat exchanger (13a), the ventilation surface (13d, 13c) are each other row flat, the spacing of each other the It is arrange | positioned so that it may become smaller than the sum total of the width | variety in the direction perpendicular | vertical to the said ventilation surface (13d, 13c) of the 1st, 2nd low temperature fluid side heat exchanger (13b, 13a). Item 3. The cooling device according to Item 1 or 2 . In the hot fluid side flow path (31), a high temperature fluid fan of a pushing type (on the upstream side of the first and second hot fluid side heat exchangers (12b, 12a)) 14)
In the low temperature fluid side flow path (32), on the upstream side of the low temperature fluid flow from the first and second low temperature fluid side heat exchangers (13b, 13a), a push type cryogenic fluid fan ( 15. The cooling device according to any one of claims 1 to 3 , wherein 15) is arranged. The cooling device according to claim 4 , wherein a plurality of the low-temperature fluid fans (15) are arranged. The case (11) has a cross-sectional shape in which the length in the first direction is shorter than the length in the second direction orthogonal to the first direction, and the high-temperature fluid side flow wherein the road (31) cryogen flow path (32), inside the casing (11), one of 5 claims 1, characterized in that arranged side by side in the second direction The cooling device according to one. The case (11) includes a front surface (21), a back surface (22) positioned on the back side of the front surface (21), a left side surface (23) positioned on the left side toward the front surface (21), A right side surface (24) positioned on the right side toward the front surface (21), an upper surface (25) positioned above the front surface (21), and a lower surface (26) positioned below the front surface (21). A rectangular parallelepiped shape having
By dividing the inside of the case (11) into two regions arranged in the left-right direction toward the front surface (21) by the partition plate (27), the inside of the case (11) has the high temperature fluid side. A flow path (31) and the low-temperature fluid side flow path (32) are provided,
The high-temperature fluid flows in from the high-temperature fluid intake port (22a) provided in the upper portion of the back surface (22), flows in the high-temperature fluid side flow path (31) from the top to the bottom, and the back surface (22). It flows out from the discharge port (22b) of the high-temperature fluid provided in the lower part of
The cryogenic fluid flows in from the cryogenic fluid inlet (21a) provided at the lower part of the front surface (21), flows in the cryogenic fluid side channel (32) from the bottom upward, and the front surface (21). Out of the discharge port (21b) of the cryogenic fluid provided in the upper part of
The total width in the direction perpendicular to the ventilation surfaces (12d, 12c) of the first and second high-temperature fluid side heat exchangers (12b, 12a), and the first and second low-temperature fluid side heat exchangers The total width in the direction perpendicular to the ventilation surfaces (13d, 13c) of (13b, 13a) is less than half of the width in the direction perpendicular to the front surface (21) of the case (11). Yes,
The first and second low-temperature fluid side heat exchangers (13b, 13a) are above the first and second high-temperature fluid side heat exchangers (12b, 12a), and the front surface (21). In the direction perpendicular to the front side of the case (11) and the ventilation surface (13c, 13d) are arranged in parallel to the front surface (21),
The first and second high-temperature fluid side heat exchangers (12b, 12a) are closer to the back surface (22) than the center of the case (11) in a direction perpendicular to the front surface (21), and The cooling device according to claim 6 , wherein the ventilation surfaces (12d, 12c) are arranged so as to be parallel to the back surface (22).

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