JP2009270731A - Fin tube type heat exchanger, and refrigerating device and hot water supply device comprising the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fin tube type heat exchanger capable of suppressing degradation of heat exchanging performance by frost formation while suppressing increase of costs of a heat exchanger even in increasing compressive strength of a heat transfer tube. <P>SOLUTION: A heat transfer tube 41 and a heat transfer tube 42 respectively penetrate through a through-hole O1 and a through-hole O2 of a fin 61. Risings W11, W14 and the like are disposed near the through-holes O1, O2 within a range of 1/3 of the closest distance between the through-holes, and extend in the plate thickness direction. A flat section R free from the shape projecting to the plate thickness direction is formed between the rising W11 and the rising W14. The fin 61 is formed so that a value obtained by dividing a distance between centers of holes as a distance from the center of the through-hole O1 to the center of the through-hole O2 by an outer diameter D of the heat transfer tubes 41, 42 is 3.0 or more. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a finned tube heat exchanger that allows heat exchange without directly contacting fluids, and a refrigeration apparatus and a hot water supply apparatus including the same.

  2. Description of the Related Art Conventionally, as a heat exchanger for a refrigeration apparatus, a heat exchanger having a structure in which a tube row penetrates plate-like fin groups arranged at narrow intervals is used.

As a refrigerant flowing through such a finned tube heat exchanger, from the viewpoint of protecting the global environment, instead of conventionally used fluorocarbon refrigerants such as R-12 and R-22, HFCs such as R-32 are used. Natural refrigerants such as refrigerant and CO ₂ have been used.

Here, in the case of using a natural refrigerant such as CO ₂ , the operating pressure in the refrigeration cycle exceeds the critical pressure, and higher pressure resistance than in the past is required in piping design and the like. For this reason, for example, as shown in Patent Document 1 below, a technique for ensuring the pressure strength by increasing the thickness of the heat transfer tube of the finned tube heat exchanger has been studied.
JP 2006-162100 A

  When the above-described heat transfer tube is employed, the cost of the heat transfer tube per unit length is increased as compared with the conventional heat transfer tube, and as a result, the cost of the entire heat exchanger is increased. Furthermore, since the wall thickness increases, the total weight of the heat exchanger increases.

  On the other hand, even when heat transfer tubes with increased pressure resistance are used, the increase in cost can be suppressed and the total weight increased by reducing the number of tubes used so that the total length is shortened. Can also be suppressed.

  However, if the number of heat transfer tubes existing per unit area of the flat plate fins is reduced in this way, there arises a problem that the heat exchange performance is deteriorated.

  In view of this, it is conceivable to further suppress a decrease in heat exchange performance by increasing the number density of the flat fins in the plate thickness direction, or by providing irregularities in a part of the flat fins.

  However, when the number density of the plate fins in the plate thickness direction is increased as described above, or when unevenness is provided on a part of the plate fins, frost tends to adhere to the plate fins disposed outdoors. . If frosting occurs in this way, the reduction in heat exchange performance cannot be minimized.

  Even if it is a case where the subject of this invention wants to increase the pressure-resistant intensity | strength of a heat exchanger tube, it can suppress the increase in the cost of a heat exchanger small, and can suppress the fall of the thermal performance by frost formation small It is providing a type | mold heat exchanger, a freezing apparatus provided with this, and a hot water supply apparatus.

  A finned tube heat exchanger according to a first aspect of the present invention is a finned tube heat exchanger that performs heat exchange without directly contacting fluids, and includes a first heat transfer tube, a second heat transfer tube, and fins. . The first heat transfer tube has a cylindrical shape. The second heat transfer tube has a cylindrical shape whose outer diameter is substantially equal to that of the first heat transfer tube. The fin has a first through hole, a second through hole, a protruding portion, and a substantially flat portion. The inside of the first through hole is in contact with the outer periphery of the first heat transfer tube. The inner side of the second through hole is in contact with the outer periphery of the second heat transfer tube. The protrusion is provided at a position where the distance from at least one of the first through hole and the second through hole is within 1/3 of the closest distance between the first through hole and the second through hole. Protrudes in the direction. The substantially flat portion is not provided with a shape protruding in the plate thickness direction at a position between the first through hole and the second through hole except for the protruding portion. And the value which remove | divided the distance between hole centers which is the distance from the center of a 1st through-hole to the center of a 2nd through-hole by the outer diameter of a 1st heat exchanger tube is larger than 3.0. The value obtained by dividing the distance between the hole centers by the outer diameter of the first heat transfer tube is more preferably greater than 3.5. Further, the first heat transfer tube and the second heat transfer tube may be connected via a U-shaped tube or the like.

  In this fin tube type heat exchanger, the value obtained by dividing the distance between the hole centers by the outer diameter of the first heat transfer tube is set to be greater than 3.0. For this reason, the number of heat transfer tubes is reduced in order to shorten the outer diameter to increase the strength of the heat transfer tube or to increase the material cost and weight increase associated with this by increasing the thickness to ensure the pressure strength. Even if the density is kept small, the heat exchange performance is hardly lowered by the provision of the protruding portion.

  Moreover, since the part which can perform heat exchange effectively on a fin is provided by providing a protrusion part, heat exchange performance can be improved also by this.

  And near the heat transfer tube and the vicinity of the protruding part, frost formation is likely to occur depending on the usage conditions, but this fin has a substantially flat part, which is compared with the vicinity of the heat transfer tube and the protruding part. Frosting hardly occurs.

  For this reason, even if frost formation occurs in the vicinity of the heat transfer tube and the protruding portion depending on the use situation, heat exchange can be effectively performed with the passing air without frost formation on this substantially flat portion. Even under partially frosted conditions, it is possible to suppress a decrease in heat exchange performance.

  In order to keep the number of heat transfer tubes to a small number, even when heat transfer tubes with sufficient pressure resistance are used, the increase in the total weight of the heat exchanger itself can be kept small, and the fin tube type heat The exchanger is light and easy to handle.

  The finned tube heat exchanger of the second invention is the finned tube heat exchanger of the first invention, and is projected in a direction orthogonal to the longitudinal direction of the fin on the surface of the fin out of the length of the protrusion. A value obtained by dividing the length component by the outer diameter of the first heat transfer tube is larger than 1.0 and smaller than 2.5.

  In this fin tube type heat exchanger, when the ratio here is 1.0 or less, it is not possible to sufficiently obtain the effect of the protruding portion that promotes heat transfer. Moreover, when the ratio here is 2.5 or more, it is not possible to maintain a good air flow and heat exchange efficiency is reduced. For this reason, as a value obtained by dividing the length component of the protruding portion in the direction orthogonal to the longitudinal direction of the fin by the outer diameter of the first heat transfer tube, a range larger than 1.0 and smaller than 2.5 By adopting, it becomes possible to promote heat transfer while maintaining good air flow omission.

  The finned tube heat exchanger of the third invention is the finned tube heat exchanger of the first invention or the second invention, wherein the fin length is in the direction perpendicular to the longitudinal direction of the fin on the fin surface. A value obtained by dividing the fin width by the outer diameter of the first heat transfer tube is larger than 2.2 and smaller than 3.5.

  In this finned tube heat exchanger, when the ratio here is 2.2 or less, it becomes difficult to reduce the relationship between the heat transfer tubes, and the heat obtained from the refrigerant flowing through the heat transfer tubes The fin area for exchanging heat with the external air is insufficient. If the ratio is 3.5 or more, the heat of the refrigerant supplied through the heat transfer tube cannot be transferred to the end in the fin width direction, and heat exchange is effective at the end in the fin width direction. However, ventilation resistance increases. For this reason, as a value obtained by dividing the fin width by the outer diameter of the first heat transfer tube, a range larger than 2.2 and smaller than 3.5 is adopted, so that an effective heat exchange can be achieved while suppressing an increase in ventilation resistance. It becomes possible to secure the required fin area.

  The finned tube heat exchanger according to a fourth aspect of the present invention is the finned tube heat exchanger according to any one of the first to third aspects of the present invention, wherein the protrusions are near the center of the first through hole and near the center of the second through hole. Of the fin regions divided into two by the line connecting the two, the region is provided only in the region on the leeward side in the air flow direction.

  In this fin tube type heat exchanger, frost formation is likely to occur on the windward side of the heat exchanger. On the other hand, in this finned-tube heat exchanger, a protrusion is provided only in a region that is downstream of the wind in the air flow direction, and no protrusion is provided in a region that is on the windward side. Thereby, generation | occurrence | production of frost formation can be suppressed now.

  The finned tube heat exchanger according to a fifth aspect of the present invention is the finned tube heat exchanger according to any one of the first to fourth aspects of the present invention, wherein the protruding portion has fins on the leeward side rather than on the leeward side in the air flow direction. An inclined portion having a long protruding length, which is a length in the plate thickness direction, is at least partially included.

  In this finned tube heat exchanger, if a portion with a long protruding length is provided on the windward side of the air flow, a large dead water area is generated on the downstream side of the portion, so that air is likely to stay and efficient. The part which performs heat exchange will be reduced. On the other hand, in this fin tube heat exchanger, it is possible to keep the dead water area as small as possible by forming the projection length to be shorter on the windward side.

  The finned tube heat exchanger according to a sixth aspect of the present invention is the finned tube heat exchanger according to any one of the first to fifth aspects of the present invention, wherein the protruding portion is a first protruding portion located on the upstream side in the air flow direction, A second projecting portion which is separated from the first projecting portion and is located downstream of the first projecting portion;

  The finned tube heat exchanger can improve the heat exchange performance, and can leak the air flow through a portion that is divided and has nothing, thereby improving water drainage.

  The finned tube heat exchanger of the seventh invention is the finned tube heat exchanger of the sixth invention, wherein the protruding length of the first protruding part in the thickness direction is not less than a predetermined length.

  By setting the protruding length of the first protruding portion in the plate thickness direction to be equal to or longer than a predetermined length that can be manufactured by cutting and raising the fins, it is possible to improve reliability in manufacturing.

  The finned tube heat exchanger according to an eighth aspect of the present invention is the finned tube heat exchanger according to any one of the first to seventh aspects, wherein the fin has a thickness of more than 0.05 mm and less than 0.50 mm. However, a plurality of sheets are provided. The plurality of fins are arranged so as to overlap each other in the plate thickness direction. And the space | interval of the plate | board thickness direction of fins is larger than 1.0 mm, and smaller than 3.0 mm.

  This fin tube type heat exchanger can improve the heat exchange performance per unit area by shortening the fin pitch.

  The finned tube heat exchanger of the ninth invention is the finned tube heat exchanger of the eighth invention, wherein the value obtained by dividing the length of the protruding portion in the plate thickness direction by the interval in the plate thickness direction of the fins is 0.00. 9 or less.

  In this finned tube heat exchanger, the height of the protrusions is set to be less than the distance between the fins in the plate thickness direction, so that air flows between the protrusions and the fins located above the protrusions. Since it can flow, it becomes possible to prevent air from stagnating in the vicinity of the protrusion.

  The finned tube heat exchanger according to a tenth aspect of the present invention is the finned tube heat exchanger according to any one of the first to ninth aspects, wherein the fin has a plurality of folds extending in the longitudinal direction.

  In this fin tube heat exchanger, the fin is curved in a corrugated shape, and the fold line extends in the longitudinal direction, so that the strength of the fin can be improved.

  The finned tube heat exchanger of the eleventh aspect of the invention is the finned tube heat exchanger of the tenth aspect of the invention, wherein the protruding part is separated from the first protruding part and the first protruding part located on the upstream side in the air flow direction. And a second protrusion located downstream from the first protrusion. The first protrusion and the second protrusion are each positioned between the plurality of folds of the fin and are not positioned on the fold.

  In this fin tube type heat exchanger, since the protrusions are located between the folds, the manufacture becomes easy. Moreover, since the protrusion part is divided | segmented, the air which finished heat exchange in a protrusion part can be flowed toward the space between protrusion parts, and the stagnation of air can be prevented.

  The finned tube heat exchanger according to a twelfth aspect of the present invention is the finned tube heat exchanger according to any one of the first to eleventh aspects of the present invention, wherein the fin is located at a position in the downstream direction of the air flow with respect to the substantially flat portion. And a protruding wall extending in the plate thickness direction of the fin.

  In this finned tube heat exchanger, the air flowing in avoiding the heat transfer tubes and the protrusions located on the upstream side hits the protruding wall and flows. For this reason, it becomes possible to further improve heat exchange performance by heat exchange in the protruding wall.

  A finned tube heat exchanger according to a thirteenth aspect of the present invention is the finned tube heat exchanger according to any one of the first to twelfth aspects of the present invention, further comprising a cylindrical third heat transfer tube. The fin is further located in the downstream direction of the air flow with respect to the substantially flat portion, and further includes a third through hole whose inner side is in contact with the outer periphery of the third heat transfer tube.

  In this finned-tube heat exchanger, even if frost formation occurs near the heat transfer tube or the protruding portion on the upstream side of the air flow, the third transfer on the downstream side via the substantially flat portion where frost formation does not easily occur. Air will be sent to the heat pipe. For this reason, even if it is a case where frosting arises in the heat exchanger tube and protrusion part of an upstream, it becomes possible to suppress the fall of heat exchange performance small.

  Further, even in a situation where no frost formation occurs, the air flow toward the first heat transfer tube is the first heat transfer tube, and the air flow toward the second heat transfer tube is the second heat transfer tube toward the protruding portion. About an air flow, heat exchange can be performed in the protrusion part which is easy to obtain heat in the vicinity of a heat exchanger tube, respectively. Then, the air flow guided to the vicinity of the substantially flat portion by the vicinity of the protrusion portion without going to the first heat transfer tube, the second heat transfer tube, and the protrusion portion, or just the middle between the first heat transfer tube and the second heat transfer tube. About an air flow, heat exchange can be performed in a 3rd heat exchanger tube. Thereby, it becomes possible to perform sufficient heat exchange in each place.

  A finned tube heat exchanger according to a fourteenth aspect of the present invention is the finned tube heat exchanger according to any one of the first to twelfth aspects of the present invention, wherein the cylindrical third heat transfer tube and the inner side are in contact with the outer periphery of the third heat transfer tube. And a downstream fin having a third through hole. The third heat transfer tube and the downstream fin are located in the downstream direction of the air flow with respect to the first heat transfer tube, the second heat transfer tube, and the fin. The third heat transfer tube is located on the downstream side of the air flow with respect to the substantially flat portion. In addition, you may provide the heat transfer tube in multiple steps | paragraphs of 3 steps or more.

  In this finned tube heat exchanger, even if frost formation occurs near the first heat transfer tube, the second heat transfer tube, or the protruding portion on the upstream side of the air flow, a substantially flat portion that hardly generates frost is formed. Thus, air is sent to the third heat transfer tube on the downstream side. For this reason, even if it is a case where frosting arises in the heat exchanger tube and protrusion part of an upstream, it becomes possible to suppress the fall of heat exchange performance small.

  Further, even in a situation where no frost formation occurs, the air flow toward the first heat transfer tube is the first heat transfer tube, and the air flow toward the second heat transfer tube is the second heat transfer tube toward the protruding portion. About an air flow, heat exchange can be performed in the protrusion part which is easy to obtain heat in the vicinity of a heat exchanger tube, respectively. Then, the air flow guided to the vicinity of the substantially flat portion by the vicinity of the protrusion portion without going to the first heat transfer tube, the second heat transfer tube, and the protrusion portion, or just the middle between the first heat transfer tube and the second heat transfer tube. About an air flow, heat exchange can be performed in a 3rd heat exchanger tube. Thereby, it becomes possible to perform sufficient heat exchange in each place.

  The fifteenth fin-tube heat exchanger is the fin-tube heat exchanger according to any one of the first to twelfth inventions, wherein the cylindrical third heat transfer tube and the inner side are in contact with the outer periphery of the third heat transfer tube. A downstream fin having a third through hole. The downstream fin has a first projecting wall and a second projecting wall extending in the longitudinal direction of the downstream fin and the plate thickness direction of the downstream fin, and the first projecting wall, the third through hole, and the second projecting wall. Are arranged in this order in the longitudinal direction of the downstream fin. And a 3rd heat exchanger tube and a downstream fin are located in the downstream direction of an air flow with respect to a 1st heat exchanger tube, a 2nd heat exchanger tube, and a fin. Furthermore, the 3rd heat exchanger tube is located in the downstream direction of an air flow with respect to a substantially flat part. The first protruding wall is located in the downstream direction of the air flow with respect to the first heat transfer tube. The second protruding wall is located in the downstream direction of the air flow with respect to the second heat transfer tube.

  In this finned tube heat exchanger, even if frost formation occurs near the first heat transfer tube, the second heat transfer tube, or the protruding portion on the upstream side of the air flow, a substantially flat portion that hardly generates frost is formed. Thus, air is sent to the third heat transfer tube on the downstream side. Moreover, when the 1st protrusion wall and the 2nd protrusion wall are provided, the air which flows into a downstream fin can be collected in the 3rd heat exchanger tube vicinity, and frost formation has arisen in the heat exchanger tube and protrusion vicinity of an upstream side Even so, it is possible to suppress a decrease in heat exchange performance.

  Further, even in a situation where no frost formation occurs, the air flow toward the first heat transfer tube is the first heat transfer tube, and the air flow toward the second heat transfer tube is the second heat transfer tube toward the protruding portion. About an air flow, heat exchange can be performed in the protrusion part which is easy to obtain heat near the heat exchanger tube, respectively. Then, the air flow led to the vicinity of the substantially flat portion by the vicinity of the protrusion portion without going to the first heat transfer tube, the second heat transfer tube, and the protrusion portion, or just the middle between the first heat transfer tube and the second heat transfer tube. About an air flow, heat exchange can be performed in a 3rd heat exchanger tube. Thereby, it becomes possible to perform sufficient heat exchange in each place.

  The finned tube heat exchanger according to a sixteenth aspect of the present invention is the finned tube heat exchanger according to any one of the first to fifteenth aspects of the present invention, wherein the fin has a cut portion that is partially cut in the thickness direction. . The projecting portion is a cut-and-raised portion obtained by raising the cut portion in the plate thickness direction.

  In this fin tube type heat exchanger, it is not necessary to separately attach the protruding portion, and the flow of the passing air can be cut and raised by the raised portion. Thereby, since the cut-and-raised part arrange | positioned in the vicinity of the heat exchanger tube can fully contact with passing air, heat exchange efficiency can be improved. Furthermore, since the cut portion has an air flow that passes through the air, the dead water area on the downstream side of the cut portion can be reduced, and the heat exchanged air can be prevented from stagnation and effectively. Heat exchange can be performed.

  The finned tube heat exchanger of the seventeenth invention is the finned tube heat exchanger of the sixteenth invention, wherein the cut-and-raised portion is closer to the center of the first through hole and the center of the second through hole. The distance is shorter on the leeward side than on the leeward side. The angle of attack, which is an angle formed by the longitudinal direction of the cut and raised portion and the direction orthogonal to the longitudinal direction of the fin on the surface of the fin, is larger than 10 degrees and smaller than 40 degrees. In addition, from the relationship between ventilation resistance and heat exchange performance, the angle of attack is preferably 14 degrees.

  In this fin tube type heat exchanger, an increase in ventilation resistance can be suppressed by making the angle of attack smaller than 40 degrees. Moreover, heat exchange performance is fully securable by making an angle of attack larger than 10 degree | times. Thereby, heat exchange performance can be improved, suppressing increase in ventilation resistance.

  The finned tube heat exchanger according to an eighteenth aspect of the present invention is the finned tube heat exchanger according to any one of the first to the seventeenth aspects, wherein the first heat transfer tube and the second heat transfer tube are made of copper or an alloy containing copper. The outer diameter is 4 mm or more and 7 mm or less.

  In this finned tube heat exchanger, it is possible to reliably ensure the pressure strength even when the refrigerant pressure in the refrigeration cycle is high.

  The finned tube heat exchanger of the nineteenth invention is the finned tube heat exchanger of any one of the first to eighteenth inventions, wherein the working refrigerant is carbon dioxide.

  When the working refrigerant of the finned tube heat exchanger is carbon dioxide, the refrigeration cycle is performed at a high pressure exceeding the critical pressure. Even in this case, it is possible to maintain the capacity while ensuring the pressure strength. Become.

  The refrigeration apparatus according to a twentieth aspect of the present invention is the finned-tube heat exchanger according to any one of claims 1 to 19, wherein the refrigeration apparatus functions only as a refrigerant evaporator in a refrigeration cycle and is disposed outdoors. The air supply part which supplies an air flow to a container, the compressor, the heat source side heat exchanger, and the expansion mechanism are provided.

  In this refrigeration apparatus, even if the outside air temperature is lowered during the heating operation and frost formation is likely to occur, it is possible to maintain high thermal performance.

  The hot-water supply device according to a twenty-first aspect of the present invention is the finned-tube heat exchanger according to any one of claims 1 to 19, wherein the hot-water supply device functions only as a refrigerant evaporator in a refrigeration cycle and is disposed outdoors. The air supply part which supplies an air flow to an apparatus, the compressor, the heat source side heat exchanger, the expansion mechanism, and the water circuit which supplies the water used as a heating object to a heat source side heat exchanger are provided.

  In this hot water supply device, the fin tube type heat exchanger functions as a refrigerant evaporator to draw heat and heat the water flowing through the water circuit. For this reason, depending on the environment around the finned tube heat exchanger, the finned tube heat exchanger is likely to be frosted. On the other hand, here, it is possible to suppress a decrease in the heat exchange performance even under such a situation where frost formation is likely to occur or a partial frost formation.

  In the 1st invention, it becomes possible to suppress the fall of heat exchange performance small even under the situation where it partially frosted.

  In the second aspect of the invention, it is possible to promote heat transfer while maintaining good airflow escape.

  In the third aspect of the invention, it is possible to secure a fin area required for effective heat exchange while suppressing an increase in ventilation resistance.

  In 4th invention, generation | occurrence | production of frost formation can be suppressed now.

  In the fifth invention, it is possible to keep the dead water area as small as possible.

  In the sixth aspect of the invention, the air flow can be leaked through a portion that is divided and has nothing, and water drainage can be improved.

  In the seventh invention, reliability in manufacturing can be improved.

  In the eighth invention, it is possible to improve the heat exchange performance per unit area.

  In the ninth aspect of the invention, air can flow between the protrusion and the fin located above it, so that it is possible to prevent the air from stagnating in the vicinity of the protrusion.

  In the tenth aspect, the strength of the fin can be improved.

  In the eleventh aspect, the manufacture is facilitated and the stagnation of air can be prevented.

  In the twelfth aspect, the heat exchange performance can be further improved by the heat exchange in the protruding wall.

  In the thirteenth aspect, sufficient heat exchange can be performed at various places.

  In the fourteenth aspect, sufficient heat exchange can be performed at various places.

  In the fifteenth aspect, sufficient heat exchange can be performed at various places.

  In the sixteenth aspect of the invention, the cut-and-raised part can sufficiently contact with the passing air, so that the heat exchange efficiency can be improved, and the cut-off part can prevent the heat exchanged air from being stagnant and effective. Can be made to exchange heat.

  In the seventeenth aspect, heat exchange performance can be improved while suppressing an increase in ventilation resistance.

  In the eighteenth aspect, it is possible to ensure the pressure resistance even when the refrigerant pressure in the refrigeration cycle is high.

  In the nineteenth aspect, it is possible to maintain the capacity while ensuring the pressure strength.

  In the twentieth invention, even if the outside air temperature is lowered during the heating operation and frost formation is likely to occur, it is possible to maintain high thermal performance.

  In the twenty-first aspect, it is possible to suppress a decrease in heat exchange performance to a small extent even under conditions where frost formation tends to occur or conditions where partial frost formation occurs.

<1-1> Configuration of Hot Water Supply Apparatus FIG. 1 is a schematic configuration diagram of a hot water supply apparatus 1 as an embodiment of a refrigeration apparatus according to the present invention. The hot water supply device 1 is a device that creates hot water by performing a two-stage compression refrigeration cycle using a refrigerant (here, carbon dioxide) that operates in a supercritical region.

  The hot water supply device 1 has a water circuit 90 and a refrigerant circuit 10.

(Water circuit)
As shown in FIG. 1, the water circuit 90 includes a water inlet pipe 92 that guides water supplied from the outside to a heat source side heat exchanger 4 described later by a pump 91, and hot water from the heat source side heat exchanger 4 to a supply destination. And a water discharge pipe 93 for supplying water. The pump 91 has a motor 91m, and can adjust the amount of water supplied to the heat source side heat exchanger 4 by control.

(Refrigerant circuit)
The refrigerant circuit 10 mainly includes a compression mechanism 2, a heat source side heat exchanger 4, an expansion mechanism 5, a use side heat exchanger 6, an intermediate refrigerant pipe 22, an intermediate cooler 7, and the like.

  In the present embodiment, the compression mechanism 2 compresses the refrigerant in two stages with two compression elements.

  The intermediate refrigerant pipe 22 is a pipe that guides the refrigerant discharged from the low-stage compression element of the compression mechanism 2 to the high-stage compression element.

  The intermediate cooler 7 is an external cooling device that reduces the amount of compression work by cooling the refrigerant passing through the intermediate refrigerant pipe 22.

  The heat source-side heat exchanger 4 is a heat exchanger that functions as a refrigerant radiator in order to heat the water supplied by the water circuit 90. By heat exchange in the heat source side heat exchanger 4, the refrigerant in the refrigerant circuit 10 dissipates heat, and the water in the water circuit is heated.

  The expansion mechanism 5 is provided between the heat source side heat exchanger 4 and the use side heat exchanger 6 and adjusts the refrigerant flow rate while reducing the pressure of the refrigerant passing therethrough.

  The use side heat exchanger 6 is a finned tube heat exchanger, and exchanges heat between the refrigerant and external air supplied from the blower 3. Here, the use side heat exchanger 6 functions as an evaporator for evaporating the refrigerant decompressed in the expansion mechanism 5. Details of the use side heat exchanger 6 will be described later.

  The blower 3 has a motor 3m, and can adjust the amount of air supplied to the use side heat exchanger 6.

  The refrigerant evaporated in the use side heat exchanger 6 is sucked into the compression mechanism 2 to perform a refrigeration cycle.

<1-2> Usage side heat exchanger Next, the detailed configuration of the usage side heat exchanger 6 will be described with reference to the drawings.

  FIG. 2 is a front view of the use side heat exchanger 6. FIG. 3 is a right side view of the use side heat exchanger 6. FIG. 4 is a top view of the use side heat exchanger 6.

  In addition, the air blower 3 is provided in the front side, and the air flow which flows from the back side to the front side is formed. For this reason, hereinafter, the front side means the leeward side, and the back side means the leeward side. The expressions “right side” and “left side” indicate positions when viewed from the front side.

  The use side heat exchanger 6 is configured such that a tube row composed of a plurality of heat transfer tubes passes through a fin group composed of a plurality of fins.

  As shown in FIG. 4 which is a top view, the use side heat exchanger 6 is formed so as to be bent in a substantially L shape and cover the blower 3 from the back side and the left side.

  As shown in FIG. 4, in the use side heat exchanger 6, when the blower 3 is driven, an air flow F is formed in a direction indicated by an arrow.

  Here, the windward fins 61, 62, 63... Are arranged in the thickness direction in a plane-parallel positional relationship with the vertical direction (the depth direction in FIG. 4) as the longitudinal direction. It is composed. Further, the windward side heat transfer tubes 41, 42, 43... Passing through the windward fin group 60 in the plate thickness direction have the plate thickness direction of the fins 61, 62, 63. The windward side heat transfer tube row 40 is configured by being arranged in the vertical direction (depth direction in FIG. 4) in a parallel positional relationship.

  The leeward fins 71, 72, 73... Are the same as the leeward fin group 60 except that they are arranged on the leeward side, and constitute the leeward fin group 70. Also, the leeward heat transfer tubes 51, 52, 53,... Are the same as the leeward heat transfer tube array 40 except that they are arranged on the leeward side, and constitute the leeward heat transfer tube group 50. Yes.

  As will be described later, the use-side heat exchanger 6 functioning as an evaporator of the hot water supply device 1 may be frosted depending on the operating conditions and the ambient temperature. It begins to arise from the windward side of the group 60 and the windward side heat transfer tube group 40.

<1-3> Details of heat transfer tubes All of the heat transfer tubes 41, 42, 43..., 51, 52, 53. Note that the material of the heat transfer tubes 41, 42, 43... 51, 52, 53... Is not limited to copper, and may be formed of, for example, an alloy containing copper.

  When carbon dioxide is used as the working refrigerant in the hot water supply apparatus 1 and a refrigeration cycle having a predetermined efficiency or higher is executed, the pressure becomes high until the refrigerant pressure exceeds the critical pressure. This high pressure is much higher than the high pressure of the refrigeration cycle using a conventional fluorocarbon refrigerant such as R-22, so that the heat transfer tubes 41, 42, 43. As for 52, 53..., Copper is used as the material and the outer diameter is 7 mm in order to ensure the pressure strength. In addition, the thickness of the heat transfer tube can be a value determined based on the pipe diameter, the refrigerant used, and the laws and regulations applied to the target device from the viewpoint of sufficiently ensuring the pressure resistance. The outer diameter of the heat transfer tube is not limited to 7 mm. For example, even if the outer diameter is 4 mm or more and less than 7 mm, the pressure resistance can be ensured.

<1-4> Detailed shape of fin Hereinafter, with reference to FIGS. 5 to 9, the detailed shape of the fin of the use-side heat exchanger 6 will be described by taking the fin 61 and the heat transfer tubes 41 and 42 as examples.

  FIG. 5 is a perspective view showing a state in which the heat transfer tubes 41 and 42 pass through the fin 61.

  FIG. 6 is a front view of the fin 61.

  FIG. 7 is a partially enlarged front view of the fin 61.

  8 is a cross-sectional view of the fin 61 taken along the I-I plane shown in FIG.

  In addition, the air flow direction shown by F in each drawing has shown the air flow direction which arises when the air blower 3 drives, and demonstrates below, showing whether it is an upwind side or a leeward side on the basis of this arrow F.

  The fin 61 has folds P1, P2, P3, plates 61a, 61b, 61c, 61d, through holes O1, O2, slits S11 to S26, cut and raised W11 to W26, and a substantially flat portion R, and is formed of aluminum. Has been. In addition, you may form with the alloy containing not only aluminum but aluminum.

  The fin 61 has a thickness of 0.1 mm per sheet. In addition, this thickness is not restricted to 0.1 mm, For example, you may be larger than 0.05 mm and smaller than 0.50 mm.

  As shown in FIGS. 6 and 8, the fin 61 has folds P <b> 1 and folds P <b> 3 extending parallel to the longitudinal direction of the fin 61 as well as folds P <b> 2 extending parallel to the valleys. Furthermore, it has a waveform shape. As shown in FIG. 8, the inclination of the corrugated shape is such that it rises or falls by 0.3 mm with respect to 4.5 mm.

  Here, the plate 61 a is a plate located on the windward side of the fold line P <b> 1 of the fin 61. The plate 61b is a plate surrounded by the fold line P1 and the fold line P2 of the fin 61. The plate 61c is a plate surrounded by the fold line P2 and the fold line P3 of the fin 61. The plate 61d is a plate located on the leeward side from the fold line P3 of the fin 61.

  A heat transfer tube 41 is provided in the through hole O1. The outer periphery of the heat transfer tube 41 and the inner periphery of the through hole O1 are in close contact with each other. Similarly, the heat transfer tube 42 is provided in the through hole O2. The outer periphery of the heat transfer tube 42 and the inner periphery of the through hole O2 are in close contact with each other. With this close contact shape, the heat of the refrigerant flowing through the heat transfer tubes 41 and 42 can be efficiently transmitted to the fins 61.

  The slits S <b> 11 to S <b> 26 are portions that are cut and raised to provide the W <b> 11 to W <b> 26, and penetrate the fin 61 in the thickness direction. For example, the opening shape of the slit S11 corresponds to the shape of the cut and raised W11 and has a substantially trapezoidal shape. And slit S11 and cut-and-raised W11 are connected via one edge | side of the longitudinal direction of the fin 61 among slit S11. In other words, the slit S11 is an opening generated as a result of cutting the fin 61 and raising it in a direction extending in the plate thickness direction. The direction of the longitudinal direction (direction to be cut and raised) of the fin 61 on one side with respect to the corresponding slit is unified on the same side, which facilitates manufacture. Similarly, the cut-and-raised W11 is a protruding portion that is generated as a result of cutting the fin 61 and raising it in the direction extending in the plate thickness direction.

  It should be noted that an interval is provided between the cut and raised groups W11, W12, and W13 and the cut and raised groups W14, W15, and W16, such as between the cut and raised W11 and the cut and raised W12. For this reason, the air that has been sufficiently heat-exchanged by touching the cut and raised can flow while leaking from between the cut and raised, so that the ventilation resistance does not increase excessively. Moreover, even if it is a case where drain water arises because the space | interval of this cut and raised is provided, the drainage property can be improved.

  Further, these cut and raised portions W11, W14, W21, W24 and the slits S11, S14, S21, S24 are all located within the range of the plate 61a and do not reach the fold line P1. Further, the cuts W12, W15, W22, W25 and the slits S12, S15, S22, S25 are all located within the range of the plate 61b, and have not reached any of the folds P1, P2. Further, the cuts and rises W13, W16, W23, W26 and the slits S13, S16, S23, S26 are all located within the range of the plate 61c, and have not reached any of the folds P2, P3.

  The cut and raised W11 to W26 are provided with cut and raised W11 to W16 disposed in the vicinity of the through hole O1, and cut and raised W21 to W26 disposed in the vicinity of the through hole O2. Of these, the cut-and-raised W11, W12, W13 and the slits S11, S12, S13 are provided on one side in the longitudinal direction of the fin 61 with respect to the through-hole O1. It arrange | positions so that distance with a center line (line of the direction perpendicular | vertical to the longitudinal direction of the fin 61) may become long. Note that the cut-and-raised W11, W12, and W13 are all disposed on the same plane. Similarly, the cut-and-raised W14, W15, and W16 and the slits S14, S15, and S16 are opposite to the other side in the longitudinal direction of the fin 61 (the position where the cut-and-raised W11 and the like are provided) with respect to the through hole O1. The distance from the center line of the through hole O1 (the line in the direction perpendicular to the longitudinal direction of the fin 61) increases toward the windward side. Note that the cut-and-raised W14, W15, and W16 are all arranged on the same plane. Thereby, the cut-and-raised W11 to W16 are arranged such that the distance in the same plate 61a, 61b, 61c increases as it goes to the windward side. Here, it is an angle formed by the line extending in the width direction from the center of the through hole O1 and the intersection of the cut and raised surfaces W11, W12, and W13 and the fin 61, and spreads toward the windward side. The angle of attack is set to be 14 degrees. The angle of attack of 14 degrees is the same for the cut-and-raised W14, W15, and W16, the cut-and-raised W21, W22, and W23, and the cut-and-raised W24, W25, and W26.

  The angle of attack is not limited to 14 degrees. For example, other angles may be adopted as long as they are larger than 10 degrees and smaller than 40 degrees. Here, if the angle of attack is made smaller than 40 degrees, if the angle is made 40 degrees or more, the ventilation resistance against the air flow will increase excessively, and the heat exchange performance as a whole of the use side heat exchanger 6 can be kept good. It is not possible. Also, the reason why the angle of attack is made larger than 10 degrees is that when the angle is made 10 degrees or less, the air flow around the cut and raised portion is too early, and the heat exchange performance cannot be improved.

  As shown in FIG. 7, the substantially flat portion R is formed between the through hole O1 and the through hole O2, and is cut and raised between the cut and raised W14, W15, and W16 and the cut and raised W21, W22, and W23. It is a substantially flat portion where no etc. are provided. In other words, the substantially flat portion R has no cut and raised, slits, and the like, and has only irregularities due to the shape of the corrugated fins 61, and has a very low ventilation resistance. It should be noted that air flow in the heat transfer tubes 41 and 42 and the cut and raised W14, W15, W16, W21, W22 and W23 due to frost formation on the heat transfer tubes 41 and 42 and the cut and raised W14, W15, W16, W21, W22 and W23. Even in a situation where it has become difficult to pass through, the substantially flat portion R is less susceptible to frost formation due to low ventilation resistance, and heat exchange can be continued with the air flow.

  Note that, as described above, since the direction in which the cut-and-raised portions are cut and raised is unified, the arrangement direction of the slits relative to the cut-and-raised portion is also unified, and manufacturing is easy. For this reason, here, when the cut and raised slit is located on the nearest through hole side (for example, the slit S22 for the cut and raised W22), the cut and raised position is made closer to the leeward side (cut and raised W21 and the cut and raised W22). The distance between the cut and raised W22 and the cut and raised W23 is 2.8 mm), and the cut and raised slit is located on the opposite side of the nearest through hole (for example, the same plate 61b In the upper slit S15 for the cut and raised W15, the cut and raised positions are arranged closer to the windward side (the distance between the cut and raised W14 and the cut and raised W15 is 2.8 mm, and the cut and raised W15 and the cut and raised W16 are Is 3.5 mm). Thereby, the air heat-exchanged in the heat transfer tube 42 vicinity becomes easy to flow through slit S22, and makes it difficult to produce a dead water area. In addition, the air exchanged in the vicinity of the heat transfer tube 41 is cut and raised so that the slit W15 is arranged away from the windward side, so that even if the slit is not located between the cut and raised and the heat transfer tube 41, the air is cut off. Air becomes easy to flow through between the raising W15 and the heat transfer tube 41, thereby making it difficult to generate a dead water area.

<1-5> Detailed shape of the cut and raised As shown in FIGS. 8 and 9, the cut and raised W11 to W26 have a generally higher height on the windward side (the length of the fin 61 in the plate thickness direction). It is formed to become.

  Specifically, as shown in FIG. 7, assuming that the upper bottom is the windward side, the lower bottom is the leeward side, and the height is the length of the common side of the slit and the raised part, the shape of each raised part is as follows: become that way. The cut-and-raised W11, W14, W21, and W24 have an upper base of 0.25 mm, a lower base of 1.0 mm, and a height of 1.7 mm. Further, the cut-and-raised W12, W15, W22, and W25 have an upper base of 0.51 mm, a lower base of 0.76 mm, and a height of 2.0 mm. Further, the cut-and-raised W13, W16, W23, and W26 have an upper base of 0.65 mm, a lower base of 0.8 mm, and a height of 2.0 mm. In this way, by forming the upper side of the windward side to be shorter than the lower side, the high uplifting that causes the dead water area is prevented from existing on the windward side of the fin 61. Thereby, even on the leeward side of the cut and raised provided on the windward side, the air flow and the surface of the fin 61 can sufficiently come into contact with each other, and the heat exchange performance is improved. The sides of the cut-and-raised here are designed to be 0.25 mm or more. This is because the aluminum fin of the present embodiment having a thickness of about 0.1 mm is difficult to manufacture even if it is intended to provide a cut-and-raised portion having a side smaller than 0.25 mm.

  The cut and raised is not limited to such a shape. For example, as shown in FIG. 9, the length of each side of the cut and raised W21, W22, and W23 is set to h21f <h21b <h22 <h23 <FP (fin (Pitch).

  Furthermore, in consideration of the corrugated shape of the fins 61, the crease P1 that is a mountain may be formed with a longer leeward cut and a leeward cut of the fold P2 that is a valley. .

<1-6> Fin Stacking State FIG. 10 shows a state where the fins 61, 62, 63, 64, 65... Are stacked to form a fin group.

  In addition, the fin pitch FP which is the space | interval of the plate | board thickness direction between fins here is provided so that it may be larger than 1.0 mm and smaller than 3.0 mm, and is 1.5 mm here. Thus, the amount of heat exchange per unit volume of the use side heat exchanger 6 can be increased by narrowing the fin pitch FP.

  Furthermore, the height of the cut-and-raised W21, W22, and W23 in the fin thickness direction is designed to be 0.9 or less of the fin pitch FP. This makes it easier for air to flow between the upper end of the cut and raised and the lower surface of the fin located above it, so that the air can be prevented from stagnating in the vicinity of the cut and raised, and the heat exchange performance can be improved. It is improving.

<1-7> Relationship between the inner diameter D of the through hole (outer diameter of the heat transfer tube) and each value FIG. 11 shows the inner diameter of the through hole O1 and the through hole O2 (= heat transfer tube) as shown in the simplified shape of the fin 61. ) Is defined as D, the distance between the centers of the through holes O1 and O2 is defined as S1, and the fin width, which is the distance in the direction perpendicular to the longitudinal direction of the fins 61, is defined as S2. .

(About S1 / D)
In the fin 61 of this embodiment, the value obtained by dividing the hole center distance S1 by the outer diameter D of the heat transfer tube is designed to be greater than 3.0. Here, increasing the value of S1 / D means that the distance S1 between the hole centers is longer than the inner diameter D of the through hole (the outer diameter of the heat transfer tube), that is, the number density of the heat transfer tubes is low. Or the heat transfer tube is thin. Here, in FIG. 12, the S1 / D relationship of the conventional heat exchanger without cutting is shown by a dotted line, and the S1 / D relationship of the above embodiment is shown by a solid line. Here, in the conventional heat exchanger, the heat exchange performance ratio decreases from the point where the value of S1 / D exceeds 3, whereas in the use side heat exchanger 6 of the present embodiment, the heat exchange performance ratio. Will fall more slowly than before. In this way, to reduce the tube diameter to increase the strength of the heat transfer tube, or to increase the material cost and the total weight increase due to the increase in the thickness to ensure the pressure resistance, the heat transfer tube Even if the number density is kept small, the heat transfer performance is hardly lowered by the provision of the cut and raised portions. Since this effect becomes larger when the value of S1 / D is 3.5, 3.5 may be used instead of the value of 3.0.

(About S2 / D)
Further, here, the S2 / D value is designed to be larger than 2.2 and smaller than 3.5. In the fin shape in which the value of S2 / D falls within this range, the heat exchange performance ratio can be improved as shown in FIG. Here, when the ratio of S2 / D is 2.2 or less, it becomes difficult to reduce the relationship between the heat transfer tubes, and the heat obtained from the refrigerant flowing through the heat transfer tubes is exchanged with external air. The fin area for heat exchange is insufficient. When the ratio of S2 / D is 3.5 or more, the heat of the refrigerant supplied through the heat transfer tube cannot be transferred to the end in the fin width direction, and heat exchange is performed at the end in the fin width direction. It cannot be performed effectively, but rather the draft resistance increases. For this reason, by adopting a range larger than 2.2 and smaller than 3.5 as a value obtained by dividing the fin width S2 by the outer diameter D of the heat transfer tube, effective heat exchange is achieved while suppressing an increase in ventilation resistance. The required fin area can be secured.

(About W / D)
In the fin 61 of this embodiment, as shown in FIG. 7, the value obtained by dividing the length component W in the air flow direction of the cut and raised by the inner diameter D of the through hole (outer diameter of the heat transfer tube) is 1.0 It is designed to be larger than 2.5.

  When the value of W / D is 1.0 or less, it becomes impossible to sufficiently obtain the effect of the protruding portion that promotes heat transfer. On the other hand, when the value of W / D is 2.5 or more, the air flow cannot be kept well and the heat exchange efficiency is lowered. For this reason, in the fin shape of the present embodiment excluding these ranges, heat transfer can be promoted while maintaining good airflow omission.

<1-8> About Two-row Arrangement As shown in FIG. 4, in the use side heat exchanger 6 of the present embodiment, the fin 61 on the windward side (windward fin group 60) and the fin 71 on the leeward side (leeward) The side fin groups 70) are arranged in parallel. Here, the position of the heat transfer tube provided in the fin 61 on the leeward side and the position of the heat transfer tube provided on the fin 71 on the leeward side are staggered, that is, in the front view, the heat transfer tube and the leeward side It arrange | positions so that a hot tube may look alternately.

  FIG. 14 shows a simplified configuration diagram of a two-row arrangement.

  Here, the fins 61 are arranged on the upstream side, and the fins 71 are arranged on the downstream side.

  The shape of the leeward fin 71 is the same as that of the fin 61 described above.

  Here, for convenience of explanation, an opening provided near the center of the fin 71 and penetrating the heat transfer tube 51 is referred to as a through hole O3.

  Further, as the air flow, it is assumed that, among the fins 61, there are an air flow f1 toward the heat transfer tube 41, an air flow f2 toward the cutting and raising, and an air flow f3 toward the substantially flat portion R.

Here, sufficient heat exchange is performed by passing the air flow f <b> 1 while touching the heat transfer tube 42. Moreover, sufficient heat exchange is performed by passing the air flow f2 while touching the cut and raised provided near the heat transfer tube 42. Further, a part of the air flow f <b> 2 that has flowed so as to avoid cutting and raising flows toward the vicinity of the substantially flat portion R. Further, the air flow f3 includes a part of the air flow f2 that has flowed so as to avoid cutting and raising, and the heat resistance at the substantially flat portion R is low, and the ventilation resistance is low. Sufficient heat exchange is performed by passing toward the heat transfer tube 51 of the fin 71 while touching the heat transfer tube 51. Also,
As a result, the air flow is sufficiently heat exchanged when passing through the use side heat exchangers 6 provided in two rows, even when passing through any location.

  Moreover, even if frost formation occurs on the windward side of the fin 61 on the windward side, it occurs only in the vicinity of the heat transfer tube 42 and in the vicinity of the cut-up and does not occur in the substantially flat portion R. As a result, even in a situation where frost formation occurs, for the air flow f3, some heat exchange at the substantially flat portion and heat exchange in the heat transfer tube 51 can be ensured.

<1-9> Modification A
In the above embodiment, the case where the substantially flat portion R is not cut and raised has been described as an example.

  However, the present invention is not limited to this. For example, as shown in FIG. 15, on the leeward side of the substantially flat portion R, a wall is formed extending in the plate thickness direction and in the longitudinal direction of the fin. You may employ | adopt the fin 261 further provided with raising V1, V2, and V3.

  Here, the air flow passing through the substantially flat portion R can be sufficiently heat-exchanged by cutting and raising the air flow so as to touch the V1. Thereby, even if it is a case where it uses only not one line but one line, it becomes possible to perform heat exchange as a whole.

<1-10> Modification B
In the above embodiment, the case where the fin 61 on the leeward side and the fin 71 on the leeward side have the same shape has been described as an example.

  However, the present invention is not limited to this. For example, as shown in FIG. 16, the leeward fins 361 have the same shape as the fins 61 of the above embodiment, while the leeward fins 371 are cut. It is not provided to be inclined toward the air flow direction like the wakes W11, W12, and W13, but is cut and raised to extend downstream in the plate thickness direction and in the longitudinal direction of the fin on the downstream side of the heat transfer tube 41. K may be located on the downstream side of the heat transfer tube 42, and the cut-and-raised L extending in the plate thickness direction and in the longitudinal direction of the fins to form a wall.

<1-11> Modification C
In the above embodiment, the hot water supply device 1 has been described as an example.

  However, the present invention is not limited to this. For example, as shown in FIG. 17, a refrigeration apparatus 201 that is not limited to water heating may be used.

<1-12> Modification D
In the above embodiment, the case where the cut and raised portions are provided on the upstream side with respect to the line connecting the centers of the through holes O1 and O2 has been described as an example.

  However, the present invention is not limited to this. For example, as shown in FIG. 18, the cut-and-raised portion is not provided on the upstream side with respect to the line connecting the centers of the through holes O1 and O2. A fin 461 provided only in the case may be employed. In this case, it is possible to suppress the ventilation resistance on the windward side where frost formation is likely to occur, and to make frost formation difficult.

  The refrigeration apparatus of the present invention can suppress a decrease in thermal performance due to frosting while suppressing an increase in the cost of the heat exchanger even when it is desired to increase the pressure resistance of the heat transfer tube. Therefore, the present invention is particularly useful when applied to a finned tube heat exchanger that performs heat exchange without bringing fluids into direct contact with each other, a refrigeration apparatus equipped with the heat exchanger, and a hot water supply apparatus.

It is a schematic block diagram of the air conditioning apparatus as one Embodiment of the freezing apparatus concerning 1st Embodiment of this invention. It is a front view of a use side heat exchanger. It is a right view of a use side heat exchanger. It is a top view of a use side heat exchanger. It is a perspective view which shows a mode that the heat exchanger tube has penetrated the fin. It is a front view of a fin. It is a partial expanded front view of a fin. It is sectional drawing which shows the II surface shown in FIG. 7 of a fin. It is a shape relation figure of cut and raised. It is a figure which shows the mode of stacking of a fin. It is explanatory drawing which shows the predetermined distance of a fin. It is a figure which shows the relationship between S1 / D and heat exchange performance. It is a figure which shows the relationship between S2 / D and a heat exchange performance ratio. It is explanatory drawing which shows the airflow relationship between the fin on the leeward side and the fin on the leeward side. It is a schematic block diagram of the fin of a modification (A). It is a schematic block diagram of the fin of a modification (B). It is a schematic refrigerant circuit figure of the freezing apparatus of a modification (C). It is a schematic block diagram of the fin of a modification (D).

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Hot-water supply apparatus 2 Compression mechanism 4 Heat source side type heat exchanger 5 Expansion mechanism 6 User side type heat exchanger (fin tube type heat exchanger)
7 Intermediate Cooler 10 Refrigerant Circuit 22 Intermediate Refrigerant Tube 41 Heat Transfer Tube (First Heat Transfer Tube)
42 Heat transfer tube (second heat transfer tube)
61 Fin 71 Downstream fin 90 Water circuit 201 Refrigeration unit FP Fin pitch K Cut and raise (first protruding wall)
L Cut and raise (second protruding wall)
O1 through hole (first through hole)
O2 through hole (second through hole)
O3 through hole (third through hole)
R substantially flat portion S1 distance between hole centers S2 fin width S11 to S26 slit (cut portion)
V1, V2, V3 Cut and raised (protruding wall)
W11-W26 Cut and raise (protrusion)

Claims (21)

A fin tube type heat exchanger (6) for performing heat exchange without directly contacting fluids,
A cylindrical first heat transfer tube (41);
A cylindrical second heat transfer tube (42) having an outer diameter substantially equal to the first heat transfer tube;
A first through hole (O1) whose inner side is in contact with the outer periphery of the first heat transfer tube, a second through hole (O2) whose inner side is in contact with the outer periphery of the second heat transfer tube, and the first through hole or A protrusion provided at a position where the distance from at least one of the second through-holes is within 1/3 of the closest distance between the first through-hole and the second through-hole and protruding in the thickness direction; , (W11 to W26) and a substantially flat portion (R) that is not provided with a shape protruding in the plate thickness direction at a position between the first through hole and the second through hole excluding the protruding portion. The hole center distance (S1), which is the distance from the center of the first through hole to the center of the second through hole, is divided by the outer diameter (D) of the first heat transfer tube. A fin (61) with a value greater than 3.0;
A finned tube heat exchanger (6). Of the lengths of the protrusions (W11 to W26), the length component (W) projected in the direction orthogonal to the longitudinal direction of the fin on the surface of the fin is the outer diameter of the first heat transfer tube. The value divided by (D) is greater than 1.0 and less than 2.5.
The finned tube heat exchanger (6) according to claim 1. The value obtained by dividing the fin width (S2), which is the length of the fin in the direction orthogonal to the longitudinal direction of the fin, on the surface of the fin by the outer diameter (D) of the first heat transfer tube is 2 Greater than 2, less than 3.5,
The finned tube heat exchanger (6) according to claim 1 or 2. The protrusions (W11 to W26) are divided into two areas by the line connecting the vicinity of the center of the first through hole (O1) and the vicinity of the center of the second through hole (O2). Provided only in the area on the leeward side in the air flow direction,
The finned-tube heat exchanger (6) according to any one of claims 1 to 3. The protrusions (W11 to W26) have at least a part of an inclined portion having a long protrusion length that is a length in the plate thickness direction of the fin on the leeward side than on the leeward side in the air flow direction.
The finned tube heat exchanger (6) according to any one of claims 1 to 4. The protrusions (W11 to W26) are separated from the first protrusions (W11, W12) located on the upstream side in the air flow direction and the first protrusions, and are located downstream of the first protrusions. Second protrusions (W12, W13)
The finned tube heat exchanger (6) according to any one of claims 1 to 5. The protrusion length in the plate thickness direction of the first protrusion (W11) is not less than a predetermined length.
The finned tube heat exchanger (6) according to claim 6. A plurality of the fins having a thickness of more than 0.05 mm and less than 0.5 mm is provided per sheet,
The plurality of fins (61, 62, 63) are arranged to overlap each other in the thickness direction,
An interval (FP) between the fins in the plate thickness direction is larger than 1.0 mm and smaller than 3.0 mm.
The finned tube heat exchanger (6) according to any one of claims 1 to 7. The value obtained by dividing the length in the plate thickness direction of the protrusions (W11 to W26) by the interval (FP) in the plate thickness direction between the fins is 0.9 or less.
The finned tube heat exchanger (6) according to claim 8. The fin (61) has a plurality of folds extending in the longitudinal direction.
The finned-tube heat exchanger (6) according to any one of claims 1 to 9. The protrusions (W11 to W26) are separated from the first protrusions (W11, W12) located on the upstream side in the air flow direction and the first protrusions, and are located downstream of the first protrusions. A second protrusion (W12, W13)
The first protrusion and the second protrusion are each positioned between a plurality of folds (P1, P2, P3) of the fin and are not positioned on the folds.
The finned-tube heat exchanger (6) according to claim 10. The fin (61) has projecting walls (V1, V2, V3) extending in the longitudinal direction of the fin and the plate thickness direction of the fin at a position downstream of the substantially flat portion (R) in the air flow direction. Have
The finned tube heat exchanger (6) according to any one of claims 1 to 11. It further includes a cylindrical third heat transfer tube (51),
The fin (61) is located in the downstream direction of the air flow with respect to the substantially flat portion (R), and further has a third through hole (O3) whose inner side is in contact with the outer periphery of the third heat transfer tube. Have
The finned tube heat exchanger (6) according to any one of claims 1 to 12. A cylindrical third heat transfer tube (51);
A downstream fin (71) having a third through hole (O3) whose inner side is in contact with the outer periphery of the third heat transfer tube;
Further comprising
The third heat transfer tube and the downstream fin are located in the downstream direction of the air flow with respect to the first heat transfer tube, the second heat transfer tube and the fin,
The third heat transfer tube is located on the downstream side of the air flow with respect to the substantially flat portion (R).
The finned tube heat exchanger (6) according to any one of claims 1 to 12. A cylindrical third heat transfer tube (51);
A downstream fin (71) having a third through hole (O3) whose inner side is in contact with the outer periphery of the third heat transfer tube;
Further comprising
The downstream fin has a first projecting wall (K1, K2, K3) and a second projecting wall (L1, L2, L3) extending in the longitudinal direction of the downstream fin and the plate thickness direction of the downstream fin. The first projecting wall, the third through hole, and the second projecting wall are arranged in this order in the longitudinal direction of the downstream fin,
The third heat transfer tube and the downstream fin are located in the downstream direction of the air flow with respect to the first heat transfer tube, the second heat transfer tube and the fin,
The third heat transfer tube (71) is located in the downstream direction of the air flow with respect to the substantially flat portion (R),
The first protruding wall (K) is located in the downstream direction of the air flow with respect to the first heat transfer tube (41),
The second protruding wall (L) is located in the downstream direction of the air flow with respect to the second heat transfer tube (51),
The finned tube heat exchanger (6) according to any one of claims 1 to 12. The fin (61) has a cut portion (S11 to S26) that is partially cut in the thickness direction.
The protruding portion is a cut-and-raised portion (W11 to W26) obtained by raising the cut portion (S11 to S26) in the thickness direction.
The finned tube heat exchanger (6) according to any one of claims 1 to 15. The cut-and-raised portions (W11 to W26) are shorter on the leeward side than on the leeward side, the distance between the center of the first through hole and the center of the second through hole being closer.
The angle of attack, which is the angle formed by the longitudinal direction of the cut and raised portion and the direction perpendicular to the longitudinal direction of the fin on the surface of the fin, is greater than 10 degrees and less than 40 degrees.
The finned tube heat exchanger (6) according to claim 16. The first heat transfer tube and the second heat transfer tube are made of copper or an alloy containing copper, and have an outer diameter of 4 mm to 7 mm.
The finned-tube heat exchanger (6) according to any one of claims 1 to 17. The working refrigerant is carbon dioxide,
The finned tube heat exchanger (6) according to any one of claims 1 to 18. The finned tube heat exchanger (6) according to any one of claims 1 to 19, wherein the finned tube heat exchanger (6) is allowed to function only as a refrigerant evaporator in a refrigeration cycle and is disposed outdoors.
A blower (3) for supplying an air flow to the finned tube heat exchanger;
A compressor (2);
A heat source side heat exchanger (4);
An expansion mechanism (5);
A refrigeration apparatus (201). The finned tube heat exchanger (6) according to any one of claims 1 to 19, wherein the finned tube heat exchanger (6) is allowed to function only as a refrigerant evaporator in a refrigeration cycle and is disposed outdoors.
A blower (3) for supplying an air flow to the finned tube heat exchanger;
A compressor (2);
A heat source side heat exchanger (4);
An expansion mechanism (5);
A water circuit (90) for supplying water to be heated to the heat source side heat exchanger (4);
A hot water supply device (1).

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