JP2019078421A - Shell-and-tube type heat exchanger - Google Patents

Abstract

To provide a shell-and-tube type heat exchanger which reduces pressure loss.SOLUTION: A shell-and-tube type heat exchanger comprises a shell 201, multihole flat pipes 202, a header 203, a spray nozzle 204, a refrigerant circulation circuit 205, a refrigerant circulation pump 206, an inflow pipe 207, and an outflow pipe 208, and the multihole flat pipes 202 are arranged in the vertical direction. The spray nozzle 204 sprays into a gap of the array of the multihole flat pipes 202, and a space formed between the flat surfaces of the adjacent multihole flat pipes 202 has an opening on the outflow pipe 208 side. Thereby, while holding a favorable heat transmission state, pressure loss of refrigerant vapor flowing in a flow passage space does not increase, and evaporation performance can be improved.SELECTED DRAWING: Figure 2

Description

  The present disclosure relates to a shell and tube heat exchanger.

  FIG. 11 shows the configuration of a shell-and-tube heat exchanger using a conventional flat tube described in Patent Document 1. As shown in FIG. As shown in FIG. 11, the conventional shell-and-tube type heat exchanger using a flat tube comprises a shell 1, a flat heat transfer tube 2, a nozzle member 3 and a cooling medium inflow tube 4. The shell-and-tube type heat exchanger according to the conventional example is arranged such that the flat heat transfer tube group 2 has three rows and four stages in a state where the flat surface of each flat heat transfer tube 2 is horizontal. The cooling medium is jetted out correspondingly from the nozzle members 3 provided on both sides of the shell 1 between the flat heat transfer tubes 2 of the flat heat transfer tube 2 group arranged horizontally. The cooling medium ejected from the nozzle member 3 flows horizontally and contacts the flat surface of the flat heat transfer tube 2 to exchange heat with the heat medium flowing inside the flat heat transfer tube 2.

JP, 2013-53620, A

  However, in the case where the flat heat transfer tubes are arranged in a plurality of rows in the horizontal direction as in the above-described conventional configuration, the droplets stay on the flat surface of the flat heat transfer tube when the cooling medium involves evaporation or condensation. The flow path between the heat pipes is blocked and the pressure loss increases. Furthermore, the conventional flat heat transfer tube has a relatively thick flat thickness because of the pipe line that makes the circular pipe flat, and the pressure resistance performance decreases because the flow path is a single hole, so the length of the flat surface It can not be enlarged. For this reason, in the conventional example, although arranged in threes, a space portion formed between the flat heat transfer tubes adjacent in the flat surface direction (the end portion of one flat heat transfer tube and the other flat heat transfer tube Space is large, and this space is large. Disruption of the flow of the cooling medium ejected from the nozzle member in this space increases the pressure loss and impairs the straightness of the movement of the cooling medium. In particular, in a large-capacity system, the number of flat heat transfer tube arrangements increases, and the number of flow disturbances increases. In particular, when the cooling medium ejected from the nozzle member is in the mist state, the cooling medium in the mist state is difficult to reach in the flat heat transfer tube downstream from the nozzle member. In this conventional example, the nozzles are jetted so as to be sandwiched by the nozzle members from both sides in the horizontal direction of the flat heat transfer tube, but when the number of stations becomes more, the nozzles at predetermined intervals of the number of stations in the horizontal direction The need arises to arrange the components. As described above, there is a problem that the evaporation temperature is reduced and the heat transfer performance is reduced since the pressure loss is increased due to the blockage of the flow path due to the stagnation of the cooling medium and the generation of the flow disturbance due to the arrangement of the flat heat transfer tube. The

  The present invention solves the above-mentioned conventional problems, and provides an arrangement configuration of a flat heat transfer tube for reducing pressure loss when a cooling medium flows in a shell, and a flat heat transfer tube structure for realizing the same. It is provided.

  In order to solve the above-mentioned conventional problems, the shell-and-tube heat exchanger of the present invention has a plurality of flat surfaces inclined with respect to the horizontal on the surface, and the plurality of flat surfaces are arranged to face each other A heat transfer pipe, an inflow pipe in which the refrigerant flows in, and an outflow pipe in which the refrigerant flows out, and a shell for accommodating the plurality of heat transfer pipes, formed between the flat surfaces of the adjacent heat transfer pipes The space is formed to have an opening on the outflow pipe side.

  Thus, the refrigerant liquid existing between the flat surfaces of the adjacent heat transfer tubes flows down along the inclination of the flat surfaces of the heat transfer tubes. Further, the refrigerant vapor present around the heat transfer tube moves toward the outflow tube. At this time, the moving refrigerant vapor moves along the flat surface of the heat transfer pipe, and moves to the outflow pipe through the opening on the outflow pipe side constituted by the flat surface of the adjacent heat transfer pipes, so evaporation on each heat transfer surface The vaporized refrigerant vapor travels to the outflow pipe along the shortest path.

  The shell-and-tube heat exchanger of the present disclosure can minimize the pressure loss in the shell accompanying the movement of the working fluid.

  Further, as a result, since the average evaporation temperature can be maintained, the temperature difference between the working fluid and the heat source can be reduced. That is, since the pressure ratio between the suction pressure and the discharge pressure of the compressor in the refrigeration cycle apparatus can be reduced, the power consumption of the compressor can be reduced, and the system performance can be improved.

Refrigeration cycle diagram of a water-cooled refrigeration system for carrying out the present disclosure Lateral cross-sectional view of an evaporator for practicing the present disclosure Horizontal cross-sectional view of an evaporator for practicing the present disclosure Sectional view from the front of the evaporator for carrying out the present disclosure Sectional drawing in the modification of the secondary side channel of the evaporator for carrying out the present disclosure Illustration of a first variant of the arrangement of multi-hole flat tubes for implementing the present disclosure Diagram of a second variant of the multi-hole flat tube arrangement for practicing the present disclosure Enlarged view of the cross section of a multi-hole flat tube Arrangement plan of conventional flat heat transfer tubes and multi-hole flat tubes of the present disclosure State diagram of multi-hole flat tube and nozzle spray for practicing the present disclosure Configuration diagram of heat exchanger using conventional flat heat transfer tube

  The first disclosure has a flat surface inclined with respect to the front surface on the surface, and the plurality of heat transfer pipes arranged so as to face the flat surface, the inflow pipe into which the refrigerant flows, and the refrigerant flow And a shell for accommodating the plurality of heat transfer tubes, and a space formed between the flat surfaces of the adjacent heat transfer tubes is formed to have an opening on the side of the discharge tube. It is a thing.

  Thus, the refrigerant liquid present between the flat surfaces of the adjacent heat transfer tubes flows down along the inclination of the flat surfaces of the heat transfer tubes. Further, the refrigerant vapor present around the heat transfer tube moves toward the outflow tube. At this time, the moving refrigerant vapor moves along the flat surface of the heat transfer pipe, and moves to the outflow pipe through the opening on the outflow pipe side constituted by the flat surface of the adjacent heat transfer pipes, so evaporation on each heat transfer surface The vaporized refrigerant vapor travels to the outflow pipe along the shortest path.

  For this reason, since the refrigerant vapor travels along the shortest path to the outflow pipe in a smooth flow, the pressure loss when the refrigerant vapor travels in the shell is reduced. Further, even under the condition that the spray amount of the refrigerant liquid to the heat transfer pipe becomes excessive with the decrease of the cooling load, the refrigerant liquid passes without being bridged between the flat surfaces of the heat transfer pipe. Since the flow passage area does not decrease, the increase in pressure loss can be suppressed. For this reason, evaporation performance can be improved.

  According to a second disclosure, particularly in the first invention, the heat transfer tube is a multi-hole flat tube.

  As a result, since the heat transfer tube is a multi-hole flat tube, the heat transfer tube has a partition that divides the flow passage in the tube, and the pressure resistance in the width direction and the thickness direction increases in the heat transfer tube cross section. Thereby, the width of the flat surface (the length in the direction in which the in-pipe flow channels are arranged) can be increased. In addition, the thickness of the flat tube can be reduced. That is, the number of flat tubes arranged in the flat surface direction can be reduced per width of the same distance.

  For this reason, the end gap between the flat tubes arranged in the flat surface direction is reduced. Therefore, the disturbance of the flow of the refrigerant vapor along the flat surface which has been generated in the end gap can be reduced, and the pressure loss can be reduced. In particular, in a large-capacity system, an increase in pressure loss can be suppressed even when the number of flat tubes is increased. For this reason, evaporation performance can be improved.

  Further, as an additional effect, since the flow passage interval between the heat transfer tubes can be narrowed, it is possible to suppress the deterioration of the secondary side diversion and to reduce the header volume and achieve miniaturization.

  According to a third disclosure, particularly in the first or second invention, a nozzle for spraying a refrigerant liquid on the surface of the heat transfer tube is provided.

  As a result, a flow passage space constituted by the flat surfaces of the adjacent flat tubes is obtained. The refrigerant liquid sprayed on the surface of the flat tube exchanges heat with the heat medium flowing in the flat tube, evaporates and evaporates, and functions as an evaporator.

  The sprayed refrigerant liquid flows into the flow passage space constituted by the flat surfaces of the adjacent flat tubes as the refrigerant liquid in a finely atomized state. The refrigerant liquid in the atomized state which has flowed in is uniformly and thinly in contact with the flat surface of the flat tube, and is evaporated and vaporized by heat exchange on the flat surface (heat transfer surface). The evaporated and vaporized refrigerant vapor travels along the flat surface in the flow path space formed by the flat surfaces of the adjacent flat tubes. At this time, since the particle size of the droplets present in the flow passage space is small, the flow passage space is not blocked. In addition, the spray nozzle can be freely disposed in accordance with the disposition direction of the flat surface of the flat tube, and the spray can have directivity.

  For this reason, the refrigerant liquid contacts the flat surface of the flat tube uniformly and in a thin film state. The refrigerant liquid sprayed on the surface of the flat tube exchanges heat with the heat medium flowing in the flat tube, evaporates and evaporates, and functions as an evaporator. The evaporated and vaporized refrigerant vapor travels along the flat surface in the flow path space formed by the flat surfaces of the adjacent flat tubes. At this time, since the particle size of the droplets present in the flow passage space is fine, when moving the flow passage space to the heat transfer surface, the flow passage space is blocked because the liquid is uniformly diffused in the flow passage space in the atomized state. do not do. For this reason, even when acting as an evaporator, the blockage of the flow passage space by the refrigerant liquid sprayed to the heat transfer pipe in addition to the refrigerant vapor moving in the flow passage space can be suppressed, so an increase in pressure loss is suppressed. be able to.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention is not limited by the embodiment.

Embodiment 1
FIG. 1 shows a refrigeration cycle diagram of a water-cooled refrigerator for implementing the present disclosure.

  In FIG. 1, a refrigeration cycle apparatus 100 includes an evaporator 101, a compressor 102, a condenser 103, a flow valve 104, and flow paths 110a to 110d. The outlet of the evaporator 101 is connected to the suction port of the compressor 102 by a flow path 110a. The outlet of the compressor 102 is connected to the inlet of the condenser 103 by a flow path 16 b. The outlet of the condenser 103 is connected to the inlet of the flow valve 104 by a flow passage 110c. The outlet of the flow valve 104 is connected to the inlet of the evaporator 101 by a flow path 110 d. The flow paths 110a and 110b are steam paths, and the flow paths 110c and 110d are liquid paths. Each path is constituted by, for example, at least one metal pipe.

  Thus, the refrigeration cycle is configured, and the refrigerant is heated and evaporated in the evaporator 101. Thereby, a gas phase refrigerant (refrigerant vapor) is generated. The generated gas phase refrigerant is sucked into the compressor 102 and compressed. A gas phase refrigerant compressed to a high temperature and high pressure is supplied from the compressor 102 to the condenser 103. The supplied high temperature / high pressure gas phase refrigerant is cooled by the condenser 103 and is condensed and liquefied to generate a liquid phase refrigerant (refrigerant liquid). The liquid phase refrigerant is returned from the condenser 103 to the evaporator 101 as a liquid phase refrigerant via the flow rate valve 104.

  The refrigeration cycle apparatus 100 is, for example, a commercial or home air conditioner. The heat medium cooled by the evaporator 101 is supplied to the room and used for cooling the room. Alternatively, the heat medium heated by the condenser 103 is supplied into the room and used to heat the room. The heat medium is, for example, water. However, the refrigeration cycle apparatus 100 is not limited to the air conditioning apparatus, and may be another apparatus such as a chiller or a heat storage apparatus.

  Next, FIG. 2 is a cross-sectional view of the evaporator 101 (A-A cross section in FIG. 1). As shown in FIG. 2, the evaporator 101 is configured of a shell-and-tube heat exchanger. Specifically, the main components include a shell 201, a multi-hole flat tube 202, a header 203, a spray nozzle 204, a refrigerant circulation circuit 205, a refrigerant circulation pump 206, an inflow pipe 207, and an outflow pipe 208. The flow path 110 d and the flow path 110 a can be connected to the inflow pipe 207 and the outflow pipe 208, respectively. The multi-hole flat tube 202 is vertically disposed, and the ends of the multi-hole flat tube are connected by the header 203 in the vertical direction. Further, the spray nozzle 204 is disposed to spray horizontally from the side toward the multi-hole flat tube 202, and the spray nozzle 204a is disposed toward the outflow pipe 208, and the cross section of the outflow pipe 208 flows in the flow direction The spray nozzle that sprays the refrigerant liquid to the multi-hole flat tubes 202 disposed in the projection area viewed from (axial direction) is disposed in the direction opposite to the outflow direction of the outflow pipe 208. As shown in FIG. 2, the width (W1) of the header 203 is larger than the width (W2) of the multi-hole flat tube 202 group. With such a configuration, the possibility of the refrigerant liquid flowing down from the end of the header adhering to the multi-hole flat tube 202 can be reduced.

  FIG. 3 shows a cross section B-B in FIG. The multi-hole flat tubes 202 are arranged at predetermined intervals (for example, a space of 5 mm) in the shell 201, and the spray nozzles 204 are directed to the gaps of the array of the multi-hole flat tubes 202 in the liquid phase refrigerant (not shown) ) To spray. The spray nozzle 204 a is a spray nozzle that sprays the refrigerant liquid on the multi-hole flat tubes 202 arranged in the projection area when the cross section of the outflow pipe 208 is viewed from the flow direction (axial direction). And are arranged in the opposite direction. Further, the direction axis (α axis) of the flat surface of the multi-hole flat tube 202 and the direction axis (β axis) of the outlet pipe 207 are disposed in parallel. That is, the opening 210 of one space constituted by the ends of the multi-hole flat tubes 202 adjacent to each other opens in the direction in which the outflow pipe 208 is disposed. The header 203 of the multi-hole flat tube 202 shown in FIG. 2 is connected to the tube sheet cover 209, and the heat medium on the secondary side flows from the tube sheet cover 209. Also in FIG. 3, as in FIG. 2, the width of the header 203 is larger than the width of the multi-hole flat tube 202 group. With such a configuration, the possibility of the refrigerant liquid flowing down from the end of the header adhering to the multi-hole flat tube 202 can be reduced.

  In the present embodiment, the shell 201 has a rectangular cross-sectional shape, but may have a circular cross-sectional shape. Moreover, it may be a pressure-resistant container.

  FIG. 4 shows a cross section taken along the line C-C in FIG. The multi-hole flat tube 202 is vertically disposed, and the inlet (lower) and the outlet (upper) of the multi-hole flat tube 202 are connected to the header 203. The inlet and outlet of the header 203 are connected to the tube sheet cover 209. The tube sheet cover 209a is provided with an inlet pipe 301 through which the heat medium flows, and the tube sheet cover 209b is provided with an outlet pipe 302 through which the heat medium heat-exchanged in the multi-hole flat pipe 202 flows out. The flow path is partitioned by the partition plate 303 in the tube sheet cover 209, and the inside of the tube sheet cover 209 is partitioned so that the heat medium flowing out of the header 203 flows into the header 203 immediately above.

  FIG. 5 is a modification of the secondary side flow passage. The tube sheet cover 209 is installed on one side of the shell 201, and the inlet pipe 301 and the outlet pipe 302 are provided on the same tube sheet cover 209. Although the flow direction of the heat medium on the secondary side is the same in the configuration flowing from the bottom to the top, since the inlet pipe 301 and the outlet pipe 302 are provided on the same side with respect to the shell 201, both shown in FIG. As compared with the type provided with the tube sheet tube bar 209 on the side, it can be miniaturized in the width direction by the thickness of the tube sheet cover 209.

  6 and 7 show modifications of the arrangement of the multi-hole flat tube 202. FIG. 6 shows the case where it is inclined as seen from the direction of the outflow pipe 208, and FIG. 7 shows the case where it is inclined as seen from the tube sheet cover 209 side. In FIG. 6, the connection of the header 203 is at the top and bottom of the multi-hole flat tube 202 and is similar to the case shown in FIGS. 4 and 5, but the distance can be reduced in the height direction The height of the shell 201 can be lowered. Further, in FIG. 7, the multi-hole flat tube 202 is arranged in the horizontal direction and has an inclination, and the inlet and the outlet of the multi-hole flat tube 202 are disposed on the tube sheet cover 209 side, and the header 203 is required. Thus, the size and weight can be reduced.

  FIG. 8 is an enlarged view of the cross section of the multi-hole flat tube 202. The multi-hole flat tube 202 is composed of an outer wall 401 and a partition 402, and a space surrounded by the outer wall 401 and the partition 402 becomes a heat medium flow path 403. The outer wall 401 and the partition 403 are thin plates, and have a thickness of, for example, about 0.5 to 0.8 mm. On the other hand, the cross-sectional shape of the heat medium channel 403 is quadrangular in the present embodiment, and for example, it has a capillary shape having a quadrangular cross section of about 0.5 mm to 3 mm on one side. In the present embodiment, the cross-sectional shape of the heat medium channel 403 is a square, but may be a circle, a triangle, or the like. Further, the surface area may be increased by forming fine grooves or fins on the inner wall surface in the flow direction of the flow path.

  The operation and action of the shell-and-tube evaporator configured as described above will be described below.

  In such a configuration, the refrigerant liquid is heated and evaporated in the evaporator 101. The vaporized low temperature low pressure refrigerant vapor is drawn into the compressor 102 through the flow path 110a and compressed into high temperature high pressure refrigerant vapor. The compressed high-temperature and high-pressure refrigerant vapor flows into the condenser 103 through the flow path 110b. The high-temperature, high-pressure refrigerant vapor that has flowed into the condenser 103 is cooled by the condenser 103 and is condensed and liquefied. The condensed and liquefied high-pressure refrigerant liquid is returned to the evaporator 101 as a low-pressure refrigerant liquid from the flow path 110d while being decompressed through the flow path 110c and being reduced via the flow rate valve 104.

  In such a refrigeration cycle, in the evaporator 101, the refrigerant liquid (not shown) pressure-fed by the refrigerant liquid circulation pump 206 passes through the refrigerant liquid circulation circuit 205 to form a multi-hole flat as refrigerant liquid in an atomized state from the spray nozzle 204. It is sprayed towards the tube 202. The refrigerant liquid in the atomized state sprayed from the spray nozzle 204 flows into the space sandwiched by the adjacent multi-hole flat tubes 202 and moves toward the opening 210 located on the outflow tube 208 side, It adheres to the flat surface. The refrigerant liquid in the atomized state exchanges heat with the heat medium (not shown) flowing in the heat medium flow of the multi-hole flat tube 202 shown in FIG. Become. The generated refrigerant vapor moves in the space sandwiched by the multi-hole flat tube 202 toward the opening 210 located on the outflow pipe 208 side and flows out from the outflow pipe 208.

  At this time, as shown in FIG. 3, the multi-hole flat tube 202 is arranged in two in the present embodiment in the β-axis (x-axis) direction. A space E is formed between the multi-hole flat pipe 202 on the upstream side and the multi-hole flat pipe 202 on the downstream side located on the spray nozzle 204 side, and the refrigerant liquid in the atomized state and the multi-hole are sprayed from the spray nozzle 204. The refrigerant vapor evaporated on the heat transfer surface of the flat tube 202 moves from the upstream multi-hole flat tube 202 to the downstream multi-hole flat tube 202 beyond the space E formed.

  Here, FIG. 9 (a) is a case where the conventional flat heat transfer tubes 2 are continuously arranged, and FIG. 9 (b) is a view when the multi-hole flat tube 202 of the present embodiment is continuously arranged. The conventional flat heat transfer tube shown in FIG. 9 (a) has a relatively thick flat thickness because it is a pipe line that flattens a circular pipe, and the pressure resistance performance is lowered because the flow path is a single hole. The face length can not be increased. Therefore, in order to ensure the same length (the same heat transfer area), a plurality of continuous arrangements are required. That is, the number of spaces E formed by the upstream flat heat transfer pipe 2 and the downstream flat heat transfer pipe 2 is also plural. On the other hand, when the multi-hole flat tube 202 is used, as shown in FIG. 9B, the number of spaces E decreases and the size of the space E in the cross-sectional direction decreases.

  In this space E, in the flow of the atomized refrigerant liquid and the evaporated refrigerant vapor generated in the atomized state, behind the obstacle (for example, Karman vortex generated behind the cylinder placed in the flow field) Flow turbulence occurs due to the generated vortices. This impairs the straightness of the flow and can be a factor of pressure loss. In addition, it is difficult for the refrigerant liquid in the atomized state to be sprayed by the spray nozzle 204 to reach the flat heat transfer tube 2 located downstream with the disturbance of the flow. On the other hand, as compared with the conventional flat heat transfer tube 2 as described above, in the multi-hole flat tube 202, it is possible to reduce the place where the flow disturbance occurs and to reduce the size of the disturbance. . For this reason, the atomized refrigerant liquid that has been sprayed can easily reach the surface of the multi-hole flat tube 202 downstream. In addition, pressure loss can be reduced also in the flow of refrigerant vapor generated by evaporation.

  Furthermore, in the conventional flat heat transfer tube 2, the thickness (the distance of the flat surface tube) of the heat transfer tube is larger than that of the multi-hole heat transfer tube 202. That is, the ratio of the area occupied by the end portion (arc portion) of the flat heat transfer tube 2 is larger than that of the multi-hole flat tube 202. In this case, even when the flat heat transfer tubes 2 are arranged in series, the front flat heat transfer tubes 2 become a shadow of the rear flat heat transfer tubes 2 and the refrigerant liquid can not reach the end (arc). On the other hand, even when the multi-hole flat tubes 202 are similarly arranged, the ratio of the area occupied by the end portion (arc portion) is small because the distance between flat surfaces (the thickness of the multi-hole flat tube 202) is small. Since the portion shaded by the multi-hole flat 202 disposed forward is small, the obstruction of the refrigerant liquid from reaching the end (arc) is alleviated. Also in this case, in the multi-hole flat tube 202, a good state can be formed in the contact between the heat transfer surface and the refrigerant liquid, and the heat transfer performance can be improved.

  Furthermore, since one of the flow path spaces formed by the parallel multi-hole flat tubes 202 opens to the outflow pipe 208 side, the refrigerant vapor evaporated on each heat transfer surface of the multi-hole flat tubes 202 is Since the flow path space can be moved toward the outflow pipe 208 in the shortest distance, the pressure loss due to the movement distance in the flow path space can be minimized. Furthermore, since the multi-hole flat tube 202 is vertically disposed in the present embodiment, for example, the amount of sprayed refrigerant liquid to the heat transfer tube becomes excessive with a decrease in cooling load. Even under normal conditions, the refrigerant liquid flows down the flow passage space between the flat surfaces of the heat transfer tube, and the excess refrigerant liquid does not stay in the flow passage space, and the flow passage area through which the refrigerant vapor passes does not decrease. Therefore, the increase in pressure loss can be suppressed. Therefore, the average evaporation temperature can be maintained without lowering the evaporation pressure, and the evaporation performance can be improved.

  Moreover, FIG. 10 is a state figure at the time of combining the spray nozzle 204 which sprays a refrigerant | coolant liquid with the multi-hole flat tube 202. As shown in FIG. As shown in FIG. 10, by combining the multi-hole flat tube 202 with the spray nozzle 204 for spraying the coolant liquid, it is possible to realize an appropriate spray state of the coolant liquid regardless of the arrangement direction of the multi-hole flat tube 202. In addition, the refrigerant liquid can be circulated between the multi-hole flat tubes 202 in an atomized state. At this time, even when the multi-hole flat tubes 202 are arranged in series as shown in FIG. 9 (b), the sprayed refrigerant liquid can sufficiently reach the multi-hole flat tubes 202 located at the rear without impairing the rectilinearity. In addition to the above, the refrigerant liquid in the atomized state shown in the region S in FIG. 10 is uniformly applied to the flat surface (heat transfer surface) of the multi-hole flat tube 202 while passing between the multi-hole flat tubes 202 aligned in parallel. Adhere to. Furthermore, since the adhering refrigerant liquid adheres in atomized form, as shown in the region L in FIG. 10, the liquid film thickness on the heat transfer surface can be made uniform and thin, so that the heat of the liquid film itself The resistance can be reduced, and the heat transfer performance can be improved. Furthermore, in the flow passage space constituted by the multi-hole flat tubes 202 arranged in parallel, the refrigerant liquid in an atomized state moves with the evaporated refrigerant vapor on the heat transfer surface of the multi-hole flat tubes 202, At this time, the refrigerant liquid is in an atomized state, and the flowability of the fluid is promoted by the arrangement of the multi-hole flat tubes 202 having a small thickness, so that the flow path space is hardly clogged by the refrigerant liquid. Thus, the evaporation performance can be improved without increasing the pressure loss of the refrigerant vapor flowing in the flow passage space while maintaining a good heat transfer state.

  The shell and tube evaporator disclosed herein is particularly useful for air conditioners such as commercial air conditioners. The refrigeration cycle apparatus disclosed in the present specification is not limited to an air conditioner, and may be another apparatus such as an absorption refrigerator, a chiller, a heat storage apparatus, and the like.

201 Shell 202 Multi-hole flat tube (heat transfer tube)
204 Spray nozzle (nozzle)
207 inflow pipe 208 outflow pipe

Claims (3)

A plurality of heat transfer tubes having flat surfaces inclined with respect to the horizontal on the surface, the flat surfaces being arranged to face each other;
A shell having an inflow pipe into which the refrigerant flows and an outflow pipe from which the refrigerant flows out, the shell containing the plurality of heat transfer pipes;
A space formed between flat surfaces of adjacent heat transfer tubes has an opening on the outflow tube side, and a shell-and-tube heat exchanger. The shell-and-tube heat exchanger according to claim 1, wherein the heat transfer tube is a multi-hole flat tube. The shell and tube type heat exchanger according to claim 1, further comprising a nozzle for spraying a refrigerant liquid on a surface of the heat transfer tube.