JP2019135418A - Shell-and-tube heat exchanger - Google Patents

Abstract

To solve a problem that dry out is prominently confirmed on flat tube surfaces, in particular, high heat flux areas and an effective heat transfer area is reduced to deteriorate heat transfer performance in a shell-and-tube heat exchanger using flat tubes as heat transfer tubes.SOLUTION: A shell-and-tube heat exchanger includes: heat transfer tubes each comprising a heat transfer part header 11 and a heat transfer part 12; a shell 10 which stores the heat transfer tubes; and nozzles 13 which spray a refrigerant liquid to surfaces of the heat transfer parts 12. The shell 10 comprises: a refrigerant inflow tube 26 which is located at a lower part as seen in a vertical direction and enables the refrigerant liquid to flow thereinto; and a refrigerant outflow tube 27 which is located at an upper part as seen in the vertical direction and discharges the refrigerant liquid.SELECTED DRAWING: Figure 2

Description

  This development relates to a shell and tube heat exchanger using a flat tube as a heat transfer tube.

  In the refrigeration cycle apparatus, a refrigerant circulates as a working medium in a heat pump cycle, an evaporator that evaporates the refrigerant to generate a refrigerant vapor, a compressor that sucks and compresses the refrigerant vapor, and a compressor that compresses the refrigerant And a condenser that sucks and condenses the refrigerant vapor. Among them, the evaporator is a heat exchanger that evaporates the refrigerant liquid by heat absorbed from cold water or the like, and is an indirect heat exchanger that exchanges heat through a heat transfer surface such as a heat transfer tube. FIG. 9 shows a 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. 9, a conventional shell and tube heat exchanger using a flat tube includes an evaporator shell 22, a flat heat transfer tube 23, a nozzle member 24, and a cooling medium inflow tube 25. In this conventional example, the flat heat transfer tubes 23 are horizontally arranged in three rows and four stages. The cooling medium is ejected from the nozzle members 24 provided at both ends of the shell 22 in correspondence with the flat heat transfer tubes 23 of the flat heat transfer tubes 23 arranged horizontally. The cooling medium ejected from the nozzle member 24 flows out in the horizontal direction, contacts the flat surface of the flat heat transfer tube 23, and exchanges heat with the heat medium flowing through the flat heat transfer tube 23.

JP2013-53620A

  In a conventional shell-and-tube heat exchanger using a flat tube, a plurality of flat heat transfer tubes are horizontally stacked, and a refrigerant liquid stays between the flat heat transfer tubes. In particular, when the coolant is used as water, the contact angle is large, so that it is easy to bridge between horizontally arranged flat heat transfer tubes, the liquid film becomes thick, and heat resistance is reduced due to thermal resistance. Therefore, by arranging the flat surface of the flat tube perpendicular to the horizontal, the refrigerant liquid between the flat tubes flows down in the vertical downward direction and does not stay on the flat tube surface. Thereby, thermal resistance can be reduced. However, for the arrangement of the flat tubes, the flow direction of the heat medium and the positional relationship of the refrigerant liquid sprayed on the flat tube surface are important. In a region where the temperature difference between the refrigerant evaporation temperature and cold water is large (for example, near the entrance of the heat medium), a thirsty surface (dryout) occurs, and the effective heat transfer area decreases, resulting in a decrease in heat transfer performance. It had the problem that.

  In order to solve the conventional problem, the shell and tube heat exchanger of the present invention is a shell and tube heat exchanger using a flat tube as a heat transfer tube, and has a plurality of heat transfer tubes having a flat surface on the surface. A plurality of heat transfer tube units arranged in the vertical direction, a nozzle arranged between the plurality of heat transfer tube units in the vertical direction and spraying a refrigerant liquid on the surface of the heat transfer tubes, and the plurality of heat transfer tubes The heat transfer tube unit includes a shell that houses the unit and the nozzle and has a refrigerant inflow pipe that allows the refrigerant liquid to flow in a vertical direction and a refrigerant outflow pipe that discharges the refrigerant liquid in a vertical direction. Moves a heat transfer unit that bundles the heat transfer tubes and a heat transfer medium that is located outside the heat transfer unit and that exchanges heat with the refrigerant liquid via the heat transfer tubes to another adjacent heat transfer tube unit. Heat transfer section header The shell has an inlet for allowing the heat medium to flow downward in the vertical direction, and the heat medium outflow from the lowermost heat transfer tube unit in the vertical direction to the uppermost heat transfer tube unit in the vertical direction. And an outflow port.

  Thereby, a heat medium (for example, cold water) flows from the refrigerant inflow pipe of the heat transfer pipe provided in the lower part of the shell to the upper part. On the other hand, the refrigerant liquid is divided into a plurality of nozzles and sprayed uniformly on the surface of the flat tube. At this time, the refrigerant liquid that has not contributed to evaporation in the flat tube at the upper part of the shell flows down along the surface of the flat tube and reattaches to the flat tube at the lower part. That is, the lower the flat tube, the greater the temperature difference between the evaporation temperature of the refrigerant and the cold water, and the more likely the thirsty surface (dryout) occurs. However, the amount of refrigerant liquid on the tube surface increases compared to the upper tube. As a result, in the region where the temperature difference between the evaporation temperature of the refrigerant and the cold water is large, the occurrence of dryout is suppressed, so the effective heat transfer area is increased and the heat transfer performance is improved.

  According to the shell-and-tube heat exchanger described above, since the temperature difference between the evaporation temperature of the refrigerant and the cold water is large and a sufficient amount of refrigerant liquid is secured in the flat tube in the lower part where a dry surface (dryout) is likely to occur. Suppresses the occurrence of dryout. Thereby, especially in a high heat flux area, an effective heat transfer area increases and heat transfer performance can be improved. As a result, the heat exchange volume can be reduced, and the installation area of the refrigeration cycle apparatus can be reduced.

The block diagram of the refrigerating-cycle apparatus in Embodiment 1 of this invention. The block diagram of the shell and tube heat exchanger in Embodiment 1 of this invention. Sectional drawing of the shell and tube heat exchanger in Embodiment 1 of this invention. Sectional drawing of the heat-transfer part in Embodiment 1 of this invention. The block diagram of the shell and tube heat exchanger in Embodiment 2 of this invention. The block diagram of the shell and tube heat exchanger in Embodiment 3 of this invention. The block diagram of the shell and tube heat exchanger in Embodiment 4 of this invention. Sectional drawing of the heat-transfer part in Embodiment 5 of this invention. The block diagram of the conventional shell and tube heat exchanger.

  A first invention is a shell and tube heat exchanger using a flat tube as a heat transfer tube, including a plurality of heat transfer tubes having a flat surface on a surface, and a plurality of heat transfer tube units arranged in a vertical direction; The nozzle is arranged between the plurality of heat transfer tube units in the vertical direction and sprays the refrigerant liquid on the surface of the heat transfer tube, and the refrigerant that houses the plurality of heat transfer tube units and the nozzle and allows the refrigerant liquid to flow downward in the vertical direction. A shell having an inflow pipe and a refrigerant outflow pipe for discharging the refrigerant liquid in the vertical direction is provided, and the heat transfer tube unit is located adjacent to the heat transfer portion that bundles the heat transfer tubes and the heat transfer portion. A heat transfer section header that moves the heat transfer medium that exchanges heat with the refrigerant liquid to the other heat transfer pipe unit via the heat transfer pipe, and the shell includes an inlet that allows the heat transfer medium to flow downward in the vertical direction. Vertical from the lowest heat transfer tube unit in the vertical direction Until the uppermost heat transfer tube unit in countercurrent, which is constituted so as to have an outlet for heat medium outflow and. A heat medium (for example, cold water) flows from the refrigerant inflow pipe of the heat transfer pipe provided in the lower part of the shell to the upper part. On the other hand, the refrigerant liquid is divided into a plurality of nozzles and sprayed uniformly on the surface of the flat tube. At this time, the refrigerant liquid that has not contributed to evaporation in the flat tube at the upper part of the shell flows down along the surface of the flat tube and reattaches to the flat tube at the lower part. That is, the lower the flat tube, the greater the temperature difference between the evaporation temperature of the refrigerant and the cold water, and the more likely the thirsty surface (dryout) occurs. However, the amount of refrigerant liquid on the tube surface increases compared to the upper tube. As a result, in the region where the temperature difference between the evaporation temperature of the refrigerant and the cold water is large, the occurrence of dryout is suppressed, so the effective heat transfer area is increased and the heat transfer performance is improved.

  According to a second aspect of the present invention, in particular, in the shell-and-tube heat exchanger according to the first aspect of the present invention, the shell stores the refrigerant liquid sprayed from the nozzle below the vertical direction of the shell, and the storage unit and the nozzle A refrigerant liquid circulation circuit that connects to the nozzle, and a refrigerant liquid circulation pump that pumps the refrigerant liquid in the reservoir to the nozzle through the refrigerant liquid circulation circuit and circulates between the nozzle and the reservoir with the refrigerant liquid. It is configured. In order to spray the refrigerant liquid corresponding to the evaporation capacity on the surface of the flat tube, the rotational speed of the refrigerant liquid circulation pump is varied. Thereby, in any operating condition, since the refrigerant liquid suitable for the evaporation amount is sprayed, the thin film having a small liquid film thermal resistance is maintained while the dry-out is suppressed, so that the heat transfer performance is improved.

  In a third aspect of the invention, in particular, in the shell and tube heat exchanger of the first or second aspect of the invention, the refrigerant liquid circulation circuit is provided with an adjustment mechanism for adjusting the flow rate of the nozzle. By adjusting the opening of the valve, the amount of refrigerant liquid sprayed from the nozzle located in the lower part of the shell where the refrigerant liquid easily evaporates is changed to the amount of refrigerant liquid sprayed from the nozzle located in the upper part. Adjust the flow rate so that there is more. Thereby, the spray amount of the refrigerant liquid is sufficiently ensured in the lower portion, and the dry-out is suppressed even when the dry-out particularly easily occurs in an overload state. Therefore, especially in a high heat flux region, the effective heat transfer area is increased and the heat transfer performance is improved.

  In particular, in the shell and tube heat exchanger of the first to third inventions, the fourth invention is such that the surface area of the heat transfer section gradually increases from the inlet to the outlet across the heat transfer header. It is arranged. The heat transfer tube near the inlet provided in the lower part of the shell has a large evaporation amount because the temperature difference between the evaporation temperature of the refrigerant and cold water increases, but the evaporation amount gradually decreases toward the outlet, The surface area of the heat transfer portion is gradually increased from the upstream portion to the downstream portion in accordance with the evaporation amount of each heat transfer portion so that the spray amount per heat transfer area becomes appropriate. Therefore, since a valve for adjusting the spray amount of the refrigerant liquid according to the evaporation amount of each heat transfer section is not required, dryout can be suppressed with a minimum number of components. Thereby, an effective heat transfer area increases and heat transfer performance improves.

  In the fifth invention, particularly in the shell-and-tube heat exchangers of the first to fourth inventions, the flow path cross-sectional area of the heat medium flowing inside the heat transfer section gradually decreases from the inlet toward the outlet. Is arranged. By reducing the cross-sectional area of the chilled water passage from the inlet to the outlet of the heat transfer tube, the flow rate of the chilled water at the outlet increases even with the same chilled water flow rate. As a result, the heat transfer tube in the vicinity of the outlet has a higher heat transfer coefficient in the tube than the inlet, so that the heat transfer performance is improved in the vicinity of the outlet where the amount of evaporation is small without increasing the surface area of the heat transfer section. .

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

(Embodiment 1)
FIG. 1 shows a configuration diagram of a refrigeration cycle apparatus according to Embodiment 1a of the present invention.

  In FIG. 1, a refrigeration cycle apparatus 1 a includes an evaporator 2 that evaporates refrigerant to generate refrigerant vapor, a compressor 4 that sucks and compresses refrigerant vapor, and sucks refrigerant vapor compressed by the compressor 4. The condenser 6 is configured to condense, a heat absorption circuit 8 and a heat radiation circuit 9.

  About the refrigerating-cycle apparatus 1a comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  In FIG. 1, a refrigeration cycle apparatus 1a is a refrigeration cycle apparatus using a refrigerant such as an HFC refrigerant such as R134a or a non-fluorocarbon refrigerant such as ammonia or carbon dioxide as a working medium.

  The evaporator 2 is a heat exchanger that evaporates the refrigerant liquid by absorbing heat from the outside of the refrigeration cycle apparatus 1a and generates refrigerant vapor, and is, for example, a shell-and-tube indirect heat exchanger.

  The compressor 4 is a compressor that absorbs and compresses the refrigerant vapor generated in the evaporator 2, and is, for example, a speed type compressor such as a turbo compressor or a positive displacement compressor such as a screw compressor.

  The condenser 6 is a heat exchanger that introduces the refrigerant vapor compressed by the compressor 4 and dissipates the heat to the outside of the refrigeration cycle apparatus 1a to condense the refrigerant vapor, for example, a shell-and-tube indirect heat exchange. It is a vessel.

  The first refrigerant vapor channel 3 is connected from the refrigerant vapor outlet of the evaporator 2 toward the refrigerant vapor inlet of the compressor 4, and conveys the refrigerant vapor generated in the evaporator 2 to the compressor 4. The second refrigerant vapor channel 5 is connected from the refrigerant vapor outlet of the compressor 4 toward the refrigerant vapor inlet of the condenser 6, and conveys the refrigerant vapor compressed by the compressor 4 to the condenser 6. .

  The refrigerant liquid flow path 7 is connected from the condenser 6 toward the evaporator 2, and conveys the refrigerant liquid in the condenser 6 to the evaporator 2.

  FIG. 2 shows a configuration diagram of the evaporator 2 according to Embodiment 1 of the present invention.

  In FIG. 2, the evaporator 2 is a shell and tube heat exchanger 1b which is an indirect heat exchanger. The shell and tube heat exchanger 1b includes a shell 10, a heat transfer section header 11, a heat transfer section 12, a nozzle 13, an inlet 16, an outlet 17, a refrigerant inlet pipe 26, and a refrigerant outlet pipe 27.

  The flat surface of the heat transfer unit 12 is provided perpendicular to the horizontal, and includes a plurality of heat transfer units 12 so that the flat surfaces face each other. The heat transfer unit 12 includes a plurality of paths, and the end of each heat transfer unit 12 is connected by a heat transfer unit header 11 in the vertical direction.

  The cold water of the heat absorption circuit 8 flows in from the refrigerant inflow pipe 26 located in the lower part of the shell 10, and flows out of the refrigerant located in the upper part of the shell 10 through the plurality of heat transfer part headers 11 and the heat transfer parts 12. It flows out from the pipe 27. That is, the plurality of heat transfer unit headers 11 and the heat transfer units 12 extend from the lower part of the shell 10 toward the upper part in the vertically upward direction.

  The outlet 17 is connected to the first refrigerant vapor channel 3, and the refrigerant vapor generated in the evaporator 2 is conveyed to the compressor 4 via the outlet 17 and the first refrigerant vapor channel 3.

  3 is a cross-sectional view taken along the line AA in FIG. The heat transfer units 12 are arranged in the shell 10 at a predetermined interval (for example, a space interval of 5 mm), and the nozzle 13 is configured to spray the refrigerant liquid toward the gap in the arrangement of the heat transfer units 12. .

  Further, the direction axis of the flat surface of the heat transfer unit 12 and the direction axis of the outlet 17 are arranged in parallel. That is, the space formed between the flat surfaces of the adjacent heat transfer parts 12 has an opening on the outlet 17 side.

  In the present embodiment, the shell 10 has a rectangular cross-sectional shape, but may have a circular cross-sectional shape. Moreover, a pressure vessel may be used.

  FIG. 4 is an enlarged view of a cross section of the heat transfer section 12, for example, a multi-hole flat tube. The heat transfer section 12 includes a flat tube outer wall 18 and a flat tube partition wall 19, and a space surrounded by the flat tube outer wall 18 and the flat tube partition wall 19 serves as a heat medium flow path 20. The flat tube outer wall 18 and the flat tube partition wall 19 are thin plates and have a thickness of about 0.5 to 0.8 mm, for example. On the other hand, the cross-sectional shape of the heat medium flow path 20 has a rectangular shape in the present embodiment, and is, for example, a thin tube shape having a rectangular cross section with a side of about 0.5 to 3 mm. In the present embodiment, the cross-sectional shape of the heat medium flow path 20 is rectangular, but it may be circular, triangular, 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 heat exchanger 1b configured as described above will be described below with reference to FIG.

  In such a configuration, in the shell 10 of the evaporator 2, the refrigerant liquid is sprayed from the plurality of nozzles 13 toward the heat transfer section 12 as atomized refrigerant liquid. The refrigerant liquid sprayed from the plurality of nozzles 13 flows down toward the space formed between the flat surfaces of the adjacent heat transfer units 12 and adheres to the surface of the heat transfer unit 12. The refrigerant liquid attached here exchanges heat with a heat medium (for example, cold water) flowing through the heat medium flow path 20 of the flat tube shown in FIG. 4 to evaporate and become refrigerant vapor on the surface of the heat transfer section 12. .

  At this time, the refrigerant liquid that has not contributed to evaporation in the heat transfer section 12 located above the shell 10 flows down vertically along the flat surface and re-appears on the surface of the heat transfer section 12 below the shell 10. Adhere to. On the other hand, the heat medium flowing through the heat medium flow path 20 of the heat transfer unit 12 flows in from the refrigerant liquid inflow pipe 26 located in the lower part of the shell 10 and passes through the plurality of heat transfer unit headers 11 and the heat transfer units 12. Then, the refrigerant flows out from the refrigerant liquid outflow pipe 27 located above the shell 10. That is, the temperature difference ΔT1 between the temperature (for example, 12 ° C.) and the evaporation temperature (for example, 6 ° C.) of the heat medium passing through the heat transfer section 12 located below the shell 10 is the upper portion of the shell 10. It becomes larger than the temperature difference ΔT2 between the heat medium (for example, 7 ° C.) through which the heat transfer section 12 located in the water passes and the evaporation temperature (for example, 6 ° C.) (ΔT1> ΔT2). Therefore, on the surface of the heat transfer part 12 located in the lower part of the shell 10, the thirty surface (dry out) is increased as compared with the upper part, so that the effective heat transfer area contributing to heat transfer is likely to decrease.

  However, the first embodiment of the present disclosure has the following two features.

  (Feature 1) A shell is arranged between a plurality of heat transfer tube units in the vertical direction, and a nozzle that sprays a refrigerant liquid on the surface of the heat transfer tube is used.

  (Characteristic 2) An inlet through which the shell allows the heat medium to flow downward in the vertical direction, and an outlet from which the heat medium flows out from the lowermost heat transfer tube unit in the vertical direction to the uppermost heat transfer tube unit in the vertical direction; Having

  Therefore, the refrigerant liquid that has flowed down from the upper heat transfer section 12 reattaches to the surface of the heat transfer section 12 at the lower portion of the shell 10. As a result, the amount of refrigerant liquid on the surface of the heat transfer section 12 in the lower part is larger than that in the upper part. As a result, the dryout that tends to occur in the lower part of the shell 10 is suppressed, and therefore, the effective heat transfer area is increased particularly in the high heat flux region, and the heat transfer performance can be improved.

(Embodiment 2)
FIG. 5 shows a configuration diagram of a shell-and-tube heat exchanger 1c according to Embodiment 2 of the present invention.

  In FIG. 5, the evaporator 2 is a shell-and-tube heat exchanger 1 c that is an indirect heat exchanger, and is disposed below the shell 10 of the evaporator 2 from the condenser 6 via the refrigerant liquid flow path 7. The conveyed refrigerant liquid is stored. The refrigerant liquid stored in the evaporator 2 flows into the refrigerant liquid circulation circuit 14 and is pumped to the plurality of nozzles 13 by the refrigerant liquid circulation pump 15.

  About the shell and tube heat exchanger 1c comprised as mentioned above, the operation | movement and an effect | action are demonstrated below. In the second embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof is partially omitted.

  In such a configuration, the refrigerant liquid sprays the refrigerant liquid on the surface of the heat transfer unit 12 by adjusting the discharge pressure by changing the rotation speed of the refrigerant liquid circulation pump 15. As a result, since the refrigerant liquid suitable for the amount of evaporation is sprayed even under any assumed operating conditions, a thin film with low liquid film thermal resistance is maintained while suppressing dryout, so that heat transfer performance is improved. I can do it.

(Embodiment 3)
FIG. 6 shows a configuration diagram of a shell and tube heat exchanger 1d according to Embodiment 3 of the present invention.

  In FIG. 6, the evaporator 2 is a shell and tube heat exchanger 1d which is an indirect heat exchanger, and the refrigerant liquid circulation circuit 14 of the shell and tube heat exchanger 1d is provided with a plurality of valves 21. . The valve 21 is disposed between the refrigerant liquid circulation pump 15 and the nozzle 13.

  About the shell and tube heat exchanger 1d comprised as mentioned above, the operation | movement and an effect | action are demonstrated below. In the third embodiment, the same components as those in the first and second embodiments are denoted by the same reference numerals, and the description thereof is partially omitted.

  In such a configuration, by adjusting the opening of the valve 21, the amount of refrigerant liquid sprayed from the nozzle 13 located in the lower part of the shell 10 where the refrigerant liquid easily evaporates is changed to the nozzle located in the upper part. The flow rate is adjusted so as to be larger than the spray amount of the refrigerant liquid sprayed from 13. As a result, the amount of refrigerant liquid sprayed at the lower part is sufficiently secured, and the effective heat transfer area increases particularly in the high heat flux region in order to suppress dryout even when it is particularly easy to dryout in an overloaded state. , Heat transfer performance is improved.

(Embodiment 4)
FIG. 7 shows a configuration diagram of a shell-and-tube heat exchanger 1e according to Embodiment 3 of the present invention.

  In FIG. 7, the evaporator 2 is a shell and tube heat exchanger 1 e that is an indirect heat exchanger, and the surface area of the heat transfer section 12 is the refrigerant liquid outflow from the refrigerant liquid inflow pipe 26 across the heat transfer section header 11. It is arranged so as to gradually increase toward the tube 27. Specifically, the width of the flat surface of the flat tube of the heat transfer section 12 is increased.

  About the shell and tube heat exchanger 1e comprised as mentioned above, the operation | movement and an effect | action are demonstrated below. In the fourth embodiment, the same components as those in the first to third embodiments are denoted by the same reference numerals, and the description thereof is partially omitted.

  In such a configuration, the heat transfer pipe in the vicinity of the refrigerant liquid inflow pipe 26 has a large evaporation amount due to a large temperature difference between the refrigerant evaporation temperature and cold water, but the evaporation amount gradually decreases toward the refrigerant liquid outflow pipe 27. Therefore, the surface area of the heat transfer section 12 is changed from the refrigerant liquid inflow pipe 26 toward the refrigerant liquid outflow pipe 27 in accordance with the evaporation amount of the heat transfer section 12 so that the spray amount per heat transfer area becomes appropriate. Increase gradually. Therefore, the valve 21 for adjusting the spray amount of the refrigerant liquid from the nozzle 13 in accordance with the evaporation amount of the heat transfer section 12 is not necessary, so that dryout can be suppressed with a minimum number of components. Thereby, an effective heat transfer area increases and heat transfer performance improves.

(Embodiment 5)
FIG. 8 shows a diagram (cross-sectional view) of heat transfer section 12 in the fifth embodiment of the present invention.

  8, (A) to (C) are cross-sectional views of the heat transfer section 12, and the cross-sectional area of the heat medium flow path 20 of the heat medium flowing inside the heat transfer section 12 is the refrigerant inflow. It arrange | positions so that it may become small gradually so that it may become (A)> (B)> (C) toward the refrigerant | coolant outflow pipe 27 from the pipe | tube 26. FIG.

  About the heat transfer part 12 comprised as mentioned above, the operation | movement and an effect | action are demonstrated below. In the fifth embodiment, the same components as those in the first to fourth embodiments are denoted by the same reference numerals, and the description thereof is partially omitted.

  In such a configuration, the refrigerant is arranged such that the cross-sectional area of the heat medium flow path 20 of the heat medium flowing inside the heat transfer section 12 gradually decreases from the refrigerant inflow pipe 26 toward the refrigerant outflow pipe 27. Even when the flow rate of cold water flowing from the inflow pipe 26 is the same, the flow rate of cold water is higher in the heat transfer section 12 near the refrigerant outflow pipe 27 than in the vicinity of the refrigerant inflow pipe 26. As a result, the heat transfer coefficient in the pipe of the heat transfer section 12 in the vicinity of the refrigerant outflow pipe 27 is improved, so that the heat transfer in the heat transfer section 12 in the vicinity of the refrigerant outflow pipe 27 with a small amount of evaporation without increasing the surface area of the heat transfer section 12. Thermal performance is improved.

  As described above, the refrigeration cycle apparatuses 1a to 1e according to the present invention are useful for air conditioners, chillers, heat storage devices, and the like, and are particularly useful for home air conditioners, commercial air conditioners, and the like.

DESCRIPTION OF SYMBOLS 1a Refrigeration cycle apparatus 1b-e Shell and tube heat exchanger 2 Evaporator 3 1st refrigerant | coolant vapor flow path 4 Compressor 5 2nd refrigerant | coolant vapor flow path 6 Condenser 7 Refrigerant liquid flow path 8 Heat absorption circuit 9 Heat radiation circuit 10 Shell 11 Heat transfer section header 12 Heat transfer section 13 Nozzle 14 Refrigerant liquid circulation circuit 15 Refrigerant liquid circulation pump 16 Inlet 17 Outlet 18 Flat tube outer wall 19 Flat tube partition 20 Heat medium flow path 21 Valve 22 Evaporator shell 23 Flat heat transfer tube 24 Nozzle member 25 Cooling medium inflow pipe 26 Refrigerant outflow pipe 27 Refrigerant outflow pipe

Claims (5)

Including a plurality of heat transfer tubes having a flat surface on the surface, and a plurality of heat transfer tube units arranged in a vertical direction;
A nozzle that is arranged between the plurality of heat transfer tube units in a vertical direction and sprays a refrigerant liquid on a surface of the heat transfer tube;
A refrigerant inflow pipe which houses the plurality of heat transfer pipe units and the nozzle and allows the refrigerant liquid to flow downward in a vertical direction;
A refrigerant outlet pipe for discharging the refrigerant liquid in the vertical direction, and a shell having
The heat transfer tube unit is a heat transfer unit that bundles the heat transfer tubes and heat that is located outside the heat transfer unit and performs heat exchange with the refrigerant liquid via the heat transfer tubes to another adjacent heat transfer tube unit. A heat transfer section header for moving the medium,
The shell includes an inflow port for allowing the heat medium to flow downward in the vertical direction, and an outflow port for allowing the heat medium to flow out from the lowermost heat transfer tube unit in the vertical direction to the uppermost heat transfer tube unit in the vertical direction. Having
Shell and tube heat exchanger. The shell has a storage part for storing the refrigerant liquid sprayed from the nozzle below the vertical direction of the shell, a refrigerant liquid circulation circuit that connects the storage part and the nozzle, and the refrigerant liquid circulation circuit A refrigerant liquid circulation pump that pumps the refrigerant liquid in the reservoir through the nozzle and circulates between the nozzle and the reservoir with the refrigerant liquid,
The shell and tube heat exchanger according to claim 1. The refrigerant liquid circulation circuit includes an adjustment mechanism for adjusting the flow rate of the nozzle.
The shell and tube heat exchanger of any one of Claim 1 or Claim 2. The surface area of the heat transfer part is arranged so as to gradually increase from the inlet to the outlet across the heat transfer header.
The shell and tube heat exchanger according to any one of claims 1 to 3. The flow path cross-sectional area of the heat medium that flows inside the heat transfer section is arranged so as to gradually decrease from the inlet to the outlet.
The shell and tube heat exchanger according to any one of claims 1 to 4.

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