Shell and tube type heat exchanger and refrigeration cycle device

Abstract

To provide a shell-and-tube type heat exchanger having an excellent heat transfer performance.SOLUTION: An evaporator 101 is constituted by a shell-and-tube-type heat exchanger. The evaporator 101 includes: a plurality of heat transfer pipes 22 in which first fluid flows; and a plurality of nozzles 24 for spraying second fluid toward the plurality of heat transfer pipes 22. When a direction in parallel with a longer direction of the plurality of heat transfer pipes 22 is defined as an X direction, a direction vertical to the X direction is defined as a Y direction, and a direction perpendicular to the X direction and the Y direction is defined as a Z direction, the plurality of nozzles 24 includes: a plurality of first nozzles 24a for spraying the second fluid toward a second side from a first side in the Z direction; and a plurality of second nozzles 24b for spraying the second fluid toward the second side from the first side in the Z direction. In a projection image acquired by projecting the plurality of first nozzles 24a and the plurality of second nozzles 24b in the Z direction, the plurality of first nozzles 24a and the plurality of second nozzles 24b show a zigzag-like arrangement pattern.SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present disclosure relates to a shell-and-tube heat exchanger and a refrigeration cycle device. [Background technology]

[0002] There is a known technology for cooling the refrigerant inside a heat transfer tube by spraying cooling water toward the heat transfer tube. Fig. 11 shows a conventional evaporative condenser described in Patent Document 1 (Fig. 9). Spray section 330 of evaporative condenser 300 has a plurality of spray nozzles 334 that sprays cooling water CW toward condensation coil 326. Heat exchange between cooling water CW and refrigerant R flowing through condensation coil 326 causes cooling water CW to evaporate, and refrigerant R to be cooled and condensed. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] International Publication No. 2017 / 073367 Summary of the Invention [Problem to be solved by the invention]

[0004] When the configuration shown in Fig. 11 is applied to a shell-and-tube heat exchanger, rough areas where liquids such as cooling water are difficult to spray occur between adjacent nozzles, causing the surface of the heat transfer tube to dry out. Furthermore, when there are many stages of heat transfer tubes, dryout occurs continuously in the direction of the stages at specific positions. When dryout occurs, the shell-and-tube heat exchanger cannot exhibit sufficient heat transfer performance.

[0005] The present disclosure provides a shell-and-tube heat exchanger having excellent heat transfer performance. [Means for solving the problem]

[0006] The shell-and-tube heat exchanger of the present disclosure comprises: A shell, A plurality of heat transfer tubes arranged in parallel to each other inside the shell, through which a first fluid flows; a plurality of nozzles disposed within the shell and configured to spray a second fluid toward the plurality of heat transfer tubes; Equipped with When the direction parallel to the longitudinal direction of the heat transfer tubes is defined as the X direction, the direction perpendicular to the X direction is defined as the Y direction, and the direction perpendicular to the X direction and the Y direction is defined as the Z direction, the plurality of nozzles include a plurality of first nozzles that spray the second fluid from a first side toward a second side in the Z direction, and a plurality of second nozzles that spray the second fluid from the first side toward the second side in the Z direction, In a projection image obtained by projecting the plurality of first nozzles and the plurality of second nozzles in the Z direction, the plurality of first nozzles and the plurality of second nozzles exhibit a staggered arrangement pattern.

[0007] The refrigeration cycle device of the present disclosure comprises: The present disclosure is provided with a shell-and-tube heat exchanger. Effect of the Invention

[0008] According to the present disclosure, a shell-and-tube heat exchanger having excellent heat transfer performance can be provided. [Brief description of the drawings]

[0009] [Figure 1] FIG. 1 is a configuration diagram of a refrigeration cycle device according to a first embodiment of the present disclosure. [Diagram 2] Longitudinal cross-section of the evaporator along line II-II [Diagram 3] Cross-sectional view of the evaporator along line III-III [Figure 4A] Side view of the evaporator along the line IVA-IVA [Figure 4B] Side view of the evaporator along line IVB-IVB [Figure 5A] Cross-section of the evaporator along the line VA-VA [Figure 5B] Cross-sectional view of the evaporator along the line VB-VB [Figure 6] FIG. 13 is a diagram showing the movement direction and dripping state of the refrigerant sprayed onto multiple heat transfer tubes from the first nozzle and the third nozzle. [Figure 7A] FIG. 13 is a diagram showing the positional relationship between a nozzle surface defined by first nozzles and third nozzles and a nozzle surface defined by second nozzles and fourth nozzles; [Figure 7B] FIG. 13 is a diagram showing the state of the coolant on each nozzle surface after the coolant is sprayed. [Figure 8] FIG. 11 is a cross-sectional view of an evaporator according to a second embodiment of the present disclosure. [Figure 9] Side view of the evaporator along line IX-IX [Figure 10A] Cross-section of the evaporator along line XA-XA [Figure 10B] Cross-section of the evaporator along line XB-XB [Figure 11] Cross-sectional view of a conventional evaporative condenser DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0010] (The knowledge and other information that formed the basis of this disclosure) When a conventional nozzle configuration is applied to a shell-and-tube heat exchanger, dryout tends to occur at a specific position. On the surface where dryout occurs, heat exchange does not occur, and the performance of the shell-and-tube heat exchanger is not fully exhibited. If dryout can be prevented, the performance of the shell-and-tube heat exchanger can be fully exhibited. Based on such findings, the present inventor has come to form the subject of the present disclosure. Note that the "dryout surface" means a surface on which no liquid film of the refrigerant exists.

[0011] Therefore, the present disclosure provides a technique for improving the heat transfer performance of a shell-and-tube heat exchanger.

[0012] Hereinafter, the embodiments will be described in detail with reference to the drawings. However, more detailed explanation than necessary may be omitted. For example, detailed explanation of already well-known matters or duplicate explanation of substantially the same configuration may be omitted. This is to avoid the following explanation becoming more redundant than necessary and to facilitate understanding by those skilled in the art.

[0013] It should be noted that the accompanying drawings and the following description are provided to enable those skilled in the art to fully understand the present disclosure, and are not intended to limit the subject matter described in the claims.

[0014] (Embodiment 1) Hereinafter, the first embodiment will be described with reference to FIG. 1 to FIG. 7B.

[0015] [1-1. Configuration of refrigeration cycle equipment] FIG. 1 shows the configuration of a refrigeration cycle device using a shell-and-tube heat exchanger. The refrigeration cycle device 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 inlet of the compressor 102 by the flow path 110a. The outlet of the compressor 102 is connected to the inlet of the condenser 103 by the flow path 110b. The outlet of the condenser 103 is connected to the inlet of the flow valve 104 by the flow path 110c. The outlet of the flow valve 104 is connected to the inlet of the evaporator 101 by the flow path 110d. The flow paths 110a and 110b are steam paths. The flow paths 110c and 110d are liquid paths. Each path is, for example, composed of at least one metal pipe.

[0016] As described later, the evaporator 101 is configured by a shell-and-tube heat exchanger.

[0017] The compressor 102 may be a velocity type compressor, such as a centrifugal compressor, or a positive displacement type compressor, such as a scroll compressor.

[0018] The type of the condenser 103 is not particularly limited. A heat exchanger such as a plate heat exchanger or a shell-and-tube heat exchanger can be used for the condenser 103.

[0019] The refrigeration cycle apparatus 100 is, for example, an air conditioner for commercial or home use. The heat medium cooled in the evaporator 101 is supplied to a room through a circuit 105 and used for cooling the room. Alternatively, the heat medium heated in the condenser 103 is supplied to a room through a circuit 106 and used for heating the room. The heat medium is, for example, water. However, the refrigeration cycle apparatus 100 is not limited to an air conditioner, and may be other devices such as a chiller or a heat storage device. The refrigeration cycle apparatus 100 may be an absorption refrigerator equipped with an evaporator, an absorber, a regenerator, and a condenser.

[0020] The circuit 105 is a circuit that circulates the heat medium to the evaporator 101. The circuit 106 is a circuit that circulates the heat medium to the condenser 103. The circuits 105 and 106 may be sealed circuits isolated from the outside air.

[0021] The heat medium is a first fluid flowing through each of the circuits 105 and 106. The heat medium is not limited to water, but may be a liquid such as oil or brine, or a gas such as air. The composition of the heat medium in the circuit 105 may be different from the composition of the heat medium in the circuit 106.

[0022] [1-2. Operation of refrigeration cycle equipment] When the compressor 102 is started, the refrigerant is heated and evaporated in the evaporator 101. As a result, a gas-phase refrigerant is generated. The gas-phase refrigerant is sucked into the compressor 102 and compressed. The compressed gas-phase refrigerant is supplied from the compressor 102 to the condenser 103. The gas-phase refrigerant is cooled in the condenser 103, where it is condensed and liquefied. As a result, a liquid-phase refrigerant is generated. The liquid-phase refrigerant is returned from the condenser 103 to the evaporator 101 via the flow valve 104.

[0023] The type of refrigerant is not particularly limited. Examples of the refrigerant include fluorocarbon refrigerants, low GWP (Global Warming Potential) refrigerants, and natural refrigerants. Examples of the fluorocarbon refrigerants include HCFC (hydrochlorofluorocarbon) and HFC (hydrofluorocarbon). Examples of the low GWP refrigerants include HFO-1234yf and water. Examples of the natural refrigerants include carbon dioxide and water.

[0024] The refrigerant may be a refrigerant containing, as a main component, a substance whose saturated vapor pressure at room temperature is negative. Examples of such refrigerants include refrigerants containing, as a main component, water, alcohol, or ether. "Main component" refers to the component that is contained in the greatest amount by mass ratio. "Negative pressure" refers to an absolute pressure that is lower than atmospheric pressure. "Room temperature" refers to a temperature within the range of 20°C ± 15°C according to Japanese Industrial Standards (JIS Z8703).

[0025] The refrigerant is an example of a second fluid that is to exchange heat with the heat medium, which is the first fluid.

[0026] [1-3. Evaporator configuration] FIG. 2 is a vertical cross-sectional view of the evaporator 101 taken along line II-II. FIG. 3 is a horizontal cross-sectional view of the evaporator 101 taken along line III-III. As shown in FIGS. 2 and 3, the evaporator 101 is configured as a shell-and-tube heat exchanger. The evaporator 101 includes a shell 21, a plurality of heat transfer tubes 22, a plurality of nozzles 24, a circulation circuit 25, and a circulation pump 26. The plurality of heat transfer tubes 22 and the plurality of nozzles 24 are disposed inside the shell 21. The plurality of nozzles 24 include a plurality of first nozzles 24a, a plurality of second nozzles 24b, a plurality of third nozzles 24c, and a plurality of fourth nozzles 24d. The plurality of heat transfer tubes 22 are disposed between a nozzle group including the plurality of first nozzles 24a and the plurality of second nozzles 24b, and a nozzle group including the plurality of third nozzles 24c and the plurality of fourth nozzles 24d. The efficiency (COP) of the refrigeration cycle can be improved by efficiently evaporating the refrigerant in the evaporator 101.

[0027] The heat transfer tubes 22 include circular tubes having a circular cross section. In Fig. 2 and Fig. 3, all of the heat transfer tubes 22 are circular tubes having a circular cross section. A heat transfer medium, which is a first fluid, flows from an inlet to an outlet of the heat transfer tubes 22. The heat transfer tubes 22 each penetrate the surfaces of the shell 21 facing each other.

[0028] The multiple heat transfer tubes 22 are arranged parallel to each other inside the shell 21. In detail, the multiple heat transfer tubes 22 are regularly arranged in multiple rows and multiple stages inside the shell 21. The regular arrangement is advantageous for uniformly thinning the liquid film on the surface of the heat transfer tubes 22.

[0029] In this specification, the direction parallel to the longitudinal direction of the heat transfer tube 22 is defined as the X direction. The direction perpendicular to the X direction is defined as the Y direction. The direction perpendicular to the X direction and the Y direction is defined as the Z direction. The Y direction and the Z direction are the row direction and the column direction, respectively. The Y direction may be parallel to the direction of gravity. The X direction and the Z direction may be parallel to the horizontal direction.

[0030] As shown in Fig. 3, in a cross section perpendicular to the X direction and parallel to the Y and Z directions, the heat transfer tubes 22 are located on the lattice points of a square lattice. In detail, the center of each heat transfer tube 22 is located at a lattice point of the square lattice. However, the arrangement of the heat transfer tubes 22 is not particularly limited. For example, the heat transfer tubes 22 may be arranged such that the center of each heat transfer tube 22 is located at a lattice point of a rectangular lattice. In Fig. 2 and Fig. 3, the heat transfer tubes 22 are arranged in 8 rows and 12 columns. The number of rows and columns is also not particularly limited.

[0031] The piping constituting the heat transfer tube 22 may be a processed tube in which grooves are formed on the inside of the tube, the outside of the tube, or both.

[0032] A heat medium that exchanges heat with the refrigerant flows inside the heat transfer tubes 22. The heat medium is a fluid such as water, ethylene glycol, or propylene glycol. The heat medium absorbs heat from the atmosphere via a heat exchanger such as a fin-and-tube heat exchanger, and flows into each heat transfer tube 22 of the evaporator 101. In each heat transfer tube 22, the heat medium is cooled by the refrigerant.

[0033] Examples of materials for the heat transfer tube 22 include metal materials such as aluminum, aluminum alloys, and stainless steel.

[0034] 2 and 3, the refrigerant is sprayed from each of the first nozzle 24a to the fourth nozzle 24d toward the heat transfer tubes 22. The first nozzles 24a and the second nozzles 24b spray the refrigerant from the first side to the second side in the Z direction. The third nozzles 24c and the fourth nozzles 24d spray the refrigerant from the second side to the first side in the Z direction. The "first side" is, for example, one side in the width direction of the heat transfer tube 22. The "second side" is the other side in the width direction of the heat transfer tube 22. The width direction of the heat transfer tube 22 may be the width direction relative to the horizontal direction.

[0035] The nozzle 24 is, for example, a pressure injection type spray nozzle. A pressure injection type spray nozzle is configured to receive pressurized refrigerant from an inlet, impart a swirling force to the refrigerant by a swirling mechanism inside the nozzle, and spray the refrigerant into a space. As a result, the sprayed refrigerant spreads in a cone shape due to centrifugal force caused by the swirling speed, becomes a thin film and a liquid thread, and then breaks into a group of droplets.

[0036] The same spray nozzle may be used for each of the first nozzle 24a to the fourth nozzle 24d. The term "same" means that the design structure and design characteristics are the same. However, the structure and dimensions of the first nozzle 24a to the fourth nozzle 24d may be different from each other.

[0037] In this embodiment, the first nozzles 24a and the second nozzles 24b are located at the same position in the Z direction. The third nozzles 24c and the fourth nozzles 24d are located at the same position in the Z direction. The first nozzles 24a and the third nozzles 24c are located at the same position in the Y direction. The second nozzles 24b and the fourth nozzles 24d are located at the same position in the Y direction. In FIG. 2 and FIG. 3, the first nozzles 24a and the second nozzles 24b are provided in one stage each. The third nozzles 24c and the fourth nozzles 24d are provided in one stage each. The first nozzles 24a and the second nozzles 24b may be arranged in a matrix in the X direction and the Y direction. The third nozzles 24c and the fourth nozzles 24d may be arranged in a matrix in the X direction and the Y direction.

[0038] Fig. 4A is a side view of the evaporator 101 along the line IVA-IVA. In Fig. 4A, elements other than the heat transfer tube 22 and the nozzle 24 are omitted. As shown in Fig. 4A, in a projection image obtained by projecting the first nozzles 24a and the second nozzles 24b in the Z direction, the first nozzles 24a and the second nozzles 24b show a staggered arrangement pattern. In detail, the projection image is an image obtained by orthogonally projecting the first nozzles 24a and the second nozzles 24b onto an arbitrary projection plane perpendicular to the Z direction.

[0039] 4B is a side view of the evaporator 101 taken along line IVB-IVB. In FIG. 4B, elements other than the heat transfer tube 22 and the nozzle 24 are omitted. As shown in FIG. 4B, in a projection image obtained by projecting the third nozzles 24c and the fourth nozzles 24d in the Z direction, the third nozzles 24c and the fourth nozzles 24d show a staggered arrangement pattern. In detail, the projection image is an image obtained by orthogonally projecting the third nozzles 24c and the fourth nozzles 24d onto an arbitrary projection plane perpendicular to the Z direction.

[0040] 4A, the multiple first nozzles 24a are arranged in the X direction. The multiple second nozzles 24b are arranged in the X direction. The position of the first nozzles 24a in the Y direction is different from the position of the second nozzles 24b in the Y direction. The multiple first nozzles 24a and the multiple second nozzles 24b are located on the same plane perpendicular to the Z direction.

[0041] 4B, the multiple third nozzles 24c are arranged in the X direction. The multiple fourth nozzles 24d are arranged in the X direction. The position of the third nozzles 24c in the Y direction is different from the position of the fourth nozzles 24d in the Y direction. The multiple third nozzles 24c and the multiple fourth nozzles 24d are located on the same plane perpendicular to the Z direction.

[0042] Fig. 5A is a cross-sectional view of the evaporator 101 taken along line VA-VA, and Fig. 5B is a cross-sectional view of the evaporator 101 taken along line IVB-IVB. Elements other than the heat transfer tube 22 and the nozzle 24 are omitted in Fig. 5A and Fig. 5B.

[0043] The spray axis O1 of the first nozzle 24a and the spray axis O2 of the second nozzle 24b are parallel to the direction inclined with respect to both the X direction and the Z direction. The spray axis O1 is the central axis of the spray flow of the refrigerant produced by the first nozzle 24a. The spray axis O2 is the central axis of the spray flow of the refrigerant produced by the second nozzle 24b. The spray axis O1 and the spray axis O2 are each inclined with respect to the row direction (Z direction). With this configuration, the first nozzle 24a and the second nozzle 24b can spray the refrigerant over a wide range. This also contributes to the uniform thinning of the liquid film on the surface of the heat transfer tube 22.

[0044] The spray axis O3 of the third nozzle 24c and the spray axis O4 of the fourth nozzle 24d are parallel to directions inclined with respect to both the X direction and the Z direction. The spray axis O3 is the central axis of the spray flow of the refrigerant produced by the third nozzle 24c. The spray axis O4 is the central axis of the spray flow of the refrigerant produced by the fourth nozzle 24d. The spray axis O3 and the spray axis O4 are each inclined with respect to the row direction (Z direction). With this configuration, the third nozzle 24c and the fourth nozzle 24d can spray the refrigerant over a wide range.

[0045] The "spray axis O1" can also be regarded as the central axis of the first nozzle 24a. The spray axis O1 can be an axis passing through the center of the opening of the first nozzle 24a. The "spray axis O2" can also be regarded as the central axis of the second nozzle 24b. The spray axis O2 can be an axis passing through the center of the opening of the second nozzle 24b. The "spray axis O3" can also be regarded as the central axis of the third nozzle 24c. The spray axis O3 can be an axis passing through the center of the opening of the third nozzle 24c. The "spray axis O4" can also be regarded as the central axis of the fourth nozzle 24d. The spray axis O4 can be an axis passing through the center of the opening of the fourth nozzle 24d.

[0046] When viewed from the Y direction, the spray axis O1 of the first nozzle 24a is inclined clockwise with respect to a first reference line L1 that passes through the center of the opening of the first nozzle 24a and is parallel to the Z direction. The spray axis O2 of the second nozzle 24b is inclined counterclockwise with respect to a second reference line L2 that passes through the center of the opening of the second nozzle 24b and is parallel to the Z direction. With this configuration, the refrigerant can be sprayed over a wide range using the minimum number of first nozzles 24a and second nozzles 24b.

[0047] When viewed from the Y direction, the spray axis O3 of the third nozzle 24c is inclined clockwise with respect to a third reference line L3 that passes through the center of the opening of the third nozzle 24c and is parallel to the Z direction. The spray axis O4 of the fourth nozzle 24d is inclined counterclockwise with respect to a fourth reference line L4 that passes through the center of the opening of the fourth nozzle 24d and is parallel to the Z direction. With this configuration, the refrigerant can be sprayed over a wide range by the minimum number of first nozzles 24a and second nozzles 24b.

[0048] When viewed in a plan view from the Y direction, the angle θ1 between the spray axis O1 of the first nozzle 24a and the first reference line L1 is equal to the angle θ2 between the spray axis O2 of the second nozzle 24b and the second reference line L2.

[0049] When viewed in a plan view from the Y direction, the angle θ3 between the spray axis O3 of the third nozzle 24c and the third reference line L3 is equal to the angle θ4 between the spray axis O4 of the fourth nozzle 24d and the fourth reference line L4.

[0050] The angles θ1, θ2, θ3, and θ4 may be equal to each other or may be different from each other. The angles θ1, θ2, θ3, and θ4 may be angles such that at least one of the outer edges of the refrigerant mist flow is non-parallel to the longitudinal direction (X direction) of the heat transfer tube 22. The angles θ1, θ2, θ3, and θ4 are, for example, 30 degrees to 40 degrees, and are typically 30 degrees. In FIG. 5A and FIG. 5B, the dashed lines indicate the spread angle α of the refrigerant mist flow. The spread angle α of the refrigerant mist flow shows a symmetric spread with respect to each of the spray axes O1, O2, O3, and O4. The spread angle α of the refrigerant mist flow may be an acute angle, for example, 60 degrees. The angles θ1, θ2, θ3, and θ4 may be half the spread angle α of the refrigerant mist flow. With this configuration, one of the outer edges of the sprayed flow of the refrigerant is approximately parallel to the reference lines L1, L2, L3, and L4. This suppresses the generation of a component of the refrigerant flow that moves in the opposite direction to the direction of movement of the refrigerant along the surface of the heat transfer tube 22. Since the movement of the refrigerant on the surface of the heat transfer tube 22 is promoted, an improvement in the heat transfer coefficient due to the increased movement speed can be expected. The angles θ1, θ2, θ3, and θ4 are determined according to conditions such as the number of nozzles 24 and the interval between adjacent nozzles 24.

[0051] The first nozzles 24a are arranged at a predetermined interval in the X direction. The interval between the first nozzles 24a adjacent to each other in the X direction is the interval W. The second nozzles 24b are arranged at a predetermined interval in the X direction. The interval between the second nozzles 24b adjacent to each other in the X direction is the interval W. The third nozzles 24c are arranged at a predetermined interval in the X direction. The interval between the third nozzles 24c adjacent to each other in the X direction is the interval W. The fourth nozzles 24d are arranged at a predetermined interval in the X direction. The interval between the fourth nozzles 24d adjacent to each other in the X direction is the interval W. In other words, the interval between the first nozzles 24a adjacent to each other in the X direction, the interval between the second nozzles 24b, the interval between the third nozzles 24c, and the interval between the fourth nozzles 24d are equal to each other. The interval W is appropriately determined according to the angle θ of the nozzle 24 and the distance from the nozzle 24 to the heat transfer tube 22. The interval between adjacent nozzles 24 in the X direction is defined as the distance between the centers of the openings of adjacent nozzles 24.

[0052] The distance between the first nozzle 24a and the second nozzle 24b in the X direction is 1 / 2 the distance between the first nozzles 24a adjacent to each other in the X direction. The distance between the third nozzle 24c and the fourth nozzle 24d in the X direction is 1 / 2 the distance between the third nozzles 24c adjacent to each other in the X direction. In other words, the distance between the first nozzle 24a and the second nozzle 24b in the X direction is W / 2. The distance between the third nozzle 24c and the fourth nozzle 24d in the X direction is W / 2.

[0053] In plan view from the Y direction, the positions of the third nozzles 24c are offset in the X direction from the positions of the first nozzles 24a. In plan view from the Y direction, the positions of the fourth nozzles 24d are offset in the X direction from the positions of the second nozzles 24b. This configuration is advantageous in avoiding overlapping of refrigerant flows in the Z direction.

[0054] The spray axis O1 of the first nozzles 24a passes between the heat transfer tubes 22 adjacent to each other in the Y direction. In other words, the positions of the first nozzles 24a are determined so that the spray axis O1 passes through the space between the heat transfer tubes 22 adjacent to each other in the Y direction. The spray axis O2 of the second nozzles 24b passes between the heat transfer tubes 22 adjacent to each other in the Y direction. In other words, the positions of the second nozzles 24b are determined so that the spray axis O2 passes through the space between the heat transfer tubes 22 adjacent to each other in the Y direction. With this configuration, the reach of the spray flow in the row direction (Z direction) is extended. This not only contributes to the miniaturization of the evaporator 101, but also contributes to the uniform thinning of the liquid film on the surface of the heat transfer tube 22.

[0055] The spray axis O3 of the third nozzles 24c passes between the heat transfer tubes 22 adjacent to each other in the Y direction. In other words, the position of the third nozzles 24c in the Y direction is determined so that the spray axis O3 passes through the space between the heat transfer tubes 22 adjacent to each other in the Y direction. The spray axis O4 of the fourth nozzles 24d passes between the heat transfer tubes 22 adjacent to each other in the Y direction. In other words, the position of the fourth nozzles 24d in the Y direction is determined so that the spray axis O4 passes through the space between the heat transfer tubes 22 adjacent to each other in the Y direction. With this configuration, the reach of the spray in the row direction (Z direction) is increased.

[0056] As shown in Fig. 4A, at least one stage of heat transfer tubes 22 is present between the first nozzles 24a and the second nozzles 24b in the Y direction. As shown in Fig. 4B, at least one stage of heat transfer tubes 22 is present between the third nozzles 24c and the fourth nozzles 24d in the Y direction. In this embodiment, three stages of heat transfer tubes 22 are present between the first nozzles 24a and the second nozzles 24b in the Y direction. Three stages of heat transfer tubes 22 are present between the third nozzles 24c and the fourth nozzles 24d in the Y direction.

[0057] As shown in Fig. 2, shell 21 is configured to store liquid-phase refrigerant in its bottom. Circulation circuit 25 connects the bottom of shell 21 to each of the multiple nozzles 24. Circulation pump 26 is disposed in circulation circuit 25. By the action of circulation pump 26, the liquid-phase refrigerant stored in the bottom of shell 21 is supplied to multiple nozzles 24 through circulation circuit 25. With this configuration, it is easy to collect the liquid-phase refrigerant, and energy consumption for supplying the liquid-phase refrigerant to multiple nozzles 24 can be reduced.

[0058] The shell 21 is provided with an inlet pipe 27 and an outlet pipe 28. The inlet pipe 27 is a flow path that guides the refrigerant into the inside of the shell 21. The outlet pipe 28 is a flow path that guides the refrigerant evaporated on the surfaces of the multiple heat transfer tubes 22 to the outside of the shell 21. The inlet pipe 27 and the outlet pipe 28 can be connected to the flow paths 110d and 110a, respectively.

[0059] The multiple nozzles 24 are connected to a circulation circuit 25 via a header 23 .

[0060] A passage cover 29a is attached to the shell 21 so as to cover one end of the heat transfer tubes 22. A passage cover 29b is attached to the shell 21 so as to cover the other end of the heat transfer tubes 22. The passage cover 29a has two partition plates 31 inside. The passage cover 29b has one partition plate 31 inside. The passage cover 29a has a secondary side inlet 32 ​​and a secondary side outlet 33. The secondary side inlet 32 ​​may be provided in the passage cover 29b. The secondary side outlet 33 may be provided in the passage cover 29b. The number of paths in the evaporator 101 of this embodiment increases by "1" every time the flow direction of the refrigerant is reversed in the passage cover 29a or 29b. In this embodiment, the secondary side inlet 32 ​​and the secondary side outlet 33 are arranged in the passage cover 29a so that the number of paths is "4".

[0061] In the present embodiment, the shell 21 has a rectangular cross-sectional shape. However, the shape of the shell 21 is not limited. The shell 21 may have a circular cross-sectional shape. The shell 21 may be a pressure-resistant container.

[0062] [1-4. Operation] The operation and function of the evaporator 101 constructed as above will be described below.

[0063] When the circulation pump 26 is started, the liquid-phase refrigerant is supplied to the nozzles 24 from the bottom of the shell 21 through the header 23. The liquid-phase refrigerant is sprayed onto the heat transfer tubes 22 from each of the first nozzles 24a and the second nozzles 24b. The liquid-phase refrigerant is sprayed onto the heat transfer tubes 22 from each of the third nozzles 24c and the fourth nozzles 24d. The heat medium flows into the flow path cover 29a from the secondary side inlet 32 ​​and flows through the heat transfer tubes 22. Next, the heat medium reverses its flow direction at the flow path cover 29b and flows through the heat transfer tubes 22. Next, the heat medium reverses its flow direction again at the flow path cover 29a and flows through the heat transfer tubes 22. The heat medium reverses its flow direction again at the flow path cover 29b and flows through the heat transfer tubes 22. Thereafter, the heat medium flows out from the secondary side outlet 33 and is discharged to the outside of the evaporator 101. When a liquid-phase refrigerant is sprayed toward the heat transfer tube 22 while a heat medium is flowing through the heat transfer tube 22, heat exchange occurs between the heat medium and the liquid-phase refrigerant in the heat transfer tube 22, and the refrigerant evaporates to generate a gas-phase refrigerant.

[0064] Here, the components of the refrigerant sprayed from each nozzle 24 will be described with reference to Figures 5A and 5B. In Figures 5A and 5B, the arrows on the heat transfer tube 22 indicate the main movement direction of the sprayed refrigerant.

[0065] The spray flow of the refrigerant sprayed from the first nozzle 24a has a flow component C1 along the spray axis O1 and a flow component C2 along the surface of the heat transfer tube 22. The component C1 is a flow component of the refrigerant sprayed from the first nozzle 24a and spreading. The component C1 is a flow component of the refrigerant moving in the space between the heat transfer tubes 22 adjacent to each other in the Y direction along the spray axis O1. The component C2 is a flow component of the refrigerant moving on the surface of the heat transfer tube 22 with a velocity component in the X direction. The spray flow of the refrigerant sprayed from the second nozzle 24b has a flow component C3 along the spray axis O2 and a flow component C4 along the surface of the heat transfer tube 22. The spray flow of the refrigerant sprayed from the third nozzle 24c has a flow component C5 along the spray axis O3 and a flow component C6 along the surface of the heat transfer tube 22. The spray flow of the refrigerant sprayed from the fourth nozzle 24d has a flow component C7 along the spray axis O4 and a flow component C8 along the surface of the heat transfer tube 22.

[0066] The flows of the refrigerant having the components C1, C3, C5, and C7 each move through the space between the heat transfer tubes 22 adjacent to each other in the Y direction. At that time, the refrigerant moves while contacting the lower surface of the heat transfer tube 22 located at the upper side and the upper surface of the heat transfer tube 22 located at the lower side. The flows of the refrigerant having the components C2 and C8 each move on the surface of the heat transfer tube 22 along the X direction. The flows of the refrigerant having the components C4 and C6 each move on the surface of the heat transfer tube 22 in the opposite direction to the flow direction of the refrigerant having the components C2 and C8. The refrigerant having these components exchanges heat with the heat medium flowing inside the heat transfer tube 22 on the surface of the heat transfer tube 22 and evaporates. The unevaporated refrigerant drips toward the heat transfer tube 22 located below.

[0067] Fig. 6 is a diagram showing the movement direction and dripping state of the refrigerant sprayed from the first nozzle 24a and the third nozzle 24c onto the multiple heat transfer tubes 22. Fig. 6 is a view from the Z direction, showing a portion seen in front of a plane including the foremost heat transfer tube 22 and a part of a portion seen behind a plane including the innermost heat transfer tube 22. In Fig. 6, the arrows on the heat transfer tubes 22 indicate the main movement direction of the sprayed refrigerant.

[0068] The spray flow of the refrigerant sprayed from the first nozzle 24a advances from the first side toward the second side in a direction between the Z direction and the X direction in a space between the heat transfer tubes 22 adjacent to each other in the Y direction. The spray axis O1 is located between the heat transfer tubes 22 in the Y direction. The spray flow of the refrigerant sprayed from the third nozzle 24c advances from the second side toward the first side in a direction between the Z direction and the X direction in a space between the heat transfer tubes 22 adjacent to each other in the Y direction. The spray axis O3 is located between the heat transfer tubes 22 in the Y direction.

[0069] At this time, a part of the refrigerant sprayed from the first nozzle 24a (component C2) moves on the surface of the heat transfer tube 22 along the X direction. A part of the refrigerant sprayed from the third nozzle 24c (component C6) moves on the surface of the heat transfer tube 22 along the X direction. The component C2 of the refrigerant flow is a component in the opposite direction to the component C6 of the refrigerant flow. When the moving speed in the X direction decreases, the refrigerant starts to drip toward the heat transfer tube 22 located below. On the other hand, the components of the refrigerant flow (components C1 and C5) sprayed from the first nozzle 24a and the third nozzle 24c hardly reach the heat transfer tube 22 located below these heat transfer tubes 22. Therefore, heat exchange is performed by the dripping of the unevaporated refrigerant in the heat transfer tube 22 located above. The same explanation can be applied to the second nozzle 24b and the fourth nozzle 24d.

[0070] 7A is a diagram showing the positional relationship between the nozzle surface defined by the first nozzle 24a and the third nozzle 24c and the nozzle surface defined by the second nozzle 24b and the fourth nozzle 24d. In FIG. 7A, for ease of understanding, only one each of the first nozzle 24a, the second nozzle 24b, the third nozzle 24c, and the fourth nozzle 24d is shown. The third nozzle 24c is in the same nozzle surface as the second nozzle 24b. In the Y direction, there are three stages of heat transfer tubes 22 between the first nozzle 24a and the second nozzle 24b. Similarly, there are three stages of heat transfer tubes 22 between the third nozzle 24c and the fourth nozzle 24d in the Y direction.

[0071] The n-th nozzle surface is defined as an XZ plane determined by the spray axis O1 (not shown in FIG. 7A) of the first nozzle 24a and the spray axis O3 (not shown in FIG. 7A) of the third nozzle 24c. The heat transfer tube 22 located above the spray axis O1 of the first nozzle 24a is defined as the heat transfer tube 22a. The heat transfer tube 22 located below the spray axis O1 of the first nozzle 24a is defined as the heat transfer tube 22b. The heat transfer tube 22a and the heat transfer tube 22b are adjacent to each other in the Y direction. The n-th nozzle surface includes the lower surface of the heat transfer tube 22a and the upper surface of the heat transfer tube 22b. The (n+1)-th nozzle surface is defined as an XZ plane determined by the spray axis O2 (not shown in FIG. 7A) of the second nozzle 24b and the spray axis O4 (not shown in FIG. 7A) of the fourth nozzle 24d. The heat transfer tube 22 located above the spray axis O2 of the second nozzle 24b is defined as the heat transfer tube 22c. The heat transfer tube 22 located below the spray axis O2 of the second nozzle 24b is defined as the heat transfer tube 22d. The heat transfer tube 22c and the heat transfer tube 22d are adjacent to each other in the Y direction. The (n+1)th nozzle surface includes the lower surface of the heat transfer tube 22c and the upper surface of the heat transfer tube 22d.

[0072] A predetermined number of stages of heat transfer tubes 22 exist between the nth nozzle surface and the (n+1)th nozzle surface.

[0073] Fig. 7B is a diagram showing the state of the refrigerant on the nth nozzle face and the (n+1)th nozzle face after the refrigerant is sprayed. In Fig. 7B, the arrows indicate the dripping direction of the refrigerant. When the refrigerant is sprayed from each of the first nozzle 24a, the second nozzle 24b, the third nozzle 24c, and the fourth nozzle 24d, a sparse and dense state of the refrigerant occurs on the nth nozzle face and the (n+1)th nozzle face as shown in Fig. 7B. Specifically, dense and sparse regions of the refrigerant occur in a staggered pattern on the nth nozzle face and the (n+1)th nozzle face.

[0074] In detail, in the n-th nozzle face, the refrigerant reaches sufficiently to the region including the heat transfer tube 22 near the first nozzle 24a and the third nozzle 24c due to the components of the refrigerant flow (components C1 and C5). The refrigerant moves sufficiently on the surface of the heat transfer tube 22 due to the components of the refrigerant flow (components C2 and C6). As a result, as shown in FIG. 7B, a dense region of the refrigerant is generated on the n-th nozzle face, and a liquid film of the refrigerant is formed. Similarly, in the (n+1)-th nozzle face, the refrigerant reaches sufficiently to the region including the heat transfer tube 22 near the second nozzle 24b and the fourth nozzle 24d due to the components of the refrigerant flow (components C3 and C7). The refrigerant moves sufficiently on the surface of the heat transfer tube 22 due to the components of the refrigerant flow (components C4 and C8). As a result, as shown in FIG. 7B, a dense region of the refrigerant is generated on the (n+1)-th nozzle face, and a liquid film of the refrigerant is formed.

[0075] On the other hand, in the n-th nozzle face, the amount of refrigerant that reaches the region including the heat transfer tube 22 located away from the first nozzle 24a and the third nozzle 24c is insufficient, or the refrigerant does not reach the region. Therefore, a sparse region of the refrigerant occurs as shown in FIG. 7B. Similarly, in the (n+1)-th nozzle face, the amount of refrigerant that reaches the region including the heat transfer tube 22 located away from the second nozzle 24b and the fourth nozzle 24d is insufficient, or the refrigerant does not reach the region. Therefore, a sparse region of the refrigerant occurs as shown in FIG. 7B. However, the unevaporated refrigerant drips from the dense region of the n-th nozzle face to the sparse region of the (n+1)-th nozzle face, improving the wet state of the sparse region.

[0076] [1-5. Effects, etc.] As described above, in the present embodiment, in a projection image obtained by projecting the first nozzles 24a and the second nozzles 24b in the Z direction, the first nozzles 24a and the second nozzles 24b show a staggered arrangement pattern. Also, in a projection image obtained by projecting the third nozzles 24c and the fourth nozzles 24d in the Z direction, the third nozzles 24c and the fourth nozzles 24d show a staggered arrangement pattern.

[0077] According to this configuration, the surfaces of the heat transfer tubes 22 can be uniformly wetted with the refrigerant sprayed by the first nozzle 24a to the fourth nozzle 24d. This makes it possible to prevent the occurrence of dry-out surfaces where the refrigerant does not reach. As a result, the heat transfer performance of the evaporator 101 can be improved.

[0078] This embodiment is particularly effective when there are many rows of heat transfer tubes 22 and some of the heat transfer tubes 22 receive only a small amount of refrigerant from the nozzles 24. According to this embodiment, the difference in wetness on each nozzle surface can be improved by the combined action of the spray-type refrigerant supply action and the falling film-type refrigerant supply action from both sides of the heat transfer tubes 22. This makes it possible to prevent the formation of a dry-out surface. In addition, in the region including the heat transfer tubes 22 where the refrigerant spray flow directly reaches and where the refrigerant moves on the surface, the heat transfer coefficient is improved by forced convection, so that the heat exchange efficiency can be further improved.

[0079] In this embodiment, the first nozzles 24a may be provided in multiple stages. The second nozzles 24b may be provided in multiple stages. The number of stages of the first nozzles 22a may or may not match the number of stages of the second nozzles 24b. The third nozzles 24a may be provided in multiple stages. The second nozzles 24b may be provided in multiple stages. The number of stages of the third nozzles 22c may or may not match the number of stages of the fourth nozzles 24d. With this configuration, even if the number of stages of the heat transfer tubes 22 is large, the occurrence of an area where the refrigerant does not reach can be more sufficiently suppressed by dripping the refrigerant onto the nozzle surface located below.

[0080] When three or more rows of first nozzles 24a are provided along the Y direction, the intervals between adjacent first nozzles 24a in the Y direction may be equal to each other or may be different. This configuration also applies to the second nozzles 24b, the third nozzles 24c, and the fourth nozzles 24d. The interval between the first nozzles 24a and the second nozzles 24b in the Y direction may be 1 / 2 the interval between adjacent first nozzles 24a in the Y direction. The interval between the third nozzles 24c and the fourth nozzles 24d in the Y direction may be 1 / 2 the interval between adjacent third nozzles 24c in the Y direction.

[0081] When viewed from the Z direction, a plurality of first nozzles 24a and second nozzles 24b may be arranged in a matrix. When four first nozzles 24a are selected to form the four vertices of a rectangle with the smallest area when viewed from the Z direction, the second nozzles 24b may be located at the center of the rectangle formed by the four first nozzles 24a. Similarly, when four second nozzles 24b are selected to form the four vertices of a rectangle with the smallest area when viewed from the Z direction, the first nozzles 24a may be located at the center of the rectangle formed by the four second nozzles 24b.

[0082] When viewed from the Z direction, a plurality of third nozzles 24c and fourth nozzles 24d may be arranged in a matrix. When four third nozzles 24c are selected to form the four vertices of a rectangle with the smallest area when viewed from the Z direction, the fourth nozzle 24d may be located at the center of the rectangle formed by the four third nozzles 24c. Similarly, when four fourth nozzles 24d are selected to form the four vertices of a rectangle with the smallest area when viewed from the Z direction, the third nozzle 24c may be located at the center of the rectangle formed by the four fourth nozzles 24d.

[0083] Two or more rows of a plurality of first nozzles 24a and two or more rows of a plurality of second nozzles 24b may be provided along the Y direction. In this case, the interval between the first nozzles 24a adjacent to each other in the Y direction may be wider than the interval W between the first nozzles 24a adjacent to each other in the X direction. The interval between the second nozzles 24b adjacent to each other in the Y direction may be wider than the interval W between the second nozzles 24b adjacent to each other in the X direction. Such a configuration is advantageous in avoiding overlapping of the coolant flows in the Y direction.

[0084] Two or more rows of a plurality of third nozzles 24c and two or more rows of a plurality of fourth nozzles 24d may be provided along the Y direction. In this case, the interval between the third nozzles 24c adjacent to each other in the Y direction may be wider than the interval W between the third nozzles 24c adjacent to each other in the X direction. The interval between the fourth nozzles 24d adjacent to each other in the Y direction may be wider than the interval W between the fourth nozzles 24d adjacent to each other in the X direction. Such a configuration is advantageous in avoiding overlapping of the coolant flows in the Y direction.

[0085] Two or more rows of a plurality of first nozzles 24a and two or more rows of a plurality of second nozzles 24b may be provided along the Y direction. In this case, the interval between the first nozzles 24a adjacent to each other in the Y direction may be equal to the interval between the second nozzles 24b adjacent to each other in the Y direction. The interval between the first nozzles 24a and the second nozzles 24b in the Y direction may be 1 / 2 the interval between the first nozzles 24a adjacent to each other in the Y direction. With such a configuration, the above-mentioned effects can be obtained more sufficiently.

[0086] Two or more rows of a plurality of third nozzles 24c and two or more rows of a plurality of fourth nozzles 24d may be provided along the Y direction. In this case, the interval between the third nozzles 24c adjacent to each other in the Y direction may be equal to the interval between the fourth nozzles 24d adjacent to each other in the Y direction. The interval between the third nozzles 24c and the fourth nozzles 24d in the Y direction may be 1 / 2 the interval between the third nozzles 24c adjacent to each other in the Y direction. With such a configuration, the above-mentioned effects can be obtained more sufficiently.

[0087] The refrigeration cycle apparatus 100 of this embodiment includes the shell-and-tube heat exchanger of this embodiment. The shell-and-tube heat exchanger may be used in the evaporator 101 or in the condenser 103. By using the shell-and-tube heat exchanger of this embodiment, the efficiency of the refrigeration cycle apparatus 100 can be improved.

[0088] (Embodiment 2) Hereinafter, the second embodiment will be described with reference to Figures 8 to 10. The same components as those in the first embodiment are designated by the same reference numerals and detailed description thereof will be omitted.

[0089] [2-1. Evaporator configuration] Fig. 8 is a cross-sectional view of an evaporator 111 according to the second embodiment of the present disclosure. Fig. 8 corresponds to Fig. 3 of the first embodiment. The evaporator 111 according to the present embodiment has the same configuration as the evaporator 101 according to the first embodiment, except that the evaporator 111 does not include the third nozzles 24c and the fourth nozzles 24d, and the number of rows of the heat transfer tubes 22 is six.

[0090] Fig. 9 is a side view of the evaporator 111 taken along line IX-IX. Elements other than the heat transfer tube 22 and the nozzle 24 are omitted in Fig. 9. As shown in Fig. 9, in a projection image obtained by projecting the plurality of first nozzles 24a and the plurality of second nozzles 24b in the Z direction, the plurality of first nozzles 24a and the plurality of second nozzles 24b show a staggered arrangement pattern.

[0091] Fig. 10A is a cross-sectional view of the evaporator 111 taken along line XA-XA, and Fig. 10B is a cross-sectional view of the evaporator 111 taken along line XB-XB. In Fig. 10A and Fig. 10B, elements other than the heat transfer tube 22 and the nozzle 24 are omitted.

[0092] [2-2. Operation] As described in the first embodiment, when the circulation pump 26 is started, the liquid-phase refrigerant is supplied from the bottom of the shell 21 to the plurality of first nozzles 24a and the plurality of second nozzles 24b through the header 23. The liquid-phase refrigerant is sprayed onto the plurality of heat transfer tubes 22 from each of the plurality of first nozzles 24a and the plurality of second nozzles 24b.

[0093] The moving direction and dripping state of the refrigerant sprayed from each of the multiple first nozzles 24a and the multiple second nozzles 24b are as described in the first embodiment.

[0094] [2-3. Effects, etc.] This embodiment is also effective when the number of rows of the heat transfer tubes 22 is small. According to this embodiment, the difference in wetness between the nozzle surfaces can be improved by the combined action of the spray type coolant supply action and the falling film type coolant supply action, thereby preventing the formation of a dry-out surface.

[0095] In this embodiment, the first nozzles 24a may be provided in multiple stages. The second nozzles 24b may be provided in multiple stages. The number of stages of the first nozzles 22a may or may not match the number of stages of the second nozzles 24b. The same explanation as in the first embodiment can be applied to such a configuration.

[0096] (Other embodiments) In the above-mentioned first embodiment, the first nozzles 24a and the third nozzles 24c are arranged to define the same nozzle surface. Also, the second nozzles 24b and the fourth nozzles 24d are arranged to define the same nozzle surface. The first nozzles 24a and the third nozzles 24c may be arranged on different nozzle surfaces. Also, the second nozzles 24b and the fourth nozzles 24d may be arranged on different nozzle surfaces. That is, the position of the first nozzles 24a in the Y direction may be different from the position of the third nozzles 24c in the Y direction. Also, the position of the second nozzles 24b in the Y direction may be different from the position of the fourth nozzles 24d in the Y direction. In a projected image obtained by projecting the multiple first nozzles 24a, the multiple third nozzles 24c, the multiple second nozzles 24b, and the multiple fourth nozzles 24d in the Z direction, the multiple first nozzles 24a, the multiple third nozzles 24c, the multiple second nozzles 24b, and the multiple fourth nozzles 24d may show a staggered arrangement pattern. [Industrial Applicability]

[0097] The shell-and-tube heat exchanger disclosed in this specification is particularly useful for air conditioners such as commercial air conditioners. The shell-and-tube heat exchanger may be used as a condenser as well as an evaporator. The refrigeration cycle device disclosed in this specification is not limited to air conditioners, and may be other devices such as absorption refrigerators, chillers, and heat storage devices. [Explanation of symbols]

[0098] 21 Shell 22 Heat transfer tube 23 Header 24 Nozzles 24a No. 1 nozzle 24b No. 2 nozzle 24c 3rd nozzle 24d 4th nozzle 25 Circulation circuit 26 Circulation Pump 27 Inflow pipe 28 Discharge pipe 29a, 29b Flow passage cover 31 Partition 32 Secondary inlet 33 Secondary outlet 100 Refrigeration cycle device 101,111 Evaporator 102 Compressor 103 Condenser 104 Flow valve 105,106 Circuit 110a, 110b, 110c, 110d flow paths

Claims

1. A shell, a plurality of heat transfer tubes arranged parallel to each other inside the shell and through which a first fluid flows; a plurality of nozzles disposed within the shell and configured to spray a second fluid toward the plurality of heat transfer tubes; Equipped with When a direction parallel to the longitudinal direction of the heat transfer tubes is defined as an X direction, a direction perpendicular to the X direction is defined as a Y direction, and a direction perpendicular to the X direction and the Y direction is defined as a Z direction, the plurality of nozzles include a plurality of first nozzles that spray the second fluid from a first side toward a second side in the Z direction, and a plurality of second nozzles that spray the second fluid from the first side toward the second side in the Z direction, In a projection image obtained by projecting the plurality of first nozzles and the plurality of second nozzles in the Z direction, the plurality of first nozzles and the plurality of second nozzles exhibit a staggered arrangement pattern, A spray axis of the first nozzle and a spray axis of the second nozzle are parallel to a direction inclined with respect to both the X direction and the Z direction, When viewed in a plan view from the Y direction, the spray axis of the first nozzle is inclined in a clockwise direction with respect to a first reference line that passes through a center of an opening of the first nozzle and is parallel to the Z direction, When viewed in a plan view from the Y direction, the spray axis of the second nozzle is inclined in a counterclockwise direction with respect to a second reference line that passes through a center of an opening of the second nozzle and is parallel to the Z direction. Shell and tube heat exchanger.

2. When viewed in a plan view from the Y direction, an angle between the spray axis of the first nozzle and the first reference line is equal to an angle between the spray axis of the second nozzle and the second reference line.

2. The shell-and-tube heat exchanger according to claim 1.

3. the plurality of nozzles include a plurality of third nozzles that spray the second fluid from the second side toward the first side in the Z direction, and a plurality of fourth nozzles that spray the second fluid from the second side toward the first side in the Z direction, In a projection image obtained by projecting the plurality of third nozzles and the plurality of fourth nozzles in the Z direction, the plurality of third nozzles and the plurality of fourth nozzles exhibit a staggered arrangement pattern.

3. The shell-and-tube heat exchanger according to claim 1 or 2.

4. The spray axis of the third nozzle and the spray axis of the fourth nozzle are parallel to a direction inclined with respect to both the X direction and the Z direction. The shell-and-tube heat exchanger according to claim 3.

5. When viewed in a plan view from the Y direction, the spray axis of the third nozzle is inclined in a clockwise direction with respect to a third reference line that passes through a center of an opening of the third nozzle and is parallel to the Z direction, When viewed in a plan view from the Y direction, the spray axis of the fourth nozzle is inclined in a counterclockwise direction with respect to a fourth reference line that passes through a center of an opening of the fourth nozzle and is parallel to the Z direction.

5. The shell-and-tube heat exchanger according to claim 4.

6. When viewed in a plan view from the Y direction, an angle between the spray axis of the third nozzle and the third reference line is equal to an angle between the spray axis of the fourth nozzle and the fourth reference line. The shell-and-tube heat exchanger according to claim 5.

7. In a plan view from the Y direction, positions of the third nozzles are offset in the X direction with respect to positions of the first nozzles, In a plan view from the Y direction, positions of the plurality of fourth nozzles are offset in the X direction with respect to positions of the plurality of second nozzles. The shell-and-tube heat exchanger according to any one of claims 3 to 6.

8. In the Y direction, the spray axes of the first nozzles pass between the heat transfer tubes adjacent to each other, In the Y direction, the spray axes of the second nozzles pass between the heat transfer tubes adjacent to each other. The shell-and-tube heat exchanger according to any one of claims 1 to 7.

9. In the Y direction, the spray axes of the third nozzles pass between the heat transfer tubes adjacent to each other, In the Y direction, the spray axes of the plurality of fourth nozzles pass between the heat transfer tubes adjacent to each other. The shell-and-tube heat exchanger according to any one of claims 3 to 7.

10. A shell, a plurality of heat transfer tubes arranged parallel to each other inside the shell and through which a first fluid flows; a plurality of nozzles disposed within the shell and configured to spray a second fluid toward the plurality of heat transfer tubes; Equipped with When a direction parallel to the longitudinal direction of the heat transfer tubes is defined as an X direction, a direction perpendicular to the X direction is defined as a Y direction, and a direction perpendicular to the X direction and the Y direction is defined as a Z direction, the plurality of nozzles include a plurality of first nozzles that spray the second fluid from a first side toward a second side in the Z direction, a plurality of second nozzles that spray the second fluid from the first side toward the second side in the Z direction, a plurality of third nozzles that spray the second fluid from the second side toward the first side in the Z direction, and a plurality of fourth nozzles that spray the second fluid from the second side toward the first side in the Z direction, In a projection image obtained by projecting the plurality of first nozzles and the plurality of second nozzles in the Z direction, the plurality of first nozzles and the plurality of second nozzles exhibit a staggered arrangement pattern, in a projection image obtained by projecting the third nozzles and the fourth nozzles in the Z direction, the third nozzles and the fourth nozzles show a staggered arrangement pattern, A spray axis of the third nozzle and a spray axis of the fourth nozzle are parallel to a direction inclined with respect to both the X direction and the Z direction, When viewed in a plan view from the Y direction, the spray axis of the third nozzle is inclined in a clockwise direction with respect to a third reference line that passes through a center of an opening of the third nozzle and is parallel to the Z direction, When viewed in a plan view from the Y direction, the spray axis of the fourth nozzle is inclined in a counterclockwise direction with respect to a fourth reference line that passes through a center of an opening of the fourth nozzle and is parallel to the Z direction. Shell and tube heat exchanger.

11. When viewed in a plan view from the Y direction, an angle between the spray axis of the third nozzle and the third reference line is equal to an angle between the spray axis of the fourth nozzle and the fourth reference line. The shell-and-tube heat exchanger according to claim 10.

12. In a plan view from the Y direction, positions of the third nozzles are offset in the X direction with respect to positions of the first nozzles, In a plan view from the Y direction, positions of the plurality of fourth nozzles are offset in the X direction with respect to positions of the plurality of second nozzles. The shell-and-tube heat exchanger according to claim 10 or 11.

13. In the Y direction, the spray axes of the first nozzles pass between the heat transfer tubes adjacent to each other, In the Y direction, the spray axes of the second nozzles pass between the heat transfer tubes adjacent to each other.

13. The shell-and-tube heat exchanger according to any one of claims 10 to 12.

14. In the Y direction, the spray axes of the third nozzles pass between the heat transfer tubes adjacent to each other, In the Y direction, the spray axes of the plurality of fourth nozzles pass between the heat transfer tubes adjacent to each other.

13. The shell-and-tube heat exchanger according to any one of claims 10 to 12.

15. In a cross section perpendicular to the X direction and parallel to the Y direction and the Z direction, the plurality of heat transfer tubes are located on lattice points of a square lattice.

15. The shell-and-tube heat exchanger according to any one of claims 1 to 14.

16. The plurality of heat transfer tubes include a circular tube having a circular cross section.

16. The shell-and-tube heat exchanger according to any one of claims 1 to 15.

17. A refrigeration cycle apparatus comprising the shell-and-tube heat exchanger according to any one of claims 1 to 16.

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