JP2022096089A - Shell-and-tube type heat exchanger and refrigeration cycle device - Google Patents

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

The present disclosure relates to shell and tube heat exchangers and refrigeration cycle devices.

A technique for cooling the refrigerant inside the heat transfer tube by spraying cooling water toward the heat transfer tube is known. FIG. 11 shows a conventional evaporative condenser described in Patent Document 1 (FIG. 9). The watering unit 330 of the evaporative condenser 300 has a plurality of watering nozzles 334 that sprinkle the cooling water CW toward the condensing coil 326. By exchanging heat between the cooling water CW and the refrigerant R flowing through the condensing coil 326, the cooling water CW evaporates, and the refrigerant R is cooled and condensed.

International Publication No. 2017/073367

When the configuration shown in FIG. 11 is applied to a shell-and-tube heat exchanger, a rough region where a liquid such as cooling water is difficult to be sprayed is generated between adjacent nozzles, and the surface of the heat transfer tube is dried out. .. Further, when the number of stages of the heat transfer tube is large, dryout occurs continuously in the stage direction at a specific position. When dryout occurs, the shell-and-tube heat exchanger cannot exhibit sufficient heat transfer performance.

The present disclosure provides a shell-and-tube heat exchanger with excellent heat transfer performance.

The shell-and-tube heat exchangers of the present disclosure are:
With the shell
A plurality of heat transfer tubes arranged parallel to each other inside the shell and through which the first fluid flows,
A plurality of nozzles arranged inside the shell and spraying a second fluid toward the plurality of heat transfer tubes.
Equipped with
The direction parallel to the longitudinal direction of the plurality of heat transfer tubes is defined as the X direction, the direction vertical 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. When
The plurality of nozzles include a plurality of first nozzles that spray the second fluid from the first side to the second side in the Z direction, and the first side to the second side in the Z direction. Including a plurality of second nozzles for spraying the second fluid.
In the 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 show a staggered arrangement pattern. ..

The refrigeration cycle apparatus of the present disclosure is
The shell-and-tube heat exchanger of the present disclosure is provided.

According to the present disclosure, it is possible to provide a shell-and-tube heat exchanger having excellent heat transfer performance.

Configuration diagram of the refrigeration cycle device according to the first embodiment of the present disclosure. Longitudinal section of the evaporator along line II-II Cross section of the evaporator along lines III-III Side view of the evaporator along the IVA-IVA line Side view of the evaporator along the IVB-IVB line Cross section of the evaporator along the VA-VA line Cross section of evaporator along VB-VB line The figure which shows the moving direction and the dropping state of the refrigerant sprayed from the 1st nozzle and the 3rd nozzle to a plurality of heat transfer tubes. The figure which shows the positional relationship between the nozzle surface defined by the 1st nozzle and the 3rd nozzle, and the nozzle surface defined by the 2nd nozzle and the 4th nozzle. The figure which shows the state of the refrigerant on each nozzle surface after spraying the refrigerant. Cross-sectional view of the evaporator according to the second embodiment of the present disclosure. Side view of the evaporator along the IX-IX line Cross section of the evaporator along the XA-XA line Cross section of the evaporator along the XB-XB line Sectional view of a conventional evaporative condenser

(Knowledge, etc. that became the basis of this disclosure)
When the conventional nozzle configuration is applied to shell and tube heat exchangers, dryouts tend to occur at specific locations. Heat exchange does not occur on the surface where dryout occurs, and the performance of the shell-and-tube heat exchanger is not fully exhibited. If the occurrence of dryout can be prevented, the performance of the shell-and-tube heat exchanger can be fully exhibited. Based on such findings, the inventor has come to constitute the subject matter of the present disclosure. The “dry-out surface” means a surface on which the liquid film of the refrigerant does not exist.

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

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

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

(Embodiment 1)
Hereinafter, the first embodiment will be described with reference to FIGS. 1 to 7B.

[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 path 110c and the flow path 110d are liquid paths. Each path is composed of, for example, at least one metal pipe.

The evaporator 101 is composed of a shell-and-tube heat exchanger, as will be described later.

The compressor 102 may be a speed type compressor such as a centrifugal compressor, or may be a positive displacement compressor such as a scroll compressor.

The model of the condenser 103 is not particularly limited. Heat exchangers such as plate heat exchangers and shell and tube heat exchangers can be used in the condenser 103.

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

The circuit 105 is a circuit for circulating a heat medium through the evaporator 101. The circuit 106 is a circuit for circulating a heat medium in the condenser 103. The circuit 105 and the circuit 106 may be a closed circuit isolated from the outside air.

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

[1-2. Operation of refrigeration cycle device]
When the compressor 102 is started, the refrigerant is heated and evaporated in the evaporator 101. This produces a gas phase refrigerant. The vapor phase refrigerant is sucked into the compressor 102 and compressed. The compressed vapor phase refrigerant is supplied from the compressor 102 to the condenser 103. The vapor phase refrigerant is cooled by the condenser 103 to condense and liquefy. This produces a liquid phase refrigerant. The liquid phase refrigerant is returned from the condenser 103 to the evaporator 101 via the flow valve 104.

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

The refrigerant may be a refrigerant containing a substance having a negative saturated vapor pressure at room temperature as a main component. Examples of such a refrigerant include a refrigerant containing water, alcohol or ether as a main component. The "main component" means the component contained most in the mass ratio. "Negative pressure" means pressure that is absolute and lower than atmospheric pressure. "Room temperature" means a temperature within the range of 20 ° C ± 15 ° C according to the Japanese Industrial Standards (JIS Z8703).

The refrigerant is an example of a second fluid that should exchange heat with a heat medium that is the first fluid.

[1-3. Evaporator configuration]
FIG. 2 is a vertical sectional view of the evaporator 101 along the line II-II. FIG. 3 is a cross-sectional view of the evaporator 101 along the line III-III. As shown in FIGS. 2 and 3, the evaporator 101 is composed of 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 arranged 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. A plurality of heat transfer tubes 22 are arranged between a nozzle group including a plurality of first nozzles 24a and a plurality of second nozzles 24b and a nozzle group including a plurality of third nozzles 24c and a plurality of fourth nozzles 24d. .. The efficiency (COP) of the refrigeration cycle can be improved by efficiently evaporating the refrigerant in the evaporator 101.

The plurality of heat transfer tubes 22 include a circular tube having a circular cross section. In FIGS. 2 and 3, all of the plurality of heat transfer tubes 22 are circular tubes having a circular cross section. A heat medium, which is the first fluid, flows from the inlet to the outlet of the heat transfer tube 22. Each of the plurality of heat transfer tubes 22 penetrates the surfaces of the shells 21 facing each other.

The plurality of heat transfer tubes 22 are arranged parallel to each other inside the shell 21. Specifically, the plurality of heat transfer tubes 22 are regularly arranged in a plurality of rows and a plurality of stages inside the shell 21. The regular arrangement is advantageous for uniform thinning of the liquid film on the surface of the heat transfer tube 22.

In the present specification, the direction parallel to the longitudinal direction of the heat transfer tube 22 is defined as the X direction. The direction vertical to the X direction is defined as the Y direction. The direction perpendicular to the X and Y directions is defined as the Z direction. The Y direction and the Z direction are the step direction and the column direction, respectively. The Y direction can be parallel to the direction of gravity. The X and Z directions can be parallel to the horizontal direction.

As shown in FIG. 3, in a cross section perpendicular to the X direction and parallel to the Y and Z directions, the plurality of heat transfer tubes 22 are located on the grid points of the square grid. Specifically, the center of each heat transfer tube 22 is located at a grid point in a square grid. However, the arrangement of the heat transfer tubes 22 is not particularly limited. The plurality of heat transfer tubes 22 may be arranged so that the center of each heat transfer tube 22 is located at a grid point in a rectangular lattice, for example. In FIGS. 2 and 3, the plurality of heat transfer tubes 22 are arranged in 8 stages and 12 rows. The number of stages and the number of columns are not particularly limited.

The pipe constituting the heat transfer pipe 22 may be a machined pipe in which the inside of the pipe, the outside of the pipe, or both of them are grooved.

A heat medium that exchanges heat with the refrigerant flows inside the heat transfer tube 22. The heat medium is a fluid such as water, ethylene glycol, or propylene glycol. The heat medium absorbs heat in the atmosphere through 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.

Examples of the material of the heat transfer tube 22 include metal materials such as aluminum, aluminum alloy, and stainless steel.

As shown in FIGS. 2 and 3, the refrigerant is sprayed from each of the first nozzle 24a to the fourth nozzle 24d toward the plurality of heat transfer tubes 22. The plurality of first nozzles 24a and the plurality of second nozzles 24b spray the refrigerant from the first side to the second side in the Z direction. The plurality of third nozzles 24c and the plurality of 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 with respect to the horizontal direction.

The nozzle 24 is, for example, a pressure injection type spray nozzle. The pressure injection type spray nozzle is configured to receive the pressurized refrigerant from the inlet, apply a swirling force to the refrigerant by a swirling mechanism inside the nozzle, and inject it into the space. As a result, the injected refrigerant spreads in a conical shape due to the centrifugal force due to the swirling speed, is thinned and liquefied, and then splits into a group of droplets.

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

In the present embodiment, the plurality of first nozzles 24a and the plurality of second nozzles 24b are present at the same position in the Z direction. The plurality of third nozzles 24c and the plurality of fourth nozzles 24d are present at the same position in the Z direction. Further, the plurality of first nozzles 24a and the plurality of third nozzles 24c are present at the same position in the Y direction. The plurality of second nozzles 24b and the plurality of fourth nozzles 24d are present at the same position in the Y direction. In FIGS. 2 and 3, the first nozzle 24a and the second nozzle 24b are each provided in one stage. The third nozzle 24c and the fourth nozzle 24d are each provided in one stage. The plurality of first nozzles 24a and the plurality of second nozzles 24b may be arranged in a matrix in the X direction and the Y direction. The plurality of third nozzles 24c and the plurality of fourth nozzles 24d may be arranged in a matrix in the X direction and the Y direction.

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

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

As shown in FIG. 4A, the plurality of first nozzles 24a are arranged in the X direction. The plurality of second nozzles 24b are arranged in the X direction. The position of the first nozzle 24a in the Y direction is different from the position of the second nozzle 24b in the Y direction. The plurality of first nozzles 24a and the plurality of second nozzles 24b are located on the same plane perpendicular to the Z direction.

As shown in FIG. 4B, the plurality of third nozzles 24c are arranged in the X direction. The plurality of fourth nozzles 24d are arranged in the X direction. The position of the third nozzle 24c in the Y direction is different from the position of the fourth nozzle 24d in the Y direction. The plurality of third nozzles 24c and the plurality of fourth nozzles 24d are located on the same plane perpendicular to the Z direction.

FIG. 5A is a cross-sectional view of the evaporator 101 along the VA-VA line, and FIG. 5B is a cross-sectional view of the evaporator 101 along the IVB-IVB line. In FIGS. 5A and 5B, elements other than the heat transfer tube 22 and the nozzle 24 are omitted.

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

The spray shaft O3 of the third nozzle 24c and the spray shaft O4 of the fourth nozzle 24d are parallel to the inclined direction with respect to both the X direction and the Z direction. The spray shaft O3 is the central shaft of the spray flow of the refrigerant produced by the third nozzle 24c. The spray shaft O4 is the central shaft of the spray flow of the refrigerant produced by the fourth nozzle 24d. The spray shaft O3 and the spray shaft O4 are each inclined with respect to the row direction (Z direction). According to such a configuration, the refrigerant can be sprayed over a wide range by the third nozzle 24c and the fourth nozzle 24d.

The "spray axis O1" can also be regarded as the central axis of the first nozzle 24a. The spray shaft O1 may be a shaft that passes 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 shaft O2 may be a shaft that passes 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 shaft O3 may be a shaft that passes 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 shaft O4 may be a shaft that passes through the center of the opening of the fourth nozzle 24d.

When viewed in a plan view from the Y direction, the spray axis O1 of the first nozzle 24a is inclined in the clockwise direction with respect to the first reference line L1 which passes through the center of the opening of the first nozzle 24a and is parallel to the Z direction. The spray shaft O2 of the second nozzle 24b is inclined counterclockwise with respect to the second reference line L2 which passes through the center of the opening of the second nozzle 24b and is parallel to the Z direction. According to such a configuration, the refrigerant can be sprayed over a wide range by the minimum necessary number of the first nozzles 24a and the second nozzles 24b.

When viewed in a plan view from the Y direction, the spray axis O3 of the third nozzle 24c is inclined clockwise with respect to the third reference line L3 which passes through the center of the opening of the third nozzle 24c and is parallel to the Z direction. The spray shaft O4 of the fourth nozzle 24d is inclined counterclockwise with respect to the fourth reference line L4 which passes through the center of the opening of the fourth nozzle 24d and is parallel to the Z direction. According to such a configuration, the refrigerant can be sprayed over a wide range by the minimum necessary number of the first nozzles 24a and the second nozzles 24b.

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

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

The angle θ1, the angle θ2, the angle θ3, and the angle θ4 may be equal to or different from each other. The angle θ1, the angle θ2, the angle θ3, and the angle θ4 may be such that at least one of the outer edges of the spray stream of the refrigerant is non-parallel to the longitudinal direction (X direction) of the heat transfer tube 22. The angle θ1, the angle θ2, the angle θ3, and the angle θ4 are, for example, 30 to 40 degrees, typically 30 degrees. In FIGS. 5A and 5B, the broken line indicates the spread angle α of the spray flow of the refrigerant. The spread angle α of the spray flow shows a spread symmetrical with respect to each of the spray axes O1, O2, O3 and O4. The spread angle α of the spray flow may be an acute angle, for example, 60 degrees. The angle θ1, the angle θ2, the angle θ3, and the angle θ4 can be half of the spread angle α of the spray flow. According to such a configuration, one of the outer edges of the spray stream of the refrigerant is substantially parallel to the reference lines L1, L2, L3 and L4. As a result, the generation of the component of the flow of the refrigerant that goes against the moving direction of the refrigerant that moves along the surface of the heat transfer tube 22 is suppressed. Since the movement of the refrigerant on the surface of the heat transfer tube 22 is promoted, it can be expected that the heat transfer coefficient will be improved by improving the movement speed. The angle θ1, the angle θ2, the angle θ3, and the angle θ4 are determined according to conditions such as the number of nozzles 24 and the distance between adjacent nozzles 24.

The plurality of first nozzles 24a are arranged at predetermined intervals in the X direction. The distance between the first nozzles 24a adjacent to each other in the X direction is the distance W. The plurality of second nozzles 24b are arranged at predetermined intervals in the X direction. The distance between the second nozzles 24b adjacent to each other in the X direction is the distance W. The plurality of third nozzles 24c are arranged at predetermined intervals in the X direction. The distance between the third nozzles 24c adjacent to each other in the X direction is the distance W. The plurality of fourth nozzles 24d are arranged at predetermined intervals in the X direction. The distance between the fourth nozzles 24d adjacent to each other in the X direction is the distance W. That is, the distance between the first nozzles 24a adjacent to each other in the X direction, the distance between the second nozzles 24b, the distance between the third nozzles 24c, and the distance 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 distance between the nozzles 24 adjacent to each other in the X direction is defined as the distance between the centers of the openings of the adjacent nozzles 24.

The distance between the first nozzle 24a and the second nozzle 24b in the X direction is ½ of 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 ½ of the distance between the third nozzles 24c adjacent to each other in the X direction. That is, 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 2 in the X direction is W / 2.

In a plan view from the Y direction, the positions of the plurality of third nozzles 24c are offset in the X direction with respect to the positions of the plurality of first nozzles 24a. Further, in a plan view from the Y direction, the positions of the plurality of fourth nozzles 24d are offset in the X direction with respect to the positions of the plurality of second nozzles 24b. Such a configuration is advantageous in avoiding overlapping refrigerant flows in the Z direction.

The spray shafts O1 of the plurality of first nozzles 24a pass between the heat transfer tubes 22 and the heat transfer tubes 22 that are adjacent to each other in the Y direction. In other words, the positions of the plurality of first nozzles 24a are set so that the spray shaft O1 passes through the space between the heat transfer tubes 22 adjacent to each other in the Y direction. The spray shafts O2 of the plurality of second nozzles 24b pass between the heat transfer tubes 22 and the heat transfer tubes 22 that are adjacent to each other in the Y direction. In other words, the positions of the plurality of second nozzles 24b are set so that the spray shaft O2 passes through the space between the heat transfer tubes 22 adjacent to each other in the Y direction. According to such a 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.

The spray shafts O3 of the plurality of third nozzles 24c pass between the heat transfer tubes 22 and the heat transfer tubes 22 that are adjacent to each other in the Y direction. In other words, the position of the third nozzle 24c in the Y direction is determined so that the spray shaft O3 passes through the space between the heat transfer tubes 22 and the heat transfer tubes 22 adjacent to each other in the Y direction. The spray shafts O4 of the plurality of fourth nozzles 24d pass between the heat transfer tubes 22 and the heat transfer tubes 22 that are adjacent to each other in the Y direction. In other words, the position of the fourth nozzle 24d in the Y direction is determined so that the spray shaft O4 passes through the space between the heat transfer tubes 22 and the heat transfer tubes 22 adjacent to each other in the Y direction. According to such a configuration, the reach of the spray flow in the row direction (Z direction) is extended.

As shown in FIG. 4A, there are at least one or more heat transfer tubes 22 between the plurality of first nozzles 24a and the plurality of second nozzles 24b in the Y direction. As shown in FIG. 4B, there is at least one or more heat transfer tubes 22 between the plurality of third nozzles 24c and the plurality of fourth nozzles 24d in the Y direction. In the present embodiment, there are three stages of heat transfer tubes 22 between the plurality of first nozzles 24a and the plurality of second nozzles 24b in the Y direction. In the Y direction, there are three stages of heat transfer tubes 22 between the plurality of third nozzles 24c and the plurality of fourth nozzles 24d.

As shown in FIG. 2, the shell 21 is configured to store a liquid phase refrigerant at the bottom thereof. The circulation circuit 25 connects the bottom of the shell 21 to each of the plurality of nozzles 24. A circulation pump 26 is arranged in the circulation circuit 25. By the action of the circulation pump 26, the liquid phase refrigerant stored in the bottom of the shell 21 is supplied to the plurality of nozzles 24 through the circulation circuit 25. According to such a configuration, the liquid phase refrigerant can be easily recovered, and the energy consumption for supplying the liquid phase refrigerant to the plurality of nozzles 24 can be suppressed.

The shell 21 is provided with an inflow pipe 27 and a discharge pipe 28. The inflow pipe 27 is a flow path for guiding the refrigerant into the shell 21. The discharge pipe 28 is a flow path that guides the refrigerant evaporated on the surfaces of the plurality of heat transfer pipes 22 to the outside of the shell 21. A flow path 110d and a flow path 110a may be connected to the inflow pipe 27 and the discharge pipe 28, respectively.

The plurality of nozzles 24 are connected to the circulation circuit 25 via the header 23.

A flow path cover 29a is attached to the shell 21 so as to cover one end of the plurality of heat transfer tubes 22. A flow path cover 29b is attached to the shell 21 so as to cover the other ends of the plurality of heat transfer tubes 22. The flow path cover 29a has two partition plates 31 inside. The flow path cover 29b has one partition plate 31 inside. The flow path cover 29a has a secondary side inflow port 32 and a secondary side outflow port 33. The secondary side inflow port 32 may be provided on the flow path cover 29b. The secondary side outlet 33 may be provided on the flow path cover 29b. The number of passes in the evaporator 101 of the present embodiment increases by "1" each time the flow direction of the refrigerant is reversed at the flow path cover 29a or 29b. In the present embodiment, the secondary side inflow port 32 and the secondary side outflow port 33 are arranged on the flow path cover 29a so that the number of passes is “4”.

In this 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.

[1-4. motion]
The operation and operation of the evaporator 101 configured as described above will be described below.

When the circulation pump 26 is started, the liquid phase refrigerant is supplied from the bottom of the shell 21 to the plurality of nozzles 24 via the header 23. The liquid phase refrigerant is sprayed from each of the plurality of first nozzles 24a and the plurality of second nozzles 24b onto the plurality of heat transfer tubes 22. Further, the liquid phase refrigerant is sprayed from each of the plurality of third nozzles 24c and the plurality of fourth nozzles 24d onto the plurality of heat transfer tubes 22. The heat medium flows into the flow path cover 29a from the secondary side inflow port 32 and flows through the heat transfer tube 22. Next, the heat medium reverses the flow direction at the flow path cover 29b and flows through the heat transfer tube 22. Next, the heat medium reverses the flow direction again at the flow path cover 29a and flows through the heat transfer tube 22. The heat medium again reverses the flow direction at the flow path cover 29b and flows through the heat transfer tube 22. After that, the heat medium flows out from the secondary side outlet 33 and is discharged to the outside of the evaporator 101. If the liquid phase refrigerant is sprayed toward the heat transfer tube 22 while flowing the heat medium through the heat transfer tube 22, heat exchange between the heat medium and the liquid phase refrigerant is performed in the heat transfer tube 22, and the refrigerant evaporates to produce the gas phase refrigerant. Generated.

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

The spray flow of the refrigerant sprayed from the first nozzle 24a has a flow component C1 along the spray shaft O1 and a flow component C2 along the surface of the heat transfer tube 22. The component C1 is a component of the flow of the refrigerant sprayed and spread from the first nozzle 24a. The component C1 is a component of the flow of the refrigerant that moves in the space between the heat transfer tubes 22 and the heat transfer tubes 22 that are adjacent to each other in the Y direction along the spray shaft O1. The component C2 is a component of the flow of the refrigerant that moves 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 shaft 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 shaft O3 and a flow component C6 along the surface of the heat transfer tube 22. The spray stream of the refrigerant sprayed from the fourth nozzle 24d has a flow component C7 along the spray shaft O4 and a flow component C8 along the surface of the heat transfer tube 22.

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

FIG. 6 is a diagram showing a moving direction and a dropping state of the refrigerant sprayed from the first nozzle 24a and the third nozzle 24c onto the plurality of heat transfer tubes 22. FIG. 6 shows a part of a portion viewed from the Z direction and visible from the surface including the frontmost heat transfer tube 22 with respect to the front, and a part visible from the surface including the innermost heat transfer tube 22 with respect to the back. There is. In FIG. 6, the arrow on the heat transfer tube 22 indicates the main moving direction of the sprayed refrigerant.

The spray stream of the refrigerant sprayed from the first nozzle 24a forms a space between the heat transfer tubes 22 and the heat transfer tubes 22 adjacent to each other in the Y direction from the first side to the second side in the Z direction and the X direction. Proceed in the direction between and. The spray shaft O1 is located between the heat transfer tube 22 and the heat transfer tube 22 in the Y direction. The spray stream of the refrigerant sprayed from the third nozzle 24c forms a space between the heat transfer tubes 22 and the heat transfer tubes 22 adjacent to each other in the Y direction from the second side to the first side in the Z direction and the X direction. Proceed in the direction between and. The spray shaft O3 is located between the heat transfer tube 22 and the heat transfer tube 22 in the Y direction.

At this time, a part of the refrigerant (component C2) sprayed from the first nozzle 24a 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 refrigerant flow component C2 is a component in the opposite direction to the refrigerant flow component C6. 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 (components C1 and C5) of the flow of the refrigerant sprayed from the first nozzle 24a and the third nozzle 24c hardly reach the heat transfer tube 22 located below the heat transfer tube 22. Therefore, heat exchange is performed by dropping the unevaporated refrigerant in the heat transfer tube 22 located above. The same description can be applied to the second nozzle 24b and the fourth nozzle 24d.

FIG. 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 first nozzle 24a, one second nozzle 24b, one third nozzle 24c, and one fourth nozzle 24d are shown. The third nozzle 24c is on the same nozzle surface as the second nozzle 24b. In the Y direction, there is a three-stage heat transfer tube 22 between the first nozzle 24a and the second nozzle 24b. Similarly, in the Y direction, there is a three-stage heat transfer tube 22 between the third nozzle 24c and the fourth nozzle 24d.

The n-th nozzle surface is defined as an XZ surface defined by the spray shaft O1 of the first nozzle 24a (not shown in FIG. 7A) and the spray shaft O3 of the third nozzle 24c (not shown in FIG. 7A). The heat transfer tube 22 located above the spray shaft O1 of the first nozzle 24a is defined as the heat transfer tube 22a. The heat transfer tube 22 located below the spray shaft 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 a lower surface of the heat transfer tube 22a and an upper surface of the heat transfer tube 22b. The first (n + 1) nozzle surface is defined as an XZ surface defined by the spray shaft O2 of the second nozzle 24b (not shown in FIG. 7A) and the spray shaft O4 of the fourth nozzle 24d (not shown in FIG. 7A). The heat transfer tube 22 located above the spray shaft O2 of the second nozzle 24b is defined as the heat transfer tube 22c. The heat transfer tube 22 located below the spray shaft 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 first (n + 1) nozzle surface includes a lower surface of the heat transfer tube 22c and an upper surface of the heat transfer tube 22d.

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

FIG. 7B is a diagram showing the state of the refrigerant on the nth nozzle surface and the (n + 1) th nozzle surface after spraying the refrigerant. In FIG. 7B, the arrow indicates the direction in which the refrigerant is dropped. 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, the refrigerant as shown in FIG. 7B is on the nth nozzle surface and the (n + 1) nozzle surface. A coarse and dense state occurs. Specifically, on the nth nozzle surface and the (n + 1) th nozzle surface, dense regions and coarse regions of the refrigerant are generated in a staggered manner.

Specifically, on the n-th nozzle surface, the refrigerant sufficiently reaches the region including the heat transfer tube 22 in the vicinity of the first nozzle 24a and the third nozzle 24c by the components of the flow of the refrigerant (components C1 and C5). .. The components of the flow of the refrigerant (components C2 and C6) allow the refrigerant to sufficiently move on the surface of the heat transfer tube 22. As a result, as shown in FIG. 7B, a dense region of the refrigerant is formed on the n-th nozzle surface, and a liquid film of the refrigerant is formed. Similarly, on the first (n + 1) nozzle surface, the refrigerant sufficiently reaches the region including the heat transfer tube 22 in the vicinity of the second nozzle 24b and the fourth nozzle 24d by the components of the flow of the refrigerant (components C3 and C7). do. The components of the flow of the refrigerant (components C4 and C8) allow the refrigerant to sufficiently move on the surface of the heat transfer tube 22. As a result, as shown in FIG. 7B, a dense region of the refrigerant is formed on the (n + 1) th nozzle surface, and a liquid film of the refrigerant is formed.

On the other hand, on the nth nozzle surface, the amount of the refrigerant that reaches is not sufficient or the refrigerant does not reach the region including the heat transfer tube 22 that is located away from the first nozzle 24a and the third nozzle 24c. Therefore, as shown in FIG. 7B, a rough region of the refrigerant is generated. Similarly, on the first (n + 1) nozzle surface, the amount of the refrigerant that reaches is not sufficient or the refrigerant does not reach the region including the heat transfer tube 22 that is located away from the second nozzle 24b and the fourth nozzle 24d. Therefore, as shown in FIG. 7B, a rough region of the refrigerant is generated. However, the unevaporated refrigerant drops from the dense region of the n-th nozzle surface to the rough region of the (n + 1) th nozzle surface, so that the wet state of the rough region is improved.

[1-5. Effect, etc.]
As described above, in the projection image obtained by projecting the plurality of first nozzles 24a and the plurality of second nozzles 24b in the Z direction in the present embodiment, the plurality of first nozzles 24a and the plurality of second nozzles are present. Reference numeral 24b shows a staggered arrangement pattern. Further, in the projection image obtained by projecting the plurality of third nozzles 24c and the plurality of fourth nozzles 24d in the Z direction, the plurality of third nozzles 24c and the plurality of fourth nozzles 24d show a staggered arrangement pattern. ..

According to such a configuration, the surface of the plurality of heat transfer tubes 22 can be uniformly wetted by the refrigerant sprayed from the plurality of first nozzles 24a to the fourth nozzle 24d. This makes it possible to prevent the generation of a dry-out surface that the refrigerant does not reach. Therefore, the heat transfer performance of the evaporator 101 can be improved.

This embodiment is particularly effective when there is a heat transfer tube 22 having a large number of rows of heat transfer tubes 22 and a small amount of refrigerant reaching from the nozzle 24. According to the present embodiment, the difference in wet state on each nozzle surface is determined by the superimposing action of the refrigerant supply action by the spray type and the refrigerant supply action by the flowing liquid film type from both sides of the plurality of heat transfer tubes 22. Can be improved. This makes it possible to prevent the formation of a dry-out surface. Further, in the region including the heat transfer tube 22 where the spray stream of the refrigerant directly reaches and the refrigerant moves on the surface, the heat transfer coefficient is improved by the forced convection, so that the heat exchange efficiency can be further improved.

In the present embodiment, the first nozzle 24a may be provided in a plurality of stages. The second nozzle 24b may be provided in a plurality of stages. The number of stages of the first nozzle 22a may or may not match the number of stages of the second nozzle 24b. The third nozzle 24a may be provided in a plurality of stages. The second nozzle 24b may be provided in a plurality of stages. The number of stages of the third nozzle 22c may or may not match the number of stages of the fourth nozzle 24d. According to such a configuration, even when the number of stages of the plurality of heat transfer tubes 22 is large, it is possible to more sufficiently suppress the generation of a region where the refrigerant does not reach due to the dropping of the refrigerant on the nozzle surface located below.

When a plurality of first nozzles 24a having three or more stages are provided along the Y direction, the distances between the first nozzles 24a adjacent to each other in the Y direction may be equal to or different from each other. Such a configuration also applies to the second nozzle 24b, the third nozzle 24c and the fourth nozzle 24d. The distance between the first nozzle 24a and the second nozzle 24b in the Y direction may be ½ of the distance between the first nozzles 24a adjacent to each other in the Y direction. The distance between the third nozzle 24c and the fourth nozzle 24d in the Y direction may be ½ of the distance between the third nozzles 24c adjacent to each other in the Y direction.

When viewed in a plan view from the Z direction, the plurality of first nozzles 24a and the second nozzle 24b may be arranged in a matrix. When four first nozzles 24a forming the four vertices of the quadrangle having the smallest area are selected in a plan view from the Z direction, the second nozzle 24b may be located at the center of the quadrangle formed by the four first nozzles 24a. .. Similarly, when four second nozzles 24b are selected so as to form the four vertices of the quadrangle having the smallest area in a plan view from the Z direction, the first nozzle is located in the center of the quadrangle formed by the four second nozzles 24b. 24a can be located.

When viewed in a plan view from the Z direction, the plurality of third nozzles 24c and the fourth nozzle 24d may be arranged in a matrix. When four third nozzles 24c forming the four vertices of the quadrangle having the smallest area are selected in a plan view from the Z direction, the fourth nozzle 24d may be located in the center of the quadrangle formed by the four third nozzles 24c. .. Similarly, when the four fourth nozzles 24d are selected so as to form the four vertices of the quadrangle having the smallest area when viewed in a plan view from the Z direction, the third nozzle is located in the center of the quadrangle formed by the four fourth nozzles 24d. 24c can be located.

A plurality of first nozzles 24a having two or more stages and a plurality of second nozzles 24b having two or more stages may be provided along the Y direction. In this case, the distance between the first nozzles 24a adjacent to each other in the Y direction may be wider than the distance W between the first nozzles 24a adjacent to each other in the X direction. The distance between the second nozzles 24b adjacent to each other in the Y direction may be wider than the distance W between the second nozzles 24b adjacent to each other in the X direction. Such a configuration is advantageous in avoiding overlapping refrigerant flows in the Y direction.

A plurality of third nozzles 24c having two or more stages and a plurality of fourth nozzles 24d having two or more stages may be provided along the Y direction. In this case, the distance between the third nozzles 24c adjacent to each other in the Y direction may be wider than the distance W between the third nozzles 24c adjacent to each other in the X direction. The distance between the fourth nozzles 24d adjacent to each other in the Y direction may be wider than the distance W between the fourth nozzles 24d adjacent to each other in the X direction. Such a configuration is advantageous in avoiding overlapping refrigerant flows in the Y direction.

A plurality of first nozzles 24a having two or more stages and a plurality of second nozzles 24b having two or more stages may be provided along the Y direction. In this case, the distance between the first nozzles 24a adjacent to each other in the Y direction may be equal to the distance between the second nozzles 24b adjacent to each other in the Y direction. The distance between the first nozzle 24a and the second nozzle 24b in the Y direction may be ½ of the distance between the first nozzles 24a adjacent to each other in the Y direction. With such a configuration, the above-mentioned effect can be more sufficiently obtained.

A plurality of third nozzles 24c having two or more stages and a plurality of fourth nozzles 24d having two or more stages may be provided along the Y direction. In this case, the distance between the third nozzles 24c adjacent to each other in the Y direction may be equal to the distance between the fourth nozzles 24d adjacent to each other in the Y direction. The distance between the third nozzle 24c and the fourth nozzle 24d in the Y direction may be ½ of the distance between the third nozzles 24c adjacent to each other in the Y direction. With such a configuration, the above-mentioned effect can be more sufficiently obtained.

The refrigeration cycle apparatus 100 of the present embodiment includes the shell-and-tube heat exchanger of the present 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 the present embodiment, the efficiency of the refrigeration cycle apparatus 100 can be improved.

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

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

FIG. 9 is a side view of the evaporator 111 along the IX-IX line. In FIG. 9, elements other than the heat transfer tube 22 and the nozzle 24 are omitted. As shown in FIG. 9, in the 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 are staggered. The arrangement pattern of is shown.

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

[2-2. motion]
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 via the header 23. The liquid phase refrigerant is sprayed from each of the plurality of first nozzles 24a and the plurality of second nozzles 24b onto the plurality of heat transfer tubes 22.

The moving direction and the dropping state of the refrigerant sprayed from each of the plurality of first nozzles 24a and the plurality of second nozzles 24b are as described in the first embodiment.

[2-3. Effect, etc.]
This embodiment is also effective when the number of rows of the heat transfer tubes 22 is small. According to the present embodiment, it is possible to improve the difference in the density of the wet state on each nozzle surface by the superimposing action between the supply action of the refrigerant by the spray type and the supply action of the refrigerant by the flowing liquid film type. This makes it possible to prevent the formation of a dry-out surface.

In the present embodiment, the first nozzle 24a may be provided in a plurality of stages. The second nozzle 24b may be provided in a plurality of stages. The number of stages of the first nozzle 22a may or may not match the number of stages of the second nozzle 24b. The same description as in the first embodiment may be applied to such a configuration.

(Other embodiments)
In the first embodiment described above, the plurality of first nozzles 24a and the plurality of third nozzles 24c are arranged so as to define the same nozzle surface. Further, a plurality of second nozzles 24b and a plurality of fourth nozzles 24d are arranged so as to define the same nozzle surface. The plurality of first nozzles 24a and the plurality of third nozzles 24c may be arranged on different nozzle surfaces. Further, the plurality of second nozzles 24b and the plurality of fourth nozzles 24d may be arranged on different nozzle surfaces. That is, the position of the first nozzle 24a in the Y direction may be different from the position of the third nozzle 24c in the Y direction. Further, the position of the second nozzle 24b in the Y direction may be different from the position of the fourth nozzle 24d in the Y direction. A plurality of first nozzles 24a, a plurality of first nozzles 24a, in a projection image obtained by projecting a plurality of first nozzles 24a, a plurality of third nozzles 24c, a plurality of second nozzles 24b, and a plurality of fourth nozzles 24d in the Z direction. The third nozzle 24c, the plurality of second nozzles 24b, and the plurality of fourth nozzles 24d may exhibit a staggered arrangement pattern.

The shell-and-tube heat exchangers disclosed herein are 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 refrigerating cycle device disclosed in the present specification is not limited to the air conditioner, and may be another device such as an absorption chiller, a chiller, or a heat storage device.

21 Shell 22 Heat transfer tube 23 Header 24 Nozzle 24a 1st nozzle 24b 2nd nozzle 24c 3rd nozzle 24d 4th nozzle 25 Circulation circuit 26 Circulation pump 27 Inflow pipe 28 Discharge pipe 29a, 29b Flow path cover 31 Partition plate 32 Secondary side Inlet 33 Secondary side Outlet 100 Refrigeration cycle device 101, 111 Evaporator 102 Compressor 103 Condensator 104 Flow valve 105, 106 Circuit 110a, 110b, 110c, 110d Flow path

Claims (14)

With the shell
A plurality of heat transfer tubes arranged parallel to each other inside the shell and through which the first fluid flows,
A plurality of nozzles arranged inside the shell and spraying a second fluid toward the plurality of heat transfer tubes.
Equipped with
The direction parallel to the longitudinal direction of the plurality of heat transfer tubes is defined as the X direction, the direction vertical 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. When
The plurality of nozzles include a plurality of first nozzles that spray the second fluid from the first side to the second side in the Z direction, and the first side to the second side in the Z direction. Including a plurality of second nozzles for spraying the second fluid.
In the 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 show a staggered arrangement pattern. ,
Shell and tube heat exchanger. The spray axis of the first nozzle and the spray axis of the second nozzle are parallel to the inclined direction with respect to both the X direction and the Z direction.
The shell-and-tube heat exchanger according to claim 1. When viewed in a plan view from the Y direction, the spray axis of the first nozzle passes through the center of the opening of the first nozzle and is inclined clockwise with respect to the first reference line parallel to the Z direction. ,
When viewed in a plan view from the Y direction, the spray axis of the second nozzle passes through the center of the opening of the second nozzle and is inclined counterclockwise with respect to the second reference line parallel to the Z direction. Yes,
The shell-and-tube heat exchanger according to claim 2. When viewed in a plan view from the Y direction, the angle formed by the spray axis of the first nozzle and the first reference line is equal to the angle formed by the spray axis of the second nozzle and the second reference line.
The shell-and-tube heat exchanger according to claim 2 or 3. The plurality of nozzles are a plurality of third nozzles that spray the second fluid from the second side to the first side in the Z direction, and from the second side to the first side in the Z direction. Includes a plurality of fourth nozzles that spray the second fluid towards.
In the 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 show a staggered arrangement pattern. ,
The shell-and-tube heat exchanger according to any one of claims 1 to 4. The spray axis of the third nozzle and the spray axis of the fourth nozzle are parallel to the inclined direction with respect to both the X direction and the Z direction.
The shell and tube heat exchanger according to claim 5. When viewed in a plan view from the Y direction, the spray axis of the third nozzle passes through the center of the opening of the third nozzle and is inclined clockwise with respect to the third reference line parallel to the Z direction. ,
When viewed in a plan view from the Y direction, the spray axis of the fourth nozzle passes through the center of the opening of the fourth nozzle and is inclined counterclockwise with respect to the fourth reference line parallel to the Z direction. Yes,
The shell and tube heat exchanger according to claim 6. When viewed in a plan view from the Y direction, the angle formed by the spray axis of the third nozzle and the third reference line is equal to the angle formed by the spray axis of the fourth nozzle and the fourth reference line.
The shell-and-tube heat exchanger according to claim 6 or 7. In a plan view from the Y direction, the positions of the plurality of third nozzles are offset in the X direction with respect to the positions of the plurality of first nozzles.
In a plan view from the Y direction, the positions of the plurality of fourth nozzles are offset in the X direction with respect to the positions of the plurality of second nozzles.
The shell-and-tube heat exchanger according to any one of claims 5 to 8. In the Y direction, the spray shafts of the plurality of first nozzles pass between the heat transfer tubes adjacent to each other and the heat transfer tubes.
In the Y direction, the spray shafts of the plurality of second nozzles pass between the heat transfer tubes adjacent to each other and the heat transfer tubes.
The shell-and-tube heat exchanger according to any one of claims 1 to 9. In the Y direction, the spray shafts of the plurality of third nozzles pass between the heat transfer tubes adjacent to each other and the heat transfer tubes.
In the Y direction, the spray shafts of the plurality of fourth nozzles pass between the heat transfer tubes adjacent to each other and the heat transfer tubes.
The shell-and-tube heat exchanger according to any one of claims 5 to 9. 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 grid points of a square lattice.
The shell-and-tube heat exchanger according to any one of claims 1 to 11. The plurality of heat transfer tubes include a circular tube having a circular cross section.
The shell-and-tube heat exchanger according to any one of claims 1 to 12. A refrigeration cycle apparatus comprising the shell-and-tube heat exchanger according to any one of claims 1 to 13.

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