JP6880277B1 - Evaporator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make it difficult for carryover to occur. An evaporator 10 is immersed in a pressure container 11 having a refrigerant outlet pipe 16 for discharging the evaporated refrigerant and a liquid phase refrigerant stored in a storage unit 11c provided in the lower part of the pressure container 11. A full-liquid heat transfer tube group 14 having a plurality of first heat transfer tubes 14a through which the water to be cooled flows, and a liquid phase refrigerant stored in the lower part of the pressure vessel 11 are provided above the liquid level S. A liquid film type heat transfer tube group 15 having a plurality of second heat transfer tubes 15a through which the water to be cooled flows, and a refrigerant tray 13 that supplies a liquid phase refrigerant to the liquid film type heat transfer tube group 15 from above. It includes a gas-liquid separation flow path 20 that guides the refrigerant evaporated in the liquid film type heat transfer tube group 15 to the refrigerant outlet tube 16. The gas-liquid separation flow path 20 connects the ascending flow path 23 in which the refrigerant flows from the bottom to the top, the descending flow path 24 in which the refrigerant flows from the top to the bottom, and the ascending flow path 23 and the descending flow path 24 to connect the refrigerant. It has a connection flow path 25 that folds back. [Selection diagram] Fig. 1

Description

The present disclosure relates to an evaporator.

As an evaporator used in a refrigerator, a liquid film type evaporator that supplies a liquid phase refrigerant from above to a group of heat transfer tubes through which a medium to be cooled flows is known (for example, Patent Document 1). ).
Patent Document 1 describes an evaporator in which the refrigerant evaporated in the heat transfer tube group is guided to a suction tube provided in the shell via a suction slot formed in the baffle wall.

U.S. Pat. No. 8,944,152

In the liquid film type evaporator, since the heat transfer tube group is arranged up to the upper part of the pressure vessel, the heat transfer tube group and the outlet of the refrigerant tend to be close to each other. Therefore, a phenomenon (so-called carryover) in which the gas phase refrigerant discharged to the outside of the housing is accompanied by the liquid phase refrigerant is likely to occur. Further, by arranging the heat transfer tube group up to the upper part of the pressure vessel, the space above the heat transfer tube group becomes narrow. Therefore, for example, there is a problem that it is difficult to arrange the gas-liquid separation structure in the space above the heat transfer tube group.

Further, in Patent Document 1, since the refrigerant guided to the suction pipe is folded back in the horizontal direction, the gas-liquid separation of the refrigerant is not sufficiently performed, and the gas-phase refrigerant discharged to the outside of the housing is the liquid phase. A phenomenon accompanied by a refrigerant (so-called carryover) may occur. When carryover occurs, the liquid phase refrigerant is sucked into the turbo compressor arranged on the wake side of the evaporator. When the liquid phase refrigerant is sucked into the turbo compressor, the compression ratio of the turbo compressor is lowered, the efficiency is lowered, and there is a risk of damaging the blades and the like of the turbo compressor.

Further, in order to separate the refrigerant into gas and liquid, it is conceivable to provide a demister or the like between the refrigerant outlet leading to the outside of the housing and the heat transfer tube group. However, the demista is a relatively expensive member. Further, in order to secure the separation performance of the demister, it is necessary to suppress the flow velocity in front of the demister, which leads to an increase in the size of the evaporator. Therefore, if a demister is provided, the initial cost of the evaporator may increase.

The present disclosure has been made in view of such circumstances, and an object of the present disclosure is to provide an evaporator capable of making carryover less likely to occur.
Another object of the present invention is to provide an evaporator capable of reducing the initial cost.

In order to solve the above problems, the evaporator of the present disclosure employs the following means.
The evaporator according to the embodiment of the present disclosure has a refrigerant outlet for discharging the evaporated refrigerant, and has a housing forming an outer shell and a storage unit housed in the housing and provided in the lower part of the housing. A group of first heat transfer tubes having a plurality of first heat transfer tubes that are immersed in a liquid-phase refrigerant stored in the above and have a plurality of first heat transfer tubes through which a medium to be cooled flows, and a group of first heat transfer tubes housed in the housing and at the lower part of the housing. A group of second heat transfer tubes provided above the liquid level of the refrigerant of the liquid phase to be stored and having a plurality of second heat transfer tubes through which the medium to be cooled flows, and a group of second heat transfer tubes housed in the housing and described from above. A refrigerant supply unit that supplies a liquid phase refrigerant to the second heat transfer tube group and a flow path that guides the refrigerant evaporated in the second heat transfer tube group to the refrigerant outlet are provided, and the flow path is from bottom to top. It has a first flow path through which the refrigerant flows, a second flow path through which the refrigerant flows from above to below, and a connection flow path that connects the first flow path and the second flow path and returns the refrigerant.

According to the present disclosure, carryover can be made less likely to occur. In addition, the initial cost can be reduced.

It is a schematic vertical sectional view of the evaporator which concerns on 1st Embodiment of this disclosure. It is a vertical cross-sectional view which shows the modification of FIG. It is a vertical cross-sectional view which shows the modification of FIG. It is an enlarged perspective view of the main part (IV part) of FIG. It is a cross-sectional view taken along the line VV of FIG. It is a schematic vertical sectional view of the evaporator which concerns on 1st Embodiment of this disclosure. It is a vertical cross-sectional view which shows the modification of FIG.

Hereinafter, an embodiment of the evaporator according to the present disclosure will be described with reference to the drawings.
[First Embodiment]
Hereinafter, the first embodiment of the present disclosure will be described with reference to FIG. In the following description and drawings, the vertical vertical direction will be the Z-axis direction, the extending direction of the heat transfer tube will be the X-axis direction, and the Z-axis direction and the direction orthogonal to the X-axis direction will be described as the Y-axis direction.

The evaporator 10 according to the present embodiment is applied to a turbo refrigerating apparatus. The turbo refrigerating device includes a turbo compressor that compresses the refrigerant (not shown), a condenser that condenses the refrigerant that has been boosted by the turbo compressor (not shown), and an expansion valve that expands the refrigerant condensed by the condenser (not shown). It is configured in a unit shape with an evaporator (not shown) and an evaporator that evaporates the refrigerant decompressed by the expansion valve. Each device is connected by a pipe through which a refrigerant flows. As the refrigerant, for example, a low-pressure refrigerant such as R1233zd used at a maximum pressure of less than 0.2 MPaG is used. The applicable refrigerant is not limited to the low pressure refrigerant. For example, a high-pressure refrigerant may be used as the refrigerant.

As shown in FIG. 1, the evaporator 10 is provided below the pressure container (housing) 11 forming the outer shell, the refrigerant inlet pipe 12 for introducing the refrigerant into the pressure container 11, and the refrigerant inlet pipe 12. In the refrigerant tray (refrigerant supply unit) 13, the full-liquid heat transfer tube group (first heat transfer tube group) 14 immersed in the liquid phase refrigerant stored in the lower part of the pressure container 11, and the lower part of the pressure container 11. The liquid film type heat transfer tube group (second heat transfer tube group) 15 provided above the liquid level S (see FIGS. 2 and 3) of the stored liquid phase refrigerant and the evaporated refrigerant are discharged from the pressure vessel 11. Refrigerant outlet pipe (refrigerant outlet) 16 and a baffle plate 17 that covers the liquid film type heat transfer tube group 15 from the side, and the refrigerant evaporated by the full liquid type heat transfer tube group 14 and the liquid film type heat transfer tube group 15 are discharged to the refrigerant outlet. It has a gas-liquid separation flow path (flow path) 20 that leads to the tube 16.

The pressure vessel 11 has a cylindrical portion 11a whose central axis extends along the X-axis direction and two tube plates (illustrated) that close both ends of the cylindrical portion 11a in the direction along the central axis (X-axis direction). Omitted) and integrally. The cylindrical portion 11a is arranged so that the central axis is substantially horizontal. Each tube plate is a disk-shaped plate material. Further, a liquid phase refrigerant is stored in the lower part of the pressure vessel 11. Hereinafter, the region in which the liquid phase refrigerant is stored is referred to as a storage unit 11c.
In the following description, the terms "inside" and "outside" mean "inside" and "outside" with respect to the central axis of the cylindrical portion 11a. That is, "inside" means the central axis side of the cylindrical portion 11a, and "outside" means the inner peripheral surface side of the cylindrical portion 11a.

The refrigerant inlet pipe 12 is a cylindrical member extending in the vertical direction, and is formed in a substantially linear shape. The refrigerant inlet pipe 12 is provided so as to penetrate the upper portion of the cylindrical portion 11a in the vertical direction. The refrigerant inlet pipe 12 is provided at substantially the center of the cylindrical portion 11a in the X-axis direction. The refrigerant inlet pipe 12 is connected to a pipe (not shown) that connects the evaporator 10 and the expansion valve. That is, the refrigerant expanded by the expansion valve is guided to the inside of the pressure vessel 11 via the refrigerant inlet pipe 12.

The refrigerant tray 13 is a member having a substantially rectangular plate shape. The refrigerant tray 13 is arranged above the inside of the pressure vessel 11 so that the plate surface is substantially horizontal. Further, the refrigerant tray 13 is provided so that the lower end of the refrigerant inlet pipe 12 and the plate surface face each other. Both ends of the refrigerant tray 13 in the Y-axis direction are arranged so as to be separated from the inner peripheral surface of the cylindrical portion 11a of the pressure vessel 11 by a predetermined distance. Further, the refrigerant tray 13 is provided over substantially the entire area of the pressure vessel 11 in the X-axis direction. Both ends of the refrigerant tray 13 in the X-axis direction are fixed to the tube plate. The refrigerant tray 13 is formed with a large number of holes penetrating in the vertical direction. A large number of holes are formed in substantially the entire area of the refrigerant tray 13. The liquid refrigerant discharged from the refrigerant inlet pipe 12 is discharged onto the refrigerant tray 13. The refrigerant discharged to the refrigerant tray 13 flows on the upper surface of the refrigerant tray 13 and then falls downward through a large number of holes. In this way, the refrigerant tray 13 distributes the refrigerant supplied from the refrigerant inlet pipe 12 in the X-axis direction and the Y-axis direction.

The full-liquid heat transfer tube group 14 is housed in the pressure vessel 11. Further, the full-liquid heat transfer tube group 14 is immersed in the refrigerant stored in the storage unit 11c. That is, it is arranged below the liquid level S of the stored refrigerant. The full-liquid heat transfer tube group 14 has a plurality of first heat transfer tubes 14a extending along the X-axis direction. The plurality of first heat transfer tubes 14a are arranged substantially in parallel. The plurality of first heat transfer tubes 14a are arranged side by side at predetermined intervals in the vertical direction (Z-axis direction) and the Y-axis direction. Specifically, the plurality of first heat transfer tubes 14a are arranged in a plurality of stages in the vertical direction and in a plurality of rows in the Y-axis direction. Water as a cooling medium (hereinafter referred to as "cooled water") is circulated inside each of the first heat transfer tubes 14a. Further, each first heat transfer tube 14a is formed in a straight line. Further, each first heat transfer tube 14a extends from one end to the other end of the pressure vessel 11 in the X-axis direction and penetrates each tube plate.

The liquid film type heat transfer tube group 15 is housed in the pressure vessel 11. The liquid film type heat transfer tube group 15 is arranged above the liquid level S of the stored refrigerant. The liquid film type heat transfer tube group 15 has a plurality of second heat transfer tubes 15a extending along the X-axis direction. The plurality of second heat transfer tubes 15a are arranged substantially in parallel. The plurality of second heat transfer tubes 15a are arranged side by side at predetermined intervals in the vertical direction (Z-axis direction) and the Y-axis direction. Specifically, the plurality of second heat transfer tubes 15a are arranged in a plurality of stages in the vertical direction and in a plurality of rows in the Y-axis direction. Water as a medium to be cooled is circulated inside each of the second heat transfer tubes 15a. Further, each second heat transfer tube 15a is formed in a straight line. Further, each of the second heat transfer tubes 15a extends from one end to the other end of the pressure vessel 11 in the X-axis direction and penetrates each tube plate.

The refrigerant outlet pipe 16 is a cylindrical member extending so as to be inclined with respect to the Z-axis direction. The refrigerant outlet pipe 16 is provided so as to communicate with an opening formed in the upper part of the cylindrical portion 11a. The refrigerant outlet pipe 16 is provided on the end side of the cylindrical portion 11a in the X-axis direction. That is, the refrigerant outlet pipe 16 is provided in the vicinity of the pipe plate of the pressure vessel 11. The refrigerant vaporized in the evaporator 10 is discharged to the outside of the pressure vessel 11 via the refrigerant outlet pipe 16.

The baffle plate 17 is a flat plate-like member arranged so that the plate surface faces a vertical plane. The baffle plates 17 are arranged on both sides of the liquid film type heat transfer tube group 15. That is, the baffle plate 17 is arranged outside the liquid film type heat transfer tube group 15 in the Y-axis direction. Each baffle plate 17 is arranged so that the plate surface faces the liquid film type heat transfer tube group 15. The baffle plate 17 extends downward from both ends of the refrigerant tray 13 in the Y-axis direction by a predetermined distance. The lower end of the baffle plate 17 is located above the lower end of the liquid film type heat transfer tube group 15. Further, the baffle plate 17 extends along the liquid film type heat transfer tube group 15 over substantially the entire area of the pressure vessel 11 in the X-axis direction. The baffle plate 17 may be provided only in a part in the X-axis direction.

The gas-liquid separation flow path 20 is a flow path that guides the refrigerant evaporated in the full-liquid heat transfer tube group 14 and the refrigerant evaporated in the liquid film heat transfer tube group 15 to the refrigerant outlet pipe 16. The refrigerant flowing into the pressure vessel 11 from the refrigerant inlet pipe 12 contains the gas phase refrigerant. The gas-liquid separation flow path may guide the refrigerant of the gas phase that has flowed into the space where the liquid film type heat transfer tube group 15 is arranged through the refrigerant inlet pipe 12 and the refrigerant tray 13 to the refrigerant outlet pipe 16.
Gas-liquid separation flow paths 20 are provided on both sides of the liquid film type heat transfer tube group 15. Since the two gas-liquid separation flow paths 20 are provided symmetrically with respect to the XZ plane passing through the central axis of the pressure vessel, one of the gas-liquid separation flow paths 20 will be described in the following description. The description of one gas-liquid separation flow path 20 will be omitted.
The gas-liquid separation flow path 20 is arranged outside the flat plate-shaped first flow path defining portion 21 arranged outside the obstruction plate 17 in the Y-axis direction and outside the first flow path defining portion 21 in the Y-axis direction. It has a plate-shaped second flow path defining portion 22 and. The gas-liquid separation flow path 20 is provided over substantially the entire area of the pressure vessel 11 in the X-axis direction.

The first flow path defining portion 21 is arranged so as to face the baffle plate 17. The first flow path defining portion 21 is arranged so that the plate surface faces the vertical plane. The first flow path defining portion 21 and the baffle plate 17 are separated from each other. An ascending flow path 23 through which the refrigerant evaporated mainly in the liquid film type heat transfer tube group 15 flows is formed between the first flow path defining portion 21 and the baffle plate 17. That is, the ascending flow path 23 is defined by the plate surface of the first flow path defining portion 21 and the plate surface of the baffle plate 17.
The lower end of the first flow path regulating portion 21 is located below the liquid level S of the refrigerant stored in the storage portion 11c. Further, the lower end of the first flow path regulating portion 21 is separated from the inner peripheral surface of the pressure vessel 11. That is, a gap G is formed between the lower end of the first flow path regulating portion 21 and the inner peripheral surface of the pressure vessel 11. The upper end of the first flow path defining portion 21 is located below the upper end of the baffle plate 17 and above the lower end of the baffle plate 17. Specifically, the upper end of the first flow path defining portion 21 is located at substantially the same height as the vicinity of the central portion of the baffle plate 17 in the Z-axis direction.
Further, a first peeling prevention portion 27 is provided at the upper end portion of the first flow path regulating portion 21 in order to prevent peeling of the flowing refrigerant. The first peeling prevention portion 27 projects from the outer plate surface of the first flow path defining portion 21.

The second flow path defining portion 22 integrally includes a curved portion 22a extending outwardly downward from the end portion of the refrigerant tray 13 in the Y-axis direction and a vertical portion 22b extending downward from the lower end of the curved portion 22a. Have.

The curved portion 22a is arranged above the first flow path defining portion 21. Below the curved portion 22a, a connecting flow path 25 that connects the ascending flow path 23 and the descending flow path 24, which will be described later, is formed.

The vertical portion 22b is arranged outside the first flow path defining portion 21 in the Y-axis direction. The vertical portion 22b is arranged so as to face the first flow path defining portion 21. The vertical portion 22b is arranged so that the plate surface faces the vertical surface. The vertical portion 22b and the first flow path defining portion 21 are separated from each other. The distance between the vertical portion 22b and the first flow path defining portion 21 is longer than the distance between the first flow path defining portion 21 and the baffle plate 17. A descending flow path 24 through which the refrigerant evaporated mainly in the liquid film type heat transfer tube group 15 flows is formed between the vertical portion 22b and the first flow path defining portion 21. That is, the descending flow path 24 is defined by the plate surface of the vertical portion 22b and the plate surface of the first flow path defining portion 21. As described above, the distance between the vertical portion 22b and the first flow path defining portion 21 is longer than the distance between the first flow path defining portion 21 and the baffle plate 17. Therefore, the flow path area of the ascending flow path 23 is smaller than the flow path area of the descending flow path 24.

The outer plate surface of the vertical portion 22b faces the inner peripheral surface of the cylindrical portion 11a. A pressure vessel flow path (housing flow path) 26 through which the refrigerant evaporated in the liquid film type heat transfer tube group 15 mainly flows is formed between the vertical portion 22b and the cylindrical portion 11a. That is, the pressure vessel flow path 26 is defined by the plate surface of the vertical portion 22b and the inner peripheral surface of the cylindrical portion 11a. The pressure vessel flow path 26 is formed so that the inner peripheral surface of the pressure vessel 11 (see P in FIG. 1) is located at a position where the inflowing refrigerant collides. Further, the distance between the vertical portion 22b and the inner peripheral surface of the cylindrical portion 11a is longer than the distance between the vertical portion 22b and the first flow path defining portion 21. Therefore, the flow path area of the pressure vessel flow path 26 is larger than the flow path area of the descending flow path 24.

The lower end of the vertical portion 22b is located above the lower end of the first flow path defining portion 21. The lower end of the vertical portion 22b is located below the upper end of the first flow path defining portion 21.
Further, a second peeling prevention portion 28 is provided at the lower end portion of the vertical portion 22b in order to prevent peeling of the flowing refrigerant. The second peeling prevention portion 28 projects from the outer plate surface of the vertical portion 22b.

In the evaporator 10 configured as described above, the refrigerant flows as follows.
As shown in FIG. 1, in the evaporator 10, the refrigerant flows into the pressure vessel 11 from the refrigerant inlet pipe 12. The refrigerant flowing into the pressure vessel 11 is dispersed in the X-axis direction and the Y-axis direction of the pressure vessel 11 by the refrigerant tray 13, and then passes through a large number of holes formed in the refrigerant tray 13 and falls downward.
The liquid-phase refrigerant that has fallen from the refrigerant tray 13 comes into contact with the second heat transfer tube 15a arranged at the uppermost stage of the liquid film type heat transfer tube group 15 and covers the outer peripheral surface of the second heat transfer tube 15a in a film shape. The refrigerant that covers the outer peripheral surface of the second heat transfer tube 15a in a film shape exchanges heat with the water to be cooled inside the second heat transfer tube 15a. The refrigerant exceeding the boiling point evaporates due to heat exchange, and the refrigerant not exceeding the boiling point falls further down to the second heat transfer tube 15a. Such heat exchange is continuously repeated. The refrigerant that has not evaporated even by heat exchange with the water in the second heat transfer tube 15a arranged at the lowermost part is stored in the storage portion 11c provided in the lower part of the pressure vessel 11. In this way, a pool of liquid phase refrigerant is formed in the storage portion 11c inside the pressure vessel 11. The level of the liquid level S of the refrigerant pool is automatically adjusted to a predetermined height.

On the other hand, the refrigerant evaporated in the liquid film type heat transfer tube group 15 bypasses the lower end of the baffle plate 17 and flows into the ascending flow path 23 as shown by the arrow A1. The refrigerant that has flowed into the ascending flow path 23 circulates in the ascending flow path 23 from below to above. The refrigerant flowing through the ascending flow path 23 flows into the connecting flow path 25 from the upper end of the ascending flow path 23. The refrigerant flowing into the connecting flow path 25 turns back in the flow direction as shown by the arrow A2. The refrigerant folded back in the connecting flow path 25 flows into the descending flow path 24. The refrigerant that has flowed into the descending flow path 24 flows from above to below in the descending flow path 24, as shown by arrow A3. The refrigerant discharged from the second flow path bypasses the lower end of the vertical portion 22b of the second flow path regulation portion 22 and heads upward. At this time, the refrigerant discharged from the second flow path collides with the collision position P on the inner peripheral surface of the cylindrical portion 11a of the pressure vessel 11, as shown by the arrow A4. As shown by the arrow A5, the refrigerant that has collided with the collision position P moves upward along the inner peripheral surface of the cylindrical portion 11a in the pressure vessel flow path 26, and flows into the space above the refrigerant tray 13. The refrigerant that has flowed into the space above the refrigerant tray 13 is guided to the refrigerant outlet pipe 16 and discharged to the outside of the pressure vessel 11. The refrigerant discharged from the refrigerant outlet pipe 16 is sucked and compressed by the turbo compressor.

The first heat transfer tube 14a of the full-liquid heat transfer tube group 14 is in a state of being immersed in the refrigerant of the liquid phase stored in the storage section 11c. The water to be cooled flowing in the second heat transfer tube 15a exchanges heat with the refrigerant stored in the storage unit 11c. The refrigerant that has exchanged heat with the second heat transfer tube 15a evaporates and is guided upward from the liquid level S. The refrigerant evaporated in the liquid film type heat transfer tube group 15 and the full liquid type heat transfer tube group 14 is guided to the refrigerant outlet pipe 16. The refrigerant guided to the refrigerant outlet pipe 16 is discharged to the outside of the pressure vessel 11. The refrigerant discharged from the refrigerant outlet pipe 16 is sucked and compressed by the turbo compressor.

According to this embodiment, the following effects are exhibited.
In the present embodiment, the refrigerant evaporated in the liquid film type heat transfer tube group 15 flows through the gas-liquid separation flow path 20. The refrigerant flowing through the gas-liquid separation flow path 20 turns back in the flow direction from above to below in the connection flow path 25. At this time, centrifugal force acts on the refrigerant flowing through the connection flow path 25. As a result, the refrigerant can be centrifuged into the gas phase refrigerant and the liquid phase refrigerant. As a result, it is possible to prevent the phenomenon that the refrigerant discharged from the refrigerant outlet pipe 16 to the outside of the pressure vessel 11 accompanies the liquid phase refrigerant (so-called carryover).
Further, in the present embodiment, the gas-liquid separation of the refrigerant is performed by the gas-liquid separation flow path 20. This makes it possible to perform gas-liquid separation of the refrigerant without using an expensive member such as a demister. Therefore, the initial cost of the evaporator 10 can be reduced.

Further, in the present embodiment, the flow path area of the ascending flow path 23 connected to the upstream side of the connecting flow path 25 is smaller than the flow path area of the descending flow path 24 connected to the downstream side of the connecting flow path 25. It has become. As a result, the flow velocity of the refrigerant flowing through the ascending flow path 23 connected to the upstream side of the connecting flow path 25 can be increased. Therefore, it is possible to increase the centrifugal force acting on the refrigerant when flowing through the connection flow path 25. Therefore, the refrigerant can be more effectively centrifuged into the gas phase refrigerant and the liquid phase refrigerant.

Further, in the present embodiment, the refrigerant flowing into the pressure vessel flow path 26 collides with the inner peripheral surface of the pressure vessel 11. The refrigerant undergoes gas-liquid separation (so-called collision separation) due to the impact when it collides with the inner peripheral surface of the pressure vessel 11. Therefore, the pressure vessel flow path 26 can separate the refrigerant into a gas phase refrigerant and a liquid phase refrigerant. Therefore, carryover can be made less likely to occur.

Further, in the present embodiment, the flow path area of the pressure vessel flow path 26 is larger than the flow path area of the ascending flow path 23 and the descending flow path 24. As a result, the flow velocity of the refrigerant flowing through the pressure vessel flow path 26 can be slowed down. In the pressure vessel flow path 26, the refrigerant flows from the bottom to the top. Therefore, by slowing down the flow velocity, gas-liquid separation of the refrigerant can be more preferably performed by gravity. Therefore, carryover can be made less likely to occur.

Further, the lower end of the first flow path regulating portion 21 is provided below the liquid level S. That is, the lower end of the first flow path regulating portion 21 is immersed in the refrigerant stored in the storage portion 11c. As a result, the liquid-phase refrigerant adhering to the first flow path regulation portion 21 is guided to the storage portion 11c through the first flow path regulation portion 21. Therefore, the liquid phase refrigerant can be preferably returned to the storage unit 11c.
Further, a gap G is formed between the lower end of the first flow path defining portion 21 and the inner peripheral surface of the cylindrical portion 11a of the pressure vessel 11. As a result, the space inside the first flow path defining portion 21 and the space outside the first flow path defining portion 21 can be connected by the gap G. Therefore, even when the gas-liquid separated liquid-phase refrigerant is returned to the outside of the first flow path defining portion 21, the liquid-phase refrigerant returned to the storage portion 11c passes through the gap G. Then, it can be guided to the space where the full-liquid heat transfer tube group 14 is provided.

[Modification 1]
A modified example of this embodiment will be described. In the above description, the case where the baffle plate 17 is provided has been described, but the present disclosure is not limited to this. For example, as shown in FIG. 2, the baffle plate 17 may be omitted. When the baffle plate 17 is omitted, the ascending flow path 23 and the connecting flow path 25 do not exist.
Even in such a configuration, when the refrigerant evaporated in the liquid film type heat transfer tube group 15 flows into the pressure vessel flow path 26 from the descending flow path 24, the flow direction is folded back in the vertical direction, so that the refrigerant is centrifuged. Be separated. Further, as in the case where the baffle plate 17 is present, the refrigerant collides and separates when flowing into the pressure vessel flow path 26, and the refrigerant is gravitationally separated when flowing through the pressure vessel flow path 26. Therefore, even when the baffle plate 17 is omitted, carryover can be made less likely to occur.

[Modification 2]
Further, as shown in FIG. 3, a first drain pipe (first drain portion) 30 may be provided at the lower end of the vertical portion 22b of the second flow path defining portion 22. The first drain pipe 30 extends along the Z-axis direction. As shown in FIGS. 4 and 5, the first drain pipe 30 has a shape in which a cylindrical member is divided into two along the longitudinal direction. Further, the upper end of the first drain pipe 30 is connected to the lower end of the vertical portion 22b as shown in FIGS. 3 and 4. Further, as shown in FIG. 3, the lower end of the first drain pipe 30 is located below the liquid level S of the refrigerant stored in the storage unit 11c. Further, the lower end of the first drain pipe 30 is separated from the inner peripheral surface of the pressure vessel 11. As shown in FIG. 4, the first drain pipe 30 is provided in a part of the vertical portion 22b in the X-axis direction. Further, a plurality of first drain pipes 30 may be provided. When a plurality of them are provided, they may be arranged side by side at predetermined intervals in the X-axis direction. Further, as shown in FIG. 5, the first drain pipe 30 is arranged so that the cylindrical outer peripheral surface faces the upstream side of the refrigerant flow flowing through the gas-liquid separation flow path 20.

According to this modification, the following effects are obtained.
When flowing through the gas-liquid separation flow path 20, a part of the refrigerant in the gas-liquid separated liquid phase adheres to the second flow path defining portion 22. In this modification, the adhering refrigerant can be guided to the storage unit 11c via the first drain pipe 30. The refrigerant guided to the storage unit 11c evaporates by exchanging heat with the full-liquid heat transfer tube group 14. In this way, since the refrigerant in the gas-liquid separated liquid phase can be guided to the full-liquid heat transfer tube group 14, the refrigerant that is not supplied to each heat transfer tube group can be reduced. Therefore, the performance of the evaporator 10 can be improved.

Further, in this modification, the first drain pipe 30 is arranged so that the cylindrical outer peripheral surface faces the upstream side of the refrigerant flow flowing through the gas-liquid separation flow path 20. As a result, the first drain pipe 30 can cover the refrigerant W (see FIG. 5) flowing through the first drain pipe 30 from the upstream side. Therefore, as shown by the broken line arrow in FIG. 4, the refrigerant flowing through the gas-liquid separation flow path 20 passes around the first drain pipe 30. Therefore, the refrigerant W guided by the first drain pipe 30 can be made difficult to be scattered by the refrigerant flowing through the gas-liquid separation flow path 20. Therefore, the liquid phase refrigerant can be suitably guided to the storage unit 11c.

Further, the lower end of the first drain pipe 30 is provided below the liquid level S. That is, the lower end of the first drain pipe 30 is immersed in the refrigerant stored in the storage portion 11c. As a result, the liquid phase refrigerant adhering to the first drain pipe 30 is guided to the storage unit 11c through the first drain pipe 30. Therefore, the liquid phase refrigerant can be preferably returned to the storage unit 11c.

[Second Embodiment]
Next, the second embodiment according to the present disclosure will be described with reference to FIG.
In the present embodiment, the structure of the gas-liquid separation flow path is mainly different from that of the first embodiment. Since the other points are the same as those in the first embodiment, the same structures are designated by the same reference numerals and detailed description thereof will be omitted.

The gas-liquid separation flow path 40 according to the present embodiment is arranged outside the baffle plate 17 in the Y-axis direction, and is provided above the lower end of the baffle plate 17 with a third flow path defining portion 41 and a third flow path. It has a fourth flow path defining portion 42 provided above the defining portion 41. The gas-liquid separation flow path 40 is provided over substantially the entire area of the pressure vessel 11 in the X-axis direction.

The third flow path defining portion 41 is formed from a plate-shaped first horizontal portion 41a extending outward in the Y-axis direction from the outer plate surface of the baffle plate 17 and an outer end portion of the first horizontal portion 41a in the Y-axis direction. It integrally has a plate-shaped first vertical portion 41b that is bent at a substantially right angle and extends upward.

The first horizontal portion 41a is arranged so that the plate surface is a horizontal plane. The inner end of the first horizontal portion 41a in the Y-axis direction is in contact with or in close proximity to the lower portion of the baffle plate 17. Further, the outer end portion in the Y-axis direction extends to the vicinity of the inner peripheral surface of the cylindrical portion 11a.

The first vertical portion 41b is arranged so that the plate surface faces the vertical surface. The outer plate surface of the first vertical portion 41b faces the inner peripheral surface of the cylindrical portion 11a. A pressure vessel flow path (housing flow path) 43 through which the refrigerant evaporated in the liquid film type heat transfer tube group 15 mainly flows is formed between the first vertical portion 41b and the cylindrical portion 11a. That is, the pressure vessel flow path 43 is defined by the plate surface of the first vertical portion 41b and the inner peripheral surface of the cylindrical portion 11a.

The fourth flow path defining portion 42 has a plate-shaped second horizontal portion 42a extending inward in the Y-axis direction from the inner peripheral surface of the cylindrical portion 11a and a substantially right angle downward from the inner end portion of the second horizontal portion 42a. A plate-shaped second vertical portion 42b that bends and extends downward, a plate-shaped collecting portion 42c that bends at a substantially right angle from the lower end of the second vertical portion 42b and extends outward in the Y-axis direction, and a collecting portion 42c. It integrally has a plate-shaped third vertical portion 42d that is bent at a substantially right angle from the outer end portion in the Y-axis direction and extends upward.

The second horizontal portion 42a is arranged so that the plate surface is a horizontal plane. The second horizontal portion 42a is provided above the upper end of the first vertical portion 41b. The outer end of the second horizontal portion 42a in the Y-axis direction is in contact with or in close proximity to the inner peripheral surface of the cylindrical portion 11a. Further, the inner end portion in the Y-axis direction extends to the vicinity of the baffle plate 17. The inner end of the second horizontal portion 42a in the Y-axis direction is separated from the baffle plate 17. Further, below the second horizontal portion 42a, a connecting flow path 47 connecting the pressure vessel flow path 43 and the descending flow path 46 described later is formed.

The second vertical portion 42b is arranged so that the plate surface faces the vertical surface. The inner plate surface of the second vertical portion 42b faces the baffle plate 17. An ascending flow path 44 through which the refrigerant evaporated mainly in the liquid film type heat transfer tube group 15 flows is formed between the second vertical portion 42b and the baffle plate 17. That is, the ascending flow path 44 is defined by the second vertical portion 42b and the baffle plate 17. The lower end of the second vertical portion 42b is arranged above the first horizontal portion 41a. The lower end of the second vertical portion 42b is separated from the first horizontal portion 41a.

The collecting portion 42c is arranged so that the plate surface is a horizontal plane. The collecting portion 42c is arranged above the first horizontal portion 41a. Further, the collecting portion 42c is arranged below the upper end of the first vertical portion 41b. The lower surface of the collecting portion 42c faces the upper surface of the first horizontal portion 41a. A horizontal flow path 45 is formed between the lower surface of the collecting portion 42c and the upper surface of the first horizontal portion 41a. That is, the horizontal flow path 45 is defined by the collecting portion 42c and the first horizontal portion 41a. A space for collecting the centrifugally separated liquid phase refrigerant is formed between the upper surface of the collecting portion 42c and the lower surface of the second horizontal portion 42a. The inside of this space in the Y-axis direction is defined by the second vertical portion 42b.

The collecting section 42c is provided with a second drain pipe (second drain section) 50 that guides the collected liquid phase refrigerant to the storage section 11c. The second drain pipe 50 is different from the first drain pipe 30 described in the second modification of the first embodiment in that the upper end is connected to the upper surface of the collecting portion 42c. Since the other points are substantially the same as those of the first drain pipe 30, detailed description of the second drain pipe 50 will be omitted.

Further, the horizontal flow path 45 is provided with a third drain pipe 51 that guides the liquid phase refrigerant to the storage portion 11c. The third drain pipe 51 is different from the first drain pipe 30 described in the second modification of the first embodiment in that the upper end is connected to the upper surface of the first horizontal portion 41a. Since the other points are substantially the same as those of the first drain pipe 30, detailed description of the third drain pipe 51 will be omitted. The third drain pipe 51 is provided in the vicinity of the vertically lower portion of the ascending flow path 44.

The third vertical portion 42d is arranged so that the plate surface faces the vertical surface. The outer plate surface of the third vertical portion 42d faces the inner plate surface of the second vertical portion 42b. A descending flow path 46 through which the refrigerant evaporated mainly in the liquid film type heat transfer tube group 15 flows is formed between the third vertical portion 42d and the second vertical portion 42b. That is, the descending flow path 46 is defined by the third vertical portion 42d and the first vertical portion 41b. The flow path area of the descending flow path 46 is smaller than the flow path area of the ascending flow path 44.
The upper end of the third vertical portion 42d is arranged below the second horizontal portion 42a. The upper end of the third vertical portion 42d is separated from the second horizontal portion 42a. Further, the upper end of the third vertical portion 42d is arranged below the upper end of the first vertical portion 41b.

Next, the method of distributing the refrigerant in the present embodiment will be described. The same applies to the first embodiment except for the flow of the refrigerant evaporated in each heat transfer tube group, and thus the description thereof will be omitted.
In the present embodiment, the refrigerant evaporated in the liquid film type heat transfer tube group 15 bypasses the lower end of the baffle plate 17 and reaches the collision position P on the inner peripheral surface of the cylindrical portion 11a of the pressure vessel 11 as shown by the arrow A6. collide. As shown by the arrow A7, the refrigerant that has collided with the collision position P moves upward along the inner peripheral surface of the cylindrical portion 11a in the pressure vessel flow path 43. The refrigerant flowing through the pressure vessel flow path 43 flows into the connection flow path 47 from the upper end of the pressure vessel flow path 43. The refrigerant that has flowed into the connecting flow path 47 turns back in the flow direction. Since the liquid-phase refrigerant has a higher density than the gas-phase refrigerant, it makes a large turn when it is turned back, as shown by the arrow A8. The large-turned liquid-phase refrigerant is collected in the collecting unit 42c. On the other hand, the low-density gas-phase refrigerant makes a small turn and flows into the descending flow path 46 as shown by the arrow A9. The refrigerant that has flowed into the descending flow path 46 flows in the descending flow path 46 from above to below. The refrigerant flowing through the descending flow path 46 flows through the horizontal flow path 45. The refrigerant flowing through the horizontal flow path 45 flows into the ascending flow path 44. The refrigerant that has flowed into the ascending flow path 44 flows from below to above in the ascending flow path 44, as shown by arrow A10. The refrigerant flowing through the ascending flow path 44 flows into the space above the refrigerant tray 13. The refrigerant that has flowed into the space above the refrigerant tray 13 is guided to the refrigerant outlet pipe 16 and discharged to the outside of the pressure vessel 11.

According to this embodiment, the following effects are exhibited.
In the present embodiment, the refrigerant evaporated in the liquid film type heat transfer tube group 15 is first guided to the pressure vessel flow path 43. As a result, the refrigerant can be collided with the inner peripheral surface of the pressure vessel 11 to be separated from the refrigerant before being centrifuged in the connection flow path 47. Therefore, the speed of the refrigerant colliding with the inner peripheral surface of the pressure vessel 11 can be increased. Therefore, more effectively, gas-liquid separation of the refrigerant can be performed by collision separation.

Further, in the present embodiment, a collecting portion 42c for collecting the refrigerant of the separated liquid phase is provided on the downstream flow path (downward flow path 46) side of the connected flow paths. As a result, the centrifugally separated liquid phase can be suitably collected.

Further, in the present embodiment, the collected refrigerant is guided to the storage unit 11c via the second drain pipe 50. The refrigerant guided to the storage unit 11c evaporates by exchanging heat with the full-liquid heat transfer tube group 14. In this way, since the refrigerant in the gas-liquid separated liquid phase can be guided to the full-liquid heat transfer tube group 14, the refrigerant that is not supplied to each heat transfer tube group can be reduced. Therefore, the performance of the evaporator 10 can be improved.

[Modification 3]
The collecting portion 42c may be inclined along the X-axis direction with respect to the horizontal plane. In this case, if the collecting portion 42c is inclined so that the portion where the second drain pipe 50 is provided is lowered, the liquid phase refrigerant collects in the second drain pipe 50, so that the liquid is more preferably liquid. The phase refrigerant can be returned to the reservoir 11c. Further, when a plurality of second drain pipes 50 are arranged side by side along the X-axis direction, the collecting portion 42c has a plurality of inclinations so that the portion where each of the second drain pipes 50 is provided is lowered. It may have a surface.

[Modification example 4]
Further, as shown in FIG. 7, the third flow path defining portion may be formed of a curved surface. The third flow path defining portion (curved portion) 60 according to this modified example is a first portion 61 extending upward from the lower end of the baffle plate 17 in the Y-axis direction and extending upward, and a first portion. It integrally has a second portion 62 which is inside in the Y-axis direction from the upper end of 61 and extends while curving upward. The upper end of the second portion 62 extends to the vicinity of the second horizontal portion 42a. The upper end of the second portion 62 and the second horizontal portion 42a are separated from each other. Further, the upper end of the second portion 62 and the second vertical portion 42b are separated from each other.
Further, the third drain pipe 51 is provided in the first portion 61. Specifically, it is provided at the lower end of the first portion 61.

In this modification, the refrigerant evaporated in the liquid film type heat transfer tube group 15 flows between the third flow path defining portion 60 and the inner peripheral surface of the pressure vessel 11 as shown by an arrow A11. Next, as shown by an arrow A12, it circulates between the upper end of the second portion 62 and the second horizontal portion 42a, and between the upper end of the second portion 62 and the second vertical portion 42b. Next, as shown by arrow A13, the refrigerant flows in between the first portion 61 and the third vertical portion 42d and flows along the first portion 61. Then, as shown by the arrow A14, the refrigerant flows into the ascending flow path 44 and flows into the space above the refrigerant tray 13. The refrigerant that has flowed into the space above the refrigerant tray 13 is guided to the refrigerant outlet pipe 16 and discharged to the outside of the pressure vessel 11.

In this modification, the third flow path defining portion 60 is curved. This reduces the pressure loss on the refrigerant flowing through the gas-liquid separation flow path. Therefore, the refrigerant can be suitably guided to the refrigerant outlet pipe 16.
Further, since the third flow path defining portion 60 is curved, even if the liquid-phase refrigerant separated by gas and liquid falls at any position on the upper surface of the first portion 61, the liquid-phase refrigerant is drained to the third drain. It can be led to the pipe 51. Thereby, for example, as in the second embodiment, the region where the refrigerant is guided to the third drain pipe 51 can be widened as compared with the case where the third flow path defining portion is formed only by the flat plate member. Therefore, the liquid phase refrigerant can be preferably returned to the storage unit 11c.

The present disclosure is not limited to the above embodiment, and can be appropriately modified without departing from the gist thereof.
For example, in each of the above embodiments, an example in which a flow path through which the refrigerant flows upward is connected to the upstream side of the connection flow path and a flow path through which the refrigerant flows downward is connected to the downstream side has been described. Is not limited to this. For example, a flow path through which the refrigerant flows downward may be connected to the upstream side of the connection flow path.
Further, for example, in each of the above embodiments, an example in which a refrigerant tray is used as a device for supplying a refrigerant to a liquid film type heat transfer tube group or the like has been described, but the present disclosure is not limited to this. The device for supplying the refrigerant may have a structure capable of supplying the refrigerant to the liquid film type heat transfer tube group, and may be, for example, a pipe-shaped member extending along the X-axis direction.

The evaporator described in the present embodiment described above is grasped as follows, for example.
The evaporator according to one aspect of the present disclosure has a refrigerant outlet (16) for discharging the evaporated refrigerant, and has a housing (11) forming an outer shell and a housing (11) housed in the housing and at the lower part of the housing. With the first heat transfer tube group (14) having a plurality of first heat transfer tubes (14a) that are immersed in the liquid phase refrigerant stored in the provided storage section (11c) and through which the cooled medium flows. , A plurality of second heat transfer tubes (15a) housed in the housing and provided above the liquid level (S) of the liquid phase refrigerant stored in the lower part of the housing and through which the cooled medium flows. (15), a refrigerant supply unit (13) housed in the housing and supplying a liquid phase refrigerant from above to the second heat transfer tube group, and the second heat transfer tube group. The flow path (20) for guiding the refrigerant evaporated in the above to the refrigerant outlet is provided, and the flow path has a first flow path (23) in which the refrigerant flows from the bottom to the top and a refrigerant flows from the top to the bottom. It has a second flow path (24) and a connection flow path (25) that connects the first flow path and the second flow path and returns the refrigerant.

In the above configuration, the refrigerant evaporated in the second heat transfer tube group flows through the flow path. The refrigerant flowing through the flow path is folded back from the upper side to the lower side or from the lower side to the upper side in the connecting flow path. At this time, centrifugal force acts on the refrigerant flowing through the connecting flow path. As a result, the refrigerant can be centrifuged into the gas phase refrigerant and the liquid phase refrigerant. As a result, it is possible to prevent the phenomenon that the refrigerant discharged from the refrigerant outlet to the outside of the housing accompanies the liquid phase refrigerant (so-called carryover).
Further, in the above configuration, gas-liquid separation of the refrigerant is performed by the flow path. This makes it possible to perform gas-liquid separation of the refrigerant without using an expensive member such as a demister. Therefore, the initial cost can be reduced.
The first flow path and the second flow path are names for convenience, and "first" and "second" do not mean the order in which the refrigerant flows.

Further, in the evaporator according to one aspect of the present disclosure, the flow path area of the first flow path or the second flow path connected to the upstream side of the connection flow path is connected to the downstream side of the connection flow path. It is smaller than the flow path area of the first flow path or the second flow path.

In the above configuration, the flow path cross-sectional area of the flow path provided on the upstream side of the connection flow path is small. As a result, the flow velocity of the refrigerant flowing through the flow path provided on the upstream side of the connection flow path can be increased. Therefore, it is possible to increase the centrifugal force acting on the refrigerant when flowing through the connecting flow path. Therefore, the refrigerant can be more effectively centrifuged into the gas phase refrigerant and the liquid phase refrigerant.

Further, in the evaporator according to one aspect of the present disclosure, the flow path has a housing flow path (26) in which a part is defined by the inner peripheral surface of the housing, and the housing flow path is a housing flow path. The inner peripheral surface of the housing is arranged at a position where the inflowing refrigerant collides.

In the above configuration, the refrigerant flowing into the housing flow path collides with the inner peripheral surface of the housing. The refrigerant undergoes gas-liquid separation (so-called collision separation) due to the impact when it collides with the inner peripheral surface of the housing. Therefore, the refrigerant can be separated into a gas phase refrigerant and a liquid phase refrigerant by the housing flow path. Therefore, it is possible to make it more difficult for the refrigerant discharged from the refrigerant outlet to the outside of the housing to accompany the liquid phase refrigerant (so-called carryover).

Further, in the evaporator according to one aspect of the present disclosure, the housing flow path is provided on the upstream side of the connection flow path.

In the above configuration, the refrigerant can be collided and separated by colliding with the inner peripheral surface of the housing before centrifuging at the connection portion. As a result, the speed of the refrigerant colliding with the inner peripheral surface of the housing can be increased. Therefore, more effectively, gas-liquid separation of the refrigerant can be performed by collision separation.

Further, in the evaporator according to one aspect of the present disclosure, a first drain portion (30) for guiding the liquid phase refrigerant to the storage portion is provided in the flow path.

In the above configuration, the liquid-phase separated liquid-phase refrigerant adheres to the flow path when flowing through the flow path. The adhering refrigerant is guided to the storage section via the first drain section. The refrigerant guided to the storage section evaporates by exchanging heat with the first heat transfer tube group. In this way, since the refrigerant in the gas-liquid separated liquid phase can be guided to the first heat transfer tube group, it is possible to reduce the refrigerant that is not supplied to each heat transfer tube group. Therefore, the performance of the evaporator can be improved.
The first drain portion may have a shape in which, for example, a cylindrical member is divided into two along the longitudinal direction, and may be arranged so that the cylindrical surface is located on the upstream side of the refrigerant flow flowing through the flow path. .. By doing so, the first drain portion can cover the refrigerant guided by the first drain portion from the upstream side of the refrigerant flow flowing through the flow path. Therefore, the refrigerant guided by the first drain portion can be made less likely to be scattered by the refrigerant flowing through the flow path. Therefore, the liquid phase refrigerant can be suitably guided to the storage portion.
Further, the first drain portion may be arranged so that the upper end is connected to the flow path, the lower end is located in the refrigerant stored in the storage portion, and the first drain portion is separated from the inner peripheral surface of the housing.

Further, in the evaporator according to one aspect of the present disclosure, the connection flow path is provided with a collection unit (42c) for collecting the separated liquid phase refrigerant on the flow path side on the downstream side to be connected. ..

The liquid phase refrigerant centrifuged at the connection has a higher density than the separated gas phase refrigerant. As a result, the separated liquid-phase refrigerant makes a larger turn than the gas-phase refrigerant when it is turned back. That is, the liquid-phase refrigerant circulates near the downstream flow path when it is turned back. In the above configuration, a collecting portion for collecting the separated liquid phase refrigerant is provided on the downstream side of the connected flow paths. As a result, the centrifugally separated liquid phase can be suitably collected.

Further, in the evaporator according to one aspect of the present disclosure, the collecting portion is provided with a second drain portion (50) for guiding the collected liquid phase refrigerant to the storage portion.

In the above configuration, the collected refrigerant is guided to the storage section via the second drain section. The refrigerant guided to the storage section evaporates by exchanging heat with the first heat transfer tube group. In this way, since the refrigerant in the gas-liquid separated liquid phase can be guided to the first heat transfer tube group, it is possible to reduce the refrigerant that is not supplied to each heat transfer tube group. Therefore, the performance of the evaporator can be improved.

Further, in the evaporator according to one aspect of the present disclosure, the collecting portion is inclined so that the position where the second drain portion is provided is lowered.

In the above configuration, the collecting portion is inclined so that the position where the second drain portion is provided is lowered. As a result, the liquid phase refrigerant collected in the collecting section flows toward the second drain section. Therefore, more preferably, the refrigerant collected through the second drain portion can be guided to the storage portion.

Further, in the evaporator according to one aspect of the present disclosure, the flow path has a curved portion (60) in which the surface defining the flow path is curved.

In the above configuration, the flow path has a curved portion. As a result, in the curved portion, the pressure loss with respect to the refrigerant flowing through the flow path is reduced. Therefore, the refrigerant can be suitably guided to the refrigerant outlet.

10: Evaporator 11: Pressure vessel (housing)
11a: Cylindrical part 11c: Storage part 12: Refrigerant inlet pipe 13: Refrigerant tray (refrigerant supply part)
14: Full-liquid heat transfer tube group (first heat transfer tube group)
14a: 1st heat transfer tube 15: Liquid film type heat transfer tube group (2nd heat transfer tube group)
15a: Second heat transfer pipe 16: Refrigerant outlet pipe (refrigerant outlet)
17: Obstacle plate 20: Gas-liquid separation flow path (flow path)
21: 1st flow path regulation part 22: 2nd flow path regulation part 22a: Curved part 22b: Vertical part 23: Ascending flow path (1st flow path)
24: Downward flow path (second flow path)
25: Connection flow path 26: Pressure vessel flow path (housing flow path)
27: 1st peeling prevention part 28: 2nd peeling prevention part 30: 1st drain pipe (1st drain part)
40: Gas-liquid separation flow path 41: Third flow path regulation part 41a: First horizontal part 41b: First vertical part 42: Fourth flow path regulation part 42a: Second horizontal part 42b: Second vertical part 42c: Capture Collection part 42d: Third vertical part 43: Pressure vessel flow path (housing flow path)
44: Ascending flow path 45: Horizontal flow path 46: Down flow path 47: Connecting flow path 50: Second drain pipe (second drain portion)
51: 3rd drain pipe 60: 3rd flow path regulation part 61: 1st part 62: 2nd part G: Gap P: Collision position S: Liquid level

Claims (10)

A housing that has a refrigerant outlet that discharges evaporated refrigerant and forms an outer shell,
A first heat transfer tube having a plurality of first heat transfer tubes housed in the housing, immersed in a liquid phase refrigerant stored in a storage portion provided in the lower part of the housing, and having a plurality of first heat transfer tubes through which a medium to be cooled flows. Heat transfer tube group and
A second heat transfer tube housed in the housing, provided above the liquid level of the liquid phase refrigerant stored in the lower part of the housing, and having a plurality of second heat transfer tubes through which a medium to be cooled flows. With the group
A refrigerant supply unit housed in the housing and supplying a liquid phase refrigerant from above to the second heat transfer tube group.
A flow path for guiding the refrigerant evaporated in the second heat transfer tube group to the refrigerant outlet is provided.
The flow path connects the first flow path through which the refrigerant flows from the bottom to the top, the second flow path through which the refrigerant flows from the top to the bottom, and the first flow path and the second flow path in this order. It has a connecting flow path that turns back the refrigerant,
The refrigerant outlet is provided in the upper part of the housing, and is an evaporator through which the refrigerant is guided from below. The flow path area of the first flow path or the second flow path connected to the upstream side of the connection flow path is the first flow path or the second flow path connected to the downstream side of the connection flow path. The evaporator according to claim 1, which is smaller than the flow path area of the above. The flow path has a housing flow path whose part is defined by the inner peripheral surface of the housing.
The evaporator according to claim 1 or 2, wherein the inner peripheral surface of the housing is arranged at a position where the inflowing refrigerant collides with the housing flow path. The evaporator according to claim 3, wherein the housing flow path is provided on the upstream side of the connection flow path. The evaporator according to any one of claims 1 to 4, wherein the flow path is provided with a first drain portion that guides a liquid phase refrigerant to the storage portion. The evaporator according to any one of claims 1 to 5, wherein the connecting flow path is provided with a collecting portion for collecting the refrigerant of the separated liquid phase on the flow path side on the downstream side to be connected. The evaporator according to claim 6, wherein the collecting section is provided with a second drain section that guides the collected liquid phase refrigerant to the storage section. The evaporator according to claim 7, wherein the collecting portion is inclined so that the position where the second drain portion is provided is lowered. The evaporator according to any one of claims 1 to 8, wherein the flow path has a curved portion whose surface defining the flow path is curved. A housing that has a refrigerant outlet that discharges evaporated refrigerant and forms an outer shell,
A first heat transfer tube having a plurality of first heat transfer tubes housed in the housing, immersed in a liquid phase refrigerant stored in a storage portion provided in the lower part of the housing, and having a plurality of first heat transfer tubes through which a medium to be cooled flows. Heat transfer tube group and
A second heat transfer tube housed in the housing, provided above the liquid level of the liquid phase refrigerant stored in the lower part of the housing, and having a plurality of second heat transfer tubes through which a medium to be cooled flows. With the group
A refrigerant supply unit housed in the housing and supplying a liquid phase refrigerant from above to the second heat transfer tube group.
A flow path for guiding the refrigerant evaporated in the second heat transfer tube group to the refrigerant outlet is provided.
The flow path connects the first flow path through which the refrigerant flows from the bottom to the top, the second flow path through which the refrigerant flows from the top to the bottom, and the first flow path and the second flow path to supply the refrigerant. Has a connecting flow path that folds back,
An evaporator in which a collecting portion for collecting the separated liquid phase refrigerant is provided in the connecting flow path on the downstream side of the connecting flow path.

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