WO2021201278A1 - Evaporator - Google Patents

Abstract

An object is to improve heat-exchange efficiency of a heat exchange tube group. An evaporator (10) includes a pressure vessel (11) that has a coolant outlet tube (16) for discharging evaporated coolant, a liquid film heat exchange tube group (15) that is accommodated in the pressure vessel (11) and that has a plurality of liquid film heat exchange tubes (15a) through which water to be cooled flows, a coolant tray (13) that supplies coolant in a liquid phase to the liquid film heat exchange tube group (15) from above, a baffle plate (17) that covers the liquid film heat exchange tube group (15) from a side, and a blow-up prevention plate (18) that covers the liquid film heat exchange tube group (15) from above. A gap (G) is formed between the baffle plate (17) and the blow-up prevention plate (18).

Description

Evaporator

This 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 cooling medium flows inside is known. In the liquid film type evaporator, a plate-shaped member may be provided above or to the side of the heat transfer tube group for the purpose of suitably evaporating the refrigerant in the heat transfer tube group (for example, Patent Document 1).

US Pat. An evaporator is described with a wall extending towards the lower portion.

Special Table 2008-516187

In the evaporator of Patent Document 1, the end of the hood located above the tube bundle and the upper end of the wall located on the side of the tube bundle are connected. That is, in the evaporator of Patent Document 1, a space closed above is formed between the hood and the wall, and the tube bundle is arranged in this space. In such a configuration, when the flush gas of the supplied refrigerant and the refrigerant evaporated in the tube bundle are discharged from the space where the tube bundle is provided, most of the refrigerant passes between the tubes. Therefore, the resistance (pressure loss) becomes large. Therefore, the pressure in the space increases. When the pressure in the space where the tube side is arranged rises, it becomes difficult for the refrigerant to evaporate on the surface of the tube bundle. Therefore, the heat exchange efficiency of the tube bundle may be lowered, and the performance of the evaporator may be lowered.

Further, the evaporator described in Patent Document 1 in which the end of the hood and the upper end of the wall are connected has only a route that passes through the lower end of the space when the refrigerant vaporized in the tube flows out of the space. .. In such a case, at the lower end of the space (that is, near the lower end of the wall), the flow velocity of the vaporized refrigerant toward the outlet of the pressure vessel becomes high. As a result, there is a possibility that the gas phase refrigerant discharged to the outside of the pressure vessel is likely to be accompanied by the liquid phase refrigerant (so-called carryover).

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 improving the heat exchange efficiency of the heat transfer tube group.

In order to solve the above problems, the evaporator of the present disclosure employs the following means.
The evaporator according to one aspect of the present disclosure is provided with a refrigerant outlet for discharging the evaporated refrigerant to the outside, and has a housing forming an outer shell and a plurality of liquids housed in the housing and having a cooling medium flowing inside. A liquid film type heat transfer tube group having a film heat transfer tube, a refrigerant supply unit housed in the housing and supplying a liquid phase refrigerant from above to the liquid film type heat transfer tube group, and the liquid film type heat transfer tube group. A side plate portion that covers the liquid film type heat transfer tube group from the side and an upper plate portion that covers the liquid film type heat transfer tube group from above are provided, and a gap is formed between the side plate portion and the upper plate portion. There is.

According to the present disclosure, the heat exchange efficiency of the heat transfer tube group can be improved.

It is a perspective view which shows the evaporator which concerns on 1st Embodiment of this disclosure. It is a schematic vertical sectional view which shows the evaporator which concerns on 1st Embodiment of this disclosure. It is a schematic vertical sectional view which shows the evaporator which concerns on 2nd Embodiment of this disclosure. It is a schematic vertical sectional view which shows the modification of FIG. It is a schematic vertical sectional view which shows the modification of FIG. It is a schematic vertical sectional view which shows the modification of FIG. It is a schematic vertical sectional view which shows the modification of FIG. It is a schematic vertical sectional view which shows the evaporator which concerns on 3rd Embodiment of this disclosure. It is a schematic vertical sectional view which shows the modification of FIG. It is a schematic vertical sectional view which shows the evaporator which concerns on 4th Embodiment of this disclosure. It is a schematic vertical sectional view which shows the modification of FIG. It is a schematic vertical sectional view which shows the modification of FIG. It is a schematic perspective view which shows the evaporator which concerns on 5th Embodiment of this disclosure. It is a schematic vertical sectional view which shows the evaporator which concerns on 5th Embodiment of this disclosure. It is a schematic perspective 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 FIGS. 1 and 2. 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 this embodiment is applied to a turbo refrigeration system. The turbo refrigeration system includes a turbo compressor that compresses the refrigerant (not shown), a condenser that condenses the refrigerant compressed 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 expanded 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 FIGS. 1 and 2, the evaporator 10 includes a pressure container (housing) 11 forming an outer shell, a refrigerant inlet pipe 12 for introducing a liquid into the pressure container 11, and a lower portion of the refrigerant inlet pipe 12. A refrigerant tray (refrigerant supply unit) 13 provided in the A liquid film type heat transfer tube group 15 provided above the liquid level S of the phase refrigerant (see FIGS. 2 and 3), a refrigerant outlet pipe (refrigerant outlet) 16 for discharging the evaporated refrigerant from the pressure vessel 11, and It has a baffle plate (side plate portion) 17 that covers the liquid film type heat transfer tube group 15 from the side, and a blow-up prevention plate (upper plate portion) 18 that covers the liquid film type heat transfer tube group 15 from above. .. In FIG. 1, for the sake of illustration, the pressure vessel 11, the full-liquid heat transfer tube group 14, and the refrigerant outlet tube 16 are omitted.

As shown in FIG. 2, the pressure vessel 11 closes a cylindrical portion 11a whose central axis extends along the X-axis direction and both ends of the cylindrical portion 11a in the direction along the central axis (X-axis direction). It has two tube plates (not shown) 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.

As shown in FIGS. 1 and 2, 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 substantially rectangular plate-shaped member. 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.

As shown in FIG. 2, 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-filled heat transfer tube group 14 has a plurality of full-filled heat transfer tubes 14a extending along the X-axis direction. The plurality of heat transfer tubes 14a for filling liquid are arranged substantially in parallel. The plurality of liquid 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 heat transfer tubes 14a for filling liquid 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 full heat transfer tube 14a. Further, each full liquid heat transfer tube 14a is formed in a straight line. Further, each liquid 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 as shown in FIGS. 1 and 2. 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 liquid film heat transfer tubes 15a extending along the X-axis direction. The plurality of liquid film heat transfer tubes 15a are arranged substantially in parallel. The plurality of liquid film 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 liquid film 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 cooling medium is circulated inside each liquid film heat transfer tube 15a. Further, each liquid film heat transfer tube 15a is formed in a straight line. Further, each liquid film heat transfer tube 15a extends from one end to the other end of the pressure vessel 11 in the X-axis direction and penetrates each tube plate.

As shown in FIG. 2, 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 at the end 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 refrigerant outlet pipe 16 is provided above the baffle plate 17.

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 a predetermined distance downward from the vicinity from both ends of the refrigerant tray 13 in the Y-axis direction. The lower end of the baffle plate 17 is located above the lower end of the liquid film type heat transfer tube group 15. Specifically, the baffle plate 17 covers substantially the entire area in the Z-axis direction except for the lower end of the liquid film type heat transfer tube group 15 from the side.
The upper end of the baffle plate 17 is located below the blow-up prevention plate 18. A gap G is formed between the upper end of the baffle plate 17 and the blow-up prevention plate 18.
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 blow-up prevention plate 18 has a flat plate portion 18a arranged so that the plate surface is a horizontal plane, and an inclined portion 18b that bends from both ends of the flat plate portion 18a in the Y-axis direction and extends diagonally downward. doing. The blow-up prevention plate 18 is arranged above the refrigerant tray 13. The blow-up prevention plate 18 is arranged away from the baffle plate 17. The refrigerant inlet pipe 12 penetrates the central portion of the flat plate portion 18a of the blow-up prevention plate 18 in the X-axis direction and the Y-axis direction. The lower end of the inclined portion 18b is located above the baffle plate 17. A gap G is formed between the lower end of the inclined portion 18b and the upper end of the baffle plate 17. Further, the blow-up prevention plate 18 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 blow-up prevention plate 18 may be provided only in a part in the X-axis direction.

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 liquid film heat transfer tube 15a arranged at the uppermost stage of the liquid film heat transfer tube group 15, and forms a film on the outer peripheral surface of the liquid film heat transfer tube 15a. cover. The refrigerant that covers the outer peripheral surface of the liquid film heat transfer tube 15a in a film shape exchanges heat with the water to be cooled inside the liquid film 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 liquid film 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 liquid film heat transfer tube 15a arranged at the lowermost part is stored in the storage portion 11c provided at the lower part of the pressure vessel 11 (see FIG. 2). 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, as shown in FIG. 2, the mainstream of the refrigerant evaporated in the liquid film type heat transfer tube group 15 rises around the lower end of the baffle plate 17 as shown by arrow A1 and is guided to the refrigerant outlet tube 16. .. Further, a part of the refrigerant evaporated in the liquid film type heat transfer tube group 15 passes through the gap G formed between the obstruction plate 17 and the blow-up prevention plate 18 as shown by the arrow A2, and passes through the refrigerant outlet pipe. Guided to 16.
The full-liquid 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 stored liquid phase of the storage section 11c. The water to be cooled flowing in the heat transfer tube 15a for the liquid film exchanges heat with the refrigerant stored in the storage unit 11c. The refrigerant that has exchanged heat with the liquid film heat transfer tube 15a evaporates and is discharged upward from the liquid level S. The refrigerant discharged from the liquid level S is guided to the refrigerant outlet pipe 16 as shown by the arrow A3.

The refrigerant that evaporates in the liquid film type heat transfer tube group 15 and the full liquid type heat transfer tube group 14 and is 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 baffle plate 17 covers the liquid film type heat transfer tube group 15 from the side. Further, the blow-up prevention plate 18 covers the liquid film type heat transfer tube group 15 from above. That is, the baffle plate 17 and the blow-up prevention plate 18 form a space (hereinafter, referred to as "inner space S1") in which the liquid film type heat transfer tube group 15 is provided. Further, the baffle plate 17 and the blow-up prevention plate 18 separate the inner space S1 from the space formed outside the inner space S1 (hereinafter, referred to as "outer space S2"). In the present embodiment, a gap G is formed between the blow-up prevention plate 18 and the baffle plate 17. That is, the gap G connects the inner space S1 and the outer space S2. In the present embodiment, when the refrigerant is supplied from the refrigerant tray 13 to the liquid film type heat transfer tube group 15, the refrigerant evaporates. When the refrigerant evaporates, the evaporated refrigerant diffuses in the inner space S1. A part of the diffused refrigerant passes through the gap G formed between the blow-up prevention plate 18 and the baffle plate 17 and moves to the outer space S2. As a result, it is possible to suppress an increase in pressure in the inner space S1 as compared with the case where the gap G is not formed (that is, when the baffle plate 17 and the blow-up prevention plate 18 are connected). Therefore, since the environment around the liquid film type heat transfer tube group 15 can be made an environment suitable for heat exchange, the heat exchange efficiency of the liquid film type heat transfer tube group 15 can be improved. Therefore, the performance of the evaporator 10 can be improved.

Further, in the present embodiment, two routes for the refrigerant to flow from the inner space S1 to the outer space S2 are formed, a route passing through the lower end of the inner space S1 and a route passing through the gap G. Therefore, it is possible to suppress a situation in which the flow velocity of the vaporized refrigerant becomes high at the lower end of the inner space S1 (that is, near the lower end of the baffle plate 17). As a result, it is possible to make it difficult for the gas phase refrigerant discharged to the outside of the pressure vessel 11 to accompany the liquid phase refrigerant (so-called carryover).

Further, a part of the refrigerant supplied from the refrigerant tray 13 is vaporized before reaching the liquid film type heat transfer tube group 15 due to the decrease in pressure. In the present embodiment, the vaporized refrigerant (hereinafter referred to as "flash gas") easily moves to the outer space S2 through the gap G formed between the blow-up prevention plate 18 and the obstruction plate 17. .. Therefore, it is possible to suppress an increase in pressure in the inner space S1 due to the flash gas. Further, since the flash gas is discharged from the inner space S1, the liquid phase refrigerant supplied to the liquid film type heat transfer tube group 15 without being vaporized is not easily affected by the flash gas. Therefore, the refrigerant can be accurately supplied to the liquid film type heat transfer tube group 15.

Further, in the present embodiment, the baffle plate 17 is provided. As a result, the flow of the refrigerant from the side with respect to the liquid film type heat transfer tube group 15 can be blocked, so that the situation in which the refrigerant supplied in the liquid film type heat transfer tube group 15 is scattered can be suppressed.
Further, in the present embodiment, the blow-up prevention plate 18 is provided. As a result, it is possible to suppress a situation in which the refrigerant supplied to the liquid film type heat transfer tube group 15 is blown up.

Further, in the present embodiment, the refrigerant outlet pipe 16 is provided above the lower end of the baffle plate 17. In the evaporator 10 having such a structure, the refrigerant that evaporates in the liquid film type heat transfer tube group 15 and heads for the refrigerant outlet tube 16 is easily blocked by the obstruction plate 17 and the blow-up prevention plate 18. Therefore, the evaporated refrigerant tends to stay in the inner space S1, so that the pressure in the inner space S1 tends to increase. On the other hand, in the present embodiment, since the gap G is formed between the baffle plate 17 and the blow-up prevention plate 18, the refrigerant evaporated in the liquid film type heat transfer tube group 15 passes through the gap G to the outer space S2. You can move. As a result, it is possible to prevent the refrigerant from staying in the inner space S1. Therefore, even if the structure is such that the refrigerant outlet pipe 16 is provided above the lower end of the baffle plate 17, the increase in pressure in the inner space S1 can be more preferably suppressed. Therefore, it is possible to preferably improve the heat exchange efficiency of the liquid film type heat transfer tube group 15 and improve the performance of the evaporator 10.

Further, in the present embodiment, the refrigerant tray 13 is provided above the liquid film type heat transfer tube group 15. In the evaporator 10 having such a structure, since the flash gas tends to stay in the inner space S1, the pressure in the inner space S1 tends to increase. On the other hand, in the present embodiment, since the gap G is formed between the baffle plate 17 and the blow-up prevention plate 18, the flash gas can pass through the gap G and move to the outer space S2. As a result, it is possible to prevent the refrigerant from staying in the inner space S1. Therefore, even if the refrigerant tray 13 has a structure provided above the liquid film type heat transfer tube group 15, the increase in pressure in the inner space S1 can be more preferably suppressed. Therefore, more preferably, the heat exchange efficiency of the liquid film type heat transfer tube group 15 can be improved, and the performance of the evaporator 10 can be improved.

[Second Embodiment]
Next, the evaporator according to the second embodiment of the present disclosure will be described with reference to FIG.
The evaporator 20 according to the present embodiment is first in that a lower plate portion 21 provided between the lower end of the liquid film type heat transfer tube group 15 and the liquid level S is provided instead of the baffle plate 17. It is different from the embodiment. Since other points are the same as those of the first embodiment, the same reference numerals are given to the same configurations, and detailed description thereof will be omitted.

As shown in FIG. 3, the evaporator 20 includes a pair of lower plate portions 21 provided between the lower end of the liquid film type heat transfer tube group 15 and the liquid level S. The pair of lower plate portions 21 are arranged apart from each other in the Y-axis direction. The pair of lower plate portions 21 are provided symmetrically with respect to the center in the Y-axis direction. Each lower plate portion 21 is inclined so that the outer end portion in the Y-axis direction is higher than the inner end portion in the Y-axis direction. The outer end portion of each lower plate portion 21 in the Y-axis direction is arranged outside the outer end portion of the liquid film type heat transfer tube group 15 in the Y-axis direction.
The pair of lower plate portions 21 extend 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 pair of lower plate portions 21 may be provided only in a part in the X-axis direction.

According to this embodiment, the following effects are exhibited.
In the present embodiment, the lower plate portion 21 is provided between the liquid film type heat transfer tube group 15 and the liquid level S. As a result, the refrigerant that evaporates by the full-liquid heat transfer tube group 14 and goes from the liquid level S to the liquid film type heat transfer tube group 15 is blocked by the lower plate portion 21. The refrigerant blocked by the lower plate portion 21 bypasses the outside of the lower plate portion 21 and is guided to the refrigerant outlet pipe 16 as shown by the broken line arrow in FIG. Therefore, it is possible to make it difficult for the refrigerant evaporated in the full-liquid heat transfer tube group 14 to reach the liquid film heat transfer tube group 15. Therefore, the situation in which the refrigerant supplied to the liquid film type heat transfer tube group 15 is scattered by the refrigerant evaporated in the liquid film type heat transfer tube group 14 can be suppressed, so that the environment around the liquid film type heat transfer tube group 15 can be suppressed. Can be an environment suitable for heat exchange. Therefore, the heat exchange efficiency of the liquid film type heat transfer tube group 15 can be improved, and the performance of the evaporator 10 can be improved.

Further, in the present embodiment, it is possible to suppress a situation in which the refrigerant supplied to the liquid film type heat transfer tube group 15 is scattered by the refrigerant evaporated in the full liquid type heat transfer tube group 14. This makes it difficult for carryover to occur.

Further, in the present embodiment, the inner ends of the pair of lower plate portions 21 are separated from each other. Further, each lower plate portion 21 is inclined so that the inner end portion is downward. As a result, even if the liquid film type heat transfer tube group 15 does not completely evaporate and the liquid phase refrigerant toward the storage portion 11c falls on the upper surface of the lower plate portion 21, as shown by the solid line arrow in FIG. , The liquid phase refrigerant moves on the upper surface of the lower plate portion 21 to the inner end and falls from the inner end to the storage portion 11c. As a result, the amount of refrigerant that is not supplied to each heat transfer tube group can be reduced, so that the performance of the evaporator 10 can be improved.

[Modification 1]
The shape of the lower plate portion is not limited to the shape described above. For example, like the lower plate portion 26 shown in FIG. 4, a plate-shaped member that is inclined so as to be positioned downward from both ends in the Y-axis direction toward the center portion may be used. Further, the lower plate portion 26 may be provided with a refrigerant discharge pipe 27 at the center portion in the Y-axis direction. The refrigerant discharge pipe 27 is formed in a straight line extending in the Z-axis direction. The upper end of the refrigerant discharge pipe 27 is connected to the lower plate portion 26, and the lower end is arranged below the full-liquid heat transfer pipe group 14. The upper end of the refrigerant discharge pipe 27 is open on the upper surface of the lower plate portion 26.

With this configuration, the refrigerant stored on the upper surface of the lower plate portion 26 is guided to the lower side of the full-liquid heat transfer tube group 14 via the refrigerant discharge pipe 27. Therefore, the refrigerant on the upper surface of the lower plate portion 26 can be guided to the storage portion 11c. As a result, the amount of refrigerant that is not supplied to each heat transfer tube group can be reduced, so that the performance of the evaporator 10 can be improved.

Further, the refrigerant on the upper surface of the lower plate portion 26 is guided to the lower side of the full-liquid heat transfer tube group 14. As a result, the refrigerant guided from the upper surface of the lower plate portion 26 to the storage portion 11c can be prevented from interfering with the refrigerant that evaporates in the full-liquid heat transfer tube group 14 and heads toward the liquid level S. Therefore, since heat exchange can be suitably performed in the full-liquid heat transfer tube group 14, the performance of the evaporator 10 can be improved.

[Modification 2]
Further, like the lower plate portion 31 shown in FIG. 5, the lower plate portion 26 may have the same shape as the lower plate portion 26 shown in the first modification and may have a plurality of through holes penetrating from the upper surface to the lower surface. With this configuration, the refrigerant that has fallen to the lower plate portion 31 passes through the through hole and is guided to the storage portion 11c. Therefore, it is possible to prevent the refrigerant from being stored on the upper surface of the lower plate portion 31. Therefore, the refrigerant that is not supplied to each heat transfer tube group can be reduced, so that the performance of the evaporator 10 can be improved. The lower plate portion 31 may be formed of a wire mesh instead of forming a plurality of through holes.

[Modification 3]
Further, like the lower plate portion 36 shown in FIG. 6, it integrally has a flat bottom surface portion 36a and an inclined portion 36b that bends from both ends of the bottom surface portion 36a in the Y-axis direction and extends diagonally upward. It may be a dish-shaped member. Further, the lower plate portion 36 may be provided with a plurality of refrigerant discharge pipes 37 (three as an example in the present embodiment) on the bottom surface portion 36a. The plurality of refrigerant discharge pipes 37 are arranged side by side in the Y-axis direction. The upper end of the refrigerant discharge pipe 37 is connected to the lower plate portion 36, and the lower end is arranged below the full-liquid heat transfer tube group 14.

With this configuration, the refrigerant stored on the upper surface of the lower plate portion 36 is guided to the lower side of the full-liquid heat transfer tube group 14 via the refrigerant discharge pipe 37. Therefore, the refrigerant on the upper surface of the lower plate portion 36 can be guided to the storage portion 11c. As a result, the amount of refrigerant that is not supplied to each heat transfer tube group can be reduced, so that the performance of the evaporator 10 can be improved.

[Modification example 4]
Further, like the lower plate portion 41 shown in FIG. 7, the lower plate portion 31 may have the same shape as the lower plate portion 31 shown in the second modification and may have a plurality of through holes penetrating from the upper surface to the lower surface. With this configuration, the refrigerant that has fallen to the lower plate portion 41 passes through the through hole and is guided to the storage portion 11c. Therefore, it is possible to prevent the refrigerant from being stored on the upper surface of the lower plate portion 41. Therefore, the refrigerant that is not supplied to each heat transfer tube group can be reduced, so that the performance of the evaporator 10 can be improved. The lower plate portion 41 may be formed of a wire mesh instead of forming a plurality of through holes.

[Third Embodiment]
Next, the evaporator according to the third embodiment of the present disclosure will be described with reference to FIG.
The evaporator 50 according to the present embodiment is different from the first embodiment in that a pressure loss increasing portion is provided instead of the baffle plate 17. Since other points are the same as those of the first embodiment, the same reference numerals are given to the same configurations, and detailed description thereof will be omitted.

As shown in FIG. 8, the evaporator 50 is provided with a pair of lower end side plate portions (pressure loss increasing portions) 51 arranged on both sides of the lower end portion of the liquid film type heat transfer tube group 15. The pair of lower end side plate portions 51 are arranged so as to sandwich the lower end portions of the liquid film type heat transfer tube group 15. That is, the pair of lower end side plate portions 51 cover the liquid film type heat transfer tube group 15 from the Y-axis direction. The pair of lower end side plate portions 51 increases the pressure loss of the route passing through the region where the lower end portion of the liquid film type heat transfer tube group 15 is arranged (hereinafter, referred to as "lower end region P"). Each lower end side plate portion 51 is a flat plate-shaped member. The lower end side plate portion 51 may be formed with a plurality of through holes penetrating in the plate thickness direction. Further, instead of forming a plurality of through holes, it may be formed of a wire mesh.

The length of the lower end side plate portion 51 in the Z-axis direction is set to be less than half the length of the liquid film type heat transfer tube group 15 in the Z-axis direction. That is, a large gap is formed above the lower end side plate portion 51 with the blow-up prevention plate 18.
The pair of lower end side plate portions 51 extend 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 pair of lower end side plate portions 51 may be provided only in a part in the X-axis direction.

According to this embodiment, the following effects are exhibited.
In the present embodiment, a pair of lower end side plate portions 51 are provided as pressure loss increasing portions for increasing the pressure loss in the lower end region P. The pair of lower end side plate portions 51 cover the lower end portions of the liquid film type heat transfer tube group 15 from both sides. As a result, the pressure loss in the lower end region P can be increased, so that the refrigerant that evaporates by the full-liquid heat transfer tube group 14 and goes from the liquid level S to the refrigerant outlet tube 16 is shown by the broken line arrow in FIG. , It is difficult to flow into the lower end region P. Therefore, it is possible to make it difficult for the refrigerant evaporated in the full-liquid heat transfer tube group 14 to reach the liquid film heat transfer tube group 15. Therefore, the situation in which the refrigerant supplied to the liquid film type heat transfer tube group 15 is scattered by the refrigerant evaporated in the liquid film type heat transfer tube group 14 can be suppressed, so that the environment around the liquid film type heat transfer tube group 15 can be suppressed. Can be an environment suitable for heat exchange. Therefore, the heat exchange efficiency of the liquid film type heat transfer tube group 15 can be improved, and the performance of the evaporator 10 can be improved.

[Modification 5]
Further, as shown in FIG. 9, instead of the pair of lower end side plate portions 51, a plurality of dummy tubes 56 may be provided on both sides of the lower end portion of the liquid film type heat transfer tube group 15 as pressure loss increasing portions. good. The inside of the dummy tube 56 is hollow, and no fluid or the like flows through the inside. The plurality of dummy tubes 56 are arranged so that the distance between the adjacent dummy tubes 56 is shorter than the distance between the adjacent liquid film heat transfer tubes 15a. By arranging in this way, the pressure loss of the flow path passing between the dummy tubes 56 can be increased. Therefore, the pressure loss in the lower end region P can be increased.
A fluid such as water may be circulated in the dummy pipe 56. With this configuration, the dummy pipe 56 can also exchange heat with the refrigerant, so that the heat exchange efficiency can be improved. Therefore, the performance of the evaporator 10 can be improved.

[Fourth Embodiment]
Next, the evaporator according to the fourth embodiment of the present disclosure will be described with reference to FIG.
The evaporator 60 according to the present embodiment is different from the first embodiment in that a rectifying unit is provided instead of the baffle plate 17. Since other points are the same as those of the first embodiment, the same reference numerals are given to the same configurations, and detailed description thereof will be omitted.

As shown in FIG. 10, the evaporator 60 is provided with a pair of lower side plate portions (rectifying portions) 61 arranged on both sides of the lower portion of the liquid film type heat transfer tube group 15. The pair of lower side plate portions 61 are arranged so as to sandwich the lower portion of the liquid film type heat transfer tube group 15. That is, the pair of lower plate portions 61 covers the liquid film type heat transfer tube group 15 from the Y-axis direction. The pair of lower side plate portions 61 guide the refrigerant evaporated in the full-liquid heat transfer tube group 14 to the refrigerant outlet tube 16. That is, the refrigerant evaporated in the full-liquid heat transfer tube group 14 is suppressed from flowing into the region where the liquid film type heat transfer tube group 15 is provided.
Each lower plate portion 61 is a flat plate-shaped member. Further, each lower plate portion 61 is arranged so that the plate surface faces a vertical plane. The lower plate portion 61 may be formed with a plurality of through holes penetrating in the plate thickness direction. Further, instead of forming a plurality of through holes, it may be formed of a wire mesh.

The length of the lower plate portion 61 in the Z-axis direction is set to be less than half the length of the liquid film type heat transfer tube group 15 in the Z-axis direction. That is, a large gap is formed above the lower side plate portion 61 with the blow-up prevention plate 18. The lower part of the liquid film type heat transfer tube group 15 may be lower than the central part of the liquid film type heat transfer tube group 15 in the Z-axis direction.
The pair of lower side plate portions 61 extend 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 pair of lower plate portions 61 may be provided only in a part in the X-axis direction.
Further, as shown in FIG. 11, each lower plate portion 61 may be inclined with respect to the vertical plane so that the lower end is located inside in the Y-axis direction.

According to this embodiment, the following effects are exhibited.
In the present embodiment, a pair of lower side plate portions 61 are provided as rectifying portions for guiding the refrigerant evaporated in the full-liquid heat transfer tube group 14 to the refrigerant outlet pipe 16. A pair of lower plate portions 61 cover the lower portion of the liquid film type heat transfer tube group 15 from both sides. As a result, the refrigerant that evaporates in the full-liquid heat transfer tube group 14 and goes from the side to the liquid film type heat transfer tube group 15 is discharged by the pair of lower side plate portions 61 as shown by the broken line arrows in FIG. You will be guided to the pipe 16. Therefore, it is possible to make it difficult for the refrigerant evaporated in the full-liquid heat transfer tube group 14 to reach the liquid film heat transfer tube group 15. Therefore, the situation in which the refrigerant supplied to the liquid film type heat transfer tube group 15 is scattered by the refrigerant evaporated in the liquid film type heat transfer tube group 14 can be suppressed, so that the environment around the liquid film type heat transfer tube group 15 can be suppressed. Can be an environment suitable for heat exchange. Therefore, the heat exchange efficiency of the liquid film type heat transfer tube group 15 can be improved, and the performance of the evaporator 10 can be improved.
Further, since the lower side plate portion 61 is arranged so as to sandwich the lower portion of the liquid film type heat transfer tube group 15, the refrigerant rising from the liquid level S can be guided to the refrigerant outlet pipe 16 relatively early. .. Therefore, it is possible to make it more difficult for the refrigerant evaporated in the full-liquid heat transfer tube group 14 to reach the liquid film heat transfer tube group 15.

[Modification 6]
Further, as shown in FIG. 12, instead of the pair of lower side plate portions 61, a plurality of dummy tubes 66 may be provided on both sides of the lower portion of the liquid film type heat transfer tube group 15 as rectifying portions. The inside of the dummy tube 66 is hollow, and no fluid or the like flows through the inside. The plurality of dummy tubes 66 are arranged so that the distance between the adjacent dummy tubes 66 is shorter than the distance between the adjacent liquid film heat transfer tubes 15a. By arranging in this way, the pressure loss of the flow path passing between the dummy tubes 66 can be increased. Therefore, it is possible to prevent the refrigerant evaporated in the full-liquid heat transfer tube group 14 from flowing into the region where the liquid film heat transfer tube group 15 is provided.
A fluid such as water may be circulated in the dummy pipe 66. With this configuration, the dummy tube 66 can also exchange heat with the refrigerant, so that the heat exchange efficiency can be improved. Therefore, the performance of the evaporator 10 can be improved.

[Fifth Embodiment]
Next, the evaporator according to the fifth embodiment of the present disclosure will be described with reference to FIGS. 13 and 14.
The evaporator 70 according to the present embodiment is different from the first embodiment in that a cross plate portion is provided instead of the baffle plate 17. Since other points are the same as those of the first embodiment, the same reference numerals are given to the same configurations, and detailed description thereof will be omitted. In FIG. 13, for the sake of illustration, the pressure vessel 11 and the full-liquid heat transfer tube group 14 and the like are omitted. Further, in FIG. 13, due to the illustration, the liquid film heat transfer tubes 15a are not shown one by one, but are collectively shown as a liquid film type heat transfer tube group 15.

As shown in FIGS. 13 and 14, a plurality of evaporators 70 are arranged so as to intersect the X-axis direction on both sides of the liquid film type heat transfer tube group 15 in the Y-axis direction (an example in the present embodiment). 3) Cross plate portions 71 are provided. The plurality of intersecting plate portions 71 are arranged side by side at predetermined intervals in the X-axis direction. The length of the cross plate portion 71 in the Z-axis direction is substantially the same as the length of the liquid film type heat transfer tube group 15 in the Z-axis direction. Each cross plate portion 71 is formed of a flat plate-shaped member.

According to this embodiment, the following effects are exhibited.
The refrigerant outlet pipe 16 is provided at the end of the pressure vessel 11 in the X-axis direction. Therefore, the refrigerant evaporated in the liquid-filled heat transfer tube group 14 and the liquid film-type heat transfer tube group 15 is guided to the refrigerant outlet tube 16 while moving in the X-axis direction. For example, when the cross plate portion 71 is not provided, the refrigerant evaporated in the liquid film type heat transfer tube group 15 moves along the X-axis direction with almost no increase to the lower region of the refrigerant outlet tube 16. Then, they merge in the region below the refrigerant outlet pipe 16 and soar. Therefore, the flow velocity of the refrigerant rising toward the refrigerant outlet pipe 16 becomes high.
On the other hand, in the present embodiment, the cross plate portion 71 arranged so as to intersect the X-axis direction is provided on the side of the liquid film type heat transfer tube group 15. That is, the space formed inside the pressure vessel 11 is divided into a plurality of spaces in the X-axis direction by the cross plate portion 71. As a result, as shown by the broken line arrows in FIGS. 13 and 14, the refrigerant evaporated in the liquid film type heat transfer tube group 15 moves upward in each of the divided spaces. Therefore, it is possible to suppress a rapid rise of the refrigerant in the region below the refrigerant outlet pipe 16. Therefore, carryover can be made less likely to occur.

Further, in the present embodiment, the cross plate portion 71 can increase the pressure loss with respect to the movement of the refrigerant in the X-axis direction. Therefore, since the flow velocity of the refrigerant can be reduced, carryover can be less likely to occur.

The cross plate portion is not limited to the structure described above. As shown in the cross plate portion 76 of FIG. 15, a plurality of through holes penetrating in the plate thickness direction may be formed. Further, instead of forming a plurality of through holes, it may be formed of a wire mesh. With this configuration, the flow velocity of the refrigerant can be reduced while ensuring the movement of the refrigerant in the X-axis direction.

Note that the present disclosure is not limited to the above embodiment, and can be appropriately modified as long as it does not deviate from the gist thereof.

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.
For example, in each of the above embodiments, an example in which the refrigerant outlet pipe 16 is provided in the upper part of the pressure vessel 11 has been described, but the present disclosure is not limited to this. For example, the refrigerant outlet pipe 16 may be provided on the side of the pressure vessel 11. Further, the refrigerant outlet pipe 16 may be provided in the lower part of the pressure vessel 11.
Further, for example, each of the above embodiments may be combined.

The evaporator described in the present embodiment described above is grasped as follows, for example.
The evaporator (10) according to one aspect of the present disclosure is provided with a refrigerant outlet (16) for discharging the evaporated refrigerant to the outside, and is housed in the housing, and a plurality of liquid films through which the cooled medium flows inside. A liquid film type heat transfer tube group (15) having a heat transfer tube (15a) for use, and a refrigerant supply unit (13) housed in the housing and supplying a liquid phase refrigerant from above to the liquid film type heat transfer tube group. A side plate portion (17) that covers the liquid film type heat transfer tube group from the side and an upper plate portion (18) that covers the liquid film type heat transfer tube group from above are provided. A gap (G) is formed between the upper plate portion and the upper plate portion.

In the above configuration, the side plate portion covers the liquid film type heat transfer tube group from the side. In addition, the upper plate portion covers the liquid film type heat transfer tube group from above. That is, the side plate portion and the upper plate portion form a space (hereinafter, referred to as "inner space") in which the liquid film type heat transfer tube group is provided. Further, the side plate portion and the upper plate portion separate the inner space from the space formed outside the inner space (hereinafter, referred to as "outer space"). In the above configuration, a gap is formed between the upper plate portion and the side plate portion. That is, the gap connects the inner space and the outer space. In the above configuration, when the refrigerant is supplied from the refrigerant supply unit to the liquid film type heat transfer tube group, the refrigerant evaporates. When the refrigerant evaporates, the evaporated refrigerant diffuses in the inner space. The diffused part passes through the gap formed between the upper plate portion and the side plate portion and moves to the outer space. As a result, it is possible to suppress an increase in pressure in the inner space as compared with the case where no gap is formed. Therefore, since the environment around the liquid film type heat transfer tube group can be made an environment suitable for heat exchange, the heat exchange efficiency of the liquid film type heat transfer tube group can be improved. Therefore, the performance of the evaporator can be improved.
Further, since the increase in pressure in the inner space can be suppressed, it is possible to suppress the situation where the flow velocity of the vaporized refrigerant becomes high at the lower end of the inner space (that is, near the lower end of the side plate portion). As a result, it is possible to make it difficult for the gas phase refrigerant discharged to the outside of the housing to accompany the liquid phase refrigerant (so-called carryover).
Further, a part of the refrigerant supplied from the refrigerant supply unit is vaporized before reaching the liquid film type heat transfer tube group due to the decrease in pressure. In the above configuration, the vaporized refrigerant (hereinafter referred to as "flash gas") easily moves to the outer space through the gap formed between the upper plate portion and the side plate portion. Therefore, it is possible to suppress an increase in pressure in the inner space due to the flash gas. Further, since the flash gas is discharged from the inner space, the liquid phase refrigerant supplied to the liquid film type heat transfer tube group without vaporization is not easily affected by the flash gas. Therefore, the refrigerant can be accurately supplied to the liquid film heat transfer tube.

Further, the evaporator according to one aspect of the present disclosure is housed in the housing and is immersed in a liquid phase refrigerant stored in the lower part of the housing, and a plurality of filled mediums through which the cooling medium flows are filled. A full-liquid heat transfer tube group (14) having a liquid heat transfer tube (14a) is provided, and the liquid film type heat transfer tube group (15) is the liquid level of the liquid phase refrigerant stored in the lower part of the housing. It is provided above (S).

In the above configuration, a part of the refrigerant evaporated in the full-liquid heat transfer tube group can also pass through the gap formed between the upper plate portion and the side plate portion and head toward the refrigerant outlet. As a result, it is possible to suppress an increase in pressure in the inner space.

Further, in the evaporator according to one aspect of the present disclosure, the refrigerant outlet is provided above the lower end of the side plate portion.

In the above configuration, the refrigerant outlet is provided above the lower end of the side plate portion. In the evaporator having such a structure, the refrigerant that evaporates in the liquid film type heat transfer tube group and goes to the refrigerant outlet is easily blocked by the side plate portion and the upper plate portion. Therefore, the evaporated refrigerant tends to stay in the inner space, and the pressure in the inner space tends to increase.
In the above configuration, since a gap is formed between the side plate portion and the upper plate portion, the refrigerant evaporated in the liquid film type heat transfer tube group can pass through the gap and move to the outer space. This makes it difficult for the refrigerant to stay in the inner space. Therefore, the increase in pressure in the inner space can be suppressed more preferably. Therefore, more preferably, the heat exchange efficiency of the liquid film type heat transfer tube group can be improved, and the performance of the evaporator can be improved.

Further, in the evaporator according to one aspect of the present disclosure, the refrigerant supply unit is provided above the liquid film type heat transfer tube group, and the side plate portion is on the upper side of the liquid film type heat transfer tube group. It covers from the side.

In the above configuration, the refrigerant supply unit is provided above the liquid film type heat transfer tube group. In an evaporator having such a structure, the flash gas tends to stay in the inner space, so that the pressure in the inner space tends to increase.
In the above configuration, since a gap is formed between the side plate portion and the upper plate portion, the flash gas can pass through the gap and move to the outer space. This makes it difficult for the refrigerant to stay in the inner space. Therefore, the increase in pressure in the inner space can be suppressed more preferably. Therefore, more preferably, the heat exchange efficiency of the liquid film type heat transfer tube group can be improved, and the performance of the evaporator can be improved.

Further, the evaporator (20) according to one aspect of the present disclosure has a refrigerant outlet (16) for discharging the evaporated refrigerant to the outside, and is housed in a housing (11) forming an outer shell and the housing. A full-liquid heat transfer tube group (14) having a plurality of full-liquid heat transfer tubes (14a) immersed in a liquid-phase refrigerant stored in the lower part of the housing and having a cooled medium flowing inside. , A plurality of liquid film heat transfer tubes 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. A liquid film type heat transfer tube group (15) having 15a), a refrigerant supply unit (13) housed in the housing and supplying a liquid phase refrigerant from above to the liquid film type heat transfer tube group, and the liquid film. A lower plate portion (21) provided between the type heat transfer tube group and the liquid level is provided.

In the above configuration, a lower plate portion is provided between the liquid film type heat transfer tube group and the liquid level. As a result, the refrigerant that evaporates by the full-liquid heat transfer tube group and goes from the liquid level to the liquid film type heat transfer tube group is blocked by the lower plate portion. Therefore, it is possible to make it difficult for the refrigerant evaporated in the full-liquid heat transfer tube group to reach the liquid film heat transfer tube group. Therefore, it is possible to suppress the situation where the refrigerant supplied to the liquid film type heat transfer tube group is scattered by the refrigerant evaporated in the liquid film type heat transfer tube group, so that the environment around the liquid film type heat transfer tube group is heat exchanged. The environment can be suitable for. Therefore, the heat exchange efficiency of the liquid film type heat transfer tube group can be improved, and the performance of the evaporator can be improved.
Further, in the above configuration, it is possible to suppress a situation in which the refrigerant supplied to the liquid film type heat transfer tube group is scattered by the refrigerant evaporated in the liquid film type heat transfer tube group. As a result, it is possible to prevent the phenomenon that the gas phase refrigerant flowing toward the refrigerant outlet is accompanied by the liquid phase refrigerant (so-called carryover).

Further, the evaporator according to one aspect of the present disclosure includes a refrigerant discharge pipe (27) whose upper end is connected to the lower plate portion and whose lower end is arranged below the full-liquid heat transfer tube group, and the lower plate is provided. The portion is provided below the liquid film type heat transfer tube group.

In the above configuration, the lower plate portion is provided below the liquid film type heat transfer tube group. As a result, the liquid phase refrigerant that has not completely evaporated in the liquid film type heat transfer tube group is stored on the upper surface of the lower plate portion. In the above configuration, the upper end is connected to the lower plate portion, and the lower end is provided with a refrigerant discharge pipe arranged below the full-liquid heat transfer tube group. As a result, the refrigerant stored on the upper surface of the lower plate portion is guided to the lower side of the full-liquid heat transfer tube group via the refrigerant discharge pipe. Therefore, the refrigerant on the upper surface of the lower plate portion can be guided to the portion where the refrigerant is stored in the lower part of the housing (hereinafter, referred to as “storage portion”). As a result, the amount of refrigerant that is not supplied to each heat transfer tube group can be reduced, so that the performance of the evaporator can be improved.
Further, the refrigerant on the upper surface of the lower plate portion is guided to the lower side of the full-liquid heat transfer tube group. As a result, the refrigerant guided from the upper surface of the lower plate portion to the storage portion can be made less likely to interfere with the refrigerant that evaporates in the full-liquid heat transfer tube group and heads toward the liquid surface.

Further, in the evaporator according to one aspect of the present disclosure, the lower plate portion has a hole penetrating from the upper surface to the lower surface.

In the above configuration, the lower plate portion has a hole penetrating from the upper surface to the lower surface. As a result, the refrigerant that has not completely evaporated in the liquid film type heat transfer tube group and has fallen to the lower plate portion passes through the holes and is guided to the storage portion below the lower plate portion. Therefore, it is possible to prevent the refrigerant from being stored on the upper surface of the lower plate portion. Therefore, it is possible to reduce the amount of refrigerant that is not guided to the liquid film type heat transfer tube group, and thus it is possible to improve the performance of the evaporator.

Further, the evaporator (50) according to one aspect of the present disclosure is provided with a refrigerant outlet (16) for discharging the evaporated refrigerant to the outside, and is housed in a housing (11) forming an outer shell and the housing. A full-liquid heat transfer tube group (14) having a plurality of full-liquid heat transfer tubes (14a) immersed in a liquid-phase refrigerant stored in the lower part of the housing and having a cooled medium flowing inside. , A plurality of liquid film heat transfer tubes 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. A liquid film type heat transfer tube group (15) having 15a), a refrigerant supply unit (13) housed in the housing and supplying a liquid phase refrigerant from above to the liquid film type heat transfer tube group, and the liquid film. A pressure loss increasing portion (51) is provided on the side of the lower end portion of the type heat transfer tube group and increases the pressure in the region where the lower end portion of the liquid film type heat transfer tube group is arranged.

The above configuration includes a pressure loss increasing portion that increases the pressure in the region where the lower end portion of the liquid film type heat transfer tube group is arranged (hereinafter, referred to as "lower end region"). As a result, the pressure in the lower end region can be increased, so that the refrigerant that evaporates by the full-liquid heat transfer tube group and goes from the liquid surface to the liquid film type heat transfer tube group does not easily flow into the lower end region. Therefore, it is possible to make it difficult for the refrigerant evaporated in the full-liquid heat transfer tube group to reach the liquid film heat transfer tube group. Therefore, it is possible to suppress the situation where the refrigerant supplied to the liquid film type heat transfer tube group is scattered by the refrigerant evaporated in the liquid film type heat transfer tube group, so that the environment around the liquid film type heat transfer tube group is heat exchanged. The environment can be suitable for. Therefore, the heat exchange efficiency of the liquid film type heat transfer tube group can be improved, and the performance of the evaporator can be improved.

Further, in the evaporator according to one aspect of the present disclosure, the pressure loss increasing portion is arranged so as to sandwich the lower end portion of the liquid film type heat transfer tube group, and a pair of lower ends that cover the liquid film type heat transfer tube group from the side. It has a side plate portion (51).

In the above configuration, a pair of lower end side plates cover the lower end of the liquid film type heat transfer tube group from both sides. As a result, the pressure in the lower end region can be increased more than in other regions. Therefore, it is possible to make it difficult for the refrigerant that evaporates by the full-liquid heat transfer tube group and goes from the liquid surface to the liquid film type heat transfer tube group to flow into the lower end region. Therefore, it is possible to make it difficult for the refrigerant evaporated in the full-liquid heat transfer tube group to reach the liquid film heat transfer tube group.

Further, the evaporator (60) according to one aspect of the present disclosure is provided with a refrigerant outlet (16) for discharging the evaporated refrigerant to the outside, and is housed in a housing (11) forming an outer shell and the housing. A full-liquid heat transfer tube group (14) having a plurality of full-liquid heat transfer tubes (14a) immersed in a liquid-phase refrigerant stored in the lower part of the housing and having a cooled medium flowing inside. , A plurality of liquid film heat transfer tubes 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 a medium to be cooled flows inside. A liquid film type heat transfer tube group (15) having 15a), a refrigerant supply unit (13) housed in the housing and supplying a liquid phase refrigerant from above to the liquid film type heat transfer tube group, and the liquid film. It is provided with a rectifying unit (61) arranged so as to sandwich the lower portion of the type heat transfer tube group and guiding the refrigerant evaporated in the full-liquid type heat transfer tube group to the refrigerant outlet.

In the above configuration, rectifying sections for guiding the refrigerant evaporated in the full-liquid heat transfer tube group to the refrigerant outlet are provided on both sides of the liquid film type heat transfer tube group. As a result, the refrigerant that evaporates in the full-liquid heat transfer tube group and heads for the liquid film type heat transfer tube group from the side is guided to the refrigerant outlet by the rectifying section. Therefore, it is possible to make it difficult for the refrigerant evaporated in the full-liquid heat transfer tube group to reach the liquid film heat transfer tube group. Therefore, it is possible to suppress the situation where the refrigerant supplied to the liquid film type heat transfer tube group is scattered by the refrigerant evaporated in the liquid film type heat transfer tube group, so that the environment around the liquid film type heat transfer tube group is heat exchanged. The environment can be suitable for. Therefore, the heat exchange efficiency of the liquid film type heat transfer tube group can be improved, and the performance of the evaporator can be improved.
Further, since the rectifying unit is arranged so as to sandwich the lower part of the liquid film type heat transfer tube group, the refrigerant rising from the liquid surface can be guided to the refrigerant outlet relatively early. Therefore, it is possible to make it more difficult for the refrigerant evaporated in the full-liquid heat transfer tube group to reach the liquid film heat transfer tube group.

Further, in the evaporator according to one aspect of the present disclosure, the rectifying portion has a pair of lower side plate portions (61) that cover the liquid film type heat transfer tube group from both sides.

In the above configuration, a pair of lower plate portions cover the lower part of the liquid film type heat transfer tube group from both sides. As a result, the refrigerant that evaporates in the full-liquid heat transfer tube group and goes from the side to the liquid film type heat transfer tube group is blocked by the lower side plate portion. Therefore, it is possible to make it difficult for the refrigerant evaporated in the full-liquid heat transfer tube group to reach the liquid film heat transfer tube group.

Further, in the evaporator (70) according to one aspect of the present disclosure, the housing extends in a predetermined direction and intersects the predetermined direction on the side of the liquid film type heat transfer tube group. A plurality of arranged cross plate portions (71) are provided.

The refrigerant evaporated in the full-liquid heat transfer tube group and the liquid film heat transfer tube group is guided to the refrigerant outlet while moving in a predetermined direction. In the above configuration, a cross plate portion arranged so as to intersect a predetermined direction is provided on the side of the liquid film type heat transfer tube group. This makes it possible to increase the pressure loss with respect to the movement of the refrigerant in a predetermined direction. Therefore, since the flow velocity of the refrigerant can be reduced, it is possible to make it difficult for the gas phase refrigerant flowing toward the refrigerant outlet to accompany the liquid phase refrigerant (so-called carryover).

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 14a: Full-liquid heat transfer tube 15: Liquid film type heat transfer tube group 15a: Liquid film heat transfer tube 16: Refrigerant outlet tube (refrigerant outlet)
17: Disturbing plate (side plate)
18: Blow-up prevention plate (upper plate)
18a: Flat plate portion 18b: Inclined portion 20: Evaporator 21: Lower plate portion 26: Lower plate portion 27: Refrigerant discharge pipe 31: Lower plate portion 36: Lower plate portion 36a: Bottom plate portion 36b: Inclined portion 37: Refrigerant discharge pipe 41: Lower plate part 50: Evaporator 51: Lower end side plate part (pressure loss increasing part)
56: Dummy tube 60: Evaporator 61: Lower plate part (rectifying part)
66: Dummy pipe 70: Evaporator 71: Cross plate part 76: Cross plate part

Claims (12)

1. A housing that is provided with a refrigerant outlet that discharges the evaporated refrigerant to the outside and forms an outer shell,
   A group of liquid film type heat transfer tubes housed in the housing and having a plurality of liquid film heat transfer tubes in which a medium to be cooled flows.
   A refrigerant supply unit housed in the housing and supplying a liquid phase refrigerant from above to the liquid film type heat transfer tube group.
   A side plate portion that covers the liquid film type heat transfer tube group from the side, and
   An upper plate portion that covers the liquid film type heat transfer tube group from above is provided.
   An evaporator in which a gap is formed between the side plate portion and the upper plate portion.
2. A group of full-liquid heat transfer tubes housed in the housing, immersed in a liquid-phase refrigerant stored in the lower part of the housing, and having a plurality of full-fill heat transfer tubes in which a cooling medium flows. Prepare,
   The evaporator according to claim 1, wherein the liquid film type heat transfer tube group is provided above the liquid level of the liquid phase refrigerant stored in the lower part of the housing.
3. The evaporator according to claim 1 or 2, wherein the refrigerant outlet is provided above the lower end of the side plate portion.
4. The refrigerant supply unit is provided above the liquid film type heat transfer tube group, and is provided.
   The evaporator according to any one of claims 1 to 3, wherein the side plate portion covers the upper part of the liquid film type heat transfer tube group from the side.
5. A housing that has a refrigerant outlet that discharges evaporated refrigerant to the outside and forms an outer shell,
   A group of full-liquid heat transfer tubes housed in the housing, immersed in a liquid-phase refrigerant stored in the lower part of the housing, and having a plurality of full-fill heat transfer tubes in which a cooling medium flows. ,
   A liquid film type having a plurality of heat transfer tubes for a liquid film, which are housed in the housing and are provided above the liquid level of the liquid phase refrigerant stored in the lower part of the housing, and have a plurality of heat transfer tubes for the liquid film in which the cooling medium flows. Heat transfer tube group and
   A refrigerant supply unit housed in the housing and supplying a liquid phase refrigerant from above to the liquid film type heat transfer tube group.
   An evaporator including a lower plate portion provided between the liquid film type heat transfer tube group and the liquid level.
6. The lower end is connected to the lower plate portion, and the lower end is provided with a refrigerant discharge pipe arranged below the full-liquid heat transfer tube group.
   The evaporator according to claim 5, wherein the lower plate portion is provided below the liquid film type heat transfer tube group.
7. The evaporator according to claim 5 or 6, wherein the lower plate portion has a hole penetrating from the upper surface to the lower surface.
8. A housing that is provided with a refrigerant outlet that discharges the evaporated refrigerant to the outside and forms an outer shell,
   A group of full-liquid heat transfer tubes housed in the housing, immersed in a liquid-phase refrigerant stored in the lower part of the housing, and having a plurality of full-fill heat transfer tubes in which a cooling medium flows. ,
   A liquid film type having a plurality of heat transfer tubes for a liquid film, which are housed in the housing and are provided above the liquid level of the liquid phase refrigerant stored in the lower part of the housing, and have a plurality of heat transfer tubes for the liquid film in which the cooling medium flows. Heat transfer tube group and
   A refrigerant supply unit housed in the housing and supplying a liquid phase refrigerant from above to the liquid film type heat transfer tube group.
   An evaporator comprising a pressure loss increasing portion which is arranged on the side of the lower end portion of the liquid film type heat transfer tube group and increases the pressure loss in the region where the lower end portion of the liquid film type heat transfer tube group is arranged.
9. The evaporation according to claim 8, wherein the pressure loss increasing portion is arranged so as to sandwich the lower end portion of the liquid film type heat transfer tube group, and has a pair of lower end side plate portions that cover the liquid film type heat transfer tube group from the side. vessel.
10. A housing that is provided with a refrigerant outlet that discharges the evaporated refrigerant to the outside and forms an outer shell,
    A group of full-liquid heat transfer tubes housed in the housing, immersed in a liquid-phase refrigerant stored in the lower part of the housing, and having a plurality of full-fill heat transfer tubes in which a cooling medium flows. ,
    A liquid film type having a plurality of heat transfer tubes for a liquid film, which are housed in the housing and are provided above the liquid level of the liquid phase refrigerant stored in the lower part of the housing, and have a plurality of heat transfer tubes for the liquid film in which the cooling medium flows. Heat transfer tube group and
    A refrigerant supply unit housed in the housing and supplying a liquid phase refrigerant from above to the liquid film type heat transfer tube group.
    An evaporator provided with a rectifying unit that is arranged across the lower portion of the liquid film type heat transfer tube group and guides the refrigerant evaporated in the full liquid type heat transfer tube group to the refrigerant outlet.
11. The evaporator according to claim 10, wherein the rectifying unit has a pair of lower side plate portions that cover the liquid film type heat transfer tube group from both sides.
12. The housing extends in a predetermined direction and
    The evaporator according to any one of claims 1 to 11, wherein a plurality of crossing plate portions arranged so as to intersect the predetermined direction are provided on the side of the liquid film type heat transfer tube group.

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