JP7386436B2 - Shell and tube absorber and refrigerator - Google Patents

Description

The present disclosure relates to shell-and-tube absorbers and refrigerators.

Conventionally, absorption refrigerators equipped with an absorber have been known.

Patent Document 1 describes, as shown in FIG. 9, an absorption system including a heat exchanger tube 301, a steam flow path 302, an inflow section 303, an absorption liquid distribution device 304, an air bleed port 307, and an absorption liquid discharge port 308. A container 300 is described. Absorption liquid 305 is sprayed from absorption liquid spraying device 304 toward heat transfer tube 301 . According to the absorber 300, the steam flow path 302 between the tube group region where the heat transfer tubes 301 are densely arranged and the wall surface can reduce the flow resistance of steam, and the non-condensable gas can be extracted from the bleed port 307 with high efficiency. can be discharged.

Japanese Patent Application Publication No. 6-307735

The technique described in Patent Document 1 has room for reexamination from the viewpoint of achieving both a high-density arrangement of heat exchanger tubes and appropriate wetting of the heat exchanger tubes with an absorbing liquid.

Therefore, the present disclosure provides an advantageous absorber from the viewpoint of achieving both a high-density arrangement of heat exchanger tubes and appropriate wetting of the heat exchanger tubes with an absorbing liquid.

This disclosure:
A shell that stores the absorbent liquid;
A heat exchanger tube group having a plurality of heat exchanger tubes in which a heat medium flows, which are arranged in multiple stages in the direction of gravity and in multiple rows in a direction perpendicular to the direction of gravity and arranged parallel to each other inside the shell;
a first supply path that supplies the absorption liquid to the shell;
a second supply path for supplying refrigerant vapor to the shell;
a dropper that drops the absorption liquid supplied by the first supply path toward the heat exchanger tube group,
The heat exchanger tube group includes a left row and a right row that are adjacent to each other, and when the left row and the right row are viewed along the longitudinal direction of the heat exchanger tubes, the center axis of the heat exchanger tubes is included in the right row. A horizontal plane is located between a pair of horizontal planes including the central axes of two heat exchanger tubes adjacent in the direction of gravity in the left row, or a horizontal plane including the central axes of the heat exchanger tubes in the left row A plane is located between a pair of horizontal planes including central axes of the two heat exchanger tubes adjacent in the direction of gravity in the right row,
The distance between the central axis of the heat exchanger tube in any upper stage of the left row and the central axis of the lower heat exchanger tube one stage below the upper stage in the left row is such that the distance is adjacent to the upper heat exchanger tube in the left row. equal to the distance between the central axis of the heat exchanger tube in the right row and the central axis of the heat exchanger tube in the right row adjacent to the lower heat exchanger tube in the left row;
Provides shell and tube type absorbers.

The shell-and-tube type absorber of the present disclosure is advantageous from the viewpoint of achieving both a high-density arrangement of heat exchanger tubes and appropriate wetting of the heat exchanger tubes with an absorbing liquid.

FIG. 1 is a cross-sectional view of a shell-and-tube absorber according to an example of an embodiment of the present disclosure. FIG. 2 is a sectional view showing the dropper of the shell-and-tube absorber shown in FIG. 1. FIG. 3 is a sectional view of a shell-and-tube absorber according to a reference example. FIG. 4 is a configuration diagram showing an example of the refrigerator of this embodiment. FIG. 5 is a cross-sectional view of a shell-and-tube absorber according to another example of the embodiment of the present disclosure. FIG. 6 is a cross-sectional view of a shell-and-tube absorber according to yet another example of the embodiment of the present disclosure. FIG. 7 is a cross-sectional view of the dropper of the shell-and-tube absorber shown in FIG. 6. FIG. 8 is a cross-sectional view of a shell-and-tube absorber according to yet another example of the embodiment of the present disclosure. FIG. 9 is a sectional view showing a conventional absorber.

(Findings that formed the basis of this disclosure)
In shell-and-tube absorbers, the absorbed heat typically generated by absorption of refrigerant vapor into an absorbing liquid is radiated to a heat transfer medium flowing through heat transfer tubes. From the viewpoint of dripping the absorption liquid while maintaining it in a desired state, it is advantageous to appropriately wet the heat transfer tubes, which are arranged in multiple stages in the direction of gravity, with the absorption liquid. Inside the shell of a shell-and-tube type absorber, multiple heat transfer tubes are arranged parallel to each other in multiple stages in the direction of gravity and in multiple rows in a direction perpendicular to the direction of gravity to form a group of heat transfer tubes. It is possible to do so. In this case, in two adjacent rows of heat transfer tubes, the other heat transfer tube of the two rows of heat transfer tubes is arranged between two heat transfer tubes that are adjacent to each other in the gravity direction of one of the rows of two heat transfer tubes. is possible. In this specification, such an arrangement of heat exchanger tubes is referred to as a staggered arrangement. According to the staggered arrangement, the distance between heat exchanger tubes and the height of a group of heat exchanger tubes in this arrangement of heat exchanger tubes are equal to the distance between heat exchanger tubes and the height of a group of heat exchanger tubes in a lattice arrangement of multiple heat exchanger tubes. can be kept. In addition, the width of the heat exchanger tube group in the direction perpendicular to the direction of gravity is reduced, making it easier to realize a high-density arrangement of the heat exchanger tubes.

On the other hand, the present inventors have newly discovered that in a shell-and-tube type absorber, when a plurality of heat exchanger tubes are arranged in a staggered manner, it may become difficult to appropriately wet the heat exchanger tubes with an absorbing liquid. For example, the distance between two adjacent heat exchanger tubes in the gravity direction of one row of two adjacent heat exchanger tubes is the same as the distance between each of the two heat exchanger tubes in the other row of two adjacent heat exchanger tubes. The distance between them may become narrower. When the distance between two heat exchanger tubes adjacent to each other in the gravity direction is small, the flow rate of refrigerant vapor passing between the heat exchanger tubes increases. As a result, the absorption liquid falling through the space where the distance between the heat transfer tubes in the adjacent row is wide is dragged by the flow of the refrigerant vapor at a high flow rate. As a result, it becomes difficult for the absorption liquid to come into contact with the heat exchanger tubes in the lower stage, and it becomes difficult to properly wet the heat exchanger tubes with the absorption liquid.

Therefore, the present inventors have conducted extensive studies on the arrangement of heat exchanger tubes that can appropriately wet the heat exchanger tubes with absorbent liquid even when a plurality of heat exchanger tubes are arranged in a staggered manner. I devised a container.

(Summary of one aspect of the present disclosure)
The shell and tube absorber according to the first aspect of the present disclosure includes:
a shell that stores the absorbent liquid;
A heat exchanger tube group having a plurality of heat exchanger tubes in which a heat medium flows, which are arranged in multiple stages in the direction of gravity and in multiple rows in a direction perpendicular to the direction of gravity and arranged parallel to each other inside the shell;
a first supply path that supplies the absorption liquid to the shell;
a second supply path for supplying refrigerant vapor to the shell;
a dropper that drops the absorption liquid supplied by the first supply path toward the heat exchanger tube group,
The heat exchanger tube group includes an adjacent left row and a right row, and includes a central axis of the heat exchanger tubes in the right row when looking at the left row and the right row along the longitudinal direction of the heat exchanger tubes. A horizontal plane is located between a pair of horizontal planes including the central axes of two heat exchanger tubes adjacent in the direction of gravity in the left row, or a horizontal plane including the central axes of the heat exchanger tubes in the left row A plane is located between a pair of horizontal planes including central axes of the two heat exchanger tubes adjacent in the direction of gravity in the right row,
The distance between the central axis of the heat exchanger tube in any upper stage of the left row and the central axis of the lower heat exchanger tube one stage below the upper stage in the left row is such that the distance is adjacent to the upper heat exchanger tube in the left row. The distance between the center axis of the heat transfer tube in the right row and the center axis of the heat transfer tube in the right row adjacent to the lower heat transfer tube in the left row is equal to the distance between the center axis of the heat transfer tube in the right row.

According to the first aspect, by arranging the heat exchanger tubes as described above in the adjacent left and right rows, the heat exchanger tubes can be arranged in a high density in the heat exchanger tube group. In addition, the distance between the center axis of the upper heat transfer tube in the left row and the center axis of the lower heat transfer tube in the left row is the same as the distance between the center axes of the heat transfer tubes in the right row adjacent to these heat transfer tubes. Since they are equal, the flow rate of refrigerant vapor tends to be kept low. Furthermore, the distance that the absorbing liquid falls tends to be shortened, and the absorbing liquid is less likely to be dragged by the flow of refrigerant vapor. As a result, the heat exchanger tubes can be appropriately wetted with the absorbing liquid.

In a second aspect of the present disclosure, for example, in the shell-and-tube absorber according to the first aspect, the distance between the central axes of the two adjacent heat exchanger tubes in the left row is the first length and the first length. It may also include a second length that is longer than the length. According to the second aspect, even if the distance between the center axes of two adjacent heat transfer tubes in the left row differs for some reason, the flow rate of the refrigerant vapor is likely to be kept low in the portion where the distance is longer. Therefore, the absorption liquid is less likely to be dragged by the flow of refrigerant vapor. The heat exchanger tubes can be appropriately wetted by the absorbing liquid.

In a third aspect of the present disclosure, for example, in the shell-and-tube absorber according to the first aspect or the second aspect, the heat exchanger tube group includes a first heat exchanger tube group in which the heat medium flows in a specific direction, and a gravitational direction. may include a second heat exchanger tube group that is arranged above the first heat exchanger tube group and in which the heat medium flows in a direction opposite to the specific direction. It may be difficult to match the distance between the first heat exchanger tube group and the second heat exchanger tube group to the distance between the heat exchanger tubes in the first heat exchanger tube group and the distance between the heat exchanger tubes in the second heat exchanger tube group. According to the third aspect, even in this case, the flow rate of the refrigerant vapor is likely to be kept low in the space between the first heat exchanger tube group and the second heat exchanger tube group. Therefore, the absorption liquid is less likely to be dragged by the flow of refrigerant vapor. The heat exchanger tubes can be appropriately wetted by the absorbing liquid.

In the fourth aspect of the present disclosure, for example, in the shell-and-tube absorber according to the third aspect, the heat medium may be guided to the second heat exchanger tube group after passing through the first heat exchanger tube group. Alternatively, the heat exchanger may be guided to the first heat exchanger tube group after passing through the second heat exchanger tube group. According to the fourth aspect, the flow path of the heat medium inside the shell becomes long, and the absorbed heat generated by absorption of refrigerant vapor into the absorption liquid can be effectively radiated to the heat medium.

In a fifth aspect of the present disclosure, for example, the shell-and-tube absorber according to the third aspect or the fourth aspect includes the uppermost heat exchanger tube in each row of the first heat exchanger tube group, and the second heat exchanger tube. It may further include a partition component that prevents the refrigerant vapor from flowing between the heat exchanger tubes at the lowest stage in each row of the group, and in a direction perpendicular to the longitudinal direction of the heat exchanger tubes and the direction of gravity. When the partition component is viewed along the gravitational direction, at least a portion of the partition component is located at an end close to the uppermost partition component in the longitudinal direction of the heat exchanger tube and in a direction perpendicular to the gravitational direction. The heat exchanger tube may be located between the heat exchanger tube located at the lowermost end on the same side as the end. According to the fifth aspect, refrigerant vapor is prevented from flowing between the uppermost heat transfer tube in each row of the first heat transfer tube group and the lowermost heat transfer tube in each row of the second heat transfer tube group. , the flow rate and flow velocity of the refrigerant vapor in this section is reduced. For this reason, the absorption liquid falling from the lowest stage in each row of the second heat exchanger tube group toward the uppermost heat exchanger tube in each row of the first heat exchanger tube group is less likely to be dragged by the flow of refrigerant vapor. As a result, the heat exchanger tubes can be appropriately wetted with the absorbing liquid.

In a sixth aspect of the present disclosure, for example, in the shell-and-tube absorber according to any one of the first to fifth aspects, the central axis of the uppermost heat transfer tube in the left row and the left row The distance between the central axis of the heat exchanger tube at the lowest stage of the heat exchanger tube may be equal to the distance between the central axis of the heat exchanger tube at the uppermost stage of the right row and the central axis of the heat exchanger tube at the lowermost stage of the right row. . According to the sixth aspect, it is easy to match the number of heat exchanger tubes in the left row with the number of heat exchanger tubes in the right row.

In a seventh aspect of the present disclosure, for example, in the shell-and-tube absorber according to any one of the first to sixth aspects, the dripper supplies the absorption liquid to the heat transfer tubes in the left row. It may have a first dripping port for dripping, and a second dripping port for dripping the absorption liquid onto the heat transfer tubes in the right row, and the dripping device may be viewed along the longitudinal direction of the heat transfer tubes. In this case, the second dripping port may be located at a position away from a horizontal plane including the first dripping port in the direction of gravity. According to the seventh aspect, it is easy to match the distance between the heat exchanger tube located at the top of the right row and the second dripping port with the distance between the heat exchanger tube located at the top of the left row and the first dripping port. This makes it easy to maintain a low flow rate of the refrigerant vapor passing between the top heat transfer tube in the left row, the top heat transfer tube in the right row, and the dropper. In addition, the distance between the heat transfer tube located at the top of the right row and the second dripping port and the distance between the heat transfer tube located at the top of the left row and the first dripping port are easily adjusted, and the absorption liquid is less likely to be dragged by the flow of refrigerant vapor. As a result, the heat exchanger tubes can be appropriately wetted with the absorbing liquid.

The shell and tube absorber according to the eighth aspect of the present disclosure includes:
A shell that stores the absorbent liquid;
The shell has a plurality of heat exchanger tubes arranged in multiple stages in the direction of gravity and in multiple rows in a direction perpendicular to the direction of gravity and arranged parallel to each other, through which a heat medium flows, and a first heat exchanger tube. a group of heat exchanger tubes, and a second group of heat exchanger tubes arranged above the first group of heat exchanger tubes in the direction of gravity;
a first supply path that supplies the absorption liquid to the shell;
a second supply path for supplying refrigerant vapor to the shell;
a dropper that drops the absorption liquid supplied by the first supply path toward the heat exchanger tube group;
a partition that prevents the refrigerant vapor from flowing between the uppermost heat transfer tube in each row of the first heat transfer tube group and the lowermost heat transfer tube in each row of the second heat transfer tube group; comprising parts and
The heat exchanger tube group includes an adjacent left row and a right row, and includes a central axis of the heat exchanger tubes in the right row when looking at the left row and the right row along the longitudinal direction of the heat exchanger tubes. A horizontal plane is located between a pair of horizontal planes including the central axes of two heat exchanger tubes adjacent in the direction of gravity in the left row, or a horizontal plane including the central axes of the heat exchanger tubes in the left row A plane is located between a pair of horizontal planes including central axes of the two heat exchanger tubes adjacent in the direction of gravity in the right row,
When the partition component is viewed along a direction perpendicular to the longitudinal direction of the heat exchanger tubes and the direction of gravity, at least a portion of the partition component is closest to the partition component in the first heat exchanger tube group in the direction of gravity. located between the lower heat exchanger tube, which is the heat exchanger tube at the uppermost stage, and the upper heat exchanger tube, which is the heat exchanger tube at the lowermost stage, which is closest to the partition component in the second heat exchanger tube group;
The distance between the center axis of the lower heat exchanger tube and the center axis of the upper heat exchanger tube is the same as the distance between the center axis of the lower heat exchanger tube and the uppermost heat exchanger tube in the row adjacent to the row of the first heat exchanger tube group including the lower heat exchanger tube, The distance is longer than the distance between the row of the second heat exchanger tube group including the upper heat exchanger tube and the lowermost heat exchanger tube in the adjacent row.

According to the eighth aspect, the amount of refrigerant vapor flowing between the upper heat exchanger tube and the lower heat exchanger tube and the flow rate of the refrigerant vapor are easily maintained within a desired range, and the direction in which the refrigerant vapor flows and the absorption liquid drips. The angle formed with the direction in which the Thereby, the absorption liquid dripped from the upper heat exchanger tube is less likely to be dragged in a direction perpendicular to the longitudinal direction of the heat exchanger tube and the direction of gravity. Therefore, the amount of refrigerant vapor flowing into the first heat exchanger tube group and the second heat exchanger tube group is maintained within a desired range, and the absorption liquid dripped from the lowest heat exchanger tube of the second heat exchanger tube group is transferred to the first heat exchanger tube group. It tends to adhere to the heat transfer tubes at the top of the group. As a result, even in operations such as absorption liquid dilution operation, in which the absorption amount of refrigerant vapor in the absorption liquid temporarily increases, the absorber is able to wet the heat transfer tubes of the first heat transfer tube group with the absorption liquid. Easily improves heat transfer rate.

In a ninth aspect of the present disclosure, for example, in the shell-and-tube type absorber according to the eighth aspect, the heat medium flows in a specific direction in the first heat exchanger tube group, and the heat medium flows in a specific direction in the second heat exchanger tube group. It may flow in the opposite direction to the specific direction. According to the ninth aspect, the absorbed heat generated by absorption of refrigerant vapor into the absorption liquid can be effectively radiated to the heat medium.

In a tenth aspect of the present disclosure, for example, in the shell-and-tube absorber according to the eighth aspect or the ninth aspect, the partition component may be located below the upper heat exchanger tube in the direction of gravity; In the direction, the distance between the central axis of the upper heat exchanger tube and the upper end of the partition component may be longer than the distance between the central axis of the lower heat exchanger tube and the lower end of the partition component. According to the tenth aspect, the angle between the direction in which the refrigerant vapor flows in and the direction in which the absorption liquid drips tends to be smaller more reliably, and the absorption liquid dripped from the upper heat exchanger tube flows in the longitudinal direction of the heat exchanger tube and in the gravitational direction. It is difficult to be dragged in a direction perpendicular to .

A refrigerator according to an eighth aspect of the present disclosure includes a shell-and-tube absorber according to any one of the first to seventh aspects. According to the eighth aspect, it is possible to provide a compact refrigerator that can exhibit a high coefficient of performance (COP).

Embodiments of the present disclosure will be described below with reference to the drawings. This disclosure is not limited to the following embodiments.

FIG. 1 is a cross-sectional view of a shell-and-tube absorber 1a according to an example of an embodiment of the present disclosure. In this specification, a "shell and tube absorber" may be simply referred to as an "absorber." Note that in the attached drawings, the Z-axis negative direction is the direction of gravity, and the XY plane is horizontal. The X-axis and Y-axis are orthogonal to each other.

As shown in FIG. 1, the absorber 1a includes a shell 2, a heat exchanger tube group 3g, a first supply path 4, a second supply path 7, and a dripper 8. Shell 2 stores absorbent liquid. The heat exchanger tube group 3g has a plurality of heat exchanger tubes 3 through which a heat medium flows. In the heat exchanger tube group 3g, the plurality of heat exchanger tubes 3 form multiple stages in the direction of gravity inside the shell 2, form multiple rows in a direction perpendicular to the direction of gravity, and are arranged parallel to each other. The first supply path 4 is a path for supplying the absorption liquid to the shell 2. The second supply path 7 is a path for supplying refrigerant vapor to the shell 2 . The dropper 8 drops the absorption liquid supplied by the first supply path 4 toward the heat transfer tube group 3g. FIG. 2 is a sectional view showing the dropper 8.

In the absorber 1a, typically, absorbed heat generated by absorption of refrigerant vapor into the absorption liquid is radiated to the heat medium flowing through the heat transfer tubes 3. By appropriately wetting the heat transfer tubes 3 arranged in multiple stages in the direction of gravity with the absorbing liquid, the absorbing liquid can be dripped while being maintained in a desired state, for example, a supercooled state.

The heat exchanger tube group 3g includes a left row 3h and a right row 3m that are adjacent to each other. When looking at the left row 3h and the right row 3m along the longitudinal direction (Y-axis direction) of the heat exchanger tubes 3, the central axis of the heat exchanger tubes 3 indicates arrangement I or arrangement II. In arrangement I, a horizontal plane containing the central axes of the heat exchanger tubes 3 in the right row 3m is located between a pair of horizontal planes containing the central axes of two heat exchanger tubes 3 adjacent in the direction of gravity in the left row 3h. In arrangement II, when looking at the left row 3h and the right row 3m along the longitudinal direction of the heat exchanger tubes 3, the horizontal plane containing the central axis of the heat exchanger tubes 3 in the left row 3h is adjacent to the right row 3m in the gravity direction. It is located between a pair of horizontal planes that include the central axes of the two matching heat exchanger tubes 3. Thereby, the heat exchanger tubes 3 can be arranged with high density in the heat exchanger tube group 3g. Note that in the left row 3h and the right row 3m, there may be a region where the central axis of the heat exchanger tubes 3 does not indicate the arrangement I or arrangement II. For example, in the region including the bottom row of the right row 3m, the central axis of the heat exchanger tubes 3 does not indicate the arrangement I.

For example, in two adjacent rows of the heat exchanger tube group 3g, the row proximal to the second supply path 7 corresponds to the left row 3h, and the row distal to the second supply path 7 corresponds to the right row 3m. Applies to.

The distance L1 between the center axis of any upper heat exchanger tube 3 in the left row 3h and the center axis of the lower heat exchanger tube 3 one step below the upper row in the left row 3h is equal to the distance L2. The distance L2 is the center axis of the heat exchanger tube 3 in the right row 3m adjacent to the upper heat exchanger tube 3 in the left row 3h and the heat exchanger tube 3 in the right row 3m adjacent to the lower heat exchanger tube 3 in the left row 3h. is the distance from the central axis of Note that the distance L1 being equal to the distance L2 means that these are substantially equal. Even if the distance L1 and the distance L2 do not completely match due to manufacturing reasons of the absorber 1a, for example, if the distance L1 is in the range of 90 to 110% of the distance L2, the distance L1 is equal to the distance L2. It can be considered as

FIG. 3 is a cross-sectional view of a shell-and-tube absorber 1r according to a reference example. The absorber 1r is configured in the same manner as the absorber 1a except for the parts to be specifically explained. Components of the absorber 1r that are the same as or correspond to the components of the absorber 1a are given the same reference numerals, and detailed explanations are omitted.

The plurality of heat exchanger tubes 3 in the heat exchanger tube group 3g of the absorber 1r are arranged in a staggered manner. In the adjacent left row 3h and right row 3m of the heat exchanger tube group 3g of the absorber 1r, the distance L1 is smaller than the distance L2 in a specific region. Thereby, the flow velocity of the refrigerant vapor passing between the heat exchanger tubes 3 in the left row 3h in the specific region increases. Therefore, in the right row 3m, the absorption liquid falling through the space where the distance between the heat transfer tubes 3 is wide is dragged by the flow of the refrigerant vapor at a high flow rate. As a result, it becomes difficult for the absorption liquid to come into contact with the heat exchanger tubes 3 in the lower stage, and it becomes difficult to properly wet the heat exchanger tubes 3 with the absorption liquid.

On the other hand, according to the absorber 1a, since the distance L1 is equal to the distance L2, the flow rate of the refrigerant vapor passing through the heat exchanger tubes 3 in the left row 3h is likely to be kept low. Further, in the right row of 3 m, the distance that the absorbing liquid falls tends to be short, and the absorbing liquid is less likely to be dragged by the flow of refrigerant vapor. Therefore, the heat exchanger tubes 3 can be appropriately wetted with the absorption liquid. As a result, the heat transfer rate in the absorber 1a tends to be high, and the absorber 1a is advantageous from the viewpoint of downsizing or providing a refrigerator that can exhibit a high COP. For example, it is also possible to adjust the heat transfer rate of the absorber 1a to about 1.3 times the heat transfer rate of a conventional absorber having a group of heat exchanger tubes arranged in a lattice arrangement.

As shown in FIG. 1, in the absorber 1a, the distance between the center axes of two adjacent heat exchanger tubes 3 in the left row 3h is a first length L3, a second length L1 longer than the first length L3, and a second length L1 longer than the first length L3. including. In the absorber 1a, the distance between the central axes of two adjacent heat exchanger tubes 3 in the left row 3h may differ due to reasons such as the arrangement of members connected to the heat exchanger tubes 3, for example. According to the absorber 1a, the flow rate of the refrigerant vapor is likely to be kept low in the region where the distance between the central axes of the heat exchanger tubes 3 indicates the second length L1. Therefore, the absorption liquid is less likely to be dragged by the flow of refrigerant vapor, and the heat exchanger tubes 3 can be appropriately wetted by the absorption liquid.

As shown in FIG. 1, the plurality of heat exchanger tubes 3 are arranged in a staggered manner in the entire heat exchanger tube group 3g of the absorber 1a. On the other hand, a plurality of heat exchanger tubes 3 may be arranged in a grid in a part of the heat exchanger tube group 3g of the absorber 1a.

In the heat exchanger tube group 3g, the left row 3h is, for example, closest to the second supply path 7 in the heat exchanger tube group 3g.

In the heat exchanger tube group 3g, the number of heat exchanger tubes 3 in the left row 3h and the number of heat exchanger tubes 3 in the right row 3m are, for example, odd numbers.

The heat exchanger tube group 3g of the absorber 1a includes, for example, a first heat exchanger tube group 3a and a second heat exchanger tube group 3b. In the first heat exchanger tube group 3a, the heat medium flows in a specific direction. The specific direction is, for example, the positive Y-axis direction. The second heat exchanger tube group 3b is arranged above the first heat exchanger tube group 3a in the direction of gravity. In the second heat exchanger tube group 3b, the heat medium flows in a direction opposite to the specific direction. The opposite direction is, for example, the Y-axis negative direction. In this case, the distance between the first heat exchanger tube group 3a and the second heat exchanger tube group 3b is defined as the distance between the heat exchanger tubes 3 in the first heat exchanger tube group 3a and the distance between the heat exchanger tubes 3 in the second heat exchanger tube group 3b. It may be difficult to match. However, in the left row 3h and the right row 3m, a plurality of heat exchanger tubes 3 are arranged as described above, so in the space between the first heat exchanger tube group 3a and the second heat exchanger tube group 3b, refrigerant vapor is Flow velocity tends to be kept low. Therefore, the absorption liquid is less likely to be dragged by the flow of refrigerant vapor, and the heat exchanger tubes 3 can be appropriately wetted by the absorption liquid. In the second heat exchanger tube group 3b, the heat medium may flow in a specific direction.

In the absorber 1a, for example, the heat medium is guided to the second heat exchanger tube group 3b after passing through the first heat exchanger tube group 3a, or is guided to the first heat exchanger tube group 3a after passing through the second heat exchanger tube group 3b. be guided. In this case, the flow path of the heat medium inside the shell 2 becomes long, and the absorbed heat generated by absorption of refrigerant vapor into the absorption liquid can be effectively radiated to the heat medium.

In the absorber 1a, when the heat medium is guided to the first heat exchanger tube group 3a after passing through the second heat exchanger tube group 3b, the temperature efficiency regarding heat dissipation of absorbed heat generated by absorption of refrigerant vapor into the absorption liquid is high. Prone. This is because in this case, the heat transfer between the heat medium and the absorbing liquid is similar to heat transfer by countercurrent flow.

In the absorber 1a, for example, the distance between the central axis of the uppermost heat exchanger tube 3 in the left row 3h and the central axis of the lowermost heat exchanger tube 3 in the left row 3h is the same as that of the uppermost heat exchanger tube 3 in the right row 3m. It is equal to the distance between the central axis and the central axis of the lowest heat exchanger tube 3 in the right row 3 m. In this case, it is easy to match the number of heat exchanger tubes 3 in the left row 3h with the number of heat exchanger tubes 3 in the right row 3m.

As shown in FIG. 1, the absorber 1a further includes, for example, a discharge path 5, a pump 6, and an eliminator 9. The absorption liquid is not limited to a specific liquid as long as it can absorb refrigerant vapor. The main component of the absorption liquid is, for example, an aqueous lithium bromide solution. As used herein, the term "main component" refers to the component that is contained the most on a mass basis. In this case, a trace amount of octyl alcohol may be added to the absorption liquid.

The shell 2 has, for example, heat insulation and pressure resistance. The shell 2 typically stores the absorption liquid and isolates the absorption liquid and refrigerant vapor inside the shell 2 from outside air (eg, air at atmospheric pressure).

A groove may be formed in at least one of the inner surface of the heat exchanger tube 3 and the outer surface of the heat exchanger tube 3. The heat medium flowing through the heat exchanger tubes 3 is not limited to a specific fluid. The heat medium flowing through the heat exchanger tubes 3 is, for example, water.

The first supply path 4 is constituted by, for example, a pipe having heat insulation properties and pressure resistance. The first supply path 4 supplies, for example, an absorption liquid concentrated outside the absorber 1a such as a regenerator to the inside of the shell 2. The concentration of lithium bromide in the absorption liquid in the first supply path 4 is about 63% by weight, and the temperature of the absorption liquid in the first supply path 4 is, for example, about 50°C. A throttle valve may be arranged in the first supply path 4. In this case, flash evaporation of the absorption liquid in the first supply path 4 can be easily prevented.

The discharge path 5 is a path for discharging the diluted absorption liquid by absorbing refrigerant vapor inside the shell 2 and guiding it to the outside of the absorber 1a such as a regenerator. The discharge path 5 is constituted by, for example, a pipe having heat insulation properties and pressure resistance. The concentration of lithium bromide in the absorption liquid in the discharge passage 5 is about 57% by weight, and the temperature of the absorption liquid in the discharge passage 5 is, for example, about 36°C.

The pump 6 is arranged in the discharge path 5, for example. By operating the pump 6, absorption liquid is sent from the inside of the shell 2 to the outside of the absorber 1a such as a regenerator. The pump 6 is, for example, a speed type pump. In this case, momentum is given to the absorption liquid by the pump 6, and then the flow rate of the absorption liquid decreases, thereby increasing the pressure of the absorption liquid. Examples of speed type pumps include centrifugal pumps, mixed flow pumps, and axial flow pumps. The pump 6 may include a mechanism for changing the rotation speed. The mechanism is, for example, a motor driven by an inverter.

The second supply path 7 is constituted by, for example, a pipe having heat insulation properties and pressure resistance. For example, refrigerant vapor supplied from the evaporator is guided to the second supply path 7, and the refrigerant vapor is supplied to the shell 2.

As shown in FIG. 2, the dripper 8 has a first dripping port 14a and a second dripping port 14b. The first dripping port 14a drips the absorption liquid toward the heat exchanger tubes 3 in the left row 3h, for example. The second dripping port 14b drops the absorption liquid toward the heat exchanger tubes 3 in the right row 3m, for example.

The dripper 8 includes, for example, an upper tray 12, a side plate 13, and a dripping part 14. The upper tray 12 is made of, for example, a thin plate made of stainless steel. A through hole is formed in the bottom surface of the upper tray 12. The side plate 13 is made of a thin plate made of stainless steel, for example. The dripping part 14 is joined to a part of the outer surface of the bottom of the upper tray 12, for example. Further, a pair of side plates 13 are joined to the outer surface of the side portion of the dripping portion 14 . The dripping portion 14 is formed with a first dripping port 14a and a second dripping port 14b.

The absorption liquid supplied to the shell 2 through the first supply path 4 is guided to the upper tray 12. The absorbent liquid passes through the through hole in the bottom of the upper tray 12 and is discharged to the outside of the upper tray 12 . The side plate 13 serves as a dam for storing the absorption liquid discharged from the upper tray 12. The absorption liquid stored by the side plate 13 is dripped mainly by the action of gravity from the first dripping port 14a and the second dripping port 14b.

The eliminator 9 is made of, for example, a thin plate made of stainless steel. The eliminator 9 forms, for example, a channel curved like a mountain in the second supply channel 7 . If the refrigerant vapor supplied to the absorber 1a contains droplets, the centrifugal force that accompanies the change in the flow direction of the refrigerant vapor along the mountain-curved flow path causes the droplets to be separated from the flow of the refrigerant vapor. separated.

An example of the operation of the absorber 1a will be explained. When the absorber 1a is left alone for a predetermined period such as at night, the inside of the absorber 1a is maintained at approximately the same temperature and pressure as the environment in which the absorber 1a is placed. For example, when the temperature of the environment in which the absorber 1a is placed is 25°C, the temperature inside the absorber 1a is maintained at about 25°C. For example, a heat medium that has released heat to the atmosphere flows inside the plurality of heat exchanger tubes 3 of the heat exchanger tube group 3g. The temperature when the heat medium flows into the heat transfer tube 3 is, for example, 32°C.

First, pump 6 is started. As a result, the absorbent liquid stored inside the shell 2 is extracted from the shell 2 and sent through the discharge path 5 to the outside of the absorber 1a, such as a regenerator. For example, the absorption liquid sent to the regenerator is concentrated and supplied to the interior of the shell 2 through the first supply path 4 . For example, the concentration of lithium bromide in the absorption liquid supplied to shell 2 is about 63% by mass, and the temperature of the absorption liquid supplied to shell 2 is about 50°C. Further, refrigerant vapor generated outside the absorber 1a such as an evaporator passes through the second supply path 7, and droplets are separated from the flow of refrigerant vapor in the eliminator 9. Thereafter, refrigerant vapor is supplied to the shell 2. The temperature of the supplied refrigerant vapor is, for example, 6°C.

The absorption liquid supplied through the first supply path 4 is stored in the dropper 8 and dripped toward the heat exchanger tube group 3g. The absorption liquid dropped onto the heat exchanger tube group 3g spreads on the outer surface of the heat exchanger tubes 3 of the heat exchanger tube group 3g and absorbs refrigerant vapor. The absorption liquid that has absorbed the refrigerant vapor is diluted, and at the same time as the dilution, the temperature of the refrigerant vapor increases due to the heat of absorption. However, the absorption liquid becomes a supercooled state by being cooled by the heat medium flowing inside the heat transfer tube 3g, and absorbs the refrigerant vapor again. In this way, the absorption liquid is diluted in the process of repeatedly absorbing refrigerant vapor, increasing the temperature, and cooling while flowing down in the direction of gravity while contacting the outer surface of the heat exchanger tubes 3 of the heat exchanger tube group 3g. The diluted absorption liquid is stored in the lower part of the shell 2. Thereafter, the absorption liquid stored inside the shell 2 passes through the discharge path 5 again and is sent to the outside of the absorber 1a such as a regenerator. In a steady state, the concentration of lithium bromide in the absorption liquid in the discharge passage 5 is about 57% by weight, and the temperature of the absorption liquid in the discharge passage 5 is, for example, about 36°C. Further, the temperature of the heat medium flowing into the heat exchanger tubes 3 is, for example, about 32°C, and the temperature of the heat medium flowing out from the heat exchanger tubes 3 is, for example, about 36°C. The heat medium flowing out from the heat exchanger tubes 3 is finally cooled down to about 32° C. by a cooling tower or the like, and then guided to the heat exchanger tubes 3 again.

FIG. 4 is a configuration diagram showing a refrigerator 100 including an absorber 1a. The refrigerator 100 includes, for example, an evaporator 50, an absorber 1a, a regenerator 60, and a condenser 70. Since the refrigerator 100 includes the absorber 1a, it is small and easily exhibits a high COP.

The refrigerator 100 is, for example, a single-effect cycle absorption refrigerator. The refrigerator 100 may be changed to a dual-effect cycle or triple-effect cycle absorption refrigerator. When a gas burner is used as the heat source of the regenerator 60, the refrigerator 100 may be a gas chiller.

The absorber 1a can be modified from various viewpoints. For example, absorber 1a may be modified as absorber 1b shown in FIG. 5 or absorber 1c shown in FIGS. 6 and 7. The absorber 1b and the absorber 1c are configured similarly to the absorber 1a except for the parts to be specifically explained. Components of the absorber 1b and the absorber 1c that are the same as or correspond to the components of the absorber 1a are given the same reference numerals, and detailed description thereof will be omitted. The description regarding absorber 1a also applies to absorber 1b and absorber 1c unless technically contradictory.

As shown in FIG. 5, the absorber 1b further includes a partition component 10. The partition component 10 prevents refrigerant vapor from flowing between the uppermost heat transfer tube 3 in each row of the first heat transfer tube group 3a and the lowermost heat transfer tube 3 in each row of the second heat transfer tube group 3b. do. The partition component 10 is viewed along the direction (X-axis direction) perpendicular to the longitudinal direction (Y-axis direction) of the heat exchanger tubes 3 and the direction of gravity (Z-axis direction). At this time, at least a portion of the partition component 10 is located between the heat exchanger tubes α and β in the direction of gravity. The heat exchanger tube α is a heat exchanger tube 3 located at an end portion close to the uppermost partition component 10 of the first heat exchanger tube group 3a in the X-axis direction. The heat exchanger tube β is the heat exchanger tube 3 located at the lowermost end of the second heat exchanger tube group 3b on the same side as the end thereof.

By reducing the pitch in the step direction of the heat exchanger tube group to an extent that does not pose a problem in terms of strength, it is possible to increase the density of the arrangement of the heat exchanger tubes. For example, headers for heat medium flow paths in the first heat exchanger tube group 3a and the second heat exchanger tube group 3b are arranged. In this case, the distance between the uppermost heat exchanger tube 3 in each row of the first heat exchanger tube group 3a and the lowermost heat exchanger tube 3 of the second heat exchanger tube group 3b is the distance of the other heat exchanger tubes 3 in the direction of gravity. tends to be wider. Therefore, the flow loss of refrigerant vapor between the uppermost heat exchanger tube 3 in each row of the first heat exchanger tube group 3a and the lowermost heat exchanger tube 3 of the second heat exchanger tube group 3b is relatively small. For example, the flow loss is smaller than the flow loss of the refrigerant vapor outside the heat exchanger tubes 3 of the first heat exchanger tube group 3a and the second heat exchanger tube group 3b, and the refrigerant vapor flowing between the heat exchanger tubes α and β The amount of steam tends to be relatively large.

On the other hand, according to the absorber 1b, the partition component 10 reduces the flow rate and flow velocity of refrigerant vapor between the heat exchanger tubes α and β. For this reason, the absorption liquid falling from the lowest stage in each row of the second heat exchanger tube group 3b toward the uppermost heat exchanger tube 3 in each row of the first heat exchanger tube group 3a is not easily dragged by the flow of refrigerant vapor. As a result, the uppermost heat exchanger tube 3 of the second heat exchanger tube group 3b can be appropriately wetted with the absorption liquid, and the heat transfer rate in the absorber 1b is high. For example, the absorber 1b has a large flow rate of refrigerant vapor to be absorbed, and is easily adapted to high-load conditions where a large capacity is required. For example, it is also possible to adjust the heat transfer rate of the absorber 1b to about 1.4 times the heat transfer rate of a conventional absorber having a group of heat exchanger tubes arranged in a lattice arrangement.

As shown in FIG. 6, the absorber 1c is equipped with a dropper 8a. The dropper 8a is constructed in the same manner as the dropper 8 of the absorber 1a, except for parts that are specifically explained.

As shown in FIG. 7, when the dripper 8a is viewed along the longitudinal direction of the heat transfer tube 3, the second dripping port 14b is located at a position deviating from the horizontal plane containing the first dripping port 14a in the direction of gravity. has been done. As a result, the distance between the heat transfer tube 3 located at the top of the right row 3m and the second dripping port 14b is adjusted to the distance between the heat transfer tube 3 located at the top of the left row 3h and the first dripping port 14a. Cheap. Thereby, it is easy to keep the flow rate of the refrigerant vapor passing between the top heat exchanger tube 3 in the left row 3h and the top heat transfer tube 3 in the right row 3m and the dropper 8a low. Therefore, the absorption liquid is less likely to be dragged by the flow of refrigerant vapor. As a result, the heat exchanger tubes 3 can be appropriately wetted with the absorption liquid, and the heat transfer rate in the absorber 1c is high. The absorber 1c is easily adapted to regeneration operating conditions, for example, where the flow rate of refrigerant vapor to be absorbed is high. For example, it is also possible to adjust the heat transfer rate of the absorber 1c to about 1.5 times the heat transfer rate of a conventional absorber having a group of heat exchanger tubes arranged in a lattice arrangement.

The distance between the heat transfer tube 3 located at the top of the right row 3m and the second dripping port 14b may be equal to the distance between the heat transfer tube 3 located at the top of the left row 3h and the first dripping port 14a. .

FIG. 8 is a cross-sectional view of a shell-and-tube absorber 1d according to another example of the embodiment of the present disclosure. The absorber 1d is configured in the same manner as the absorber 1b except for the parts to be specifically explained. Components of the absorber 1d that are the same as or correspond to components of the absorber 1b are denoted by the same reference numerals, and detailed description thereof will be omitted. The description regarding absorbers 1a-1c also applies to absorber 1d, unless technically contradictory.

As shown in FIG. 8, in the absorber 1d, when the partition component 10 is viewed along the longitudinal direction of the heat exchanger tubes 3 and the direction perpendicular to the direction of gravity, at least a part of the partition component 10 is located on the lower side in the direction of gravity. It is located between the heat exchanger tube 3s and the upper heat exchanger tube 3u. The lower heat exchanger tube 3s is the uppermost heat exchanger tube 3 closest to the partition component 10 in the first heat exchanger tube group 3a. The upper heat exchanger tube 3u is the lowest heat exchanger tube 3 closest to the partition component 10 in the second heat exchanger tube group 3b. In the absorber 1d, the distance L6 between the center axis of the lower heat exchanger tube 3s and the center axis of the upper heat exchanger tube 3u is longer than the distance L7. The distance L7 is the uppermost heat exchanger tube 3 in the row adjacent to the row of the first heat exchanger tube group 3a including the lower heat exchanger tube 3s, and the row adjacent to the row of the second heat exchanger tube group 3b including the upper heat exchanger tube 3u. This is the distance from the lowest heat exchanger tube 3 in .

The partition component 10 tends to reduce the flow rate and flow velocity of refrigerant vapor flowing between the lower heat exchanger tube 3s and the upper heat exchanger tube 3u. On the other hand, since the distance L6 is longer than the distance L7, the amount of refrigerant vapor flowing between the upper heat exchanger tube 3u and the lower heat exchanger tube 3s and the flow rate of the refrigerant vapor are easily maintained within a desired range, and the refrigerant vapor flows. The angle between the direction and the direction in which the absorbing liquid is dripped tends to become small. Therefore, the absorption liquid dripped from the upper heat exchanger tube 3u is difficult to be dragged in the direction perpendicular to the longitudinal direction of the heat exchanger tube 3 and the direction of gravity. As a result, the amount of refrigerant vapor flowing into the first heat exchanger tube group 3a and the second heat exchanger tube group 3b is maintained within a desired range, and the absorption liquid dripped from the lowest heat exchanger tube 3 of the second heat exchanger tube group 3b is It tends to adhere to the uppermost heat exchanger tube of the first heat exchanger tube group 3a. As a result, even in operations such as absorption liquid dilution operation in which the amount of refrigerant vapor absorbed by the absorption liquid temporarily increases, the heat transfer tubes 3 of the first heat transfer tube group 3a can be appropriately wetted with the absorption liquid. , the heat transfer rate of the absorber 1d tends to improve. For example, it is also possible to adjust the heat transfer rate of the absorber 1d to about 1.6 times the heat transfer rate of a conventional absorber having a group of heat exchanger tubes arranged in a lattice arrangement.

In the absorber 1d, for example, the heat medium flows in a specific direction in the first heat exchanger tube group 3a, and flows in a direction opposite to the specific direction in the second heat exchanger tube group 3b. According to such a configuration, absorbed heat generated by absorption of refrigerant vapor into the absorption liquid can be effectively radiated to the heat medium. In the absorber 1d, for example, the heat medium may flow in a specific direction in the first heat exchanger tube group 3a and the second heat exchanger tube group 3b.

As shown in FIG. 8, in the absorber 1d, for example, the partition component 10 is located below the upper heat exchanger tube 3u in the direction of gravity. In other words, the upper end of the partition component 10 is located below the lower end of the upper heat exchanger tube 3u. In addition, the distance L8 between the central axis of the upper heat exchanger tube 3u and the upper end of the partition component 10 is longer than the distance L9. The distance L9 is the distance between the central axis of the lower heat exchanger tube 3s and the lower end of the partition component 10. The eliminator 9 has, for example, a channel curved in the shape of a mountain in the second supply path 7, and the refrigerant vapor passes through the eliminator 9 along the channel curved in the shape of a mountain. Therefore, the flow of refrigerant vapor tends to reach the periphery of the partition component 10 while facing diagonally downward. The fact that the distance L8 is longer than the distance L9 is advantageous in making the refrigerant vapor flow between the lower heat exchanger tube 3s and the upper heat exchanger tube 3u while keeping the flow of the refrigerant vapor directed diagonally downward. As a result, when placed between the lower heat exchanger tube 3s and the upper heat exchanger tube 3u, the angle between the direction in which the refrigerant vapor flows in and the direction in which the absorption liquid drips tends to become smaller.

The absorber 1d can be modified from various points of view. For example, in the direction of gravity, the upper heat exchanger tube 3u and the partition component 10 may overlap. In this case, the partition component 10 may have an opening. At least a portion of this opening is located, for example, below the upper heat exchanger tube 3u in the direction of gravity, and this opening is located near the lower end of the upper heat exchanger tube 3u. In this case, the flow of refrigerant vapor passes through the opening and tends to flow between the lower heat exchanger tube 3s and the upper heat exchanger tube 3u in a diagonally downward direction. As a result, when placed between the lower heat exchanger tube 3s and the upper heat exchanger tube 3u, the angle between the direction in which the refrigerant vapor flows in and the direction in which the absorption liquid drips tends to become smaller.

The shell-and-tube absorber of the present disclosure is included in an absorption chiller, and can also be applied to applications such as central air conditioning systems of buildings and chillers for process cooling.

1a, 1b, 1c, 1d Shell and tube type absorber 2 Shell 3 Heat exchanger tube 3a First heat exchanger tube group 3b Second heat exchanger tube group 3g Heat exchanger tube group 3h Left row 3m Right row 3s Lower heat exchanger tube 3u Upper heat exchanger tube 4 First supply path 7 Second supply path 8 Dropper 10 Partition part 14a First drip port 14b Second drip port 100 Freezer

Claims (9)

a shell that stores the absorbent liquid;
A heat exchanger tube group having a plurality of heat exchanger tubes in which a heat medium flows, which are arranged in multiple stages in the direction of gravity and in multiple rows in a direction perpendicular to the direction of gravity and arranged parallel to each other inside the shell;
a first supply path that supplies the absorption liquid to the shell;
a second supply path for supplying refrigerant vapor to the shell;
a dropper that drops the absorption liquid supplied by the first supply path toward the heat exchanger tube group;
Comprising a partition part,
The heat exchanger tube group includes an adjacent left row and a right row, and includes a central axis of the heat exchanger tubes in the right row when looking at the left row and the right row along the longitudinal direction of the heat exchanger tubes. A horizontal plane is located between a pair of horizontal planes including the central axes of two heat exchanger tubes adjacent in the direction of gravity in the left row, or a horizontal plane including the central axes of the heat exchanger tubes in the left row A plane is located between a pair of horizontal planes including central axes of the two heat exchanger tubes adjacent in the direction of gravity in the right row,
The distance (L1) between the central axis of the heat exchanger tube in the upper stage of the left row and the center axis of the lower heat exchanger tube, which is one stage below the upper stage in the left row, is The distance (L2 ) is equal to
The heat transfer tube group includes a first heat transfer tube group in which the heat medium flows in a specific direction, and a second heat transfer tube group that is arranged above the first heat transfer tube group in the direction of gravity and in which the heat transfer medium flows in a direction opposite to the specific direction. It has a heat tube group,
The partition component allows the refrigerant vapor to flow between the uppermost heat exchanger tube in each row of the first heat exchanger tube group and the lowermost heat exchanger tube in each row of the second heat exchanger tube group. inhibits
When the partition component is viewed along the direction perpendicular to the longitudinal direction of the heat exchanger tube and the direction of gravity, at least a portion of the partition component is in the direction perpendicular to the longitudinal direction of the heat exchanger tube and the direction of gravity in the direction of gravity. located between the heat exchanger tube located at the end of the uppermost stage near the partition component and the heat exchanger tube located at the end of the lowermost stage on the same side as the end;
Shell and tube absorber. A distance between central axes of two adjacent heat exchanger tubes in the left row includes a first length (L3) and a second length (L1) longer than the first length (L3). The shell-and-tube absorber according to item 1. The heat transfer medium is guided to the second heat exchanger tube group after passing through the first heat exchanger tube group, or is guided to the first heat exchanger tube group after passing through the second heat exchanger tube group. Or the shell-and-tube type absorber according to 2 . The distance between the central axis of the uppermost heat exchanger tube in the left row and the central axis of the lowermost heat exchanger tube in the left row is the distance between the central axis of the uppermost heat exchanger tube in the right row and the The shell-and-tube type absorber according to any one of claims 1 to 3 , wherein the distance is equal to the distance from the central axis of the heat exchanger tube at the lowest stage. The dripper has a first dripping port that drips the absorption liquid onto the heat transfer tubes in the left row, and a second dripping port that drips the absorption liquid into the heat transfer tubes in the right row.
When looking at the dripper along the longitudinal direction of the heat exchanger tube, the second dripping port is located at a position deviated from a horizontal plane including the first dripping port in the direction of gravity.
A shell-and-tube absorber according to any one of claims 1 to 4 . A shell that stores the absorbent liquid;
The shell has a plurality of heat exchanger tubes arranged in multiple stages in the direction of gravity and in multiple rows in a direction perpendicular to the direction of gravity and arranged parallel to each other, through which a heat medium flows, and a first heat exchanger tube. a group of heat exchanger tubes, and a second group of heat exchanger tubes arranged above the first group of heat exchanger tubes in the direction of gravity;
a first supply path that supplies the absorption liquid to the shell;
a second supply path for supplying refrigerant vapor to the shell;
a dropper that drops the absorption liquid supplied by the first supply path toward the heat exchanger tube group;
a partition that prevents the refrigerant vapor from flowing between the uppermost heat transfer tube in each row of the first heat transfer tube group and the lowermost heat transfer tube in each row of the second heat transfer tube group; comprising parts and
The heat exchanger tube group includes an adjacent left row and a right row, and includes a central axis of the heat exchanger tubes in the right row when looking at the left row and the right row along the longitudinal direction of the heat exchanger tubes. A horizontal plane is located between a pair of horizontal planes including the central axes of two heat exchanger tubes adjacent in the direction of gravity in the left row, or a horizontal plane including the central axes of the heat exchanger tubes in the left row A plane is located between a pair of horizontal planes including central axes of the two heat exchanger tubes adjacent in the direction of gravity in the right row,
When the partition component is viewed along a direction perpendicular to the longitudinal direction of the heat exchanger tubes and the direction of gravity, at least a portion of the partition component is closest to the partition component in the first heat exchanger tube group in the direction of gravity. located between the lower heat exchanger tube, which is the heat exchanger tube at the uppermost stage, and the upper heat exchanger tube, which is the heat exchanger tube at the lowermost stage, which is closest to the partition component in the second heat exchanger tube group;
The distance between the center axis of the lower heat exchanger tube and the center axis of the upper heat exchanger tube is the same as the distance between the center axis of the lower heat exchanger tube and the uppermost heat exchanger tube in the row adjacent to the row of the first heat exchanger tube group including the lower heat exchanger tube, longer than the distance between the row of the second heat exchanger tube group including the upper heat exchanger tube and the lowermost heat exchanger tube in an adjacent row;
Shell and tube absorber. The shell-and-tube type absorber according to claim 6 , wherein the heat medium flows in a specific direction in the first heat exchanger tube group and in a direction opposite to the specific direction in the second heat exchanger tube group. The partition component is located below the upper heat exchanger tube in the direction of gravity,
According to claim 6 or 7 , in the direction of gravity, the distance between the central axis of the upper heat exchanger tube and the upper end of the partition component is longer than the distance between the central axis of the lower heat exchanger tube and the lower end of the partition component. shell and tube type absorber. A refrigerator comprising the shell-and-tube absorber according to any one of claims 1 to 8 .

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