JP2002277090A - Plate type heat exchanger for absorption refrigerator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a plate type heat exchanger capable of being applied to an absorber or the like of an absorption refrigerator. SOLUTION: The plate type heat exchanger (30) comprises first plates (31) and second plates (32) alternately laminated. A first space (41) and a second space (42) are partitioned by laminated heat transfer plates (31, 32). The first space (41) becomes a closed space, and the second space (42) is opened at an outer edge. When the absorber is constituted of the heat exchanger (30), an absorption solution flows on the surfaces of the plates (31, 32) at the second space (42) side, and a cooling water flows in the first space (41). A gas refrigerant is introduced into the second space (42) opened at the outer edge. The solution heat exchanges with the water, and hence the water derives an absorption heat.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a heat exchanger,
In particular, the present invention relates to a plate heat exchanger configured by stacking heat transfer plates and used in an absorption refrigerator.

[0002]

2. Description of the Related Art Conventionally, 101, 1 of "Refrigeration and Air Conditioning Handbook New Edition, 5th Edition, 3 Volume, Air Conditioning" issued by Japan Refrigeration Association
As disclosed on page 02, plate heat exchangers are known. This plate heat exchanger is configured by stacking a number of heat transfer plates. In the stacking direction of the heat transfer plates, first fluid passages and second fluid passages, both of which are closed spaces, are alternately partitioned. In the plate heat exchanger, the fluid flowing through each fluid passage exchanges heat via the heat transfer plate.

[0003] On the other hand, absorption chillers have been widely known as a kind of chillers. As this type of absorption refrigerator, there is known an absorption refrigerator configured using water as a refrigerant and an aqueous solution of lithium bromide as an absorption solution.

[0004] The above-mentioned absorption refrigerator is constituted by many heat exchangers. For example, a double effect device is provided with an absorber, a high temperature generator, a low temperature generator, a condenser, and an evaporator. Among them, the absorber, the low-temperature generator, the condenser, and the evaporator are generally constituted by a shell-and-tube heat exchanger.

[0005] For example, in the case of an absorber, a gas refrigerant (water vapor) is absorbed by an absorbing liquid scattered around a heat transfer tube.
Absorption heat is taken away by cooling water flowing in the heat transfer tube. In the case of an evaporator, a liquid refrigerant (water) surrounds the heat transfer tube.
While flowing water as a heat medium into the heat transfer tube,
The water inside the tube is cooled by evaporating the liquid refrigerant outside the tube to obtain cold water.

[0006]

As described above, in a conventional absorption refrigerator, it is difficult to reduce the size of the heat exchanger because many shell and tube heat exchangers are used. On the other hand, plate heat exchangers generally have higher heat transfer performance than shell and tube heat exchangers. Therefore, it is conceivable to reduce the size of the absorption refrigerator by using a plate heat exchanger having high performance.

However, the above-mentioned conventional plate heat exchanger could not be directly applied to an absorption refrigerator. For example, when a plate heat exchanger is applied to the absorber, it is necessary for the absorbing solution to absorb gas refrigerant (water vapor) and release heat to the cooling water while flowing on the surface of the heat transfer plate. However, in the above-mentioned conventional plate heat exchanger, each of the fluid passages defined by each heat transfer plate is a closed space. For this reason, the absorbing solution and the gas refrigerant (steam) cannot be simultaneously introduced into the fluid passage, which is a closed space, and the absorber cannot be constituted by a plate heat exchanger.

[0008] The present invention has been made in view of the above points, and an object of the present invention is to provide a plate-type heat exchanger applicable to an absorber, an evaporator, and the like of the above absorption refrigerator. It is in.

[0009]

According to a first aspect of the present invention, a first heat transfer plate (31) and a second heat transfer plate (32) are alternately stacked in a horizontal direction. The target is the plate heat exchanger of the absorption refrigerator to be formed. In the stacking direction of the heat transfer plates (31, 32), a first space (41), which is a closed space surrounded by a pair of adjacent heat transfer plates (31, 32), and an outer edge are open. A second space (42) is formed alternately, and a pair of communication passages (43, 44) for making the first spaces (41) communicate with each other is provided;
The first liquid flowing through the first space (41) and the second liquid flowing along the surface of the heat transfer plates (31, 32) on the side of the second space (42) are subjected to heat exchange, while the heat transfer is performed. On the heat plates (31, 32), a large number of dimples (51) depressed toward the first space (41) are provided in a staggered arrangement with a horizontal pitch of 20 mm and a vertical pitch of 15 mm.
Each of the dimples (51) is formed in a truncated cone shape having a bottom diameter of 10 mm, a top diameter of 4 mm, and a depth of 2 mm.

A second solution taken by the present invention is an absorption refrigeration formed by alternately stacking a first heat transfer plate (31) and a second heat transfer plate (32) in the horizontal direction. It is intended for the plate heat exchanger of the machine. In the stacking direction of the heat transfer plates (31, 32), the first space (4), which is a closed space surrounded by a pair of adjacent heat transfer plates (31, 32).
1) and a second space (42) whose outer edge is open is formed alternately, and includes a pair of communication passages (43, 44) for communicating the first spaces (41) with each other. One space (41)
Heat is exchanged between the first liquid flowing through the heat transfer plate and the second liquid flowing along the surface of the heat transfer plate (31, 32) on the side of the second space (42), while the heat transfer plate (31, 32) is being exchanged. A plurality of grooves (52) which are recessed toward the first space (41) and extend along the flow direction of the first liquid in the first space (41) are provided at predetermined intervals, and each of the grooves (52) is , Depth 1.
It is formed so as to have a trapezoidal cross section of 0 mm or more and 3.0 mm or less.

A third solution taken by the present invention is the heat transfer plate (31,3) according to the first or second solution.
The surface on the side of the second space (42) in 2) is subjected to a treatment for improving the wettability of the heat transfer plates (31, 32) with the second liquid.

According to a fourth aspect of the present invention, in the first or second aspect, the first space (41) includes:
In the first space (41), a baffle part (45) for flowing the first liquid meandering right and left is provided.

-Operation- In the first and second solutions, the heat transfer plates (31, 3
2) are stacked horizontally to form a plate heat exchanger (30). In the stacking direction of the heat transfer plates (31, 32),
The first space (41) and the second space (42) are formed alternately. The first space (41) is a closed space formed by a pair of adjacent heat transfer plates (31, 32), and is surrounded by both heat transfer plates (31, 32). The plurality of first spaces (41) are communicated with each other by a pair of communication passages (43, 44). The second space (42) is partitioned on both sides by heat transfer plates (31, 32), and has an outer edge opening outside the plate heat exchanger (30).

The plate type heat exchanger (30) exchanges heat between the first liquid and the second liquid. The first liquid flows into each first space (41) through one communication path (43), and after flowing heat with the second liquid, flows out of the first space (41) to the other communication path (44). The second liquid flows along the surface of the heat transfer plate (31, 32) facing the second space (42). At this time, the second liquid spreads and flows on the surface of the heat transfer plate (31, 32) in the form of a liquid film. The second liquid flows down the surface of the heat transfer plate (31, 32) while flowing down the first space (4).
Heat exchange with the first liquid of 1).

In the first solution, a large number of dimples (51) are formed on the heat transfer plates (31, 32). Each dimple (51) is in the first space (4
It is depressed toward 1) and has a truncated cone shape with a predetermined dimension. In the standing heat transfer plates (31, 32), a large number of dimples (51) have a horizontal pitch (column pitch) of 20 mm and a vertical pitch (row pitch) of 1 mm.
They are arranged in a 5mm staggered arrangement.

On the other hand, in the second solution, a plurality of grooves (52) are formed in the heat transfer plates (31, 32). Each groove (52) is depressed toward the first space (41), which is a closed space, and is formed such that its cross section is trapezoidal with a predetermined depth. Each groove (52) is provided in the first space (4
It extends along the flow direction of the first liquid in 1).
However, the groove (52) does not need to be continuous from the inflow portion to the outflow portion of the first liquid in the first space (41), and may be divided on the way.

[0017] In the third solution, a process for increasing the "wetting property" with respect to the second liquid is performed on the surface of the heat transfer plate (31, 32) which comes into contact with the second liquid. This type of treatment involves applying a hydrophilic agent to the heat transfer plates (31, 32), or forming an oxide film on the surface of the heat transfer plates (31, 32) by heating in the presence of air. Is exemplified. When this type of treatment is performed on the heat transfer plates (31, 32), the second liquid is surely spread on the surface of the heat transfer plates (31, 32) and flows down in a liquid film form.

In the fourth solution, the baffle part (45) is provided in the first space (41) which is a closed space. The first space (41) introduced into the first space (41) through one communication passage (43)
The liquid is guided to the baffle part (45) and meanders right and left and flows. The first liquid flows in a meandering manner from side to side,
The liquid exchanges heat with the liquid, and then flows out from the first space (41) to the other communication path (44).

[0019]

According to the present invention, in the stacking direction of the heat transfer plates (31, 32), the first space (41), which is a closed space, and the second space opened outside the plate heat exchanger (30). (Four
2) and are alternately formed. In addition, heat transfer plates (31,
The second liquid flowing along the surface on the second space (42) side in 32) is heat-exchanged with the first liquid in the first space (41). Therefore, according to the present invention, a plate heat exchanger (30) that can be used as an absorber or an evaporator of an absorption refrigerator can be realized.

Specifically, in the absorber, it is necessary to bring the absorbing solution into contact with the gaseous refrigerant and at the same time exchange the heat with the cooling water. When the plate heat exchanger (30) according to the present invention is used as the absorber, the first liquid is used as the cooling water and the second liquid is used as the absorbing solution. It is the surface of the heat transfer plate (31, 32) on the side of the second space (42) that the absorbing solution as the second liquid flows, and the second space (42) of the plate heat exchanger (30). Communicates with the outside world. For this reason, the gas refrigerant can be introduced into the second space (42) from outside the plate heat exchanger (30), and the introduced gas refrigerant can be brought into contact with the absorbing solution. Therefore, the plate heat exchanger (30) according to the present invention can function as an absorber.

In the evaporator, it is necessary to exchange heat between the liquid refrigerant and a heat medium such as water, and to quickly discharge the evaporated refrigerant. When the plate heat exchanger (30) according to the present invention is used as the evaporator, the first liquid is used as a heat medium and the second liquid is used as a liquid refrigerant. The liquid refrigerant as the second liquid flows on the surface of the heat transfer plate (31, 32) on the side of the second space (42), and the second space (42) is provided in the plate heat exchanger (30). Communicates with the outside world. Therefore, the heat medium can exchange heat with the liquid refrigerant, and the evaporated refrigerant can be quickly discharged to the outside of the plate heat exchanger (30). Therefore, the plate heat exchanger (30) according to the present invention can function as an evaporator.

Further, according to the present invention, the heat transfer plate (3
By forming the dimples (51) and the grooves (52) in (1, 32), the heat transfer area can be enlarged, and the heat transfer between the first liquid and the second liquid can be promoted. Therefore, the plate heat exchanger (3
0) It is possible to improve the performance. Here, conventionally, as a measure for improving the performance of the plate heat exchanger (30), herringbone-shaped irregularities are widely formed on the heat transfer plates (31, 32) by press working or the like.
When the second liquid flows along the surface of the heat transfer plate (31, 32) having such a shape, the second liquid flows along herringbone-shaped irregularities. For this reason, it is difficult to flow the second liquid in the form of a liquid film, and there is a possibility that the performance is rather deteriorated. Therefore, by forming dimples (51) and grooves (52) having different shapes from the conventional herringbone-shaped irregularities on the heat transfer plates (31, 32), the plate-type heat exchanger (30) according to the present invention is formed. Performance can be improved.

According to the third solution, since the surface of the heat transfer plate (31, 32) is subjected to a predetermined treatment to enhance the "wettability", the surface of the heat transfer plate (31, 32) is almost completely removed. The liquid film of the second liquid can be held over the entire surface. Therefore, heat can be exchanged between the first liquid and the second liquid over substantially the entire surface of the heat transfer plates (31, 32), and the performance of the plate heat exchanger (30) can be reliably exhibited.

According to the fourth solution, the baffle part (45) is provided in the first space (41), so that the baffle part (45) is not provided in the first space (41). The drift of the first liquid can be suppressed. Also, the first
In the space (41), the first liquid flows in a meandering manner from side to side, so that the flow rate of the first liquid in the first space (41) can be increased, thereby improving the heat transfer coefficient on the first liquid side. Can be done. Therefore, according to the present solution, it is possible to improve the performance of the plate heat exchanger (30).

[0025]

Embodiment 1 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. The first embodiment is a double-effect absorption refrigerator (10) configured with water as a refrigerant and an aqueous solution of lithium bromide as an absorption solution. In particular, the absorption refrigerator (10) is configured to perform an absorption refrigeration cycle of two-stage evaporation and two-stage absorption. In addition, in the absorption refrigerator (10) according to the first embodiment, the absorber (13, 1) is used.
4) and the evaporator (11, 12) are both configured using the plate heat exchanger (30) according to the present invention.

-Overall Configuration and Operation of Absorption Refrigerator- As shown in FIG. 1, the absorption refrigerator (1
0) is a first evaporator (11), a second evaporator (12), a first absorber (13), a second absorber (14), a high-temperature generator (15), a low-temperature generator (16), And a condenser (17) connected by piping. The absorption refrigerator (10) is provided with a high-temperature heat exchanger (18) and a low-temperature heat exchanger (19).

The first evaporator (11) and the second evaporator (1)
2), the first absorber (13), and the second absorber (14) are all provided in the low-pressure cylinder (20). The inside of the low-pressure cylinder (20) is vertically divided. The low-pressure cylinder (20) has an upper part formed by a first evaporator (11) and a first absorber (13), and a lower part formed by a second evaporator (12) and a second absorber (1).
4) is configured. The lower end of the second absorber (14)
It is connected to the high-temperature generator (15) via a low-temperature heat exchanger (19) and a high-temperature heat exchanger (18). First absorber (1
3) and the absorption solution (dilute solution) whose concentration has been reduced by absorbing the gas refrigerant (steam) in the second absorber (14) is sequentially passed through the low-temperature heat exchanger (19) and the high-temperature heat exchanger (18). It passes through and is introduced into the high temperature generator (15).

The high-temperature generator (15) is provided with a gas burner and is configured almost similarly to a gas-fired boiler. The high temperature generator (15) heats the absorbed solution by heat exchange with combustion gas. In the high temperature generator (15)
The absorbed absorption solution is heated to evaporate the water, thereby increasing the concentration of the absorption solution. The absorption solution whose concentration has increased in the high-temperature generator (15) is radiated to the dilute solution in the high-temperature heat exchanger (18), and then sent to the low-temperature generator (16). The steam from the high-temperature generator (15) is sent to the low-temperature generator (16).

The low-temperature generator (16) is constituted by a shell-and-tube heat exchanger, and exchanges heat between the absorbing solution introduced from the high-temperature generator (15) and steam. The low-temperature generator (16) uses the heat of condensation of water vapor to heat the absorbing solution and further evaporates moisture from the absorbing solution. This further increases the concentration of the absorbing solution. Absorption solution (concentrated solution) with increased concentration in the low-temperature generator (16)
Is released to the dilute solution by the low temperature heat exchanger, and then sent to the first absorber (13). On the other hand, the steam of the low-temperature generator (16) is sent to the condenser (17).

The condenser (17) is constituted by a shell and tube type heat exchanger, and exchanges heat between the steam introduced from the low temperature generator (16) and the cooling water. By this heat exchange, the steam condenses into liquid water. The water in the condenser (17), together with the water condensed in the low-temperature generator (16),
The liquid refrigerant is sent to the first evaporator (11).

In the first evaporator (11), the supplied liquid refrigerant (water) and the heat transfer water exchange heat. By this heat exchange, a part of the liquid refrigerant (water) evaporates, and the heat transfer water is cooled. The gas refrigerant (water vapor) generated in the first evaporator (11)
It is sent to the first absorber (13). As described above, the absorption solution (concentrated solution) from the low-temperature generator (16) is fed into the first absorber (13). The first absorber (13) allows the supplied gas refrigerant to contact the absorbing solution and, at the same time, causes heat exchange between the absorbing solution and the cooling water. This first absorber (1
In 3), the gas refrigerant is absorbed by the absorbing solution, and the absorption heat generated at that time is taken away by the cooling water.

The second evaporator (12) includes a first evaporator (11)
The liquid refrigerant (water) which has not evaporated in is sent. In the second evaporator (12), the supplied liquid refrigerant and the heat transfer water exchange heat. By this heat exchange, the liquid refrigerant evaporates,
The heating medium is cooled. The gas refrigerant (steam) generated in the second evaporator (12) is sent to the second absorber (14). An absorption solution having a slightly reduced concentration due to absorption of the gas refrigerant by the first absorber (13) is sent into the second absorber (14). The second absorber (14) makes the supplied gas refrigerant and the absorbing solution come into contact with each other, and at the same time, causes heat exchange between the absorbing solution and the cooling water. In the second absorber (14), the gas refrigerant is absorbed by the absorbing solution, and the absorption heat generated at that time is taken by the cooling water.

During the operation of the absorption refrigerator (10), in the low-pressure cylinder (20), the upper space (22) in which the first evaporator (11) and the first absorber (13) are arranged is better. , The lower space (2) in which the second evaporator (12) and the second absorber (14) are arranged.
Lower pressure than 3). That is, the evaporation temperature of the refrigerant in the first evaporator (11) is lower than the evaporation temperature of the refrigerant in the second evaporator (12). Therefore, in this embodiment,
The heat transfer water is first introduced into the second evaporator (12), and the heat transfer water cooled by the second evaporator (12) is sent to the first evaporator (11). The heat transfer water that has flowed out of the first evaporator (11) is sent to the user side and used for indoor cooling and the like.

—Evaporator / Absorber— The configurations of the evaporator (11, 12) and the absorber (13, 14) will be described in detail.

The low-pressure cylinder (20) is formed in a horizontally long closed container having a rectangular cross section. As shown in FIG. 2, the inside of the low-pressure cylinder (20) is partitioned into an upper space (22) and a lower space (23) by a partition plate (21). An eliminator (24) is provided in each of the upper space (22) and the lower space (23). This eliminator (24)
Removes the droplet refrigerant from the gas refrigerant flowing from the evaporator (11, 12) to the absorber (13, 14), and removes only the gas refrigerant from the absorber (1).
3, 14). Eliminator (2
4) is provided at the center of the upper space (22) and the lower space (23) in the width direction (the left-right direction in FIG. 2), and partitions each space (22, 23) into right and left.

In the upper space (22) and the lower space (23),
One evaporating heat exchanger (25) and one absorbing heat exchanger (26) are arranged. The evaporating heat exchanger (25) and the absorbing heat exchanger (26) are both constituted by the plate heat exchanger (30) according to the present invention.

Specifically, in the upper space (22), the evaporator heat exchanger (25) is located on the left side of the eliminator (24) in FIG.
Is disposed, and an absorption heat exchanger (26) is disposed on the right side thereof. The left portion of the upper space (22) partitioned by the eliminator (24) constitutes a first evaporator (11), and the right portion thereof constitutes a first absorber (13). Similarly, in the lower space (23), the evaporator heat exchanger (25) is arranged on the left side of the eliminator (24) in FIG. 2, and the absorption heat exchanger (26) is arranged on the right side thereof. This eliminator (24)
The left part of the lower space (23) partitioned by the above constitutes the second evaporator (12), and the right part thereof constitutes the second absorber (14).

A liquid refrigerant header (27) is provided above the evaporating heat exchanger (25) in the first evaporator (11). The liquid refrigerant header (27) is connected to the condenser (17) by piping, and supplies the liquid refrigerant (water) sent from the condenser (17) to the evaporating heat exchanger (25). Also, the first
For the liquid refrigerant that did not evaporate in the evaporator (11), the second
It is supplied to the evaporator heat exchanger (25) of the evaporator (12).

A solution header (28) is provided above the absorption heat exchanger (26) in the first absorber (13). The solution header (28) is connected to the low-temperature generator (16) by a pipe, and supplies the absorption solution (concentrated solution) sent from the low-temperature generator (16) to the absorption heat exchanger (26). Further, the absorption solution having absorbed the gas refrigerant in the first absorber (13) is supplied to the absorption heat exchanger (26) of the second absorber (14).

-Plate Heat Exchanger- As shown in FIG. 3, the absorption heat exchanger (26) is constituted by connecting a plurality of plate heat exchangers (30) according to the present invention in series. I have. FIG. 3 shows the absorption heat exchanger (26) in the first absorber (13) as viewed from the eliminator (24). In addition, the heat exchanger for evaporation (25) is configured by connecting a plurality of plate heat exchangers (30) according to the present invention in series similarly to the heat exchanger for absorption (26). Here, the plate heat exchanger (30) will be described by taking, as an example, what constitutes the absorption heat exchanger (26).

The plate heat exchanger (30) is constituted by laminating a number of heat transfer plates (31, 32) in the horizontal direction. The heat transfer plates (31, 32) are formed by pressing a thin stainless steel plate. The heat transfer plates (31, 32) include a first plate (31) and a second plate (32) having different shapes. In the plate heat exchanger (30), the first plate (31) and the second plate (32)
Are alternately stacked. Further, the stacked heat transfer plates (31, 32) are joined by brazing at their contact portions.

First plate (31) and second plate (32)
And the first space (41) and the second space (4) in the laminating direction of the heat transfer plates (31, 32).
2) and are alternately formed. In FIG. 3, the first plate (31) is located on the right side of the first space (41), and the second plate (32) is located on the left side thereof. The first space (41) is a closed space surrounded by the adjacent first plate (31) and second plate (32). FIG.
, The second plate (32) is located on the right side of the second space (42).
And the first plate (31) is located on the left side. This second space (42) is formed by the adjacent first plate (3
The space defined by 1) and the second plate (32) is open to the outside of the plate heat exchanger (30) at the outer edge thereof.

Both sides of the plate heat exchanger (30) (FIG. 3)
Are provided with protective plates (33). The protection plate (33) is made of a stainless steel thick plate, and is joined to the adjacent heat transfer plates (31, 32) by brazing. The protection plate (33) is provided with an inflow connection portion (34) and an outflow connection portion (35). The inflow connection part (34) is provided below the protection plate (33) and communicates with an inflow path (43) described later. The inflow connection (34) is welded to the inflow connection (34) of the adjacent plate heat exchanger (30). The outflow connection part (35) is provided above the protective plate (33), and is connected to an outflow path (44) described later.
Is in communication with The outflow connection (35) is welded to the outflow connection (35) of the adjacent plate heat exchanger (30).

The heat transfer plates (31, 32) will be described with reference to FIGS. FIG. 4 shows the first
FIG. 4 shows a plan view of a plate (31). In a state where the heat transfer plates (31, 32) are stacked, the front side of the drawing in FIG. 4 is the second space (42), and the back side of the drawing is the first space (41).
Becomes

The first plate (31) includes a heat transfer section (50), an inlet header section (56), an outlet header section (58), and a peripheral section (6).
1) and a liquid reservoir forming section (63). Heat transfer section (5
0) is formed in a vertically long rectangular shape. Heat transfer section (5
Details of (0) will be described later.

The entrance header section (56) and the exit header section (5
8) is formed continuously on the right side of the heat transfer section (50) in FIG. The inlet header portion (56) has a vertically long rectangular shape shorter than the heat transfer portion (50), and is formed continuously below the heat transfer portion (50). A rectangular inflow opening (57) is formed at the center of the entrance header (56). The outlet header portion (58) has a vertically long rectangular shape shorter than the heat transfer portion (50), and is formed continuously above the heat transfer portion (50). Further, a rectangular outflow opening (59) is formed at the center of the outlet header (58).

The peripheral portion (61) is formed in a band shape so as to surround the heat transfer portion (50), the inlet header portion (56), and the outlet header portion (58). A large number of interval holding portions (62) are formed in the peripheral portion (61). The space holding portion (62) bulges in a truncated conical shape toward the near side of the drawing in FIG. 4, and its top is 6 mm higher than the peripheral edge (61). However, the interval holding section (62) provided around the entrance header section (56) and the exit header section (58)
Is shaped like a truncated cone.

The liquid reservoir forming portion (63) is formed continuously with the peripheral portion (61) along the upper side of the heat transfer portion (50).
The liquid reservoir forming portion (63) is formed in a rectangular shape, and swells toward the near side in the drawing in FIG. Specifically,
The liquid reservoir forming portion (63) bulges forward by 6 mm from the peripheral portion (61). In addition, the reservoir forming part (63) has 4
Two communication holes (64) are open.

The heat transfer section (50), the inlet header section (56),
The outlet header portion (58) bulges toward the near side in FIG. 4 from the peripheral edge portion (61). Specifically,
The heat transfer part (50) is higher than the peripheral part (61) by 2 mm. Inlet header (56) and outlet header (58)
Is 6 mm higher than the peripheral edge (61). The inlet header (56) and the outlet header (58) have a large number of opening reinforcements (60) formed facing the inflow opening (57) or the outflow opening (59). This opening reinforcement (60)
Has a truncated cone shape in half, and is recessed by 6 mm in the back side of the paper surface in FIG.

The heat transfer section (50) has dimples (5
1), a baffle forming part (53), a reinforcing part (54), and a spacing part (55) are formed.

The dimple (51) is formed so as to be depressed toward the back side of the paper in FIG. Specifically, as shown in FIG. 5, the dimple (51) is formed in a truncated cone shape having a top diameter of 4 mm, a bottom diameter of 10 mm, and a height of 2 mm. Note that the upper part in FIG. 5 corresponds to the back side of the paper in FIG. 4, and the lower part in FIG. 5 corresponds to the near side of the paper in FIG. That is, with the heat transfer plates (31, 32) stacked, the dimple (51) is depressed toward the first space (41).

The dimple (51) is provided in the heat transfer section (50).
, Many are formed in a staggered arrangement (see FIG. 4). Specifically, the arrangement of the dimples (51) is a staggered arrangement in which the pitch in the horizontal direction (column direction) in FIG. 4 is 20 mm and the pitch in the vertical direction (row direction) is 15 mm.

The baffle forming portion (53) is recessed by 2 mm toward the far side of the drawing in FIG. 4 and is formed in a groove shape extending along the short side of the heat transfer portion (50). Further, the length of the baffle forming part (53) is shorter than the length of the short side of the heat transfer part (50). The baffle forming part (53) is a heat transfer part (50)
Are formed at equal intervals. At that time, on the heat transfer surface, the baffle forming portion (53) leaning to the right side of the heat transfer portion (50) in FIG. 4 and the baffle forming portion (53) leaning to the left side of the heat transfer portion (50) The heat transfer sections (50) are arranged alternately in the longitudinal direction.

The reinforcing portion (54) is formed so as to be recessed by 2 mm toward the back side of the paper in FIG. This reinforcement (54)
Is formed in a truncated cone shape slightly smaller than the dimple (51). The heat transfer section (50) is provided with a reinforcing section (54) at the center and on both sides as appropriate.

The space holding section (55) of the heat transfer section (50) is shown in FIG.
Is formed so as to swell by 4 mm toward the front side of the drawing. The space holding portion (55) is formed in a truncated cone shape. The heat transfer unit (50) is provided with a space holding unit (55) at the center and on both sides as appropriate.

Although the first plate (31) has been described above, the heat transfer section (50), the inlet header section (56), and the second plate (32) are also similar to the first plate (31).
An outlet header part (58) and a liquid reservoir forming part (63) are provided. However, the second plate (32) is connected to the first plate (3
The shape of 1) is completely reversed. That is, when the peripheral portion (61) is used as a reference, the heat transfer portion (50) and the like in the first plate (31) swell toward the front, whereas the second plate
In the plate (32), the heat transfer portion (50) and the like are formed to be depressed. In addition, dimples (5
The same applies to 1) and the like.

The state in which the heat transfer plates (31, 32) are stacked will be described with reference to FIGS. When the first plate (31) and the second plate (32) are alternately stacked, the adjacent heat transfer plates (31, 32) come into contact with each other.
Then, the adjacent heat transfer plates (31, 32) are brazed to each other at the contact portions.

Specifically, in FIG. 6, the first plate (31) and the second plate (32) adjacent to the first plate (31) have a peripheral portion (61) and a dimple (51) of the heat transfer portion (50). , Reinforcement part (54) and baffle formation part (53), and inlet header part (5
6) and the opening reinforcing portion (60) of the outlet header portion (58), and are joined at these locations. The first plate (31) and the left adjacent second plate (32) form a closed space first space (41). In addition, the baffle formation part (53) of the adjacent heat transfer plate (31, 32)
Are brought into contact with each other to form a baffle portion (45) in the first space (41) (see FIG. 4).

Similarly, in FIG. 6, the first plate (3
1) and the second plate (32) on the right side
1) The space holding section (62), the space holding section (55) of the heat transfer section (50), the inlet header section (56), and the outlet header section (58).
And the liquid reservoir forming portion (63), and are joined at these locations. Then, a second space (42) is formed by the first plate (31) and the second plate (32) on the right side. In addition, the liquid reservoir forming portions (63) of the adjacent heat transfer plates (31, 32) abut and are joined,
A liquid reservoir (71) is formed above the heat transfer section (50).

When the heat transfer plates (31, 32) are stacked, the inflow passage (57) of each heat transfer plate (31, 32) extends in the stacking direction of the heat transfer plates (31, 32). 43) is formed. The inflow path (43) communicates with the lower end of the first space (41) to form a communication path that communicates each first space (41). Further, in this state, the outflow opening (59) of each heat transfer plate (31, 32) forms an outflow path (44) extending in the stacking direction of the heat transfer plates (31, 32). The outflow channel (44) communicates with the upper end of the first space (41) and forms a communication path that communicates each first space (41).

-Sprayer-In FIG. 6, the first plate (31) and the second plate on the right thereof
The liquid guide plate (72) is sandwiched between the plate (32). The liquid guide plate (72) is connected to the heat transfer plate (31,3).
It is installed between the liquid reservoir forming section (63) and the heat transfer section (50) in 2). That is, the liquid guide plate (72) is disposed below the liquid reservoir (71). Then, the liquid reservoir (71) and the liquid guide plate (72) are connected to the disperser (70) of the absorbing solution.
Is composed.

As described above, each heat transfer plate (31, 32)
A communication hole (64) is opened in the liquid reservoir forming portion (63). Therefore, the liquid reservoirs (71) formed by the heat transfer plates (31, 32) are each communicated by the communication hole (64). Further, a solution header (28) is provided above the liquid reservoir (71), and an absorbing solution (concentrated solution) is supplied from the solution header (28) to the liquid reservoir (71) (FIG. 3). reference). Then, the absorbing solution supplied to the liquid reservoir (71) spreads throughout the liquid reservoir (71) through the communication hole (64).

Further, as shown in FIG. 7, the liquid reservoir forming portion (63) of the heat transfer plate (31, 32) has a liquid outlet hole (65) opened at an inclined portion at the lower end thereof. The plurality of liquid outflow holes (65) are formed in a row in the longitudinal direction of the liquid reservoir forming portion (63) (perpendicular to the plane of FIG. 7). Then, the absorbing solution in the liquid reservoir (71) flows out through the liquid outflow hole (65).

The liquid guide plate (72) is formed by pressing and bending a stainless steel plate.
As shown in FIG. 8, the liquid guide plate (72) includes a chevron portion (73) having an inverted V-shaped cross section and a pair of flat plate portions (75) extending downward from respective lower ends of the chevron portion (73). Have. The length of the liquid guide plate (72) is determined according to the width of the liquid reservoir (71).

The flat portion (75) has a projection (76) and a recess (77). The protrusion (76) is a spherical protrusion swelling outward from the flat plate (75). The height of the protrusion (76) is preferably 0.1 mm to 0.8 mm, and more preferably 0.3 mm. The concave portion (77) is formed so as to be depressed toward the inside of the flat plate portion (75). Recess (77) formed in one flat plate (75)
The bottom of the recess (7) formed in the opposing flat plate (75)
7) is in contact with the bottom. In addition, the flat plate (75)
A leg (78) projecting further downward from the lower end is formed. The leg (78) protrudes from the lower end of the flat plate (75) by 0.5 mm.
Are provided one by one. On the other hand, at the left and right ends of the chevron (73), ears (74) bent upward are formed one by one.

As shown in FIG. 7, the liquid guide plate (72)
Is sandwiched between the first plate (31) and the second plate (32). In this state, the protrusions (76) formed on the flat plate portion (75) of the liquid guide plate (72) are connected to the heat transfer plate (3).
1,32). Therefore, a narrow gap is formed between the flat plate portion (75) of the liquid guide plate (72) and the heat transfer plates (31, 32), and the width of this gap is equal to the height of the projection (76). The leg (78) formed on the flat plate portion (75) of the liquid guide plate (72) contacts the upper end of the heat transfer portion (50) of the heat transfer plate (31, 32). Thereby, the liquid guide plate (72) is supported by the heat transfer plates (31, 32). Also,
A gap of 0.5 mm width is formed between the lower end of the flat plate portion (75) of the liquid guide plate (72) and the upper end of the heat transfer portion (50) of the heat transfer plates (31, 32).

As described above, the absorbing solution stored in the liquid reservoir (71) flows out through the liquid outlet (65). The outflowing absorbing solution first strikes the angled portion (73) of the liquid guide plate (72), and is guided to the gap between the flat plate portion (75) of the liquid guide plate (72) and the heat transfer plates (31, 32). . Thereafter, the absorbing solution passes through the gap between the lower end of the flat plate portion (75) and the upper end of the heat transfer portion (50), and is supplied on the entire surface of the heat transfer portion (50) on average.

-Heat exchange in the absorption heat exchanger / evaporation heat exchanger-In the plate heat exchanger (30) constituting the absorption heat exchanger (26), cooling water as the first liquid, Heat exchange takes place between the two liquid absorbing solutions.

The cooling water is first sent to the inflow path (43), and then distributed to each first space (41). The cooling water sent to the lower end of the first space (41) is guided by the baffle part (45) and flows upward while meandering left and right (see FIG. 4). Therefore, the first space (41)
In the above, no drift of the cooling water occurs. The cooling water exchanges heat with the absorbing solution while flowing through the first space (41), and absorbs the absorbed heat. Thereafter, the cooling water flows from the upper end of the first space (41) into the outflow channel (44). In the outflow path (44), the cooling water that has absorbed heat in each of the first spaces (41) merges.

On the other hand, the absorbing solution is first introduced into the liquid reservoir (71). The absorbing solution in the liquid reservoir (71) flows out through the liquid outlet (65), and is averaged over the entire surface of the heat transfer section (50) in the heat transfer plates (31, 32) by the liquid guide plate (72). (See FIG. 7). The absorbing solution flows down in the form of a liquid film along the surface of the heat transfer section (50) on the side of the second space (42). On the other hand, gas refrigerant (steam) from the evaporator (11, 12) is introduced into the second space (42). Then, the gas refrigerant is absorbed by the absorbing solution flowing along the heat transfer section (50). The absorbed heat generated at that time is the first
The absorption solution is deprived by the cooling water flowing through the space (41).

In the plate heat exchanger (30) constituting the evaporating heat exchanger (25), the heat transfer water as the first liquid and the second heat
Heat exchange is performed with a liquid refrigerant (water) that is a liquid.

The heat transfer water is first sent into the inflow channel (43), and then distributed to each first space (41). The heat transfer water sent to the lower end of the first space (41) is guided by the baffle part (45) and flows upward while meandering left and right (see FIG. 4). Therefore, the first space (41)
In this case, no drift of the heating medium water occurs. The heat transfer water exchanges heat with the liquid refrigerant while flowing through the first space (41), and radiates heat to the liquid refrigerant. Thereafter, the heat transfer water flows into the outflow path (44) from the upper end of the first space (41). This outflow channel (44)
Then, the heat transfer water radiated in each first space (41) merges.

On the other hand, the liquid refrigerant is first introduced into the liquid reservoir (71). The liquid refrigerant in the liquid reservoir (71) is supplied to the liquid outlet (65)
And is supplied to the entire surface of the heat transfer portion (50) of the heat transfer plate (31, 32) by the liquid guide plate (72) (see FIG. 7). The liquid refrigerant flows down in the form of a liquid film along the surface of the heat transfer section (50) on the side of the second space (42). Then, the liquid refrigerant exchanges heat with the heat medium water while flowing down along the heat transfer section (50), and absorbs heat from the heat medium water to evaporate. The evaporated refrigerant flows out of the second space (42),
It flows through the eliminator (24) to the absorbers (13, 14) (see FIG. 2).

-Shapes and arrangement of dimples on heat transfer plate-Shapes and arrangement of dimples (51) formed on heat transfer portion (50) of heat transfer plates (31, 32) are three types shown in FIG. Were determined after performing a performance test on the shape and the arrangement of.

The specifications of the performance test are as follows. The first specification (hereinafter referred to as specification A1)
The shape of the dimple (51) is a truncated cone having a top diameter of 6 mm, a bottom diameter of 10 mm, and a height of 2 mm, and a staggered arrangement of a horizontal pitch of 20 mm and a vertical pitch of 15 mm. Things. The second specification (hereinafter, specification A2)
The dimple (51) has a top diameter of 4
mm, a truncated cone with a bottom diameter of 10 mm and a height of 2 mm, and the arrangement was a staggered arrangement with a horizontal pitch of 20 mm and a vertical pitch of 15 mm. In the third specification (hereinafter referred to as specification B1), the shape of the dimple (51) is a truncated cone having a top diameter of 3.5 mm, a bottom diameter of 7.5 mm, and a height of 2 mm. The vertical pitch is 15 mm and the vertical pitch is 10 mm.

FIG. 10 shows the results of performance tests for the above three specifications when used as an absorption heat exchanger (26). In FIG. 10, the horizontal axis represents the liquid film flow rate of the absorbing solution flowing down the surface of the heat transfer plate (31, 32), and the vertical axis represents the heat transmission coefficient of the plate heat exchanger (30) in the specification. is there. As can be seen from FIG. 10, the heat transmission rate of the heat transfer plates (31, 32) of any specification increases as the liquid film flow rate increases. Also,
When comparing the heat transmission coefficients of the specification A1 and the specification B1, there is no clear significant difference between the two. On the other hand, when compared at the same liquid film flow rate, the heat transmission coefficient of the specification A2 is about 10% higher than the heat transmission coefficient of the specification A1 and the specification B1. Therefore, in the present embodiment, as described above, the dimple (5
As the shape and arrangement of 1), those of the above specification A2 are adopted.

In this embodiment, the absorption heat exchanger (2
6) The heat transfer plates (31, 32) of the plate heat exchanger (30) constituting the heat exchanger plates (31, 32) of the plate heat exchanger (30) constituting the heat exchanger for evaporation (25) 31,3
As for 2), dimples (5
As the shape and arrangement of 1), those of the above specification A2 are adopted. However, for absorption and evaporation,
The specification of the dimple (51) in the heat transfer plate (31, 32) may be changed.

-Effects of First Embodiment- In the plate heat exchanger (30) according to the present embodiment, the first space (41) and the second space (41) are arranged in the stacking direction of the heat transfer plates (31, 32).
Spaces (42) are alternately formed, and the outer edge of the second space (42) is open to the outside of the plate heat exchanger (30). That is, gas refrigerant can flow in and out between the second space (42) and the outside of the plate heat exchanger (30). Therefore, this plate heat exchanger (30)
It is possible to configure an absorber or an evaporator of the absorption refrigerator (10) using the above. As a result, the use of a high-performance plate heat exchanger (30) enables the absorption of the absorber (1).
3,14) and the evaporator (11,12) can be downsized.
As a result, the entire absorption refrigerator (10) can be reduced in size.

In the present embodiment, the heat transfer plate (3
The shape of the dimple (51) formed in the heat transfer section (50) of the (1,32) is frustoconical, and the adjacent heat transfer plates (31,3) are formed.
2) The dimples (51) are brought into contact with each other and brazed. Therefore, the joint portion between the adjacent heat transfer plates (31, 32) can be sufficiently secured, and the strength of the plate heat exchanger (30) can be increased. In particular, in the present embodiment, since the shape of the dimple (51) is a truncated cone, the contact portion between the dimples (51) is flat.
For this reason, reliable joining is possible by brazing and joining the contact portions of this plane.

According to the present embodiment, the sprayer (70)
Is provided, the absorbing solution and the liquid refrigerant can be supplied evenly over the entire surface of the heat transfer section (50) in the heat transfer plates (31, 32). For this reason, the absorbing solution and the liquid refrigerant can be reliably flowed in the form of a liquid film over the entire surface of the heat transfer section (50), and heat exchange can be performed by effectively using the entire heat transfer section (50). It is possible to do. Therefore, the performance of the plate heat exchanger (30) can be sufficiently exhibited.

Here, the heat transfer plates (31, 32) of the plate heat exchanger (30) according to the present embodiment are provided with a liquid reservoir (7).
Except for 1), it is vertically symmetric. Therefore, if the liquid reservoir (71) is formed not only at the upper end but also at the lower end of the heat transfer plates (31, 32), the overall shape of the heat transfer plates (31, 32) can be vertically symmetric. Thus, the heat transfer plate (3
If the heat transfer plate (31,3)
When forming 2) by pressing, the first plate (3
1) and the second plate (32) can be formed by the same mold. In other words, if the heat-transfer plates (31, 32) pressed are kept in the same posture, they become the first plate (31).
2) After pressing, the lower reservoir (7
By cutting out 1) and stacking the heat transfer plates (31, 32), the plate heat exchanger (30) according to the present embodiment is obtained.
Can be manufactured. Therefore, in this way, the heat transfer plates (31, 32) can be formed with one mold, and the manufacturing cost of the plate heat exchanger (30) can be reduced.

Modification of First Embodiment In the first embodiment, the surface of the heat transfer plate (31, 32) on the side of the second space (42), that is, the surface on which the absorbing solution or the liquid refrigerant flows, is used as the absorbing solution. Alternatively, a treatment for improving the “wettability” of the liquid refrigerant or the liquid refrigerant may be performed.

This type of treatment includes a heat transfer plate (3
1, 32) is a process of oxidizing the surface to form an oxide film. Specifically, the plate heat exchanger (30) assembled by brazing is heated to about 900 ° C. in an atmosphere in which air (oxygen) is present, and the stainless steel heat transfer plates (31, 32) are heated. The treatment is performed by oxidizing the surface.

As this type of treatment, there is a treatment of applying a hydrophilic agent to the surface of the heat transfer plate (31, 32). When this treatment is performed, the contact angle when the absorbing solution or the liquid refrigerant adheres to the surface of the heat transfer plate (31, 32) increases due to the action of the hydrophilic agent, and the heat transfer plate (31 , 32) is improved.

The surface of the heat transfer plate (31, 32) is subjected to a process for enhancing “wettability” so that the heat transfer plate (3
The liquid film of the absorbing solution or liquid refrigerant can be held over almost the entire surface of (1, 32). Therefore, the heat transfer plate (31, 32)
Heat exchange between the absorbing solution and the cooling water by effectively utilizing the entire surface of the
Alternatively, heat exchange between the liquid refrigerant and the heat transfer water can be performed,
The performance of the plate heat exchanger (30) can be reliably exhibited.

[0086]

Embodiment 2 Embodiment 2 of the present invention is different from Embodiment 1 in that dimples (51) are provided in the heat transfer portion (50) of the heat transfer plates (31, 32). A plurality of grooves (52) are formed in the heat transfer section (50) of the heat transfer plates (31, 32). Here, parts different from the heat transfer plates (31, 32) of the first embodiment will be described with reference to FIGS.
This will be described with reference to FIG.

FIG. 11 is a front view of the first plate (31) according to the second embodiment. In the first plate (31), the groove (52) is formed intermittently while meandering left and right from the lower end to the upper end of the heat transfer surface. Here, in the first space (41) of the plate heat exchanger (30),
Since the baffle part (45) is formed, the cooling water and the heat medium water meander right and left and flow. Therefore, groove (52)
Has a shape extending along the flow of cooling water or the like in the first space (41).

In the first plate (31), the groove (52)
Are recessed in the back side of the paper in FIG. As shown in FIG. 12, the groove (52) is formed so that its cross section is trapezoidal. About this groove (52),
The depth L is desirably 1.0 mm or more and 3.0 mm or less, and more desirably 1.6 mm or more and 2.0 mm or less.

On the other hand, the second plate (32) has a shape obtained by inverting the irregularities of the first plate (31). That is, the groove (52) formed in the second plate (32) has a shape protruding in the opposite direction to that of the first plate (31). When the first plate (31) and the second plate (32) are stacked, the groove (5) formed in each heat transfer plate (31, 32) is formed.
2) is recessed toward the first space (41), and the grooves (52) of the adjacent heat transfer plates (31, 32) are in contact with each other. Then, the adjacent heat transfer plates (31, 32) are brazed and joined in the abutting groove (52).

[Brief description of the drawings]

FIG. 1 is a piping diagram of an absorption refrigerator according to a first embodiment.

FIG. 2 is a schematic configuration diagram of a low-pressure cylinder according to the first embodiment.

FIG. 3 is a front view of the plate heat exchanger according to the first embodiment.

FIG. 4 is a plan view of a heat transfer plate (first plate) according to the first embodiment.

FIG. 5 is an enlarged sectional view of a dimple formed on a first plate according to the first embodiment.

FIG. 6 is an enlarged view of a main part of the plate heat exchanger according to the first embodiment.

FIG. 7 is an enlarged sectional view of a main part in FIG. 6;

FIG. 8 is a front view and a side view of the liquid guide plate according to the first embodiment.

FIG. 9 is a list showing shapes and arrangements of dimples subjected to a performance test.

FIG. 10 is a graph showing the results of a performance test, showing the relationship between the liquid film flow rate and the heat transmission coefficient.

FIG. 11 is a plan view of a heat transfer plate (first plate) according to a second embodiment.

FIG. 12 is an enlarged sectional view of a groove formed in a first plate according to the second embodiment.

[Explanation of symbols]

 (31) 1st plate (heat transfer plate) (32) 2nd plate (heat transfer plate) (41) 1st space (42) 2nd space (43) Inflow channel (communication passage) (44) Outflow channel (connection) Passage) (45) Baffle (51) Dimple (52) Groove

──────────────────────────────────────────────────の Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat ゛ (Reference) F28D 5/02 F28D 5/02 F28F 3/04 F28F 3/04 A (71) Applicant 000002853 Daikin Industries, Ltd. Umeda Center Building, 2-4-12 Nakazaki Nishi, Kita-ku, Osaka-shi, Osaka (72) Inventor Kazunori Matsumae 5-20, Kaigan, Minato-ku, Tokyo Tokyo Gas Co., Ltd. (72) Inventor Kenji Yamada Osaka-shi, Osaka Osaka Gas Co., Ltd., 1-3-1, Hokuko Shiratsu, Konohana-ku (72) Inventor Yuji Ozawa 507-2 Shinhocho, Tokai-shi, Aichi Prefecture Toho Gas Co., Ltd. (72) Inventor Mitsuharu Numata Sakai City, Osaka 1304 Okamachi Daikin Industries Kanaoka Plant, Sakai Plant Co., Ltd. (72) Inventor Kenji Yasuda 1304 Kanaokacho, Sakai City, Osaka Daikin Industries, Ltd. Inside the factory Kanaoka factory (72) Inventor Takahiro Doi 1304 Kanaokacho, Sakai City, Osaka Daikin Industries, Ltd. Inside the Sakai Factory Kanaoka Factory (72) Inventor Mitsugu Kawai 1304, Kanaokacho, Sakai City, Osaka Daikin Industries, Ltd. Kanaoka factory F-term (reference) 3L093 BB00 BB29 BB31 MM02 3L103 AA05 AA37 AA40 BB33 CC01 CC02 CC30 DD12 DD19 DD22 DD55 DD57 DD64

Claims (4)

[Claims] 1. A plate heat exchanger of an absorption refrigerator formed by alternately stacking a first heat transfer plate (31) and a second heat transfer plate (32) in a horizontal direction. In the stacking direction of the heat transfer plates (31, 32), a first space (41), which is a closed space surrounded by a pair of adjacent heat transfer plates (31, 32), and a first space (41) whose outer edge is open. Two spaces (42) are formed alternately, a pair of communication passages (43, 44) for communicating the first spaces (41) with each other is provided, and the first space (41) flowing through the first space (41) is provided. The liquid and the second liquid flowing along the surface of the heat transfer plate (31, 32) on the side of the second space (42) are subjected to heat exchange, while the heat transfer plate (31, 32) has a first liquid. A large number of dimples (51) depressed toward the space (41) are provided in a staggered arrangement with a horizontal pitch of 20 mm and a vertical pitch of 15 mm, Each of the dimples (51) is a plate-type heat exchanger of an absorption refrigerator having a truncated cone shape having a bottom diameter of 10 mm, a top diameter of 4 mm, and a depth of 2 mm. 2. A plate heat exchanger of an absorption refrigerator formed by alternately stacking a first heat transfer plate (31) and a second heat transfer plate (32) in a horizontal direction. In the stacking direction of the heat transfer plates (31, 32), a first space (41), which is a closed space surrounded by a pair of adjacent heat transfer plates (31, 32), and a first space (41) whose outer edge is open. Two spaces (42) are formed alternately, a pair of communication passages (43, 44) for communicating the first spaces (41) with each other is provided, and the first space (41) flowing through the first space (41) is provided. The liquid and the second liquid flowing along the surface of the heat transfer plate (31, 32) on the side of the second space (42) are subjected to heat exchange, while the heat transfer plate (31, 32) has a first liquid. A plurality of grooves (52) which are recessed toward the space (41) and extend along the flow direction of the first liquid in the first space (41) are provided at predetermined intervals; 52), the absorption refrigerator depth is formed so as to be 3.0mm or less trapezoidal cross section over 1.0mm plate heat exchanger. 3. The plate type heat exchanger of an absorption refrigerator according to claim 1, wherein the surface of the heat transfer plate (31, 32) on the side of the second space (42) is provided with respect to the second liquid. Heat transfer plate (31,32)
A plate heat exchanger of an absorption refrigerator, which has been treated to improve the wettability of the plate. 4. The plate type heat exchanger for an absorption refrigerator according to claim 1, wherein the first space (41) meanders left and right in the first space (41). Plate heat exchanger of absorption refrigerator equipped with baffle part (45) for flowing.