JPH1062033A - Absorption chiller / heater - Google Patents

Abstract

(57) [Summary] [Problem] To mount a plate heat exchanger in which a plurality of bag-shaped panels are stacked in an evaporator constituting an absorption type water heater / heater, including the cost of the shape of the heat transfer surface including the cost. Thus, the strength due to the pressure difference between the inside and outside of the panel 1 and the inside heat transfer coefficient due to an appropriate pressure loss and the outside heat transfer coefficient due to the improvement in wettability were improved. A horizontal groove is formed on an outer heat transfer surface of a panel. The ridges 14 were meandered vertically on the heat transfer surface so that the valleys 15 and 16 of the ridges 14 on both sides of the panel 11 intersected inside the panel 11. Refrigerant sprayed on the outer heat transfer surface can flow down while spreading in the horizontal direction by using the capillary action by the horizontal groove 4, so that the entire outer heat transfer surface can be wetted, thereby improving the outer heat transfer coefficient and moderate pressure loss. It is possible to improve the internal heat transfer coefficient and sufficiently maintain the strength due to the pressure difference between the inside and outside of the panel.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an absorption type chiller / heater used in an air conditioner and the like, and more particularly to an absorption type chiller / heater which can be downsized by improving the efficiency of a heat exchanger of each element. .

[0002]

2. Description of the Related Art Conventionally, for example, in the technique described in Japanese Utility Model Publication No. 1-44959, a plurality of plates constituting a plate heat exchanger consist of one kind of plate, and when stacked, two plates are disposed between each other. It is intended for a plate heat exchanger in which two openings corresponding to each medium are provided on the plate so that two medium passages are alternately formed.

According to the technique described in Japanese Patent Application Laid-Open No. 6-34239, a plate heat exchanger is formed from corrugated bellows fins formed by continuously bending a single thin plate, and peaks and valleys of the bellows fins. And a seal plate that seals the chamber to be closed at the end face, and has convex dimples in a zigzag pattern on the bellows fin surface.

[0004]

In the conventional plate heat exchanger described in Japanese Utility Model Publication No. 1-45959, all of the laminated plates are joined together at the periphery and at the opening, and both media are joined together. Since the closed space is a passage, as in the evaporator of an absorption chiller / heater, a passage is made in a space where one medium is sealed and heat transfer outside the space where the other medium is sealed. It is structurally impossible to use it for a heat exchanger that exchanges heat in a plane.

Further, in the configuration of the prior art plate heat exchanger described in Japanese Patent Application Laid-Open No. 6-34239, in order to improve the wettability of the outer side of the plate, a convex dimple is provided on the surface of the bellows fin, so that the heat transfer is achieved. The area is increased, and the sprayed refrigerant or solution spreads in the direction perpendicular to the flowing direction, and the wettability is improved. However, in this method, although it is considered that the wettability of the heat transfer surface on the side to be sprayed is slightly improved, the heat exchange efficiency is reduced because the heat transfer surface is recessed with respect to the inside of the plate, and the required heat exchange efficiency is obtained. If so, the size reduction, which is an advantage of the plate type, cannot be achieved.

The present invention has been made to solve the above-mentioned problems of the prior art, and an object of the present invention is to reduce the size of a heat exchanger mounted on an evaporator constituting an absorption chiller / heater. In addition, each of the above-mentioned heat exchangers has a heat exchange inside and outside the panel while maintaining the strength inside the bag-like panel constituting the plate heat exchanger. An object of the present invention is to provide an absorption chiller / heater having a plate heat exchanger with improved efficiency.

[0007]

SUMMARY OF THE INVENTION The object of the present invention is to provide an absorption type cooling and heating system in which a high-temperature regenerator, a low-temperature regenerator, a condenser, an evaporator, an absorber, a high-temperature heat exchanger, and a low-temperature heat exchanger are operatively connected by pipes. In the water machine, at least one of the low-temperature regenerator, the condenser, the evaporator, and the absorber forms a bag-shaped panel by joining inner contacting parts, in a state where a gap is formed between the panels, This is achieved by providing a plurality of plate heat exchangers arranged side by side by headers provided above and below, and providing a plurality of horizontal grooves on the outer heat transfer surface of a bag-like panel constituting the plate heat exchanger.

[0008] Further, this is achieved by providing an opening in each of the upper and lower portions of the panel, and providing a horizontal groove over substantially the entire outer heat transfer surface excluding a region where the opening is present. .

Further, the present invention is achieved by forming a ridge in which concave portions and convex portions are continuous on the heat transfer surface of the panel constituting the plate heat exchanger.

[0010] The horizontal groove provided on the heat transfer surface of the panel constituting the plate heat exchanger is achieved by having a groove width in the range of 0.05 to 0.5 mm.

Further, the horizontal groove provided on the heat transfer surface of the panel constituting the plate heat exchanger is achieved by setting the groove depth to not more than 1/2 of the panel thickness.

Further, the horizontal groove provided on the heat transfer surface of the panel constituting the plate heat exchanger is achieved by being cut by machining.

The horizontal grooves formed on the heat transfer surface of the panel constituting the plate heat exchanger are achieved by being formed by plastic working.

Further, the horizontal grooves formed on the heat transfer surface of the panel constituting the plate heat exchanger are achieved by being formed by laser processing.

Further, the panel constituting the plate heat exchanger is achieved by providing an oxide film treatment after providing the horizontal grooves.

The panel constituting the plate heat exchanger is achieved by providing a horizontal groove and then applying a hydrophilic coating material.

Further, in the panel constituting the plate heat exchanger, the outer heat transfer surface on which the horizontal grooves are machined is achieved by having a contact angle with water of 50 ° or less.

[0018]

Embodiments of the present invention will be described below with reference to the drawings. First, the main configuration and operation of the absorption chiller / heater will be described with reference to the flowchart of FIG. Absorption chiller / heater includes high temperature regenerator 301, low temperature regenerator 302, condenser 303, evaporator 304, absorber 305, low temperature heat exchanger 306, high temperature heat exchanger 3.
The system is composed of seven heat exchanger elements 07, a solution pump 308 for circulating the absorbing solution, and a pipe connecting them.

The operation of the cooling operation will be described. During the cooling operation, the refrigerant vapor generated by concentrating the solution of the high-temperature regenerator 301 heated by the external heat source is led to the heat exchanger 302a in the low-temperature regenerator 302 to heat and concentrate the solution of the low-temperature regenerator 302. The refrigerant vapor is generated, condensed and liquefied, and flows into the condenser 303. The refrigerant vapor generated in the low-temperature regenerator 302 is
Is cooled by cooling water and condensed and liquefied.
The refrigerant from 1 is sent to the evaporator 304 via a valve. The liquid refrigerant in the evaporator 304 is supplied to the heat exchanger 304a in the evaporator 304.
Is exchanged with the cold water flowing through the heat exchanger 304a to evaporate and flow into the absorber 305. The cooling effect is exerted by the latent heat of evaporation at that time. In the absorber 305, the high temperature regenerator 3
01 and the concentrated solution concentrated in the low-temperature regenerator 302
It is sprayed to the heat exchanger 305a in the inside, is cooled by the cooling water flowing in the heat exchanger 305a, absorbs the refrigerant vapor from the evaporator 304, and generates a dilute solution. Dilute solution of absorber 305
08 is divided into two parts via the low-temperature heat exchanger 306, one is supplied to the low-temperature regenerator 302, and the other is further supplied to the high-temperature heat exchanger 3
It is supplied to the high temperature regenerator 301 via 07. The cooling cycle is configured as described above.

The difference between the heating operation and the cooling operation will be described. During the heating operation, since the cooling water does not flow through the absorber 305 and the condenser 303, the refrigerant vapor guided from the low temperature regenerator 302 in the condenser 303 is sent to the evaporator 304 at a high temperature without being condensed and liquefied. When the cooling / heating switching valve 310 is opened, the high-temperature solution and the refrigerant vapor are directly guided from the high-temperature regenerator 301 to the absorber 305. The refrigerant vapor is sent to the evaporator 304 without being cooled in the absorber 305, and heats the hot water flowing in the heat exchanger 304a in the evaporator 304 together with the refrigerant vapor from the condenser 303. The heating cycle is configured as described above.

FIG. 2 shows an embodiment of a panel constituting a plate heat exchanger according to the present invention. The panel 1 is formed into a bag-like shape by adhering portions that are in contact with each other on the inside, and the cold water is applied to the panel. An opening 2 and an opening 3 for inflow and outflow into the inside, and a structure in which the opening 2 and the opening 3 are provided at the same position on the back surface of the panel 1 as viewed in FIG. Is provided with a horizontal groove 4. That is, the openings 2, 3
The horizontal groove 4 is provided over almost the entire outer heat transfer surface except for the region having the ridge.

In the present invention, at least one of the low temperature regenerator 302, the condenser 303, the evaporator 304, and the absorber 305 is constituted by a plate heat exchanger. The plate heat exchanger is configured by arranging a plurality of panels each having an inner contacting portion bonded and formed into a bag shape by headers provided vertically above and below each other with a gap provided between the panels. A plurality of horizontal grooves are provided on the outer heat transfer surface of the bag-like panel constituting the plate heat exchanger.

Next, the structure of the plate heat exchanger 100 including the panel 1 as a component will be described in detail with reference to FIG. A plurality of panels 1 are juxtaposed, that is, stacked, in accordance with the refrigerating capacity of the absorption type water heater. The panels 1 are communicated with each other by a header 5 in an opening 2 provided in the panel 1 and a header 6 in an opening 3 provided in the panel 1.
Is communicated by The gap between the panels 1 is 1 mm or more and communicates with the external space of the plate heat exchanger 100.
In addition, only one surface of one panel 1 located at both ends of the plate heat exchanger is not provided with the opening 2 and the opening 3 (not shown), and the other surface of the panel 1 is connected to the opening 2 by piping. 7 is connected, and the pipe 8 is connected to the opening 3.

FIG. 4 is an enlarged view of a cross section of the horizontal groove 4. The horizontal groove 4 provided on the outer heat transfer surface of the panel 1 will be described. The horizontal groove 4 is machined to a plate thickness t by a groove depth h, and the value of the groove depth h is 1/2 or less of the plate thickness t. The pitch P of each horizontal groove 4 is, for example, 1 mm, and the groove width W of each horizontal groove 4 is processed within a range of 0.05 to 0.5 mm or less.

Next, the heat exchange operation of the plate heat exchanger 100 shown in FIG. 3 will be described. During cooling operation in the evaporator of the absorption type water heater, cold water flows into each panel 1 from the pipe 7 via the header 5, flows out from the pipe 8 via the header 6, and condenses from the upper part of the plate heat exchanger 100. The refrigerant liquefied and condensed in the vessel is sprayed. The refrigerant sprayed on each panel 1 exchanges heat with cold water via the heat transfer surface of panel 1 to evaporate and evaporate, and the latent heat of evaporation at that time exerts cooling.

At this time, what is important in improving the heat exchange efficiency is the wettability of the outer heat transfer surface of each panel 1.
The plate heat exchanger has a small amount of water and has a corrugated shape on the heat transfer surface, so heat exchange efficiency can be improved in proportion to pressure loss, which is an effective means for miniaturization. is there. However, the plate heat exchanger generally has a structure in which two liquids alternately flow in a closed space, and is different from the embodiment shown in FIG. Therefore, when the heat transfer coefficient is determined by design, the heat transfer coefficient inside the cold water flowing through the panel 1 can be considered in the same manner as a plate heat exchanger having a structure in which two liquids alternately flow in a closed space. ,
With respect to the heat transfer coefficient of the outside of the refrigerant sprayed on the outside of the panel 1, it is a necessary condition that the heat transfer surface is entirely wet by the coolant, and a means for wetting the heat transfer surface is required. Therefore, the horizontal groove 4 is formed on the heat transfer surface as in the embodiment shown in FIG.

Next, the situation where the sprayed refrigerant flows down the heat transfer surface of the panel 1 will be described with reference to FIG. For example, a
Assuming that the refrigerant is sprayed from a point, the refrigerant can spread horizontally in the horizontal groove 4 like the refrigerant 10 by capillary action and then flow down to the next horizontal groove 4, and as a result, as shown in FIG. Surface 9 is formed. Therefore, in each panel 1 constituting the plate heat exchanger 100, by spraying the refrigerant from one or several places on the heat transfer surface of each panel 1, the entire heat transfer surface of each panel 1 can be wetted.

The horizontal groove 4 for improving the wettability is provided.
In the capillary phenomenon due to, the contact angle of the target surface is important. The contact angle θ is, as shown in FIG.
9 is dropped on a flat plate having a surface in the same state as the target surface, and the diameter L and height H of the droplet 29 at this time are measured and defined by the formula (1).

Tan (θ / 2) = H / (L / 2) (1) In order to effectively use the capillary phenomenon, it is necessary to reduce the contact angle θ shown in FIG. If the contact angle of the material is 50 ° or more, it is necessary to reduce the contact angle θ to 50 ° or less by, for example, an oxide film treatment or the application of a hydrophilic coating material. Thereby, the horizontal groove 4 is an effective means for improving the wettability.

At this time, if the groove width W of each horizontal groove 4 is less than 0.05 mm, the groove width W becomes too small and the sprayed refrigerant cannot be held in each horizontal groove 4, so that the capillary phenomenon cannot be used and Improve the performance.

Conversely, if the width W of each horizontal groove 4 is larger than 0.5 mm, the amount of refrigerant retained in each horizontal groove 4 will increase too much, and the liquid film will be thick and will have thermal resistance. It is not an effective means of improving performance.

Next, a plate heat exchanger according to FIGS.
The shape of the heat transfer surface of another embodiment different from the heat transfer surface of each panel 1 constituting 100 will be described. Regarding the shape of the heat transfer surface, it is necessary to consider the strength due to the pressure difference between the inside and outside of the panel 1, including the cost, the improvement of the inner heat transfer coefficient by the appropriate pressure loss, and the improvement of the outer heat transfer coefficient by the improvement of the wettability. is there.

The panel 11 constituting the plate heat exchanger 100 shown in FIG. 6 will be described. The panel 11 is provided with openings 12 and 13 through which cold water flows in and out, and a ridge 14 in which concave portions and convex portions are continuous meanders vertically on a heat transfer surface serving as an upper surface in the drawing, in which the horizontal groove 4 is formed. Is provided. A ridge 14 in which the same concave portions and convex portions as the front surface are continuous is also provided on the heat transfer surface serving as the upper back surface in the figure where the horizontal groove 4 is processed.

The ridges 14 on both sides of the panel 11 will be described with reference to FIGS. FIG. 7 shows a part of the heat transfer surface of the panel 11 shown in FIG. 6, 15 is a valley of the ridge 14 on the upper surface in the figure, and 16 is a valley of the ridge 14 on the upper surface in the figure. When they are overlapped, for example, the respective valleys 15 and 16 are arranged so as to be symmetrical about a line O connecting the points 17 where the respective valleys 15 and 16 contact each other inside the panel 11 in the vertical direction. At this time, the points 17 that are in contact with each other inside the panel 11 are arranged in a staggered manner, and the points 17 are bonded by, for example, brazing. In order to arrange them in a staggered manner, the relationship between the pitch b of the valleys 15 and 16 of each ridge 14 and the amplitude c of the valleys 15 and 16 of the ridge 14 needs to be as shown in Expression (2). FIG. 7 shows the case where n = 2.

C ≧ n × b (2) (where n ≧ 1) With the above arrangement, the cold water flowing inside is arranged in a staggered manner in the narrow space inside the panel 11. As a result, a vortex is generated and an appropriate pressure loss can be provided, so that the internal heat transfer coefficient can be improved. Furthermore, the points 1 arranged in a staggered manner in contact with the inside of the panel 11
7, the strength against the pressure difference between the inside and outside of the panel 11 during operation can be maintained.

Next, the flow of the refrigerant on the outer heat transfer surface of the panel 11 will be described. The mainstream of the refrigerant sprayed from the upper part of the plate heat exchanger 100 is formed in the valleys 15 and 16 of each ridge 14 on the heat transfer surface of each panel 11, and each valley 1
It flows meandering along 5,16. Further, the horizontal grooves 4 can be made to flow down while spreading in the horizontal direction by utilizing the capillary phenomenon accompanying the main flow. further,
By meandering the main flow, the force flowing down the main flow can be dispersed in the horizontal direction, so that it can be expanded in the horizontal direction by a synergistic effect with the capillary action of the horizontal groove 4, and the peaks (not shown) of the ridges 14 can be formed. The entire heat transfer surface of the panel 11 can be wetted and the outside heat transfer coefficient can be improved.

The panel 18 constituting the plate heat exchanger 100 shown in FIG. 8 will be described. The panel 18 is provided with openings 19 and 20 through which cold water flows in and out, and a ridge 21 is provided on the heat transfer surface on which the horizontal groove 4 is machined so as to meander horizontally.

The ridge 21 will be described with reference to FIGS.
FIG. 9 shows a part of the heat transfer surface of the panel 18 shown in FIG.
Reference numeral 22 denotes a valley of the ridge 21 on the upper surface in the figure, and 23 denotes a valley of the ridge 21 on the upper surface in the figure. When they are overlapped, for example, they are arranged so as to be symmetrical with a line Q connecting the points 24 where the respective valleys 22 and 23 are in contact with each other inside the panel 18 in the horizontal direction. At this time, the points 24 that are in contact with the inside of the panel 18 are arranged in a staggered manner, and the points 24 are bonded by, for example, brazing. In order to arrange the ridges 21 in a staggered manner, the relationship between the pitch d of the valleys 22 and 23 of each ridge 21 and the amplitude e of the valleys 22 and 23 of the ridges 21 needs to be as shown in Expression (3). FIG. 8 shows the case where n = 2.

E ≧ n × d (2) (where n ≧ 1) With the above arrangement, the cold water flowing inside is arranged in a staggered manner in the narrow space inside the panel 18. As a result, a vortex is generated and an appropriate pressure loss can be provided, so that the internal heat transfer coefficient can be improved. Furthermore, points 2 arranged in a zigzag pattern in contact with the inside of the panel 18
4, the strength against the pressure difference between the inside and outside of the panel 18 during operation can be maintained.

Next, the flow of the refrigerant on the outer heat transfer surface of the panel 18 will be described. The refrigerant sprayed from the upper part of the plate heat exchanger 100 crosses the ridge 21 (not shown) of the ridge 21 which is meandering laterally, and the refrigerant which cannot be exceeded meanders sideways. Valleys 22 of ridges 21
A main stream is formed at the lower part along 23 and flows down. In addition, the horizontal grooves 4 allow the refrigerant to flow down while spreading in the horizontal direction by utilizing the capillary phenomenon along with the flow of the refrigerant or the main stream that has flowed over the ridges of the ridges 21, so that the entire heat transfer surface of the panel 18 can be wetted. And the heat transfer coefficient on the outside can be improved.

The horizontal groove 4 described above is formed before the shape of the heat transfer surface is formed when the side to be processed directly touches the heat transfer surface, as in the case of forming by machining or plastic working. In the case where the side to be processed is processed with a certain distance from the heat transfer surface as in laser processing, the processing can be performed before or after the shape of the heat transfer surface is formed. Although the inner heat transfer surface in the cross-sectional view shown in FIG. 4 is flat, when the horizontal groove 4 is formed by plastic working, the inner heat transfer surface is deformed depending on the ratio of the groove depth h shown in FIG. May occur.

The shape of the horizontal groove 4 shown in FIG. 4 is rectangular for the sake of explanation. However, the present invention is not limited to this. The trapezoidal horizontal groove 25 shown in FIG. There are shapes such as a triangular horizontal groove 26, a trapezoidal horizontal groove 27 which is the reverse of FIG. 9 shown in FIG. 12, and a semicircular horizontal groove 28 shown in FIG. 13, and these horizontal grooves 25 shown in FIGS. , 2
6, 27 and 28 can obtain the same operation and effect as the horizontal groove 4 shown in FIG.

The evaporator constituting the absorption chiller / heater has been described above. However, the present invention is not limited to this, and similarly to the evaporator, the low-temperature regenerator or the absorber in which the wettability of the outer heat transfer surface affects the heat transfer performance. Also, as for the condenser and the condenser, a plate heat exchanger 100 having a structure shown in FIG. Similar effects can be obtained.

[0044]

The horizontal groove 4 is formed on the heat transfer surface of the panel 1 constituting the plate heat exchanger 100, so that the panel 1
Since the refrigerant sprayed on the outer heat transfer surface can flow down while spreading in the horizontal direction by utilizing the capillary phenomenon, the entire outer heat transfer surface can be wetted, and the outer heat transfer coefficient can be improved.

Further, the panel 1 constituting the plate heat exchanger 100 is formed such that the ridges 14 meander vertically on the heat transfer surface as in the panel 11 of another embodiment, and the ridges 14 on both sides inside the panel 11. The points 17 where the valleys 15 and 16 intersect are bonded to each other, or the ridges 21 meander sideways on the heat transfer surface like the panel 18, and the valleys 22 of the ridges 21 on both sides inside the panel 18.
By bonding the point 24 where the points 23 and 23 intersect, the point 17
And the points 24 can be arranged in a staggered manner, so that an appropriate pressure loss improves the inner heat transfer coefficient, and the panel 1
The strength due to the pressure difference between the inside and outside of 1, 18 can be sufficiently maintained.

[Brief description of the drawings]

FIG. 1 is a cycloflow diagram for one embodiment of the present invention.

FIG. 2 is a view showing one embodiment of a panel of the plate heat exchanger according to the present invention.

FIG. 3 is a diagram showing an embodiment of the configuration of the plate heat exchanger according to the present invention.

4 is a diagram showing a part of a cross-sectional enlarged view of a panel heat transfer surface shown in FIG. 2 according to the present invention.

FIG. 5 is a view showing a flowing down state of a refrigerant sprayed on the heat transfer surface outside the panel shown in FIG. 2 according to the present invention.

FIG. 6 shows a second panel of the plate heat exchanger according to the present invention.
It is a figure showing an embodiment.

FIG. 7 is a detailed view of a structure of a heat transfer surface of the panel shown in FIG.

FIG. 8 shows a third panel of the plate heat exchanger according to the present invention.
It is a figure showing an embodiment.

9 is a detailed view of a structure of a heat transfer surface of the panel shown in FIG.

FIG. 10 is a diagram showing a modification of the embodiment of FIG. 4;

FIG. 11 is a diagram showing a modification of the embodiment of FIG. 4;

FIG. 12 is a diagram showing a modification of the embodiment of FIG. 4;

FIG. 13 is a diagram showing a modification of the embodiment of FIG. 4;

FIG. 14 is an explanatory diagram of a contact angle.

[Explanation of symbols]

1, 11, 18 ... panel, 4 ... horizontal groove, P ... pitch of horizontal groove 4, W ... width of horizontal groove 4, h ... depth of horizontal groove 4, t ...
9: Wet heat transfer surface, 10: Refrigerant expanded by capillary action in horizontal groove 4, 14: Vertically meandering ridge, 1
5 valleys of ridges 14 on the front surface, 16 valleys of ridges 14 on the back surface,
17: a point where the valleys 15 and 16 are in contact on the inside of the panel 11, O: a line connecting the points 17 in the vertical direction, b: a ridge 14
Pitch of the valleys 15, 16; c ... valleys 15, 1 of the ridge 14
6 amplitude, 21... Meandering ridge, 22... Surface ridge 21
Valley part, 23 ... valley part of ridge 21 on the back surface, 24 ... point where valley parts 22 and 23 are in contact inside panel 18, Q ... line connecting points 24 in the horizontal direction, d ... valley of ridge 14. Pitch of parts 22, 23, e ... amplitude of valley parts 22, 23 of ridge 14

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Akiki Igarashi 603, Kandachicho, Tsuchiura-shi, Ibaraki Pref. Hitachi Tsuchiura Engineering Co., Ltd.

Claims (12)

[Claims] 1. An absorption chiller / heater in which a high-temperature regenerator, a low-temperature regenerator, a condenser, an evaporator, an absorber, a high-temperature heat exchanger, and a low-temperature heat exchanger are operatively connected by piping. At least one of the condenser, the evaporator, and the absorber has a plurality of panels formed by joining inner contacting parts into a bag shape, with a gap being formed between the panels, by means of headers provided above and below. An absorption type chiller / heater comprising a plurality of plate heat exchangers, wherein a plurality of horizontal grooves are provided on an outer heat transfer surface of a bag-like panel constituting the plate heat exchanger. 2. The panel according to claim 1, wherein openings are provided in upper and lower portions of the panel, respectively.
A horizontal groove is provided over substantially the entire outer heat transfer surface except for a region having the opening. 3. The absorption type cold / hot water according to claim 1, wherein a ridge in which a concave portion and a convex portion are continuous is formed on a heat transfer surface of a panel constituting the plate heat exchanger. Machine. 4. The horizontal groove provided on the heat transfer surface of the panel constituting the plate heat exchanger has a groove width in the range of 0.05 to 0.5 mm. Absorption chiller / heater described. 5. The horizontal groove provided on the heat transfer surface of the panel constituting the plate heat exchanger has a groove depth of 1/2 of the panel thickness.
The absorption chiller / heater according to any one of claims 1 to 4, wherein: 6. The plate according to claim 1, wherein the horizontal groove provided on the heat transfer surface of the panel constituting the plate heat exchanger is cut by machining. Absorption chiller / heater. 7. The plate according to claim 1, wherein the horizontal groove formed on the heat transfer surface of the panel constituting the plate heat exchanger is formed by plastic working. Absorption chiller / heater. 8. The plate according to claim 1, wherein the horizontal groove formed on the heat transfer surface of the panel constituting the plate heat exchanger is formed by laser processing. Absorption chiller / heater. 9. The absorption type panel according to claim 1, wherein the panel constituting the plate heat exchanger is subjected to an oxide film treatment after forming a horizontal groove. Hot and cold water machine. 10. The panel constituting the plate heat exchanger,
The absorption type water cooler / heater according to any one of claims 1 to 8, wherein a hydrophilic coating material is applied after the horizontal grooves are provided. 11. A panel constituting a plate heat exchanger, wherein an outer heat transfer surface formed with a horizontal groove has a contact angle with water.
The absorption chiller / heater according to any one of claims 1 to 10, wherein the angle is 50 ° or less. 12. An absorption chiller / heater in which a high-temperature regenerator, a low-temperature regenerator, a condenser, an evaporator, an absorber, a high-temperature heat exchanger, and a low-temperature heat exchanger are operatively connected by piping. Each of the condenser, the evaporator and the absorber is composed of a plate heat exchanger in which a plurality of bag-shaped panels are juxtaposed, and a large number of pouch-shaped panel outer heat transfer surfaces constituting the plate heat exchanger are provided. An absorption type water cooler / heater characterized by being provided with a horizontal groove.