JP2002081883A - Plate heat exchanger and absorption refrigerating machine comprising it - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize a plate heat exchanger in which a part noncontributable to heat transfer is reduced. SOLUTION: Heat transfer plates 1A and 1B for use in a plate heat exchanger are provided with passage holes 10-17 at respective corners. In the center of the heat transfer plate, corrugations 27 and 28 are formed while inclining from the one lateral end side to the other lateral end side of the heat transfer plate. A plurality of horizontal protrusions and recesses 25 and 26 continuous to the inclining corrugations are formed around the passage holes 11 and 14 serving as inflow holes. Fluid exiting the passage holes 11 and 14 reaches the vicinity of the passage holes 10 and 15 thus reducing a dead space where the fluid does not flow.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a plate heat exchanger, and more particularly to a plate heat exchanger and an absorption refrigerator suitable for use as a solution heat exchanger of an absorption refrigerator.

[0002]

2. Description of the Related Art Examples of conventional plate heat exchangers are disclosed in JP-A-6-241672, JP-A-11-248392 and JP-A-11-248392.
No. 1-514715. In each of these publications, a plate or a V-shaped projection or groove is formed substantially at the center of the plate constituting the plate heat exchanger. In the plate heat exchanger described in JP-A-6-24172, medium passage holes are formed at four corners of the heat transfer surface of the heat transfer plate, and a plurality of the heat transfer plates are stacked and interposed between each other. Two types of medium flow paths are formed alternately. In the center rectangular part of the heat transfer surface of the heat transfer plate and the substantially triangular part of the upper and lower outer sides of the rectangular part,
An uneven pattern is formed. A bead-like projection is formed near the top of the upper portion of the triangular portion, and an oval protrusion is formed below the lower portion.

Further, in the plate heat exchanger described in Japanese Patent Application Laid-Open No. H11-248392, a wave-shaped heat transfer promoting surface is formed on the surface of a rectangular heat transfer plate, and refrigerant flow is formed at four corners. An inlet and an outlet are formed. Around the inlet and the outlet, a plurality of ribs for suppressing the drift of the refrigerant in the flow path are provided. In addition, Tokio Table 11-514
In US Pat. No. 715, a radial waveform is formed around the inlet and outlet openings of a plate heat exchanger that uses a surrounding gasket to seal off a heat releasing or absorbing medium.

[0004]

In any of the above publications, the heat exchange performance in the corrugated portion or the heat exchange medium flow path formed substantially at the center of the plate heat exchanger is the intended purpose. The performance has been improved to such an extent that it can be achieved. However, in order to reduce the size of the heat exchanger, it is essential to improve the heat exchange performance around the opening through which the heat exchange medium flows. Conventionally, around this opening is not used as a dead space, or the heat exchange medium is evenly distributed to the corrugated part formed in the center of the plate,
It was only used as a distribution channel for the heat exchange performance of the plate heat exchanger.

For example, in Japanese Patent Application Laid-Open No. 6-241672, a bead-shaped projection or an oval-shaped projection is formed in a triangular portion below the left and right openings, and the flow rate of the refrigerant is reduced at the center of the heat transfer surface. To be evenly distributed. However, in this publication, the heat exchange performance of the triangular portion is not sufficiently considered.

In Japanese Patent Application Laid-Open No. H11-248392, ribs are formed substantially radially around the opening so as to guide the heat transfer fluid smoothly and uniformly to the main heat transfer promotion surface. However, this publication does not consider improving the heat exchange performance around the left and right openings.

Further, Japanese Patent Publication No. 11-514715 discloses that
It is described that a corrugated portion is radially formed around an opening of a plate heat exchanger which is sealed using a gasket, and a gasket is arranged in this portion to make the pressing force of the gasket uniform. However, even in this publication, there is no description about improving the heat exchange performance around the opening. That is, there is no description in any of the above publications to realize a plate heat exchanger capable of improving both the heat exchange performance around the opening and the distribution of the refrigerant.

The present invention has been made in view of the above-mentioned disadvantages of the related art, and has as its object to improve the heat exchange performance of a plate heat exchanger. Another object of the present invention is to
It is to improve the reliability of a plate-type heat exchanger having a welding structure. Still another object of the present invention is to reduce the size of a plate heat exchanger used in an absorption refrigerator. It is an object of the present invention to achieve any of these objects.

[0009]

A first feature of the present invention to achieve the above object is that a passage hole into which a first fluid flows, a passage hole through which a first fluid flows out, and a passage hole through which a second fluid flows. A plurality of heat transfer plates, each formed with a passage hole into which an inflow passage and a passage hole through which a second fluid flows out, are stacked, and a first heat exchanger through which a first fluid flows in a plate heat exchanger housed in a container. The flow path and the second flow path through which the second fluid flows are formed exclusively by forming a plurality of irregularities on the plurality of heat transfer plate surfaces, and at least one of the irregularities is formed around the heat transfer plate. .

A second feature of the present invention to achieve the above object is that a passage hole into which a first fluid flows, a passage hole through which a first fluid flows out, a passage hole through which a second fluid flows, and a second passage hole. A plurality of heat transfer plates each having a passage hole through which the fluid of the second fluid is formed are stacked, and in the plate heat exchanger housed in the container, the first flow path through which the first fluid flows and the second The second flow path through which the fluid flows is formed exclusively by forming a plurality of irregularities on the plurality of heat transfer plate surfaces, and at least one of the irregularities is substantially parallel to the periphery of the heat transfer plate. Having the first fluid is a dilute solution supplied from the absorber, and the second fluid is a concentrated solution supplied from at least one of the high-temperature regenerator and the low-temperature regenerator. Plate heat exchanger.

A third feature of the present invention for achieving the above object is that a passage hole into which a first fluid flows, a passage hole through which a first fluid flows out, a passage hole through which a second fluid flows, and a second passage hole. A plurality of heat transfer plates each having a passage hole through which the second fluid flows out are stacked, and in a plate heat exchanger housed in a container, a plurality of first flow passages through which the first fluid flows and a second flow passage are provided. A plurality of second flow paths through which the second fluid flows are formed exclusively by forming a plurality of irregularities on the plurality of heat transfer plate surfaces, and the first flow path and the second flow path are both formed. An inclined flow path from one end to the other end in the width direction of the heat transfer plate and one end of a passage hole into which at least one of the first fluid and the second fluid flows, and the other end is bent and bent. And a U-shaped flow path extending to the end of the heat transfer plate in the width direction. It is desirable that the U-shaped channel is formed substantially horizontally or vertically at the passage hole.

A fourth feature of the present invention to achieve the above object is that the present invention has a regenerator, a condenser, an evaporator, and an absorber, and generates cold water by cold heat generated by evaporation of a refrigerant in an evaporator. In the absorption refrigerator, a solution heat exchanger for heat exchange between the diluted solution sprayed on the absorber and the concentrated solution generated by concentrating the diluted solution in the regenerator is provided. A plurality of heat transfer plates each having a passage hole into which a passage hole into and a passage hole through which a concentrated solution flows and a passage hole through which a concentrated solution flows are formed and accommodated in a container. A plurality of dilute solution flow paths and a concentrated solution flow path through which the concentrated solution flows are formed exclusively by forming a plurality of irregularities on the surface of the plurality of heat transfer plates. The path is an inclined channel from one end to the other in the width direction of the heat transfer plate. And a substantially horizontal or substantially vertical portion having one end in the passage hole through which at least one of the dilute solution and the concentrated solution flows, and a continuous transmission to the horizontal or vertical portion. And a slanted flow path extending substantially parallel to the slanted flow path and extending to the widthwise end of the heat plate.

[0013] The coolant may be water, the solution may be a lithium bromide solution, and the passage hole may be formed near the corner of each heat transfer plate.

A fifth feature of the present invention to achieve the above object is that a plurality of heat transfer plates provided with passage holes serving as fluid inlets / outlets at four corners are laminated, and a space interposed between these heat transfer plates is provided. In the plate heat exchanger in which the first fluid and the second fluid flow alternately, a plurality of inclined waveforms are formed on the heat transfer plate, and at least one end of the inclined waveform has a passage hole. , A waveform in a substantially horizontal or substantially vertical direction is provided continuously to the inclined waveform.

The inclined waveform formed on the heat transfer plate has an inverted shape in the stacked adjacent heat transfer plates, and the waveform of the adjacent heat transfer plates intersects to generate a contact point. The first flow path and the second flow path may be formed exclusively, or the outer periphery of a pair of heat transfer plates may be welded to form a heat transfer plate in a bag shape, and the inner edges of the passage holes at the four corners may be welded. The stacked heat transfer plates are placed in a container, and a first flow path flowing inside the bag-shaped heat transfer plate and a second flow path flowing outside the bag-shaped heat transfer plate are formed. It may be formed.

[0016]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Some embodiments of the present invention will be described below with reference to the drawings. First, FIG. 4 shows a cycle diagram of an absorption refrigerator using the plate heat exchanger handled in the present invention. The absorption refrigerator 100 uses lithium bromide for the solution and water for the refrigerant. Heat generated by burning fuel such as city gas or waste heat generated in a combined cycle or the like heats the solution in the high-temperature regenerator 60 to generate refrigerant vapor. The generated refrigerant vapor is guided to the low-temperature regenerator 62 via a pipe 80, cooled by a dilute solution guided from an absorber 68 described later, and a part thereof is condensed. The refrigerant vapor that has not been condensed in the low-temperature regenerator 62 is guided to the condenser 64, and is cooled and condensed by the cooling water flowing in the heat transfer tube 90 arranged in the condenser 64. This condensed liquid refrigerant is
The refrigerant is guided to the evaporator 66 via 96, is provided at the tip of the pipe 94, and is sprayed from the refrigerant spraying device 54 disposed above the evaporator 66.

The refrigerant sprayed in the evaporator 66 cools the water flowing through the heat transfer pipe 92 arranged in the evaporator 66 to make it cold water. The refrigerant vapor that has been sprayed and evaporated flows into the absorber 68 through an eliminator provided at the boundary between the evaporator 66 and the absorber 68, and is absorbed by the solution sprayed in the absorber 68. The refrigerant that has not evaporated in the evaporator 66 is stored in a refrigerant tank 50 formed at the lower part of the evaporator 66, and is passed by a refrigerant pump 74 via a pipe 94 to a refrigerant spraying device.
Returned to 54.

In the absorber 68, a heat transfer tube 90 is arranged. The heat transfer tube 90 is guided from the absorber 68 to the condenser 64. Cooling water flows through the heat transfer tube 90. After leaving the condenser 64, the cooling water is cooled by exchanging heat with a cooling tower or the like (not shown) and returned to the absorber 68 again.

A concentrated solution obtained by evaporating and condensing the refrigerant in the high temperature regenerator 60 and the low temperature regenerator 62 is led to the absorber 68. The concentrated solution is sprayed on the surface of the heat transfer tube 90 in the absorber 68 from the solution spraying device 56 provided at the tip of the pipe 88. The refrigerant sprayed in the absorber 68 absorbs the refrigerant and is diluted to become a dilute solution, and is stored in a solution tank 52 provided below the absorber. The diluted solution in the solution tank 52 is supplied to the high-temperature regenerator 60 and the low-temperature regenerator by the solution pump 72.
Sent to 62.

Here, a dilute solution is sent from the absorber 68 to the high-temperature regenerator 60 and the low-temperature regenerator 62, and a concentrated solution is sent from the high-temperature regenerator 60 and the low-temperature regenerator 62 to the absorber 68. Therefore, a solution heat exchanger 70 is provided to promote heat exchange between the dilute solution and the concentrated solution. Solution heat exchanger 70
Then, in the case of the present embodiment, the low-temperature regenerator 62
A pipe 84 for sending the dilute solution is branched and provided. The dilute solution that has not been sent to the low-temperature regenerator 62 is led to the high-temperature regenerator 60 from a pipe 84. On the other hand, the concentrated solution generated in the low-temperature regenerator 62 is led to an intermediate part of the solution heat exchanger 70 from the pipe 86.
The concentrated solution generated in the high-temperature regenerator 60 flows into the solution heat exchanger from near the end of the solution heat exchanger 70.

In the present embodiment, the dilute solution led to the low-temperature regenerator and the dilute solution led to the high-temperature regenerator are heat-exchanged by a single solution heat exchanger. And a low-temperature heat exchanger. At that time, the dilute solution led to the high-temperature regenerator flows through the low-temperature heat exchanger and then through the high-temperature heat exchanger. The dilute solution led to the low-temperature regenerator
Only the low-temperature heat exchanger is distributed. With this configuration, two small heat exchangers can be arranged in an empty space in the absorption refrigerator, so that the overall absorption refrigerator can be reduced in size.

Next, the details of the solution heat exchanger 70 according to the present invention will be described with reference to FIGS. The solution heat exchanger is a shell and plate type heat exchanger. FIG.
FIG. 2 is a longitudinal sectional view of one embodiment of the plate heat exchanger. FIG. 2 is a front view of a heat transfer plate used in the plate heat exchanger shown in FIG.

As the plate type heat exchanger, in addition to the shell and plate type, the heat transfer plates may be laminated with a packing interposed between the heat transfer plates and the whole may be tightened with bolts to form a sealed container, or the heat transfer plates may be laminated. Some braze everything. In an absorption refrigerator, it is necessary to make the entire apparatus vacuum when assembling or the like, and it is necessary to prevent air from leaking into the solution heat exchanger even when the absorption refrigerator is vacuumed. In addition, an aqueous solution of lithium bromide is frequently used as a solution for the absorption refrigerator, but since this lithium bromide solution is highly corrosive, the heat exchanger is also required to have corrosion resistance and hermeticity. Normally, packing deteriorates due to corrosion and thus has a short life, and is not preferably used for a solution heat exchanger of an absorption refrigerator. Further, in the brazing heat exchanger, a potential difference occurs because the brazing material and the heat transfer plate are different metals. This potential difference may also lead to corrosion, which is also undesirable as a heat exchanger for an absorption refrigerator. Therefore, in this embodiment, a heat exchanger having a welding structure is used.

The solution heat exchanger 70 shown in FIG. 1 is a heat exchanger used as a high-temperature heat exchanger or a low-temperature heat exchanger. Heat transfer plates 1A and 1B are stacked and housed in a sealed container 7 in which the inflow and outflow ports for the dilute solution and the concentrated solution are formed. The port 7A is, for example, a concentrated solution inflow port, and the port 7B is, for example, a dilute solution outflow port. The solution heat exchanger 70 has a rectangular parallelepiped shape, and these ports are formed near each corner (four corners) on the upper surface. The method of laminating the heat transfer plates is as described below.

First, as shown in FIG. 2, an uneven pattern is formed on flat plates (heat transfer plates) 1A and 1B having rounded corners using a press or the like. At the same time, passage holes 10 to 17 for the concentrated solution and the diluted solution are formed at positions corresponding to the four ports 7A, 7B,... Of the heat exchanger. Next, the peripheral portions 20 of the heat transfer plates 1A and 1B are joined by plasma welding to form a bag-shaped container. Portions 22A, 22B of passage holes 10-17 of the bag-shaped heat transfer plates 1A, 1B.
Are laminated by welding. Stacked heat transfer plates 1A, 1B
Is stored in the container 7. Thereby, the plate heat exchanger 70 is completed. Here, since the heat transfer plates 1A and 1B are made of the same metal, no potential difference occurs and there is no possibility of causing corrosion.

The plate heat exchanger 70 thus constructed
, One fluid (for example, a dilute solution) is caused to flow inside the bag formed by the pair of heat transfer plates 1A and 1B, and the other fluid (for example, a concentrated solution) is caused to flow outside the bag. Here, on the surface of the heat transfer plate 1A, as shown in FIG.
Concavities and convexities 27 obliquely directed from upper right to lower left are formed except for around the passage holes 11 and 13 of the plate 1A. Similarly, as shown in FIG. 2B, on the surface of the heat transfer plate 1B, unevenness 28 obliquely directed from upper left to lower right is formed except for around the passage passage holes 14 and 16 of the plate 1B. Is formed.

Therefore, the unevenness of the pair of upper and lower heat transfer plates 1A and 1B is different from each other, so that as shown in the right half of FIG. Are formed. The vicinity of the passage holes 11 and 13 of the heat transfer plate 1A is a surface having the same height as the peaks (projections) of the unevenness formed on the heat transfer plate 1A, and is equal to the height of the peaks. On the other hand, the vicinity of the passage holes 10 and 12 is a surface having the same height as the concave and convex valleys (recesses) formed in the heat transfer plate 1A, and is equal to the height of the valleys.

Similarly, the passage hole 1 of the heat transfer plate 1B
The vicinity of 4 and 16 is equal to the height of the peaks (convex portions) of the unevenness formed on the heat transfer plate, and the vicinity of the passage holes 15 and 17 is equal to the height of the valleys (concave portions). When the heat transfer plate 1A is placed below and the heat transfer plate 1B is placed above, the passage holes 10
And the vicinity of the passage hole 14 are in contact with each other, and a gap is formed near the passage hole 11 and the passage hole 15. Similarly, the passage hole 12 and the passage hole 1
6, a gap is formed near the passage holes 13 and 17. By utilizing the fact that the passage holes 10 and 14 and the passage holes 12 and 16 are in contact with each other, the periphery of the passage hole is welded to prevent the fluid inside the bag from flowing out from this portion. The gaps between the passage holes 11 and 15 and between the passage holes 13 and 17 serve as entrances and exits for the fluid flowing inside the bag, and the fluid flows diagonally through the heat transfer plate.

When stacking the bag-shaped heat transfer plates in the vertical direction, the passage holes 10, 14, and 1
A gap is formed between the welding portion 22B of the passage hole 16 and the passage hole 16 in the vertical direction. This gap serves as a port for the fluid flowing outside the bag. The welded portion 22A between the passage hole 11 and the passage hole 15 and between the passage hole 13 and the passage hole 17 prevent the fluid inside the bag from flowing out of the bag. The uppermost layer and the lowermost layer of the stacked heat transfer plates 1A and 1B are respectively provided with containers.
7 are provided with heat transfer plates 1C and 1D for attaching the heat transfer plates laminated to each other and sealing the first fluid and the second fluid, and the heat transfer plates 1 laminated on the inner diameter sides of the passage holes 11 and 15 are provided.
A and 1B are welded.

The front side of the heat transfer plate 1A and the heat transfer plate 1
Fluid A flowing on the inner surface of the bag formed by the back side of B,
It flows through a flow path formed by the valleys of the heat transfer plate 1A and the peaks of the heat transfer plate 1B. When the heat transfer plate 1A and the heat transfer plate 1B overlap, a staggered contact is formed as shown on the right side of FIG. The flow of the fluid A is stopped at the contact point, and the flow direction of the fluid A is changed at the staggered contact points, and flows in a zigzag manner. Since the fluid A flows alternately between the peaks and the valleys of the heat transfer plate 1A and the heat transfer plate 1B, the fluid A also moves up and down. As a result, the movement of the fluid A becomes a spiral movement. Due to the disturbing action of this flow,
The heat transfer coefficient of the fluid is improved.

Similarly, the fluid B flowing outside the bag formed by the back side of the heat transfer plate 1A and the front side of the heat transfer plate 1B, that is, the fluid B flowing between the bags, is a peak of the heat transfer plate 1A forming two different bags. Flows through the flow path formed by the valleys of the heat transfer plate 1B. Then, in the same manner as the flow inside the bag, vertical movement is applied to form a spiral motion, which gives a disturbance to the flow of the fluid B. Thereby, the heat transfer performance of the fluid B is improved.

By the way, the plate type heat exchanger has better volume efficiency but higher fluid pressure loss than the other types of heat exchangers described above. In order to reduce the pressure loss, the width of the heat transfer plate may be increased and the flow velocity may be reduced. When the lateral width of the heat transfer plate is increased, the distance required for the fluid flowing from the passage hole to the heat transfer surface of the heat transfer plate to extend to the full width of the heat transfer plate becomes longer.

At the same time, in the inclined waveform, for example, the fluid flowing from the upper edge of the passage hole flows obliquely downward to the width end of the heat transfer plate, but the passage hole (outflow hole) formed above the reaching end thereof. )), The fluid is:
It hardly flows. That is, two triangular dead spaces including the passage holes (outflow holes) are formed diagonally. The area that does not function as the heat transfer surface becomes larger as the width of the heat transfer plate increases.

Therefore, in the present invention, as shown in FIG. 2, horizontal portions (vertical portions in the case of horizontal installation) 25 and 26 are formed in the uneven portions formed on the heat transfer plate. That is, the horizontal unevenness 25 was formed near the passage hole 11 and the passage hole 13 of the heat transfer plate 1A. This horizontal unevenness 25 has a slope waveform 2
7 and bent at its connection. Similarly, in the vicinity of the passage hole 14 and the passage hole 16 of the heat transfer plate 1B, a horizontal unevenness 26 continuous with the inclined waveform 28 is formed.

The operation of the heat transfer plate thus formed will be described below. When the fluid flows in from the passage hole 11 of the heat transfer plate 1A, the fluid flows toward the lower side in FIG. In the flow spreading horizontally, the flow flowing to the width end is indicated by a dashed arrow. The flow is a flow that passes through a concave and convex valley portion, and is a flow from the horizontal portion 42d to the inclined portion 42c. By providing the horizontal portions 25 and 26 on the unevenness, it is possible to guide the fluid to a position closer to the passage hole 10 than when the horizontal portion is not formed. That is, it is understood that the dead space not contributing to the heat transfer is reduced.

The increase in the heat transfer area of the heat transfer plate 1A shown in FIG. 2 can be achieved not only near the passage hole 11 as the fluid inlet but also near the passage hole 13 as the fluid outlet. Further, each passage hole 14 of the heat transfer plate 1B,
By forming the same horizontal unevenness around the heat transfer plate 16 as the heat transfer plate 1A, the dead space that does not contribute to the heat transfer can be reduced, and the heat transfer performance of the plate heat exchanger can be improved.

In the above embodiment, two horizontal portions of the concavo-convex portions formed on the heat transfer plate are provided diagonally, but may be provided at only one portion. At this time, a horizontal portion is formed around the passage holes 11 and 16 corresponding to the inlet portion of the fluid. This increases the heat transfer area on the fluid inflow side. On the other hand, around the passage holes 13 and 14 corresponding to the outlets of the fluid, the inertia effect of the flow is large, and the effect of the wraparound is smaller than that of the passage holes 11 and 16. Therefore, the horizontal portion may be omitted.

FIG. 3 shows another embodiment of the heat transfer plate according to the present invention. FIG. 3 shows only the upper part.
This embodiment is different from the above embodiment in that the heat transfer plates 6A and 6B do not have a bent horizontal portion connected to the inclined waveform. However, unlike the conventional inclined waveform, the ridge 2 extending almost to the center in the width direction of the heat transfer plate 2
5A and 26A are formed around the passage holes 11A and 14A. The surroundings of the passage holes 10A and 15A are the same as in the embodiment shown in FIG. In this embodiment, the number of irregularities in the horizontal direction formed on the heat transfer plates 6A and 6B is the smallest. According to the present embodiment, the heat transfer plate having the conventional inclined waveform may be changed only in the passage holes 11A and 14A, and the die can be used.

In each of the above embodiments, the fluid passage holes are arranged at diagonal positions in the heat transfer plate having the inclined waveform, but they may be arranged at the same side. Further, a herringbone waveform may be used instead of the gradient waveform. In any case, by providing the horizontal portion, the heat transfer area can be improved.

Further, in the above embodiment, the case where the fluid flows in the vertical direction of the vertically long heat transfer plate has been described.
It goes without saying that the present invention is also applicable to a case where a fluid is caused to flow in the lateral direction of the horizontally long heat transfer plate. In this case, it is natural that the horizontal portion of the uneven portion becomes a vertical portion. When the heat transfer plate is arranged horizontally, irregularities may be formed from the inflow portion of the fluid to the outflow portion of a fluid different from the fluid. In each case, a similar effect can be obtained.

When the plate heat exchanger configured as described above is used for a solution heat exchanger of an absorption refrigerator, the solution heat exchanger can be downsized by improving the heat transfer area. In particular,
When the high-temperature heat exchanger and the low-temperature heat exchanger are separate units, each heat exchanger can be accommodated even in the narrow empty space of the absorption refrigerator by reducing the size of each. Space can be saved.

[0042]

According to the present invention, the heat transfer plate used in the welding type plate heat exchanger is formed with irregularities in the direction connecting the passage holes, so that the heat transfer area contributing to the heat transfer can be increased. In addition, the size of the plate heat exchanger can be reduced.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of one embodiment of a plate heat exchanger according to the present invention.

FIG. 2 is a front view of one embodiment of a heat transfer plate used in the plate heat exchanger shown in FIG.

FIG. 3 is a front view of another embodiment of the heat transfer plate used in the plate heat exchanger shown in FIG.

FIG. 4 is a system diagram of an embodiment of an absorption refrigerator according to the present invention.

[Explanation of symbols]

1A, 1B, 6A, 6B: heat transfer plate, 7: container, 7
A, 7B: port, 10-17: passage hole, 10A, 11
A, 14A, 15A: passage hole, 25, 26: horizontal portion of uneven portion, 25A, 26A: peak portion of uneven portion, 27, 28: inclined waveform, 60: high temperature regenerator, 62: low temperature regenerator, 64 ...
Condenser, 66: evaporator, 68: absorber, 70: solution heat exchanger, 100: absorption refrigerator.

 ──────────────────────────────────────────────────の Continued on the front page (71) Applicant 000221834 Toho Gas Co., Ltd. 19-18, Sakuradacho, Atsuta-ku, Nagoya-shi, Aichi (72) Inventor Akira Nishioka 603, Kandamachi, Tsuchiura-shi, Ibaraki Prefecture Machinery Systems Division (72) Inventor Tomohisa Ouchi 603, Kandamachi, Tsuchiura-shi, Ibaraki Pref. Industrial Machinery Systems Division (72) Inventor Hisao Nao 603, Kandamachi, Tsuchiura-shi, Ibaraki Pref. Industrial Machinery Systems Division (72) Inventor Atsushi Shitara 1-5-20 Kaigan, Minato-ku, Tokyo Tokyo Gas Co., Ltd. (72) Inventor Toshikuni Ohashi 1-3-1, Kitakora Shiratsu, Konohana-ku, Osaka, Osaka (72) Inventor Koji Matsubara 507-2 Shinhocho, Tokai City, Aichi Prefecture Toho Gas Co., Ltd. F-ter (Reference) 3L093 LL03 MM02 3L103 AA05 AA27 AA36 BB33 CC01 CC02 DD15 DD57

Claims (10)

[Claims] 1. A transmission having a passage hole into which a first fluid flows, a passage hole through which a first fluid flows out, a passage hole through which a second fluid flows, and a passage hole through which a second fluid flows out. In the plate heat exchanger in which a plurality of heat plates are stacked and accommodated in a container, the first flow path through which the first fluid flows and the second flow path through which the second fluid flows are formed by the plurality of heat plates. A plate-type heat exchanger, wherein a plurality of irregularities are formed exclusively by forming a plurality of irregularities on the surface of the heat transfer plate, and at least one of the irregularities has a portion substantially parallel to the periphery of the heat transfer plate. vessel. 2. A transmission having a passage hole into which a first fluid flows, a passage hole through which a first fluid flows out, a passage hole through which a second fluid flows, and a passage hole through which a second fluid flows out. In the plate heat exchanger in which a plurality of heat plates are stacked and accommodated in a container, the first flow path through which the first fluid flows and the second flow path through which the second fluid flows are formed by the plurality of heat plates. Formed exclusively by forming a plurality of irregularities on the surface of the heat transfer plate, at least one of the irregularities has a portion substantially parallel to the periphery of the heat transfer plate, and the first fluid absorbs the first fluid. A plate heat exchanger for use in an absorption refrigerator, wherein the second fluid is a dilute solution supplied from a vessel and the second fluid is a concentrated solution supplied from at least one of a high temperature regenerator and a low temperature regenerator. 3. A transmission having a passage hole through which a first fluid flows, a passage hole through which a first fluid flows out, a passage hole through which a second fluid flows, and a passage hole through which a second fluid flows out. In a plate heat exchanger in which a plurality of heat plates are stacked and accommodated in a container, a plurality of first flow paths through which the first fluid flows and a plurality of second flow paths through which the second fluid flows Are formed exclusively by forming a plurality of irregularities on the plurality of heat transfer plate surfaces, and the first flow path and the second flow path are both formed from one end in the width direction of the heat transfer plate. An inclined channel toward the end,
A passage having at least one of a first fluid and a second fluid in the passage hole portion into which the first fluid or the second fluid flows, and a bent channel having a bent end extending to the widthwise end of the heat transfer plate; A plate heat exchanger comprising: 4. The channel according to claim 1, wherein the channel is formed substantially horizontally or vertically in the passage hole.
3. The plate heat exchanger according to 3. 5. It has a regenerator, a condenser, an evaporator, and an absorber,
In an absorption refrigerator in which cold water is generated by cold generated by evaporating a refrigerant in an evaporator, heat exchange is performed between a dilute solution sprayed on the absorber and a concentrated solution generated by concentrating the dilute solution in the regenerator. A solution heat exchanger,
A plurality of heat transfer plates each having a passage hole through which a diluted solution flows in and a passage hole through which a diluted solution flows, a passage hole through which a concentrated solution flows in, and a passage hole through which a concentrated solution is formed are stacked and accommodated in a container. A plurality of dilute solution flow paths through which the solution flows and a plurality of concentrated solution flow paths through which the concentrated solution flows are formed exclusively by forming a plurality of irregularities on the surfaces of the plurality of heat transfer plates, and the dilute solution flow path And the concentrated solution flow path are both substantially inclined having an inclined flow path from one end to the other end in the width direction of the heat transfer plate and one end in a passage hole into which at least one of the diluted solution and the concentrated solution flows. A formed horizontal portion or a substantially vertically formed vertical portion, and the material is extended to the width direction end of the heat transfer plate continuously to the horizontal portion or the vertical portion,
An absorption refrigerator having a slanted flow path portion substantially parallel to the slanted flow path. 6. The absorption refrigerator according to claim 5, wherein the refrigerant is water, and the solution is a lithium bromide solution. 7. The absorption refrigerator according to claim 5, wherein the passage hole is formed near a corner of each heat transfer plate. 8. A plurality of heat transfer plates each having a passage hole serving as a fluid inlet / outlet at four corners, and a first fluid and a second fluid alternately flow in a space interposed between the heat transfer plates. In the plate heat exchanger, a plurality of inclined waveforms are formed on the heat transfer plate, and at least one of the inclined waveforms at the end thereof and near the passage hole, in a substantially horizontal or substantially vertical direction. A plate-type heat exchanger characterized in that the waveform is provided continuously to the inclined waveform. 9. An inclined waveform formed on the heat transfer plate,
In the stacked adjacent heat transfer plates, the shape is an inverted shape, and the first flow path and the second flow path are exclusively formed by crossing the waveforms of the adjacent heat transfer plates to generate contact points. 9. The plate heat exchanger according to claim 8, wherein the plate heat exchanger is formed. 10. A heat transfer plate is formed by welding the outer periphery of a pair of heat transfer plates into a bag shape, and the inner edges of the four corner passage holes are welded and stacked, and the stacked heat transfer plates are housed in a container. The plate type according to claim 8, wherein a first flow path flowing inside the bag-shaped heat transfer plate and a second flow path flowing outside the bag-shaped heat transfer plate are formed. Heat exchanger.