WO2006077785A1

WO2006077785A1 - Plate type heat exchanger

Info

Publication number: WO2006077785A1
Application number: PCT/JP2006/300423
Authority: WO
Inventors: Iwao Sawada; Hiroshi Fukada; Kazunori Morinaga; Junichi Nakamura; Kenji Kusunoki
Original assignee: Sasakura Engineering Co., Ltd.; Hisaka Works, Ltd.
Priority date: 2005-01-18
Filing date: 2006-01-16
Publication date: 2006-07-27
Also published as: CN101137882B; TWI371568B; CN101137882A; KR20070100705A; TW200630582A; JP4321781B2; JPWO2006077785A1

Abstract

A plate type heat exchanger formed by stacking a plurality of heat transfer plates (2) and (3) so as to alternately form, therebetween, a first heat exchange chamber (4) generating or condensing steam and a second heat exchange chamber (6) heating or cooling the steam. Tunnel-like fluid passages (19) and (20) formed to extend along the heat transfer plates (2) and (3) are formed in the first heat exchange chamber (4) and the second heat exchange chamber (6) so that their both ends can be opened to the insides of the heat exchange chambers. Thus, since the stagnated parts of fluid flows in the heat exchange chambers (4) and (6) can be reduced to increase the capacity and reduce the size and weight of the heat exchanger and to reduce the occurrence of scale.

Description

Specification

Technical Field of Plate Type Heat Exchanger

[0001] The present invention is formed by laminating a plurality of heat transfer plates so that a first heat exchange chamber and a second heat exchange chamber are alternately formed by sandwiching a spacer body serving as a seal therebetween. Among plate-type heat exchangers, it relates to plate-type heat exchangers that are used to heat and evaporate liquids such as water or to cool and condense water vapor.

Background art

[0002] Patent Document 1 as a prior art describes a plate-type heat exchanger having the above-described configuration as a second type of liquid to be evaporated such as seawater or water supplied to the first heat exchange chamber among the heat exchange chambers. It is used for evaporation, which is heated and boiled by a heating fluid such as heating steam supplied to the heat exchange chamber, and the steam introduced into the first heat exchange chamber of each of the heat exchange chambers is used as the second heat. It is proposed to be used for condensation by cooling with the cooling fluid supplied to the exchange chamber.

[0003] In this case, the prior art plate-type heat exchange described in Patent Document 1 uses one of the corners on the upper side of each heat transfer plate when it is used as an evaporator. A steam outlet from each of the first heat exchange chambers is formed at a corner of the heat transfer plate, or at a part of the upper side of the heat transfer plate. In addition, each of the first heat exchange chambers is provided with an inlet for the liquid to be evaporated, while the other of the two corners on the upper side of each heat transfer plate is heated to the second heat exchange chamber. The fluid inlet is configured such that a heating fluid outlet from each of the second heat exchange chambers is provided at one of the two corners on the lower side of each of the heat transfer plates.

[0004] Further, in the prior art plate heat exchanger described in Patent Document 1, when this is used as a condenser, one of the two corners on the upper side of each heat transfer plate is used. A steam inlet into each of the first heat exchange chambers at a corner or a part of the upper side, and a corner at the other corner of the lower side of each heat transfer plate that forms a diagonal with the evaporation inlet, Condensate outlets from the first heat exchange chambers are respectively provided, while the heat transfer plates are provided. The inlet of the cooling fluid into each of the second heat exchange chambers is provided at one of the two corners on the lower side of the heat transfer plate, and the cooling fluid inlet of the two corners on the upper side of each heat transfer plate. If the cooling fluid outlets from the second heat exchange chambers are respectively provided at the other corners that are diagonal to each other, a configuration is adopted.

Patent Document 1: Japanese Patent Laid-Open No. 9-299927

Disclosure of the invention

Problems to be solved by the invention

However, when the plate type heat exchanger of the prior art is used as an evaporator, the liquid to be evaporated supplied from the liquid inlet at one corner in the first heat exchange chamber is: Mainly, the pressure loss becomes the lowest, that is, in the first heat exchange chamber while boiling and evaporating, flowing in a substantially linear direction from the liquid inlet to the vapor outlet, while one of the second heat exchange chambers. The heating fluid supplied from the heating fluid inlet at the corner is also substantially linear in the direction in which the pressure loss is lowest, that is, in the direction from the heating fluid inlet to the heating fluid outlet in the second heat exchange chamber. In the first heat exchange chamber, the left and right or one side of the main flow in the direction facing the steam outlet in the first heat exchange chamber has a stagnation portion of the flow, while the second heat exchange chamber For heating indoors There is a stagnation part of the flow on the left or right or one side of the main flow in the direction facing the fluid outlet.

[0006] The presence of the stagnation portion of the flow as described above in the first heat exchange chamber and the second heat exchange chamber cannot effectively use the entire surface of the heat transfer plate for heat exchange. Therefore, there is a problem in that the evaporation capacity per unit heat transfer area is reduced, which leads to an increase in size and weight.

[0007] In particular, when used as an evaporator, the liquid to be evaporated introduced into the first heat exchange chamber is heated by the heating fluid, and a part thereof flows toward the vapor outlet while boiling and evaporating. In a portion where boiling evaporation is relatively intense, the pressure of that portion rises due to the vapor evaporated from boiling, and the liquid to be evaporated becomes difficult to flow. For this reason, the liquid to be evaporated is originally expected and does not flow easily in the direction of the heating fluid inlet, and easily flows in the direction of the heating fluid outlet. Near the fluid inlet There is a problem that the first heat exchange chamber is prone to scale because it evaporates with a small amount of liquid to be evaporated.

[0008] Also, when the plate heat exchanger of the prior art is used as a steam condenser, the steam mainly condenses from the steam inlet to the condensed water outlet while condensing. While the cooling fluid flows almost linearly in the direction of the force, the cooling fluid mainly flows almost linearly in the direction of the force of the cooling fluid inlet force to the cooling fluid outlet in the second heat exchange chamber. As in the case described above, the left and right or one side portions of the first heat exchange chamber with respect to the flow in the diagonal direction, and the diagonal direction of the second heat exchange chamber in the diagonal direction. Since the stagnation part of the flow is formed on both the left and right sides or one side of the flow and the entire surface of the heat transfer plate cannot be used effectively for heat exchange, the condensation capacity per unit heat transfer area is reduced. , And eventually, increase the size and weight Leave you there is a problem.

[0009] As described above, the flow of stagnation in the two heat exchange chambers as described above is caused by the generation of scale in this part. The adhesion is vigorous, so frequent cleaning maintenance is performed to remove this scale. It was also a problem to have.

[0010] In particular, the tendency for the evaporation capacity or the condensation capacity per unit heat transfer area to decrease is more prominent when each heat transfer plate is made into a horizontally long rectangle in order to increase the size. It became.

[0011] It is a technical object of the present invention to provide plate-type heat exchange that solves this problem.

Means for solving the problem

In order to achieve this technical problem, claim 1 of the present invention provides:

“Preliminary plate consisting of multiple heat transfer plates stacked so as to alternately form a first heat exchange chamber for generating steam or condensing steam and a second heat exchange chamber for heating or cooling. In a heat exchanger

Tunnel-like fluid passages configured to extend along the heat transfer plates are formed in the first heat exchange chamber and the second heat exchange chamber so that both ends thereof open to the heat exchange chambers. " It is characterized by that.

[0013] Claim 2 of the present invention provides

“In the description of claim 1, the tunnel-like fluid passage is formed by a partition provided in a spacer body sandwiched between the heat transfer plates.”

It is characterized by that.

[0014] Claim 3 of the present invention provides

“In the first aspect of the present invention, the tunnel-like fluid passage is in contact with the ridgeline at the mountain-shaped ridges provided in the pair of heat transfer plates forming the heat exchange chamber in a linear manner. It is formed by doing. "

It is characterized by that.

[0015] Claim 4 of the present invention provides:

“In the description of claim 3, the mountain-shaped ridges are formed by inflating and deforming a part of the heat transfer plate.”

It is characterized by that.

[0016] Claim 5 of the present invention provides:

When the heat transfer plates are stacked by arranging a plurality of ridges extending in a mountain range on the front and back surfaces of the heat transfer plates, the ridge lines and the back surfaces of the mountain transfer ridges on the surface of the heat transfer plate are stacked. The ridgeline in each mountain-shaped ridge is in linear contact over the long part in each first heat exchange chamber and each second heat exchange chamber, and each mountain range in each first heat exchange chamber A plurality of tunnel-shaped fluid passages are formed in the portion between the ridges so that both ends open into the first heat exchange chamber, while each of the second heat exchange chambers has the mountain range. A plurality of tunnel-like fluid passages are formed in the part between the ridges so that both ends open into the second heat exchange chamber. It is characterized by that.

[0017] Claim 6 of the present invention provides: “In the description of claim 5, each mountain-shaped ridge in each heat transfer plate is formed by expanding and deforming a part of the heat transfer plate.”

It is characterized by that.

[0018] Claim 7 of the present invention provides:

“In the description of claim 5 or 6, each mountain-shaped ridge in each heat transfer plate has a herringbone pattern arrangement as viewed from the stacking direction of the heat transfer plates.”

[0019] Claim 8 of the present invention provides

“In the description of claim 5 or 6, each mountain-shaped ridge in each heat transfer plate is intermittent.”

It is characterized by that.

[0020] Claim 9 of the present invention provides:

“In the description of claim 5 or 6, each of the heat transfer plates has a rectangular shape when viewed from the stacking direction, and the upper side of each rectangular heat transfer plate includes the corners of the upper side. A steam outlet from each of the first heat exchange chambers or a steam inlet to each of the first heat exchange chambers at one corner or in the vicinity thereof or a part of the upper side is the other corner of both corners on the upper side. Alternatively, a heating fluid inlet or a heating fluid outlet for each of the second heat exchange chambers or a cooling fluid inlet or a cooling fluid outlet for each of the second heat exchange chambers is provided in the vicinity thereof. The lower side of the heat transfer plate has a liquid inlet to the first heat exchange chamber or each of the corners in the vicinity of or near the corner of the lower edge of the heat transfer plate. 1st heat exchange chamber power condensation Outlet force Each of the second heat exchanges at or near the other corner that forms a diagonal with the heating fluid inlet or heating fluid outlet or the cooling fluid inlet or cooling fluid outlet of both corners on the lower side. A heating fluid outlet or a heating fluid inlet to the chamber or a cooling fluid outlet or a cooling fluid inlet to each of the second heat exchange chambers is provided. "

[0021] Claim 10 of the present invention includes

“In the claim 5 or 6, the heat transfer plates are viewed from the stacking direction. The upper side of each rectangular heat transfer plate has a steam outlet or a steam inlet for each of the first heat exchange chambers at or near the center of the upper side. A heating steam inlet to each of the second heat exchange chambers or a cooling fluid inlet to each of the second heat exchange chambers is located at or near one of the two corners. A heating steam inlet to each of the second heat exchange chambers or a cooling fluid outlet to each of the second heat exchange chambers is provided, respectively. A liquid supply port to be evaporated to one heat exchange chamber and a steam condensate outlet for heating to each second heat exchange chamber are provided, or a condensate outlet to each first heat exchange chamber is provided. It is characterized by that.

[0022] Claim 11 of the present invention provides:

“In the description of claim 5 or 6, each of the heat transfer plates has a rectangular shape when viewed from the stacking direction, and the upper side of each of the rectangular heat transfer plates has a substantially central portion of the upper side. Or a steam outlet or steam inlet force to each first heat exchange chamber in the vicinity thereof, or a heating fluid inlet to each second heat exchange chamber or each of the second heat exchange chambers at or near one of the corners on the upper side. 2 a cooling fluid inlet to the heat exchange chamber, a heating fluid outlet to the second heat exchange chamber or a cooling fluid outlet to the second heat exchange chamber is provided at or near the other corner, The evaporative liquid supply port for each first heat exchange chamber or the condensed water outlet for each first heat exchange chamber is provided at or near the lower side of each rectangular heat transfer plate.

It is characterized by that.

The invention's effect

[0023] As described in claim 1, a pair of heat transfer plates forming the heat exchange chamber in one or both of the first heat exchange chamber and the second heat exchange chamber By forming a plurality of tunnel-like fluid passages configured to extend along the two sides so that both ends open into the heat exchange chamber, the fluid in the heat exchange chamber One end force flows into the tunnel-like fluid passage, and the other end force flows out. Each of the tunnel-like fluid passages is constructed so that the fluid extends over the entire heat exchange chamber, thereby allowing the fluid to reach the entire heat exchange chamber. Can be guided over a wide range.

[0024] In addition, in the first heat exchange chamber, the liquid to be evaporated that has flowed into the tunnel-like fluid passage at the lower side passes through the passage without being displaced in the middle even if the pressure rises due to boiling evaporation. Since it flows in the direction toward the steam outlet, the liquid to be evaporated can be sufficiently supplied even near the heating fluid inlet.

[0025] By these, since it is possible to reliably reduce the occurrence of stagnation of flow in the heat exchange chamber, it is possible to reliably improve the evaporation capacity or condensation capacity per unit heat transfer area. In addition to reducing drought, it is possible to reduce the occurrence of scale on the heat transfer surfaces in both heat exchange chambers, so the frequency of cleaning maintenance to remove the scale can be greatly reduced.

[0026] In this case, each of the tunnel-like fluid passages can have the configuration described in claim 2, but by adopting the configuration described in claim 3 or claim 5, By laminating the heat plates, the tunnel-like fluid passages can be formed at the same time, so that assembly and disassembly are extremely easy and cleaning of each heat transfer plate is easy.

[0027] In particular, according to the configuration described in claim 5, since it is possible to reliably reduce the occurrence of stagnation of flow in both the first heat exchange chamber and the second heat exchange chamber, it is possible to reduce per unit heat transfer area. The evaporation capacity or condensation capacity of can be greatly improved.

[0028] As described in claim 4 and claim 6, the mountain-like ridges in claim 3 and claim 5 are formed by inflating and deforming a part of the heat transfer plate. The effective heat transfer area of each heat transfer plate can be increased, and the mountain-shaped ridges can be formed by pressing the metal plate, thereby reducing the manufacturing cost.

[0029] In addition, in each of the fourth and sixth aspects, each tunnel-like fluid passage is formed by a ridge line in each mountain-shaped ridge provided on the surface of the heat transfer plate, and each of the tunnel-like fluid passages provided on the back surface of the heat transfer plate. Form formed by linear contact with the ridgeline in the mountainous ridge Therefore, the height of each mountain-shaped ridge can be made lower than the case where a mountain-shaped ridge is provided only on one of the front and back surfaces of the heat transfer plate. Processing becomes easier and manufacturing costs can be reduced.

[0030] Further, by arranging the mountainous ridges in a herringbone pattern as described in claim 7, the heat transfer area can be further increased.

[0031] As described in claim 8, each of the mountain-shaped ridges has an intermittent configuration, so that the fluid flowing in the tunnel-shaped fluid passage formed by each of the mountain-shaped ridges is Since it enters and exits between adjacent tunnel-like fluid passages from the point of intermittent connection, it is possible to promote the spread of the fluid to the whole by interrupting as necessary within the range that does not impede the induction effect. There is an advantage that can be.

[0032] On the other hand, when the plate-type heat exchanger having the configuration described in claim 9 is used as an evaporator, the heating fluid that has also entered the heating fluid inlet force into each second heat exchange chamber is 2 Because one end of the heat flows into each tunnel-like fluid passage formed at each mountain-like ridge on the heat transfer plate on both sides of the heat exchange chamber, the other end flows out. By configuring each of the tunnel-like fluid passages so as to extend over the entire second heat exchange chamber, the pressure loss is minimized, that is, from the heating fluid inlet to the heating fluid outlet. It can be guided over a wide range so as to prevent the pressure loss from flowing in the direction in which the pressure loss is the lowest and to reach the entire second heat exchange chamber.

[0033] The liquid to be evaporated that has flowed into the first heat exchange chambers from the liquid supply port to be evaporated evaporates by heating from the second heat exchange chamber, and heat transfer on both sides of the first heat exchange chamber. Each of the tunnel-like fluid passages is formed at each mountain-like ridge in the plate and flows so that one end force flows into each tunnel-like fluid passage and the other end flows out. By configuring the first heat exchange chamber so as to extend over the whole, the tunnel-like fluid passages flow in the direction in which the pressure loss is lowest, that is, in the direction from the liquid supply port to the vapor outlet. Can be guided over a wide range to prevent this and spread throughout the first heat exchange chamber [0034] Thereby, since it is possible to reliably reduce the stagnation of the flow in the first heat exchange chamber and the second heat exchange chamber, it is possible to reduce the evaporation capacity per unit heat transfer area to each of the heat transfer plates. Even in the case of a rectangular shape, it can be greatly improved and a small and light weight can be achieved.

[0035] When the plate heat exchanger having the structure described in claim 9 is used as a condenser, the cooling fluid flowing from the cooling fluid inlet into each second heat exchange chamber is 2 Because one end of the heat flows into each tunnel-like fluid passage formed at each mountain-like ridge on the heat transfer plate on both sides of the heat exchange chamber, the other end flows out. In the same manner as described above, each of the tunnel-like fluid passages is configured to extend and extend over the entire second heat exchange chamber, so that the pressure loss is minimized by each of the tunnel-like fluid passages. That is, it can be guided over a wide range so as to prevent the flow in the direction from the cooling fluid inlet to the cooling fluid outlet and to reach the entire second heat exchange chamber.

[0036] On the other hand, the steam that has flowed into the first heat exchange chambers from the steam inlet is condensed by cooling of the second heat exchange chamber force, and is placed on the heat transfer plates on both sides of the first heat exchange chamber. Each tunnel-like fluid passage is formed so as to flow into one of the tunnel-like fluid passages formed in each mountain-shaped ridge, so that the other end force flows out. By configuring the first heat exchange chamber so as to extend over the whole, the tunnel-like fluid passages cause the pressure loss to be lowest, that is, the steam inlet force also flows toward the condensed water outlet in the direction of the force. This can be prevented and guided over a wide range so as to reach the entire first heat exchange chamber.

[0037] Thereby, since it is possible to reliably reduce the stagnation of the flow in the first heat exchange chamber and the second heat exchange chamber, the condensing capacity per unit heat transfer area can be reduced by making each heat transfer plate horizontally long. Even in the case of a rectangular shape, it can be greatly improved and a small and light weight can be achieved.

[0038] As described above, since the stagnation of the flow in the two heat exchange chambers can be reliably reduced as described above, the force that can reduce the generation of scale on the heat transfer surfaces in the two heat exchange chambers, The frequency of cleaning maintenance to remove scale can be greatly reduced. The

[0039] By the way, if the plate-type heat exchanger used for evaporation or condensation is to be enlarged, it may be configured as described in claim 10 or as described in claim 11. Configure.

[0040] In this case as well, as described above, the ability to stagnate the flow in each of the first heat exchange chambers and each of the second heat exchange chambers can be reliably reduced, thereby greatly improving the evaporation capacity or the condensation capacity. This makes it possible to reduce the size and weight, and to greatly reduce the frequency of cleaning to remove scale.

[0041] It should be noted that the above-described various effects can be obtained even when the tunnel-like fluid passage is provided only in one of the first heat exchange chamber and the second heat exchange chamber. Not too long.

Brief Description of Drawings

FIG. 1 is a front view of a heat exchanger according to a first embodiment.

FIG. 2 is a side view of FIG.

FIG. 3 is an enlarged sectional view taken along line III-III in FIGS. 2, 5, and 6. FIG.

4 is an enlarged sectional view taken along line IV-IV in FIGS. 2, 5, and 6. FIG.

FIG. 5 is an enlarged sectional view taken along line V-V in FIGS. 1 and 3.

FIG. 6 is an enlarged sectional view taken along line VI-VI in FIGS. 1 and 4.

FIG. 7 is a perspective view of a first heat transfer plate used in the heat exchanger.

FIG. 8 is a perspective view of a second heat transfer plate used in the heat exchanger.

FIG. 9 is a perspective view showing a modification of the first heat transfer plate.

FIG. 10 is a perspective view showing a modification of the second heat transfer plate.

FIG. 11 is a perspective view showing another modification of the first heat transfer plate.

FIG. 12 is a perspective view showing another modification of the second heat transfer plate.

FIG. 13 is a front view of a heat exchanger according to a second embodiment.

FIG. 14 is a side view of FIG.

FIG. 15 is an enlarged cross-sectional view taken along the line XV--XV in FIGS. 14, 17 and 18;

FIG. 16 is an enlarged sectional view taken along line XVI--XVI in FIGS. 14, 17 and 18. FIG. 17 is an enlarged sectional view taken along lines XVII-XVII in FIGS. 13 and 16.

FIG. 18 is an enlarged sectional view taken along lines XVIII--XVIII in FIGS. 13 and 15.

FIG. 19 is a cross-sectional view of the same portion as FIG. 15 in a modification of the second embodiment.

FIG. 20 is a sectional view taken along line XX—XX in FIG.

21] FIG. 17 is a cross-sectional view of the same portion as FIG. 16 in a modification of the second embodiment. [22] FIG. 22 is a front view of heat exchange according to the third embodiment.

FIG. 23 is a side view of FIG.

FIG. 24 is an enlarged sectional view taken along the line XXIV—XXIV in FIG.

FIG. 25 is an enlarged sectional view taken along the line XXV—XXV in FIG.

[26] FIG. 25 is a cross-sectional view of the same portion as FIG. 24 in the modification of the third embodiment. 27] FIG. 26 is a cross-sectional view of the same portion as FIG. 25 in a modification of the third embodiment.圆 28] A sectional view of the same portion as FIG. 24 in another modification of the third embodiment. 29] A sectional view of the same portion as FIG. 25 in another modified example of the third embodiment. Explanation of symbols

1, 31, 61 Plate heat exchanger

2, 32, 62 1st heat transfer plate

3, 33, 63 2nd heat transfer plate

4, 34, 64 1st heat exchange chamber

5, 35, 65 1st seal body

6, 36, 6Ό Second heat exchange chamber

7, 37, 67 Second seal

11, 41, 71 Steam outlet

12, 72a Heating fluid inlet

42a, 42b Steam inlet for heating

13, 43, 73a, 73b Evaporated liquid supply port

14, 72b Heating fluid outlet

Mountainous ridges on the surface of the first heat transfer plate

Mountainous ridge on the back of the first heat transfer plate 17, 47, 77 Mountainous ridges on the surface of the second heat transfer plate

18, 48, 78 Mountainous uplift on the back of the second heat transfer plate

19, 49, 79 Tunnel-like fluid passage in the first heat exchange chamber

20, 50, 80 Tunnel-like fluid passage in the second heat exchange chamber

81 Noncondensable gas outlet

BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

[0045] FIGS. 1 to 12 show a relatively small plate-type heat exchanger 1 used for evaporation in the first embodiment.

[0046] The heat exchanger 1 includes a plurality of first heat transfer plates 2 made rectangular by a relatively thin metal plate and a plurality of second heat transfer plates 3 made rectangular by a relatively thin metal plate. A spacer body 5 serving as a seal for forming the first heat exchange chamber 4 between the first heat transfer plate 2 and the second heat transfer plate 3 is sandwiched between the first heat transfer plate 2 and the second heat transfer plate 3, and the second heat transfer plate 3 The first heat transfer plate 2 and the first heat transfer plate 2 were alternately stacked so as to sandwich the space body 7 serving as a seal for forming the second heat exchange chamber 6, and this stacked body was disposed on one end face thereof. The face plate 8 and the face plate 9 disposed on the other end face are fastened to each other with bolts 10.

[0047] Each of the heat transfer plates 2 and 3 has a steam outlet 11 communicating with the inside of each of the first heat exchange chambers 4 at one of the corners in the upper side or in the vicinity thereof. Heating fluid inlets 12 communicating with the respective second heat exchange chambers 6 are formed in the other corners or in the vicinity of both corners, and these steam outlets 11 and heating fluid inlets 12 are provided. Is open in one or both of the double-sided plates 8 and 9.

[0048] The steam outlet 11 may be provided in a part of the upper side.

[0049] Further, each of the heat transfer plates 2 and 3 has the first heat in each corner at or near the corner that forms a diagonal to the steam outlet 11 out of both corners on the lower side. The vaporized liquid supply port 13 communicating with the inside of the exchange chamber 4 has the respective corners at or near the corner that forms a diagonal to the heating fluid inlet 12 among the two corners on the lower side thereof. (2) Heating fluid outlets (14) communicating with the heat exchange chamber (6) are respectively formed, and the liquid supply port (13) and the heating fluid outlet (14) are either one of the double-sided plates (8, 9) or Open to both Yes.

[0050] In this configuration, the liquid to be evaporated supplied from the liquid supply port 13 to be evaporated into each first heat exchange chamber 4 is heated by heat transfer from the second heat exchange chamber 6 on both sides. The vapor generated by boiling and evaporating is discharged from the first heat exchange chamber 4 through the vapor outlet 11 together with a part of the liquid to be evaporated (brine) that has not evaporated.

[0051] On the other hand, the heating fluid such as heating steam supplied from the heating fluid inlet 12 into each of the second heat exchange chambers 6 is evaporated by heat transfer to the first heat exchange chamber 4 on both sides. After being heated, it is discharged as condensed water from the heating fluid outlet 14.

[0052] Of the heat transfer plates 2 and 3, the first heat transfer plate 2 has a surface 2a, that is, the first heat transfer plate 2 attached to the first heat transfer plate 2, as shown in FIG. For example, a plurality of ridges 15 extending in a mountain range in the longitudinal direction are arranged in parallel or substantially in parallel at an appropriate interval on the surface looking into the exchange chamber 4, and the back surface 2b, that is, the first heat transfer. For example, a plurality of raised portions 16 extending in a mountain range in the lateral direction are arranged in parallel or substantially in parallel at an appropriate interval on the surface where the plate 2 looks into the second heat exchange chamber 6.

[0053] On the other hand, of the heat transfer plates 2 and 3, the second heat transfer plate 3 has a back surface 3b, that is, the second heat transfer plate 3 is connected to the first heat transfer plate 3 as shown in FIG. For example, a plurality of ridges 17 extending in a mountain shape in the vertical direction are arranged on the surface looking into the exchange chamber 4 in accordance with the arrangement of the mountain ridges 16 on the surface 2a of the first heat transfer plate 2. Are arranged in parallel or substantially in parallel at appropriate intervals, and the surface 3a thereof, that is, the surface where the second heat transfer plate 3 looks into the second heat exchange chamber 6 is formed, for example, in a mountain range in the lateral direction. A plurality of extending ridges 18 are arranged in parallel or substantially in parallel at appropriate intervals according to the arrangement of the mountain-shaped ridges 16 on the back surface 2b of the first heat transfer plate 2.

[0054] Each of the mountainous ridges 15, 16, 17, 18 is formed by bulging and deforming a part of the heat transfer plate.

[0055] Then, when the heat transfer plates 2 and 3 are laminated as described above, the ridgeline of each mountain-shaped ridge 15 on the surface 2a of the first heat transfer plate 2 and the second heat transfer plate By constructing the ridgeline of each mountain-shaped ridge 17 on the back surface 3b of the plate 3 so as to make a linear contact over its long part (preferably the entire length), the inside of each first heat exchange chamber 4 Of which In the first heat exchange chamber 4, for example, in the longitudinal direction, that is, in the direction from the vaporized liquid inlet 13 toward the vapor outlet 11, the portion between the mountainous ridges 15 and 17 that are in contact with each other. A plurality of tunnel-like fluid passages 19 extending in a direction crossing the opening and having both ends opened into the first heat exchange chamber 4 are formed in parallel.

On the other hand, when the heat transfer plates 2 and 3 are laminated as described above, the ridgeline of each mountain-shaped ridge 16 on the back surface 2b of the first heat transfer plate 2 and the second heat transfer plate The ridgeline of each mountain-shaped ridge 18 on the surface 3a of 3 is configured so as to come into linear contact over the long part (preferably the entire length) thereof, so that the inside of each second heat exchange chamber 6 Of the second heat exchanging chamber 6 between the mountain-shaped ridges 16 and 18 in contact with each other, for example, in the lateral direction, that is, from the heating fluid inlet 12 to the heating fluid outlet 14. A plurality of tunnel-like fluid passages 20 extending in a direction crossing the opposite direction and having both ends open into the second heat exchange chamber 6 are formed in parallel.

With this configuration, the heating fluid such as heating steam that has flowed into each second heat exchange chamber 6 from the heating fluid inlet 12 passes into both sides of the second heat exchange chamber 6. The heat transfer plates 2 and 3 flow into the tunnel-like fluid passages 20 formed by the mountainous ridges 16 and 18, and the tunnel-like fluid passages 20 have the lowest pressure loss. As shown by the arrows in FIG. 4, for example, the direction crossing the direction from the heating fluid inlet 12 toward the heating fluid outlet 14 is (2) While being guided so as to spread throughout the heat exchange chamber (6), the liquid to be evaporated that has flowed into the first heat exchange chamber (4) from the liquid supply port (13) is supplied from the second heat exchange chamber (6). While evaporating by heating, heat transfer plates 2 on both sides of the first heat exchange chamber 4 3 formed in each mountain-like ridge 15, 17, and flows into each tunnel-like fluid passage 19, and flows through the tunnel-like fluid passage 19 in the direction in which the pressure loss becomes the lowest. As shown by an arrow in FIG. 3, the first heat exchange is performed in a direction, for example, a direction crossing the vapor outlet 11 from the liquid supply port 13 to be evaporated. By being guided so as to spread throughout the chamber 4, it is possible to reliably reduce the stagnation of the flow in the first heat exchange chamber 4 and the second heat exchange chamber 6.

[0058] In the first embodiment, the vertical mountainous ridges 15, 17 described above, As shown in Figs. 9 and 10, the mountain-shaped ridges 16 and 18 in the opposite direction are divided in such a way that they are divided at their intersections as shown in Figs. 7 and 8. For example, the vertical mountainous ridges 15 and 17 are configured to be continuous, while the horizontal mountainous ridges 16 and 18 are divided, for example, As shown in Fig. 11 and Fig. 12, the horizontal mountainous ridges 16 and 18 are configured to be continuous, while the vertical mountainous ridges 15 and 17 are configured to be intermittent. You can do it.

[0059] Each of the mountainous ridges 15, 16, 17, and 18 is separated from the heat transfer plates 2 and 3, and is attached to the heat transfer plates 2 and 3 by welding or the like. The mountainous ridges 15, 16, 17 and 18 may be formed by bulging and deforming a part of each of the heat transfer plates 2 and 3 as described above. With this configuration, it is possible to increase the effective heat transfer area in each of the heat transfer plates 2 and 3 and to form the mountainous ridges by pressing the metal plate.

[0060] Moreover, each tunnel-like fluid passage 19 in each first heat exchange chamber 4 is formed on the back surface of the mountain-shaped ridge 15 provided on the surface of the first heat transfer plate 2 and the second heat transfer plate 3. The mountain-shaped ridges 17 are formed in linear contact with each other, and the tunnel-shaped fluid passages 20 in the second heat exchange chambers 6 are provided on the surface of the second heat transfer plate 3. The ridge-like ridges 18 and the ridge-like ridges 16 provided on the back surface of the first heat transfer plate 2 are formed in linear contact with each other. The height dimension can be made lower than when the mountain-shaped ridges are provided only on the front or back surface of the heat transfer plate.

[0061] Furthermore, each of the tunnel-like fluid passages 19, 20 described above is not limited to being formed by the above-described configuration, and a part or all of the tunnel-like fluid passages 19, 20 are interposed between the heat transfer plates 2, 3. It can be configured to be formed by an extension extending inwardly from the spacer bodies 5 and 7 which are also used as seals.

[0062] In the first embodiment, the plate-type heat exchanger 1 is used as an evaporator, but the plate-type heat exchanger 1 is used as a steam generator as described below. It can be used as a condenser. That is, when used as a condenser, the steam outlet 11 is used as a steam inlet for steam to be condensed, the liquid supply outlet 13 is used as a condensed water outlet, the heating fluid inlet 12 and One of the heating fluid outlets 14 is configured as a cooling fluid inlet and the other is configured as a cooling fluid outlet. In this case, it goes without saying that the arrow indicating the direction of flow in FIG. Nor.

Next, FIGS. 13 to 18 show a plate type heat exchange according to the second embodiment.

In the second embodiment, the plate heat exchanger 31 used as an evaporator is made larger than that in the first embodiment.

[0066] The plate-type heat exchange 31 in the second embodiment includes a plurality of first heat transfer plates 32 which are rectangular with a relatively thin metal plate, and a rectangular shape with a relatively thin metal plate. A plurality of the second heat transfer plates 33 are sandwiched between the first heat transfer plate 32 and the second heat transfer plate 33, and a seal body 35 for forming the first heat exchange chamber 34 is sandwiched between the second heat transfer plate 33 and the second heat transfer plate 33. The heat plate 33 and the first heat transfer plate 32 are alternately laminated so as to sandwich the sealing body 37 for forming the second heat exchange chamber 36, and this laminated body is disposed on one end face of the face plate. 38 and the face plate 39 disposed on the other end surface are fastened to each other with bolts 40.

[0067] Each of the heat transfer plates 32, 33 has a horizontally long steam outlet 41 communicating with the inside of each of the first heat exchange chambers 34 at the substantially central portion on the upper side or in the vicinity thereof at both corners on the upper side. Heating steam inlets 42a and 42b communicating with each of the second heat exchange chambers 36 are formed in a portion near the corners or both corners, respectively, and these steam outlet 41 and both heating steam inlets 42a and 42b are The double-sided plates 38 and 39 are open to one or both of them.

[0068] The steam outlet 41 may be provided in a part of the upper side.

[0069] Furthermore, each of the heat transfer plates 32, 33 has evaporative liquid supply ports 43a, 43b communicating with each of the first heat exchange chambers 34 at or near the corners on the lower side thereof. Heating steam condensate outlets 44 communicating with the respective second heat exchange chambers 36 are formed in the central part of the lower side or in the vicinity thereof, respectively, and both the liquid to be evaporated outlets 43a, 43b and the heating outlets are provided. Similarly, the steam condensate outlet 44 is open to one or both of the double-sided plates 38 and 39. [0070] In this configuration, the liquid to be evaporated supplied from the both liquid supply ports 43a and 43b into each of the first heat exchange chambers 34 is used for heat transfer from the second heat exchange chamber 36 on both sides. Thus, the vapor generated by boiling and evaporating is discharged from the first heat exchange chamber 34 through the vapor outlet 41 together with a part of the liquid to be evaporated (brine) that has not evaporated.

On the other hand, the heating steam supplied from both heating steam inlets 42a and 42b into each second heat exchange chamber 36 is cooled by heat transfer to the first heat exchange chamber 34 on both sides. The condensed water is discharged from the condensed water outlet 44.

[0072] Of the heat transfer plates 32, 33, the first heat transfer plate 32 has the first heat transfer plate 32 in the first heat exchange chamber 34 as shown in FIG. For example, a plurality of raised portions 45 extending in a mountain range in the vertical direction are arranged in parallel at appropriate intervals on the desired surface (surface), and the first heat transfer plate 2 is placed in the second heat exchange chamber 36. For example, a plurality of raised portions 46 extending in a mountain range in the lateral direction are arranged in parallel at appropriate intervals on the desired surface (back surface).

On the other hand, among the heat transfer plates 32 and 33, the second heat transfer plate 33 has the second heat transfer plate 33 placed in the first heat exchange chamber 34 as shown in FIG. For example, a plurality of ridges 47 extending in a mountain range in the vertical direction are paralleled at an appropriate interval on the surface to be viewed (surface) according to the arrangement of the mountain ridges 46 on the surface of the first heat transfer plate 32. Are arranged side by side, and a plurality of raised portions 48 extending in a mountain range in the lateral direction, for example, are formed on the surface (back surface) of the second heat transfer plate 33 viewed in the second heat exchange chamber 36. In parallel to the arrangement of the mountain-shaped ridges 46 on the back surface of the heat plate 32, they are arranged in parallel at appropriate intervals.

[0074] Each of the mountainous ridges 45, 46, 47, 48 is formed by expanding and deforming a part of the heat transfer plate.

[0075] Then, when the heat transfer plates 32, 33 are stacked as described above, the ridgeline of each mountain-shaped ridge 45 on the surface of the first heat transfer plate 32 and the second heat transfer plate 33 By constructing the ridgeline of each mountain-shaped ridge 47 on the surface of the first heat exchange chamber 34 in such a way as to make a linear contact over its long part (preferably the entire length), In the first heat exchange chamber 34, the portions between the mountain-shaped ridges 45, 47 that are in contact with each other For example, the both ends open into the first heat exchange chamber 34 extending in the longitudinal direction, that is, in a direction transverse to the vapor outlet 41 from both the vaporized liquid inlets 43. A plurality of tunnel-like fluid passages 49 are formed in parallel.

On the other hand, when the heat transfer plates 32, 33 are stacked as described above, the ridgeline of each mountain-shaped ridge 46 on the back surface of the first heat transfer plate 32 and the second heat transfer plate 33 In the second heat exchange chamber 36, the ridgeline of each mountain-shaped ridge 48 on the back surface of the second heat exchange chamber 36 is configured to come into linear contact with the long part (preferably the entire length). In the second heat exchange chamber 36, the portion between the mountain-shaped ridges 46 and 48 that are in contact with each other, for example, in the lateral direction, that is, from both the heated steam inlets 42 to the condensed water outlet 44. A plurality of tunnel-like fluid passages 50 that extend in a direction transverse to the direction and open at both ends into the second heat exchange chamber 36 are formed in parallel.

[0077] With such a configuration, the heating steam having both the heating steam inlets 42a, 42b force flowing into each second heat exchange chamber 36 is transferred into the second heat exchange chamber 36 on the heat transfer plates on both sides thereof. It flows into the tunnel-like fluid passages 50 formed by the mountainous ridges 46 and 48 at 32 and 33, and the tunnel-like fluid passages 50 flow in the direction in which the pressure loss becomes the lowest. As shown by the arrows in FIG. 16, the second steam exchange 42a, 42b is also used for the second heat exchange, for example, in the direction of the force toward the condensate outlet 44, for example, in the direction across it. On the other hand, the liquid to be evaporated flowing from both the liquid supply ports 43a and 43b into the first heat exchange chambers 34 is guided from the second heat exchange chamber 36. While evaporating by heating, heat transfer plates on both sides of the first heat exchange chamber 34 It flows into each tunnel-like fluid passage 49 formed at each mountain-like ridge 45, 47 at 32, 33, and flows through the tunnel-like fluid passage 49 in the direction in which the pressure loss becomes the lowest. As shown by the arrows in FIG. 15, the second liquid supply ports 43a, 43b are directed from the vapor outlet 41 to the vapor outlet 41 in the direction of the force, for example, in the direction crossing them. By being guided so as to spread over the entire inside of the first heat exchange chamber 34, it is possible to reliably reduce the occurrence of stagnation in the first heat exchange chamber 34 and the second heat exchange chamber 36. [0078] In the second embodiment, the vertical mountainous ridges 45, 47 and the horizontal mountainous ridges 46, 48 are divided at the intersections as shown in the figure. Thus, instead of being configured in an intermittent manner, as in the case of the first embodiment, the vertical mountainous ridges 45, 47 may be configured to be continuous, or the horizontal mountainous ridges may be configured. The parts 46 and 48 can be configured to be continuous.

[0079] In the second embodiment, the mountain-shaped ridges on both the front and back surfaces of each first heat transfer plate 32 are bent in a square shape as shown in FIG. By forming the portions 45 'and 46' as a whole, the herringbone pattern is arranged as a whole, while the mountain-like ridges on both the front and back surfaces of each second heat transfer plate 33 are formed in a square shape as shown in FIG. By making the mountainous ridges 4, 48 'bent in a straight line, the overall herringbone pattern can be rubbed.

[0080] By arranging the herringbone pattern in this way, the heat transfer area can be further increased. The arrangement of the herringbone pattern is the same as in the first embodiment. What can be applied to is undeniable.

[0081] Also in this second embodiment, each of the mountain-shaped ridges is separated from each heat transfer plate, and is fixed to each heat transfer plate by welding or the like. Of course, it may be configured as follows.

In the second embodiment, the plate-type heat exchanger 31 is used as an evaporator. However, the plate-type heat exchanger 31 is used as a steam condenser. be able to.

[0083] When used as a condenser, the steam outlet 41 is a steam inlet, the liquid supply ports 43a and 43b are condensed water outlets, and one of the heating steam inlets 42a and 42b is used. The heating steam inlet 42a is configured as a cooling fluid inlet, and the other heating steam inlet 42b is configured as a cooling fluid inlet. In this case, the arrows indicating the flow direction in FIGS. 15 and 19 are all reversed. It goes without saying that it will be oriented.

Next, FIGS. 22 to 25 show a third embodiment.

This third embodiment is a modification of the plate type heat exchanger used as an evaporator, and is a case where it is made large as in the case of the second embodiment. [0086] The plate-type heat exchange in the third embodiment includes a plurality of first heat transfer plates 62 that are rectangular with a relatively thin metal plate, and a rectangular shape with a relatively thin metal plate. (2) A plurality of heat transfer plates (63) are sandwiched between a first heat transfer plate (62) and a second heat transfer plate (63), and a sealing body (65) is formed to form a first heat exchange chamber (64). 63 and the first heat transfer plate 62 are alternately laminated so that the seal body 67 for forming the second heat exchange chamber 66 is sandwiched between them, and this laminated body is attached to a face plate 68 disposed on one end face thereof. A face plate 69 disposed on the other end face is fastened to each other with bolts 70, and is configured.

[0087] Each of the heat transfer plates 62, 63 has a horizontally long steam outlet 71 communicating with the inside of each of the first heat exchange chambers 64 at the substantially central portion on the upper side thereof or in the vicinity thereof. A heating fluid inlet 72a such as hot water communicating with the inside of each of the second heat exchange chambers 66 is provided at one of the corners or in the vicinity thereof, and each of the second heat exchange chambers is provided at or near the other corner. 66, a heating fluid outlet 72b communicating with each other is formed, and the steam outlet 71, the heating fluid inlet 72a, and the heating fluid outlet 72b are provided on one or both of the double-sided plates 68 and 69. It is open.

[0088] The steam outlet 71 may be provided in a part of the upper side.

[0089] Furthermore, the heat transfer plates 62, 63 are provided with evaporative liquid inlets 73a, 73b communicating with the first heat exchange chambers 64 at or near the left and right corners of the lower side thereof. The two liquid-evaporated liquid inlets 73a and 73b are also open to one or both of the double-sided plates 68 and 69.

In this configuration, the liquid to be evaporated supplied from the both liquid inlets 73a and 73b into each first heat exchange chamber 64 is transferred to the heat from the second heat exchange chamber 66 on both sides. As a result, it is heated and boiled. The evaporated vapor is discharged from the first heat exchange chamber 64 through the vapor outlet 71 together with a part of the liquid to be evaporated (brine) that has not evaporated. The

On the other hand, the heating fluid supplied from the heating fluid inlet 72a into each of the second heat exchange chambers 66 transfers heat to the first heat exchange chamber 64 on both sides, and then the heating fluid. It is discharged from outlet 72b.

[0092] As shown in Fig. 24, the first heat transfer plate 62 of the heat transfer plates 62, 63 includes the first heat transfer plate 62, as in the second embodiment. Plate 62 For example, a plurality of raised portions 75 extending in a mountain shape in the vertical direction are arranged in parallel at appropriate intervals on the surface (surface) looking into the first heat exchange chamber 64, and the first heat transfer plate 62 is For example, a plurality of ridges 76 extending in a mountain range in the lateral direction are arranged in parallel at appropriate intervals on the surface (back surface) looking into the second heat exchange chamber 66.

On the other hand, among the heat transfer plates 62 and 63, the second heat transfer plate 63 has the second heat transfer plate as shown in FIG. 25, as in the second embodiment. On the surface (surface) of the plate 63 looking into the first heat exchange chamber 64, for example, a plurality of ridges 77 extending in a mountain shape in the vertical direction are provided on the surface of the first heat transfer plate 62. The second heat transfer plate 63 is arranged in parallel at an appropriate interval in accordance with the arrangement of the portions 76, and the second heat transfer plate 63 is formed on the surface (back surface) that is viewed in the second heat exchange chamber 66, for example, in a mountain range in the lateral direction. A plurality of extending ridges 78 are arranged in parallel at appropriate intervals according to the arrangement of the mountainous ridges 76 on the back surface of the first heat transfer plate 62.

[0094] Each of the mountainous ridges 75, 76, 77, 78 is formed by bulging and deforming a part of the heat transfer plate.

[0095] Then, when the heat transfer plates 62, 63 are stacked as described above, the ridgeline of each mountain-shaped ridge 75 on the surface of the first heat transfer plate 62, and the second heat transfer plate 63 In the first heat exchange chamber 64, the ridgeline of each mountain-shaped ridge 77 on the surface of each of the first heat exchange chambers 64 is configured to come into linear contact with the long part (preferably the entire length). In the first heat exchange chamber 64, in the portion between the mountain-shaped ridges 75 and 77 that are in contact with each other, for example, in the vertical direction, that is, from both the vaporized liquid inlets 73a and 73b to the vapor outlet 71 A plurality of tunnel-like fluid passages 79 that extend in a direction crossing the opposite direction and open at both ends into the first heat exchange chamber 74 are formed in parallel.

On the other hand, when the heat transfer plates 62 and 63 are stacked as described above, the ridgeline of each mountain-shaped ridge 76 on the back surface of the first heat transfer plate 62 and the second heat transfer plate 63 In the second heat exchange chamber 66, the second heat exchange chamber 66 is configured such that the ridgeline of each mountain-shaped ridge 78 on the back surface of the second heat exchange chamber 66 is in contact with the long part (preferably the entire length). In the exchange chamber 66, the portion between the mountainous ridges 76 and 78 that are in contact with each other, for example, in the lateral direction, that is, from the heating fluid inlet 72a to the heating fluid outlet 72b. A plurality of tunnel-like fluid passages 80 extending in a direction transverse to the direction of force and having both ends open into the second heat exchange chamber 66 are formed in parallel.

With this configuration, the heating fluid that has flowed into each second heat exchange chamber 66 from the heating fluid inlet 72a is transferred into the second heat exchange chamber 66 on both sides of the heat transfer plate. 62, 63, which are formed by the respective mountainous ridges 76, 78, flow into the respective tunnel-like fluid passages 80, and flow through the tunnel-like fluid passages 80 in the direction in which the pressure loss becomes the lowest. As shown by the arrow in FIG. 25, the second heat is applied from the heating fluid inlet 72a to the heating fluid outlet 72b with respect to the direction of the direction of force, for example, in the direction crossing this. While being guided so as to spread throughout the entire exchange chamber 66, the liquid to be evaporated flowing into the first heat exchange chambers 64 from both the vaporized liquid inlets 73 a and 73 b is transferred from the second heat exchange chamber 66. While boiling and condensing by heating, the heat transfer process on both sides of the first heat exchange chamber 64 Flows into the tunnel-like fluid passages 79 formed by the mountainous ridges 75 and 77 at the gates 62 and 63, and the tunnel-like fluid passages 79 cause the pressure loss to become the lowest. As shown by the arrows in FIG. 24, the flow from both the liquid inlets 73a, 73b to the vapor outlet 71 is directed to the direction of the force, for example, the direction across the direction, etc. By being guided so as to spread throughout the first heat exchange chamber 64, it is possible to reliably reduce the stagnation of the flow in the first heat exchange chamber 64 and the second heat exchange chamber 66.

Also in the third embodiment, the above-described vertical mountain-shaped ridges 75 and 77 on the front side and the horizontal mountain-shaped ridges 76 and 78 on the back side are shown in the figure. As described above, instead of being configured in an intermittent manner so as to divide at the intersection, the vertical mountainous ridges 75, 77 are the same as in the first embodiment. Can be configured to be continuous, or the mountainous ridges 76, 78 in the lateral direction can be configured to be continuous.

[0099] In this third embodiment, each mountain-shaped ridge on both the front and back surfaces of each first heat transfer plate 62 and each mountain on both front and back surfaces of each second heat transfer plate 63 are also described. By making the vein-like ridges into mountain-like ridges that are bent in a square shape, a herringbone pattern can be formed as a whole.

[0100] Also in this third embodiment, each of the mountainous ridges is connected to each heat transfer plate. Of course, it may be configured separately from the heat transfer plate and fixed to each heat transfer plate by welding or the like.

[0101] In the third embodiment, the plate-type heat exchanger 61 is used as an evaporator. However, the plate-type heat exchanger 61 is used as a steam condenser. be able to.

[0102] When used as a condenser, the steam outlet 71 is a steam inlet, the liquid supply ports 73a and 73b are condensed water outlets, and the heating fluid inlet 72a is a cooling fluid inlet. The heating fluid outlet 72b is configured as a cooling fluid outlet.

[0103] In this case, in FIG. 24, it is needless to say that the arrows indicating the direction of flow are all reversed, and in this case, the center of the lower side in each of the first heat exchange chambers 64 is also shown. While the condensate outlet 81 is provided in the part, the liquid supply ports 73a and 73b at the left and right corners of the lower side may be configured as the non-condensable gas extraction ports.

[0104] As a modification of the plate-type heat exchange according to the third embodiment, it can be configured as shown in Figs.

That is, in this modification, the heating fluid inlet 72a into the second heat exchange chamber 66 is connected to the evaporative liquid supply port 7 from one corner on the upper side of the rectangle to one corner on the lower side. 3a, the heating fluid outlet 72b from the second heat exchange chamber 66 is moved to one corner of the upper side of the rectangle, while the second heat exchange chamber 66 is swept. By providing a partition portion 6 that integrally extends inwardly from the spacer body 67, a folded flow passage is formed by directing force from the fluid heating fluid inlet 72a to the heating fluid outlet 72b.

[0106] Also in this case, a plurality of tunnel-like fluid passages 80 are formed in the mountain-shaped ridges 76 and 78 in the folded flow passage, as in the third embodiment. ! What is it! /.

With this configuration, the flow resistance can be lowered by extending along the upper side of the steam outlet 71 on the upper side of the rectangle to the other corner of the upper side, while the second heat exchange is performed. Heat transfer in the chamber 66 is caused to spread the heating fluid throughout the second heat exchange chamber 66 by forming a folded flow path by the partition 6. And by increasing the flow rate of the heating fluid, it can be greatly accelerated, so the processing capacity for evaporation or condensation can be increased. It is particularly suitable when non-condensable liquid is used as the heating fluid.

Further, as another modification of the plate heat exchanger 61 according to the third embodiment, it can be configured as shown in FIG. 28 and FIG.

[0109] That is, in this other modified example, two heating fluid inlets 72a are provided above and below one end of the rectangle, while the heating fluid outlet 72b is provided at the lower corner of the other end of the rectangle. In addition, a partitioning portion 67 "that extends integrally inward from the spacer body 67 is provided in the second heat exchange chamber 66, so that the heating fluid outlet 72a is connected to the both heating fluid inlets 72a. The structure is such that two flow passages are formed by applying force to 72b.

[0110] Also in this case, a plurality of tunnel-like fluid passages 80 are formed in each of the mountain-like ridges 76 and 78 in the two flow passages as in the third embodiment. Needless to say.

[0111] According to this configuration, as in the modification shown in Figs. 26 and 27, the flow resistance is reduced along the upper side of the steam outlet 71 to the other corner of the upper side. In addition to this, heat transfer in the second heat exchange chamber 66 can be promoted by forming two flow passages by the partition 67〃, so that the processing capacity for evaporation or condensation can be increased. It is particularly suitable when steam is used as the heating fluid.

[0112] In the modification shown in Figs. 26 and 27 and the other modification shown in Figs. 28 and 29, a tunnel-like fluid passage 80 for the heating fluid is provided in the second heat exchange chamber 66. As shown in the figure, the mountainous ridges 76 and 78 are divided by a partition section 6 and 67 mm extending integrally from the spacer body 67, so that the partition section Needless to say, 67 ^ and 67 "can be reduced.

[0113] In the modification shown in Fig. 26 and Fig. 27, the case where the return path is made only once is shown, but it can be constituted by the return path twice or three times.

Claims

The scope of the claims

[1] A plurality of heat transfer plates are laminated so that a first heat exchange chamber for generating or condensing steam and a second heat exchange chamber for heating or cooling are alternately formed between them. In the plate type heat exchanger consisting of

A tunnel-shaped fluid configured to extend in one or both of the first heat exchange chamber and the second heat exchange chamber along a pair of heat transfer plates forming the heat exchange chamber. A plate-type heat exchanger characterized in that the passage is formed so that both ends thereof open into the heat exchange chamber.

[2] In the description of claim 1, the tunnel-like fluid passage is formed by a partition portion provided in a spacer body sandwiched between a pair of heat transfer plates forming the heat exchange chamber. Plate-type heat exchange ^^

[3] In the first aspect of the present invention, the tunnel-like fluid passage is formed in a linear shape by connecting a ridge line at a mountain-shaped ridge provided in a pair of heat transfer plates forming the heat exchange chamber into the heat exchange chamber. A plate-type heat exchanger characterized by being formed by contact with

[4] The plate-type heat exchanger according to claim 3, wherein the mountain-shaped ridge is formed by expanding and deforming a part of the heat transfer plate.

[5] Laminate multiple heat transfer plates so that the first heat exchange chamber for generating or condensing steam and the second heat exchange chamber for heating or cooling are alternately formed between them. In the plate type heat exchanger consisting of

When the heat transfer plates are stacked by arranging a plurality of ridges extending in a mountain range on the front and back surfaces of each heat transfer plate, the ridge lines and the back surfaces of the mountain ridges on the surface of the heat transfer plate are stacked. The ridgeline in each mountain-shaped ridge is in linear contact over the long part in each first heat exchange chamber and each second heat exchange chamber, and each mountain range in each first heat exchange chamber A plurality of tunnel-shaped fluid passages are formed in the portion between the ridges so that both ends open into the first heat exchange chamber, while each of the second heat exchange chambers has the mountain range. A plurality of tunnel-like fluid passages are formed in the part between the ridges so that both ends open into the second heat exchange chamber. Plate type heat exchanger.

[6] The plate-type heat according to claim 5, wherein each of the mountain-shaped ridges in each heat transfer plate is formed by expanding and deforming a part of the heat transfer plate. Exchanger.

[7] The plate-type heat according to claim 5 or 6, wherein each mountain-shaped ridge in each heat transfer plate has a herringbone pattern as viewed from the stacking direction of the heat transfer plates. Exchange ^^.

[8] The plate-type heat exchanger according to claim 5 or 6, wherein each mountain-like ridge in each heat transfer plate is intermittent.

[9] In claim 5 or 6, each of the heat transfer plates has a rectangular shape when viewed from the stacking direction, and the upper side of each rectangular heat transfer plate has both corners on the upper side. The steam outlet from each of the first heat exchange chambers or the steam inlet to each of the first heat exchange chambers is located at one corner of the corner, in the vicinity thereof, or at a part of the upper side. A heating fluid inlet or a heating fluid outlet for each of the second heat exchange chambers or a cooling fluid inlet or a cooling fluid outlet for each of the second heat exchange chambers is provided at a corner or in the vicinity thereof. The lower side of each of the heat transfer plates includes a liquid inlet to the first heat exchange chamber or a corner at or near a corner of the lower side opposite to the vapor outlet or the vapor inlet. Condensation of each first heat exchange chamber force Outlet force Each of the second heat exchanges at or near the other corner that forms a diagonal with the heating fluid inlet or heating fluid outlet or the cooling fluid inlet or cooling fluid outlet of both corners on the lower side. A plate-type heat exchanger having a heating fluid outlet or a heating fluid inlet to the chamber or a cooling fluid outlet or a cooling fluid inlet to each of the second heat exchange chambers.

[10] In the above description of claim 5 or 6, each of the heat transfer plates has a rectangular shape when viewed from the stacking direction, and the upper side of each of the rectangular heat transfer plates has a substantially central portion of the upper side. The steam outlet or steam inlet for each of the first heat exchange chambers is at or near the portion, and the steam for heating the respective second heat exchange chambers at or near one of the corners on the upper side. Cooling fluid input to the inlet or each second heat exchange chamber Each of the rectangular heat transfer plates is provided with a heating steam inlet for each of the second heat exchange chambers or a cooling fluid outlet for each of the second heat exchange chambers at the other corner or in the vicinity thereof. In the lower side or the vicinity thereof, there are provided a liquid supply port to be evaporated to each first heat exchange chamber and a steam condensate outlet for heating to each second heat exchange chamber, or each first heat exchange chamber. A plate-type heat exchanger characterized by the presence of a condensate outlet.

In each of claims 5 and 6, each of the heat transfer plates has a rectangular shape when viewed from the stacking direction, and the upper side of each rectangular heat transfer plate has a substantially central portion or upper portion of the upper side. A steam outlet or steam inlet for each of the first heat exchange chambers is in the vicinity thereof, and one of the corners on the upper side or the vicinity thereof is a heating fluid inlet for the second heat exchange chambers or the vicinity. A cooling fluid inlet for each second heat exchange chamber has a heating fluid outlet for each second heat exchange chamber or a cooling fluid outlet for each second heat exchange chamber at or near the other corner. A vaporized liquid supply port for each of the first heat exchange chambers or a condensed water outlet for each of the first heat exchange chambers is provided at or near the lower side of each of the rectangular heat transfer plates. Characterized by Ruko Plate type heat exchanger.