WO2010013608A1

WO2010013608A1 - Plate heat exchanger used as evaporator or condenser

Info

Publication number: WO2010013608A1
Application number: PCT/JP2009/062943
Authority: WO
Inventors: 淳一中村; 健司楠; 稔松下; 光弘渡邊; 磐雄澤田; 博深田; 誠子土肥
Original assignee: 株式会社ササクラ; 株式会社日阪製作所
Priority date: 2008-07-29
Filing date: 2009-07-17
Publication date: 2010-02-04
Also published as: TW201013151A; JPWO2010013608A1

Abstract

In a plate heat exchanger, a plurality of heat transfer plates (12) are stacked in such a manner that a plurality of first heat exchange chambers (15) and a plurality of second heat exchange chambers are alternately formed between the heat transfer plates, and steam is generated or condensed in the first heat exchange chambers. An evaporation capacity when the steam is generated or a condensing capacity when the steam is condensed is increased in the heat exchanger. A large number of first raised parts (30) of a truncated cone shape projecting into the first heat exchange chamber (15) and a large number of second raised parts (31) of a truncated cone shape projecting into the second heat exchange chamber (16) are provided on each heat transfer plate (12). The first raised parts (30) are brought into contact with each other in the first heat exchange chamber (15), and the second raised parts (31) are brought into contact with each other in the second heat exchange chamber (16).

Description

Plate-type heat exchanger used as an evaporator or condenser

The present invention generates steam in a plate-type heat exchange device in which a plurality of rectangular heat transfer plates are laminated so that first heat exchange chambers and second heat exchange chambers are alternately formed therebetween. The present invention relates to a plate-type heat exchange device that is used as an evaporator or as a condenser that condenses steam.

Patent Document 1 as a prior art describes that the plate type heat exchange device having the above configuration is configured as described below when used as an evaporator.

That is,
“A steam outlet from the first heat exchange chamber is connected to one of the left and right corners on the upper side of the heat transfer plate, and the steam outlet of the left and right corners on the lower side of the heat transfer plate. One of the corners is provided with an evaporating liquid inlet to each of the first heat exchange chambers, and the second heat is provided at the other of the left and right corners on the upper side of the heat transfer plate. A heating fluid inlet to the exchange chamber is provided at the other of the left and right corners on the lower side of the heat transfer plate, respectively.
It is configured as follows.

However, with this configuration, the liquid to be evaporated supplied to one corner of the first heat exchange chamber mainly has a direction in which the pressure loss is lowest, that is, while boiling and evaporating in the first heat exchange chamber. The heating fluid supplied to one corner of the second heat exchange chamber mainly has the lowest pressure loss while flowing substantially linearly in the direction toward the one corner and the diagonal corner. The fluid flows widely throughout the first and second heat exchange chambers by flowing in a substantially linear direction in the second direction, that is, in a direction toward the one corner and the diagonal corner. Since it cannot be dispersed and the entire surface of the heat transfer plate cannot be used effectively for heat exchange, the evaporation capacity per unit heat transfer area is low.

Moreover, the said patent document 1 uses the plate type heat exchange apparatus of the said structure as a condenser,
“The vapor outlet is a vapor inlet, the liquid to be evaporated is a condensed liquid outlet, the heating fluid inlet is a cooling fluid inlet, and the heating fluid outlet is a cooling fluid outlet.”
The structure is as follows.

Even in this case, as in the evaporator, the fluid flows widely in the first and second heat exchange chambers by flowing the fluid mainly in the diagonal direction in the first and second heat exchange chambers. In other words, the entire surface of the heat transfer plate cannot be used effectively for heat exchange, so the condensation capacity per unit heat transfer area is low.

Therefore, the present inventors have proposed a plate-type heat exchange device that can be used as an evaporator or a condenser as described in Patent Document 2 in the prior invention.

That is, the “plate heat exchanger used as an evaporator or condenser” of the invention of the prior application is
“A plurality of rectangular heat transfer plates are laminated so that a plurality of first heat exchange chambers and a plurality of second heat exchange chambers are alternately formed between them. In addition, a steam outlet or a steam outlet for the first heat exchange chamber is provided at one corner of a lower side of each heat transfer plate, and a liquid inlet or a condensed water outlet for the first heat exchange chamber is provided, A heating fluid inlet and a heating fluid outlet or a cooling fluid inlet and a cooling fluid outlet for the second heat exchange chamber are provided side by side on one side of the left and right sides of each heat transfer plate, In each second heat exchange chamber, a fluid passage extending from the heating fluid inlet or the cooling fluid inlet to the heating fluid outlet or the cooling fluid outlet is formed in a folded shape in the left-right direction. 1 In the heat exchange chamber, the bottom A distribution fluid passage extending in the horizontal direction along the left and right sides and communicating with both of the vaporized liquid inlets, and the steam outlet along a pair of heat transfer plates forming the first heat exchange chamber from the distribution fluid passage. A plurality of first tunnel-like fluid passages configured to extend in the vertical direction toward the left and right are formed at appropriate intervals in the left-right direction, and further, the second fluid passage in the second heat exchange chamber has the second fluid passage. A plurality of second tunnel-like fluid passages configured to extend in the left-right direction along a pair of heat transfer plates forming the heat exchange chamber are formed at appropriate intervals in the vertical direction.
It was the composition.

Japanese Patent Laid-Open No. 9-299927 International Publication WO2006 / 077785

However, according to the configuration proposed in the invention of the prior application, when used as an evaporator, the liquid to be evaporated entering the first heat exchange chamber from the inlet of the liquid to be evaporated on the lower side is a fluid distribution passage extending laterally at the bottom of the liquid. And is distributed to each of the plurality of first tunnel-like fluid passages through the first tunnel-like fluid passages, and in the first tunnel-like fluid passages, the vapors are boiled and evaporated to flow upward toward the horizontally elongated steam outlet, (2) The heating fluid that has entered the heat exchange chamber flows in the second tunnel-like fluid passage in the folded fluid passage in the left-right direction toward the heating fluid outlet, whereby the liquid to be evaporated and the heating fluid Can be distributed throughout the first heat exchange chamber and the second heat exchange chamber, so that the heat transfer area can be effectively utilized.

Also, when used as a condenser, the steam that has entered the first heat exchange chamber from the horizontally long steam outlet is distributed to a plurality of first tunnel fluid passages, and the inside of the first tunnel fluid passages. , It is condensed by cooling when it flows downward, and this condensed liquid is collected in a fluid distribution passage extending laterally at the bottom, and then flows out from both condensed liquid outlets on the lower side, and enters the second heat exchange chamber The cooling fluid flows in the second tunnel-shaped fluid passage in the folded fluid passage in the left-right direction toward the cooling fluid outlet, thereby allowing the steam and the cooling fluid to pass through the first heat exchange chamber and Since the entire second heat exchange chamber can be spread, effective use of the heat transfer area can be achieved.

In this way, effective use of the heat transfer area is achieved, and an efficient plate heat exchange device can be constructed, but the plate type used as the evaporator or condenser of the present invention can be realized. A fresh water generator (a device that produces fresh water from seawater by combining an evaporator and a condenser), which is a suitable application of a heat exchange device, or a part of a concentrator, etc. It was necessary to improve the performance.

The target fluid in the fresh water generator is seawater and is corrosive. In addition, it must be able to withstand the holding pressure of the system in order to connect to a fluid system such as sea water in the ship.

To meet this requirement, the heat transfer plate of Patent Document 2 was not always sufficient. In addition, the concentrators often handle corrosive fluids and have similar problems.

In the heat transfer plate described in Patent Document 2, the exact pressure resistance and heat transfer performance are unknown because no special technique is disclosed regarding the thickness and the pattern provided on the plate.

If the fluid to be handled is not corrosive and the working pressure is not particularly high, it is possible to use a low-grade material and manufacture it with thick plates according to the required pressure resistance, in which case there is no pattern. However, it can be used economically without any problem in terms of pressure resistance.

However, if the fluid to be handled is corrosive, an expensive material with high corrosion resistance must be used. For this reason, it is necessary to use an extremely thin heat transfer plate instead of a thick plate for economic reasons. It will not be.

In other words, in order to apply commercially as the fresh water generator, etc., considering the economy, the thickness of the heat transfer plate made of an expensive material is made as thin as possible, and the pressure resistance of the thin heat transfer plate is increased. For this purpose, a pattern is provided on the heat transfer plate so as to contact the adjacent heat transfer plate at many points to support the pressure received by the heat transfer plate, and the heat transfer performance is improved by effectively using the pattern. It is essential to reduce the required area or number of sheets as much as possible.

The inventors of the present invention repeated trial manufactures with various heat transfer plates, and found a heat transfer plate having a pattern that is optimal for corrosive fluids such as seawater and high pressure, that is, unevenness.

Although the present invention basically follows the idea of the invention of the prior application, it is a technical problem to solve the problems of the invention of the prior application.

In order to achieve this technical problem, claim 1 of the present invention provides:
“A plurality of rectangular heat transfer plates are laminated so that a plurality of first heat exchange chambers and a plurality of second heat exchange chambers are alternately formed between them. , A vapor outlet from the first heat exchange chamber is provided in a horizontally long shape along the upper side, and an evaporating liquid inlet communicating with the first heat exchange chamber is provided at least one of the lower sides of the heat transfer plate A heating fluid inlet and a heating fluid outlet communicating with the second heat exchange chamber are arranged vertically on one side of the left and right sides of the heat transfer plate. In the exchange chamber, a fluid passage extending from the heating fluid inlet to the heating fluid outlet is formed in a folded shape in the left-right direction by a partition member,
The heat transfer plate has first raised portions formed by bulging and deforming the heat transfer plate into the shape of a cone so as to protrude into the first heat exchange chamber, and arranged at appropriate intervals in the vertical and horizontal directions. A plurality of the first raised portions are in the shape of a truncated cone having a flat top, and the top flat surfaces are in contact with each other in the first heat exchange chamber. The heat transfer plate has a second raised portion formed by bulging and deforming a portion between the first raised portions of the heat transfer plate into a cone shape so as to protrude into the second heat exchange chamber, A plurality of second ridges are provided in the vertical and horizontal directions at appropriate intervals. The second ridges are in the shape of truncated cones with the tops being flat, and the top planes are mutually connected in the second heat exchange chamber. It is a structure to touch. "
It is characterized by that.

Claim 2 of the present invention includes:
“A plurality of rectangular heat transfer plates are laminated so that a plurality of first heat exchange chambers and a plurality of second heat exchange chambers are alternately formed between them. , A steam inlet to the first heat exchange chamber is formed in a horizontally long shape along the upper side, and a condensed liquid outlet communicating with the first heat exchange chamber is provided at least at one corner of the lower side of the heat transfer plate. The cooling fluid inlet and the cooling fluid outlet that communicate with the second heat exchange chamber are provided side by side on one side of the left and right sides of the heat transfer plate. In the heat exchange chamber, a fluid passage extending from the cooling fluid inlet to the cooling fluid outlet is formed by folding in the left-right direction with a partition member,
The heat transfer plate has first raised portions formed by bulging and deforming the heat transfer plate into the shape of a cone so as to protrude into the first heat exchange chamber, and arranged at appropriate intervals in the vertical and horizontal directions. A plurality of the first raised portions are in the shape of a truncated cone having a flat top, and the top flat surfaces are in contact with each other in the first heat exchange chamber. The heat transfer plate has a second raised portion formed by bulging and deforming a portion between the first raised portions of the heat transfer plate into a cone shape so as to protrude into the second heat exchange chamber, A plurality of second ridges are provided in the vertical and horizontal directions at appropriate intervals. The second ridges are in the shape of truncated cones with the tops being flat, and the top planes are mutually connected in the second heat exchange chamber. It is a structure to touch. "
It is characterized by that.

Claim 3 of the present invention provides:
“In the description of claim 1, the communication with the first heat exchange chamber at the inlet of the liquid to be evaporated is configured to communicate through a small hole.”
It is characterized by that.

Claim 4 of the present invention provides:
“In the first or second aspect of the present invention, the first ridge and the second ridge are a regular quadrilateral or an array substantially close to a regular quadrilateral, and the regular quadrilateral has a diagonal up and down. It is a regular quadrilateral with direction and horizontal direction. "
It is characterized by that.

Claim 5 of the present invention provides:
“In the description of any one of the first to fourth aspects, the partition member is formed by forming a string-like body made of a soft elastic body and is sandwiched between the two heat transfer plates. A plurality of plate-like pieces bonded to one of the heat transfer plates are integrally provided at a plurality of locations along the longitudinal direction.
It is characterized by that.

Claim 6 of the present invention provides:
“In the description of claim 5, a part of the string-like body in the diametrical direction is fitted in a recessed groove provided in one of the heat transfer plates.”
It is characterized by that.

First, claim 1 is a case of using as an evaporator.

In each first heat exchange chamber, the liquid to be evaporated such as water entering from the inlet of the liquid to be evaporated in the lower part rises while boiling and evaporating by heating by heat transfer from each second heat exchange chamber and becomes steam. After the state change, the steam flows from the bottom to the top in the first heat exchange chambers, such as going out from the horizontally long steam outlet.

The plurality of first raised portions protruding into the first heat exchange chambers are in the shape of truncated cones and arranged in the vertical and horizontal directions, so that the first heat exchange chambers are directed upward. The steam that flows through the first ridges is divided into two left and right flows every time it hits the lower surface of the first ridges, and the steam that flows in the left and right directions repeats. Since the steam flow can be greatly expanded in a direction perpendicular to the steam flow direction, the steam flow can be reliably dispersed in the entire width direction of the first heat exchange chamber.

That is, the entire surface of the heat transfer plate can be effectively used without forming the tunnel-like passage described in Patent Document 2.

In addition, the first bulges support the pressure from the fluid in the second heat exchange chamber, which is usually at a higher pressure, by providing them at appropriate intervals. Deformation can be prevented.

Furthermore, as a result of the experiment, the first ridges provided at appropriate intervals not only disperse the fluid flow properly, but also give a moderate turbulence in spite of a slight increase in pressure loss, and the heat transfer coefficient is reduced. It turns out that it improves significantly.

As the heat exchange plate pattern, the most commonly used shape, herringbone, has a pressure loss that is too high, which has the adverse effect of suppressing evaporation and is not only inefficient but also poorly distributed. I couldn't omit it either.

In the case of the present invention, the first heat exchange chamber, that is, the evaporating fluid flows with the long side of the horizontally long heat transfer plate as the flow width and the short side as the flow distance. However, in the flat plate, the flow disturbance is small, the efficiency is poor, and the dispersion is also poor. By providing the first ridges at appropriate intervals, both can be remarkably improved, and a thin heat transfer plate can be used. Not only is the amount of material required, but also the heat transfer resistance through the heat transfer plate can be reduced to reduce the required area.

On the other hand, in the folded fluid passage in the left-right direction in each second heat exchange chamber, the heating fluid flows in the left-right direction.

The plurality of second raised portions protruding into the respective second heat exchange chambers are in the shape of truncated cones and arranged in the vertical and horizontal directions, so that the folded fluid passages are arranged in the horizontal direction. The heating fluid that flows through the second bulge flows repeatedly while being spread in the vertical direction at each second bulge, so that each time it hits the side surface of each second bulge, the flow is divided into two flows. Thus, the flow of the heating fluid can be greatly expanded in a direction perpendicular to the flow direction of the heating fluid.

In the second heat exchange chamber, that is, liquid heating water, in the present invention, the short side of the horizontally long heat transfer plate flows with the short side as the flow width and the long side as the flow distance. Along with this, the structure is designed to improve dispersion and heat transfer efficiency. However, since the flowing fluid is so small that it does not compare with evaporative vapor in volume, the flow is less turbulent and the efficiency is poor, and the dispersion is poor. In Patent Document 2, a folded flow is used to reduce the flow path width and increase the flow velocity to improve efficiency.

However, when that alone was not sufficient, the dispersion and efficiency were significantly improved by providing the second raised portions of the present invention at appropriate intervals.

In addition, in claim 1, since the first raised portion and the second raised portion are formed in a truncated cone shape and the top planes thereof are in contact with each other, tolerances during press forming are provided. Even if the heat transfer plates are slightly displaced due to assembly tolerances, subtle movements during operation, etc., it is possible to ensure that the top planes are in contact with each other, so that the pressure applied to each heat transfer plate can be ensured. Can be supported.

Next, claim 2 is a case of using as a condenser.

When the steam that has entered the first heat exchange chamber from the horizontally long steam inlet flows downward from the horizontally long steam inlet, it is condensed by cooling due to heat transfer to each second heat exchange chamber. Steam flows in the first heat exchange chamber from the top to the bottom, such that water collects at the bottom of the first heat exchange chamber and exits from both condensate outlets.

The plurality of first raised portions protruding into the first heat exchange chambers are in the shape of truncated cones and arranged in the vertical direction and the horizontal direction, so that the first heat exchange chambers are directed downward. When the steam flowing in the first ridge portion is divided into two left and right flows each time it hits the upper surface of each first ridge portion, Since the flow of the steam can be greatly expanded in a direction perpendicular to the flow direction of the steam, the steam can be surely dispersed in the entire width direction in the first heat exchange chamber.

As the heat transfer plate pattern, the most commonly used shape, herringbone, has a pressure loss that is too high, which has the adverse effect of suppressing condensation and is not efficient, and is not sufficiently distributed, resulting in a tunnel-like passage. I couldn't omit it either.

In the case of the present invention, the first heat exchange chamber, that is, the large volume of steam that condenses, flows with the long side of the horizontally long heat transfer plate as the flow width and the short side as the flow distance. However, in the flat plate, the flow turbulence is small, the efficiency is poor, and the dispersion is also poor. By providing the first ridges at appropriate intervals, both can be remarkably improved, and a thin heat transfer plate is used. In addition to being able to reduce the required material, the heat transfer resistance through the heat transfer plate can also be reduced and the required area can be reduced.

On the other hand, in the folded fluid passage in the left-right direction in each second heat exchange chamber, the cooling fluid flows in the left-right direction.

The plurality of second raised portions protruding into the respective second heat exchange chambers are in the shape of truncated cones and arranged in the vertical and horizontal directions, so that the folded fluid passages are arranged in the horizontal direction. The cooling fluid that flows through the second bulge flows repeatedly while being spread in the vertical direction at each second ridge so that each time it hits the side surface of each second bulge, the flow is divided into two flows. Therefore, the flow of the cooling fluid can be greatly spread in the direction perpendicular to the flow direction of the cooling fluid, so that it can be surely dispersed in the folded fluid passage in the entire width direction. .

In the second heat exchange chamber, that is, liquid cooling water, in the present invention, since the short side of the horizontally long heat transfer plate flows as the flow width and the long side as the flow distance, the pressure loss is the largest. Along with this, the structure is designed to improve dispersion and heat transfer efficiency. However, since the flowing fluid is so small that it is incomparable with the vapor that condenses volumetrically, the flow is less disturbed and the efficiency is poor and the dispersion is also poor. In Patent Document 2, a folded flow is used to reduce the flow path width and increase the flow velocity to improve efficiency.

Even in this case, in claim 2, since the first raised portion and the second raised portion are formed in a truncated cone shape, and the top surfaces thereof are in contact with each other, press forming is performed. Even if each heat transfer plate is slightly displaced due to time tolerance, assembly tolerance, or slight movement during operation, it is possible to ensure that the top planes are in contact with each other. The pressure can be reliably supported.

In the first aspect, as described in the third aspect, the communication with the first heat exchange chamber at the inlet of the liquid to be evaporated is configured to communicate with the first heat exchange chamber through a small hole. Regulating and controlling the amount of liquid to be evaporated entering the chamber through the small holes keeps the same and uniform in all the first heat exchange chambers regardless of differences or fluctuations in other conditions, and makes the evaporation uniform. , All the first heat exchange chambers can be operated uniformly to achieve the highest efficiency.

Further, in the first or second aspect, as described in the fourth aspect, the regular quadrilateral in the arrangement of the first and second bulges is a positive quadrangle whose diagonal is up and down and left and right. By making the quadrilateral, the flow of the steam and the heating fluid or the cooling fluid is such that each first ridge or each second ridge in the first first row of the rows perpendicular to the flow direction. In this case, the flow is divided into two left and right flows, and each of the two divided right and left flows is a first ridge or each second ridge in the first row in a second row located downstream of the first row. Since it flows while repeating each of the first and second ridges located between the two parts and further dividing into two left and right flows, the flow resistance can be reduced with respect to the flow direction. To increase the spread in the perpendicular direction Because it has an advantage of more conducive to the mentioned effects.

Furthermore, by configuring as described in claim 5, the partition member interposed between the heat transfer plates can be formed into a string-like body, and the heat transfer area can be increased by that amount. However, when the heat transfer plate is assembled and disassembled, the string-like body is provided integrally with the string-like body so that the string-like body falls from the heat transfer plate or deviates from a predetermined mounting position. Since it can be surely prevented by adhering one piece to one heat transfer plate, the workability in assembling and disassembling the plate heat exchanger can be improved.

In this case, by fitting a part of the string-like body in the diametrical direction into a recessed groove provided in one heat transfer plate as in claim 6, the string-like body is more reliably prevented from shifting. Therefore, the workability at the time of assembling and disassembling the plate heat exchanger can be further improved.

It is a side view which shows the plate type heat exchange apparatus by 1st Embodiment. It is a top view of FIG. 3 is an enlarged sectional view taken along line III-III in FIG. 1 and a sectional view taken along line III-III in FIG. FIG. 6 is a view showing a second heat exchange chamber in an enlarged sectional view taken along line IV-IV in FIG. 1 and a sectional view taken along line IV-IV in FIG. 5. FIG. 5 is an enlarged sectional view taken along line VV in FIGS. 3 and 4. FIG. 6 is an enlarged sectional view taken along line VI-VI in FIGS. 3 and 4. FIG. 7 is an enlarged sectional view taken along the line VII-VII in FIGS. 3 and 4. It is an enlarged view which shows the partial principal part in FIG. FIG. 9 is a sectional view taken along the line IX-IX in FIG. 8. It is a figure which shows the modification in FIG. It is a figure which shows the plate type heat exchange apparatus by 2nd Embodiment. It is a top view of FIG. It is a figure which shows a 1st heat exchange chamber by the XIII-XIII enlarged sectional view of FIG. 11, and the XIII-XIII sectional view of FIG. FIG. 16 is a view showing the second heat exchange chamber in the XIV-XIV enlarged sectional view of FIG. 11 and the XIV-XIV sectional view of FIG. FIG. 15 is an enlarged cross-sectional view taken along line XV-XV in FIGS. 13 and 14. FIG. 15 is an enlarged cross-sectional view taken along line XVI-XVI in FIGS. 13 and 14. FIG. 15 is an enlarged sectional view taken along the line XVII-XVII in FIGS. 13 and 14. It is sectional drawing of the same location as FIG. 4 in 3rd Embodiment. FIG. 19 is an enlarged cross-sectional view taken along the line XIX-XIX in FIG. 18, (a) shows a state before assembly, and (b) shows a state after assembly. FIG. 19 is an enlarged cross-sectional view taken along the line XX-XX in FIG. 18, (a) shows a state before assembly, and (b) shows a state after assembly. It is sectional drawing of the same location as FIG. 14 in 4th Embodiment. FIG. 22 is an enlarged cross-sectional view taken along the line XXII-XXII in FIG. 21, where (a) shows a state before assembly, and (b) shows a state after assembly. FIG. 22 is an enlarged cross-sectional view taken along the line XXIII-XXIII in FIG. 21, where (a) shows a state before assembly and (b) shows a state after assembly.

Embodiments of the present invention will be described below with reference to the drawings.
[First Embodiment]
1 to 9 show a first embodiment of the present invention and show a plate heat exchanger 11 used as an evaporator.

This plate-type heat exchange device 11 includes a plurality of heat transfer plates 12 made of a relatively thin metal plate in a horizontally-long rectangular shape, and a first seal body 13 and a second seal body 14 that are also used as spacers are alternately arranged around the plate. And a plurality of first heat exchange chambers 15 that are sealed with the first seal body 13 and a plurality of seals that are sealed with the second seal body 14. The second heat exchange chambers 16 are alternately formed, and the laminate is fixed to a supporting fixed face plate 17 disposed on one end face thereof and a movable face plate 18 provided on the other end face by a plurality of bolts 19. It is configured to be fastened in the stacking direction.

Further, the heat exchange device 11 is fixed to the supporting fixed face plate 17 so that a pair of left and right guide rods 20 protrude in the stacking direction, and both guide rods 20 are attached to the heat transfer plates 12. By slidably inserting into the through holes 12a and the through holes drilled in the movable face plate 18, the heat transfer plates 12 and the movable face plate 18 are fixed to the support by the guide rods 20. The face plate 17 is supported so as to be movable in the stacking direction.

As shown in FIGS. 3 and 4, each heat transfer plate 12 has a steam outlet 21 formed in a horizontally long shape in the upper side portion thereof, and one of the left and right corners in the lower side. A liquid inlet 22 to be evaporated is drilled in the corner of the liquid crystal. Further, a heating fluid inlet 23 and a heating fluid outlet 24 are vertically drilled in one of the left and right sides. Has been.

As shown in FIG. 3, the first seal body 13 that forms the periphery of each of the first heat exchange chambers 15 includes

seal pieces

13 a and 13 b that surround the heating fluid inlet 23 and the heating fluid outlet 24. And a seal piece 13c that surrounds the liquid inlet 22 to be evaporated, and the horizontally long steam outlet 21 communicates with the upper portion of each first heat exchange chamber 15 for the heating. The fluid inlet 23 and the heating fluid outlet 24 are configured not to communicate with the first heat exchange chamber 15.

Further, as shown in FIG. 4, the second seal body 14 forming the periphery of each of the second heat exchange chambers 16 includes

seal pieces

14a and 14b that surround the vapor outlet 21 and the liquid inlet 22 to be evaporated. Are integrally provided, and the heating fluid inlet 23 and the heating fluid outlet 24 communicate with one side of each of the second heat exchange chambers 16, and the vapor outlet 21 and the vaporized liquid inlet 22 are connected to the second heat exchange chamber 16. The heat exchange chamber 16 is configured not to communicate with the heat exchange chamber 16.

Further, the second seal body 14 is integrally provided with a partition member 14c that integrally extends in the left-right direction from a portion between the heating fluid inlet 23 and the heating fluid outlet 24. Each of the second heat exchange chambers 16 is configured to have a folded fluid passage that is folded in the left-right direction from the heating fluid inlet 23 toward the heating fluid outlet 24.

On the other hand, each of the first heat exchange chambers 15 and the liquid inlet 22 is a seal piece of the second seal body 14 outside the seal piece 13c of the first seal body 13 of the heat transfer plate 12. It is configured to communicate with each other through a plurality of small holes 25 drilled in a portion inside 14b.

The vaporized liquid inlet 22 and the small holes 25 can be provided at the left and right corners of the lower side of the heat transfer plate 12.

The outer surface of the supporting fixed face plate 17 communicates with a vapor outlet pipe 26 communicating with the vapor outlet 21, a liquid supply pipe 27 to be evaporated communicating with the liquid inlet 22, and a heating fluid inlet 23. A heating fluid supply pipe 28 is connected to a heating fluid outlet pipe 29 communicating with the heating fluid outlet 24.

As shown in FIG. 3, each heat transfer plate 12 has the heat transfer plate 12 placed on the entire portion of the heat transfer plate 12 inside the first seal body 13. A large number of first raised portions 30 formed by bulging and deforming toward the inside of the chamber 15 are provided in an array of appropriate intervals in the vertical direction and the horizontal direction.

As shown in FIGS. 8 and 9, each first raised portion 30 is based on a cone having a bottom surface with a diameter D0, and the top of the cone is a plane 30a parallel to the bottom surface of the cone. And the arrangement is a regular quadrilateral having a dimension P of one side or an arrangement substantially close to a regular quadrilateral, A regular quadrilateral is a regular quadrilateral with its diagonals in the vertical and horizontal directions.

In addition to this, the first raised portions 30 are configured such that their top planes 30a are in contact with each other in the first heat exchange chamber 15.

In this case, the diameter D1 of the top plane 30a of one first ridge 30 out of the first ridges 30 contacting each other in the first heat exchange chamber 15 is the top plane of the other first ridge 30. It is configured to be appropriately smaller than the diameter D2 of 30a, thereby reducing the reduction of the heat transfer area as much as possible by contacting the top planes 30a of the first raised portions 30 with each other. .

Further, as shown in FIG. 4, each of the heat transfer plates 12 includes an entire portion of the heat transfer plate 12 on the inner side of the second seal body 14. A plurality of second raised portions 31 formed by bulging and deforming a portion between the raised portions 30 toward the inside of the second heat exchange chamber 16 are provided in an arrangement with appropriate intervals in the vertical direction and the horizontal direction. Yes.

Similarly, as shown in FIGS. 8 and 9, each of the second raised portions 31 is based on a cone having a bottom surface with a diameter D0, and the top of the cone is parallel to the bottom surface of the cone. Since it is in the shape of a truncated cone having a height H formed by cutting so as to form a plane 31a, and located in a region between the first raised portions 30, the arrangement is Similar to the first raised portion 30, it is a regular quadrilateral with a dimension P of one side or an array substantially close to a regular quadrilateral, and this regular quadrilateral is a regular quadrilateral whose diagonal is up and down and left and right. It is a shape.

In addition, each of the second raised portions 31 is configured such that the flat surface 31a at the top thereof is in contact with each other in the second heat exchange chamber 16.

Even in this case, the diameter D1 of the top flat surface 31a of one second raised portion 31 of the second raised portions 31 that are in contact with each other in the second heat exchange chamber 16 is equal to that of the second raised portion 31. The size is appropriately smaller than the diameter D2 of the top flat surface 31a, and thus, the reduction of the heat transfer area due to the contact of the top flat surfaces 31a of the second raised portions 31 with each other is minimized. ing.

When the steam inlets 21 are formed in the respective heat transfer plates 12 in a horizontally long shape, the upper and lower connecting pieces 21a are left in the horizontally long steam outlets 21 so that the steam inlets 21 have a horizontally long shape. In this configuration, the strength of the heat transfer plate 12 is prevented from being reduced.

In the above-described configuration, the liquid to be evaporated such as water supplied from the liquid supply pipe 27 to be evaporated in the supporting fixed face plate 17 enters the liquid to be evaporated inlet 22 and passes through the small hole 25 from the liquid to be evaporated inlet 22. The first heat exchange chamber 15 enters the bottom.

The liquid to be evaporated is directed upward from below as indicated by an arrow A while boiling and evaporating in the first heat exchange chamber 15 on both the left and right sides by heating by heat transfer from each second heat exchange chamber 16. Then, after a part of the state changes to steam, it reaches the upper horizontally long steam outlet 21 and exits from the steam outlet pipe 26 in the supporting fixed face plate 17.

In this case, the first raised portions 30 projecting into the first heat exchange chambers 15 are in the shape of truncated cones, and a large number of them are regular quadrilaterals whose diagonals are up and down and left and right. Due to the arrangement, the steam flowing upward in the first heat exchange chamber 15 as indicated by the solid arrow A in FIG. 8 is arranged in a direction perpendicular to the flow direction. Of each of the first ridges 30 on the upstream side of the first ridges 30 are divided into two flows on the left and right sides. Since it flows while repeatedly dividing into two left and right flows when it hits each first raised portion 30 located between them, the flow resistance caused by friction with the wall surface in the steam can be greatly reduced. The flow is left Widened greatly direction is reliably dispersed throughout the first heat exchange chamber 15.

The small holes 25 for introducing the liquid to be evaporated into the first heat exchange chambers 15 regulate the amount of the liquid to be evaporated introduced into the first heat exchange chambers 15 with the small holes 25. As a result, regardless of the difference or fluctuation of other conditions, the first heat exchange chamber 15 is kept the same and uniform, and the evaporation is made uniform.

On the other hand, in the folded fluid passage in the left-right direction in each second heat exchange chamber 16, the heating fluid flows from the heating fluid inlet 23 and flows in the left-right direction as shown by arrow B, and then the heating fluid Exit from fluid outlet 24.

In this case, the second raised portions 31 protruding into the respective second heat exchange chambers 16 are in the shape of truncated cones, and many of them are regular quadrilaterals whose diagonals are up and down and left and right. Due to the arrangement, the heating fluids flowing in the left-right direction in the folded fluid passage as shown by arrow B in FIG. 8 are arranged in a row perpendicular to the flow direction. Of these, the upper and lower flows are divided into two upper and lower flows, and each of the upper and lower flows is divided between the second raised portions 31 on the upstream side of the upstream side. When the second ridge 31 is located on the second raised portion 31, the flow is further divided into two parts, the upper and lower parts, so that the flow is made up and down under the condition that the flow resistance caused by the friction with the wall surface can be reduced. Large and wide in the direction It is to be securely dispersed throughout the second heat exchange chamber 16.

In each of the first heat exchange chambers 15, a plurality of first raised portions 30 provided on the heat transfer plate 12 forming both sides thereof are in contact with each other, while in each of the second heat exchange chambers 16, Since a plurality of second raised portions 31 provided on the heat transfer plates 12 forming both sides thereof are in contact with each other, the heat transfer plates 12 can be supported with each other.

Moreover, each of the first raised portion 30 and the second raised portion 31 is obtained by bulging and deforming the heat transfer plate 12 into the shape of a truncated cone. Heat transfer area can be increased.

By the way, according to the experiments by the present inventors, in the first raised portion 30 and the second raised portion 31, the one side dimension P in the regular quadrilateral of the arrangement is 20 to 23 mm, and the diameter of the bottom surface in the truncated cone. It was preferable to set D0 to 9-12 mm.

In addition, the said 1st Embodiment was a case where the 1st protruding part 30 and the 2nd protruding part 31 which protrude in the said 1st heat exchange chamber 15 were made into the shape of the truncated cone.

The present invention is not limited to this, and the first and second raised portions 30 'and second raised portions in which the first raised portion and the second raised portion have the shape of a truncated regular quadrangular pyramid as in the modification shown in FIG. The portion 31 'can be configured.

That is, the first raised portion 30 ′ and the second raised portion 31 ′ of this modification are cut out so that the top of the regular quadrangular pyramid is parallel to the bottom of the regular quadrangular pyramid, based on the regular quadrangular pyramid. In this way, each of the side faces of the truncated regular square pyramid is inclined with respect to the vertical direction and the horizontal direction.

In this way, when the first raised part 30 'and the second raised part 31' of the truncated regular square pyramid are configured, each side surface of the truncated regular square pyramid is indicated by an arrow A in FIG. It is configured to incline with respect to both the vertical flow and the horizontal flow indicated by arrow B, that is, the diagonal direction of the truncated regular square pyramid is configured to be the vertical direction and the horizontal direction. It is preferable that the flow can be broadened in the transverse direction with respect to the flow direction in a state where the flow resistance can be further reduced.

Similarly, it goes without saying that the first raised portion and the second raised portion can be formed into the shape of a truncated regular pyramid such as a truncated regular hexagonal pyramid or a truncated regular octagonal pyramid. Each side surface of the regular pyramid is preferably configured to be inclined with respect to the vertical direction and the horizontal direction.

By the way, each of the heat transfer plates 1 is provided with the first raised portions 30 and 30 'and the second raised portions 31 and 31', and the heat transfer plate 2 is provided with a truncated cone such as a truncated cone or a truncated regular pyramid. When providing by bulging and deforming into the shape of a cone, a processing method using a press is employed.

In this pressing, the truncated cone height dimension H is set to half the spacing dimension S between the heat transfer plates 12, and the cone angle θ is set to 30 degrees to 120 degrees. Is preferred. In particular, it is more preferable to set 80 degrees to 120 degrees.

That is, by making the height dimension H of the truncated cone half the half of the distance dimension S between the heat transfer plates 12, the plastic deformation caused by pressing when the heat transfer plate 12 bulges and deforms on both the front and back surfaces. While the amount can be the lowest for all truncated cones simultaneously, all truncated cones can be simultaneously formed by pressing by setting the cone angle θ in the truncated cone to 30 degrees or more. Can be easily achieved, and the durability of the press die can be secured.

The workability by pressing the truncated cone and the durability of the press die are improved as the cone angle θ is increased. However, when the cone angle θ exceeds 120 degrees, the truncated cone is configured. In this case, since the diameter of the bottom portion increases and the flow resistance increases, the cone angle θ should be set within a range of 30 to 120 degrees in consideration of these points.

Next, according to experiments by the present inventors, the first raised portions 30, 30 'and the second raised portions 31, 31' are arranged in the shape of a truncated cone and a regular quadrilateral as described above. When the array is provided, the side dimension P in the regular quadrilateral of the array is set to 3 to 8 times the distance dimension S between the heat transfer plates 12, while the top plane of the truncated cone The diameters D1 and D2 at 30a, 30a ′, 31a, and 31a ′ are preferably set to be 1/2 to 3 times the space dimension S between the heat transfer plates 2, and in particular, 1 of the space dimension S. More preferably, the ratio is from / 2 to 1.5 times.

That is, when the one-side dimension P of the regular quadrangular array exceeds eight times the spacing dimension S, the pitch interval along the column direction perpendicular to the flow is widened. Is less effective, and when the one-side dimension P is less than three times the spacing dimension S, the pitch interval along the column direction perpendicular to the flow becomes narrow, so that the flow is dispersed. Although the effect of is high, the flow resistance is greatly increased.

Also, the

top planes

30a, 30a ', 31a, 31a' are for ensuring that they are always in contact with each other against a shift in a direction parallel to the heat transfer surface of each heat transfer plate 12. The minimum value in the diameter dimensions D1 and D2 should be ½ times the spacing dimension S. However, if the diameter dimensions D1 and D2 exceed 3 times the spacing dimension S, the above-described values are Since the diameter at the bottom of the truncated cone is remarkably increased and the flow resistance is increased, the diameter dimensions D1 and D2 are ½ to 3 times the distance dimension S in consideration of these points. Should have been set within the range.
[Second Embodiment]
Next, FIGS. 11 to 17 show a plate heat exchanger 110 used as a condenser according to a second embodiment of the present invention.

This plate type heat exchanging device 110 is basically composed of a large number of heat transfer plates 120 made of a relatively thin metal plate in the form of a horizontally long rectangle, like the plate type heat exchanging device 11 of the first embodiment. A plurality of first seal members 130 are hermetically sealed by the first seal member 130 by laminating the sheets so that the first seal member 130 and the second seal member 140 alternately serving as spacers are alternately sandwiched between them. A heat exchange chamber 150 and a plurality of second heat exchange chambers 160 each having a sealed periphery with the second seal body 140 are alternately formed, and this laminated body is disposed on one end surface thereof for support. The fixed face plate 170 and the movable face plate 180 disposed on the other end face are fastened to each other in the stacking direction by a plurality of bolts 190, while the heat transfer plates 120 and the movable face plate 180 are fixed to the supporting fixed face plate 170. And a configuration that is supported in a state of movable in stacking direction at the guide rod 200.

As shown in FIGS. 13 and 14, each of the heat transfer plates 120 has a steam inlet 210 formed in a horizontally long shape in the upper side portion, and one of the left and right corners in the lower side. Condensed liquid outlet 220 is drilled in the corner of each, and cooling fluid inlet 230 and cooling fluid outlet 240 are drilled side by side in the part of one of the left and right sides. .

As shown in FIG. 13, the first seal body 130 that forms the periphery of each of the first heat exchange chambers 150 includes

seal pieces

130a and 130b that surround the cooling fluid inlet 230 and the cooling fluid outlet 240. Are provided integrally, and the horizontally long steam inlet 210 communicates with the upper portion of each first heat exchange chamber 150 and the condensate liquid outlet 220 communicates with the lower portion. The cooling fluid inlet 230 and the cooling fluid outlet 240 is configured not to communicate with the first heat exchange chamber 150.

Note that the condensed liquid outlet 220 communicating with the lower part in each first heat exchange chamber 150 can be provided at the other corner of the lower side.

Further, as shown in FIG. 14, the second seal body 140 that forms the periphery of each of the second heat exchange chambers 160 has

seal pieces

140 a and 140 b that surround the vapor inlet 210 and the condensed liquid outlet 220. The cooling fluid inlet 230 and the cooling fluid outlet 240 communicate with one side of each of the second heat exchange chambers 160, and the vapor inlet 210 and the condensed liquid outlet 220 are connected to the second heat exchange chamber. The interior of the chamber 160 is not communicated.

Further, the second seal body 140 is integrally provided with a partition member 140c that integrally extends in a left-right direction from a portion between the cooling fluid inlet 230 and the cooling fluid outlet 240. Inside each of the second heat exchange chambers 160, a folded fluid passage is formed that is folded in the left-right direction from the cooling fluid inlet 230 toward the cooling fluid outlet 240.

The outer surface of the supporting fixed face plate 170 has a steam inlet pipe 260 communicating with the steam inlet 210, a condensed liquid outlet pipe 270 communicating with the condensed liquid outlet 220, and a cooling communicating with the cooling fluid inlet 230. A cooling fluid supply pipe 280 and a cooling fluid outlet pipe 290 communicating with the cooling fluid outlet 240 are connected.

Other structures are the same as those of the plate-type heat exchange device 11 according to the first embodiment.

That is, each heat transfer plate 120 is formed by bulging and deforming the heat transfer plate 120 into the shape of a truncated cone so as to protrude into the first heat exchange chamber 150, as shown in FIG. A large number of first raised portions 300 are provided in an arrangement with appropriate intervals in the vertical and horizontal directions, and the first raised portions 300 are configured such that the top surfaces of the first raised portions 300 are in contact with each other in the first heat exchange chamber 150. In addition, the regular quadrilateral of the array is a regular quadrilateral whose diagonal is up and down and left and right.

Further, as shown in FIG. 14, each heat transfer plate 120 is provided with a portion of the heat transfer plate 120 between the first raised portions 300 so as to protrude into the second heat exchange chamber 160. A plurality of second raised portions 310 bulging and deforming into the shape of a head cone are provided in an array with appropriate spacing in the vertical and horizontal directions, and the top surface of the second raised portion 310 is the second flat portion. The regular quadrilaterals that are in contact with each other in the heat exchange chamber 160 and that are arranged in the heat exchange chamber 160 are regular quadrilaterals whose diagonals are up and down and left and right.

In this configuration, water vapor supplied from the steam inlet pipe 260 in the supporting fixed face plate 170 enters the upper part of each first heat exchange chamber 150 from the steam inlet 210.

This steam flows through the first heat exchange chamber 150 from the top to the bottom as shown by the arrow A ′ while condensing by cooling by heat transfer to each second heat exchange chamber 160 on both the left and right sides. After condensing into the liquid, it reaches the condensed liquid outlet 220 at the bottom and exits from the condensed liquid outlet pipe 270 in the supporting fixed face plate 170.

In this case, the first raised portions 300 protruding into the first heat exchange chambers 150 are in the shape of truncated cones, and many of them are regular quadrilaterals whose diagonals are up and down and left and right. Due to the arrangement, the steam flowing downward in the first heat exchange chamber 150 as indicated by the solid arrow A ′ in FIG. 13 is perpendicular to the flow direction. The left and right flows are divided into two left and right flows when hitting each of the first ridges 300 located on the upstream side in the row, and each of the two divided right and left flows is downstream of the first ridges 300 on the upstream side. Since it flows while repeatedly dividing into two left and right flows when hitting each first ridge 300 located between the two, the flow can be reliably dispersed throughout the first heat exchange chamber 150.

On the other hand, in the folded fluid passage in the left-right direction in each second heat exchange chamber 160, the cooling fluid flows in from the cooling fluid inlet 230 and flows in the left-right direction as indicated by the arrow B ', and then cooled. Go out from the fluid outlet 240.

In this case, the second raised portions 310 protruding into the respective second heat exchange chambers 160 are in the shape of truncated cones, and many of them are regular quadrilaterals whose diagonals are up and down and left and right. Due to the arrangement, the cooling fluid flowing in the left-right direction in the folded fluid passage as indicated by arrow B ′ in FIG. 14 is arranged in a direction perpendicular to the flow direction. The upper and lower flows are divided into two upper and lower flows on the upstream side, and each of the upper and lower flows is separated from the upstream side of the second raised portions 310 on the upstream side. Since it flows while repeatedly dividing into two separate upper and lower flows when it hits each second raised portion 310 positioned between them, the flow can be reliably dispersed throughout the second heat exchange chamber 160.

In the second embodiment, it goes without saying that the first raised portion 300 and the second raised portion 310 can be configured as a truncated pyramid such as a truncated quadrangular pyramid as shown in FIG. However, it is preferable that the size, shape, and arrangement of the first raised portion 300 and the second raised portion 310 are the same as those in the first embodiment.
[Third Embodiment]
18 to 20 show a third embodiment.

In the third embodiment, the “plate type heat exchange device 11 as an evaporator” of the first embodiment shown in FIGS. 1 to 10 is folded into each second heat exchange chamber 16. The “partition member 14c” for defining the fluid passage is modified, and other configurations are the same as those in the first embodiment.

That is, the partition member 14c is separated from the second seal body 14 that seals the periphery of the second heat exchange chamber 16, and is long with a small diameter D by a soft elastic body such as heat-resistant rubber. A long string-like body 14c 'is formed, and the string-like body 14c' is formed in a concave groove 12a provided in both heat transfer plates 12 forming a part of the diameter direction on both sides of the second heat exchange chamber 16. In this state, the two heat transfer plates 12 are sandwiched while being elastically deformed.

Further, plate-like pieces 14c ″ having a width W larger than the diameter D of the string-like body 14c ′ are integrally provided at a plurality of locations along the longitudinal direction of the string-like body 14c ′. The plate-like piece 14c ″ is configured to be bonded to one of the heat transfer plates 12 using an adhesive or a double-sided adhesive tape.

However, the figure shows a case where the string-like body 14c ′ is configured to fit into the recessed grooves 12a of the two heat transfer plates 12, but this string-like body 14c ′ is not attached to the string-like body 14c ′. The provided plate-like piece 14c ″ can be configured to be fitted only in the recessed groove 12a in one heat transfer plate 12. The string-like body 14c ′ is attached to one heat transfer plate with an adhesive or You may make it adhere | attach using a double-sided adhesive tape.

According to this configuration, when the heat transfer plate 12 is assembled and disassembled, the heat transfer area can be increased by the amount of the partition member 14c formed by the string-like body 14c ′ having a small diameter D. In addition, the fact that the string-like body 14c ′ having a small diameter falls from the heat transfer plate 12 or deviates from a predetermined attachment position, the plate-like piece 14c ″ provided integrally with the string-like body 14c ′. This can be reliably prevented by adhesion to one heat transfer plate 12.
[Fourth Embodiment]
21 to 23 show a fourth embodiment.

In the fourth embodiment, the “plate type heat exchange device 110 as a condenser” of the second embodiment shown in FIGS. 11 to 17 is folded into each second heat exchange chamber 160. The “partition member 140c” for defining the fluid passage is modified, and other configurations are the same as those of the second embodiment.

That is, the partition member 140c is separated from the second seal body 140 that seals the periphery of the second heat exchange chamber 160, and is long with a small diameter D by a soft elastic body such as heat-resistant rubber. A long string-like body 140c ′ is formed, and the string-like body 140c ′ is formed in a concave groove 120a provided in both heat transfer plates 120 that form part of the diameter direction of both sides of the second heat exchange chamber 160. In this state, the two heat transfer plates 120 are sandwiched while being elastically deformed.

Further, plate-like pieces 140c ″ having a width W larger than the diameter D of the string-like body 140c ′ are integrally provided at a plurality of locations along the longitudinal direction of the string-like body 140c ′. The plate-like piece 140c ″ is configured to be bonded to one of the heat transfer plates 120 using an adhesive or a double-sided adhesive tape.

However, although the figure shows a case where the string-like body 140c ′ is configured to fit into the recessed grooves 120a of the two heat transfer plates 120, the string-like body 140c ′ is connected to the string-like body 140c ′. The provided plate-like piece 140c ″ can be configured to be fitted only in the recessed groove 120a in one heat transfer plate 120 to be bonded. The string-like body 140c ′ can be bonded to one heat transfer plate with an adhesive or You may make it adhere | attach using a double-sided adhesive tape.

According to this configuration, when the heat transfer plate 120 is assembled and disassembled, the heat transfer area can be increased by the amount of the partition member 140c formed as the string-shaped body 140c ′ having a small diameter D. In addition, the fact that the string-like body 140c ′ having a small diameter falls from the heat transfer plate 120 or deviates from a predetermined mounting position, the plate-like piece 140c ″ provided integrally with the string-like body 140c ′. This can be reliably prevented by adhesion to one heat transfer plate 120.

DESCRIPTION OF SYMBOLS 11 Plate type heat exchange apparatus used as an evaporator 110 Plate type heat exchange apparatus used as a condenser 12,120 Heat-

transfer plate

12a, 120a Recessed groove 13,130 1st seal body 14,140

2nd seal body

14c, 140c Partition member 14c ', 140c' String-like body 14c ", 140c" Plate-like piece 15,150 First heat exchange chamber 16,160 Second heat exchange chamber 17,170 Supporting fixed face plate 18,180 Movable face plate 19,190 bolt 20,200 Guide support rod 21 Steam outlet 22 Stated liquid inlet 23 Heating fluid inlet 24 Heating fluid outlet 210 Steam inlet 220 Condensed liquid outlet 230 Cooling fluid inlet 240 Cooling

fluid outlet

30, 30 ′, 300 First raised portion 30a Top plane of the first raised

portion

31, 31 ′, 310 Second raised portion 31a Top plane of the second raised portion

Claims

A plurality of rectangular heat transfer plates are laminated so that a plurality of first heat exchange chambers and a plurality of second heat exchange chambers are alternately formed between the heat transfer plates. A vapor outlet from the first heat exchange chamber is provided in a horizontally long shape along the upper side, and an evaporating liquid inlet communicating with the first heat exchange chamber is provided at least at one corner of the lower side of the heat transfer plate. A heating fluid inlet and a heating fluid outlet communicating with the second heat exchange chamber are arranged side by side on one side of the left and right sides of the heat transfer plate. In the chamber, a fluid passage extending from the heating fluid inlet to the heating fluid outlet is formed in a folded shape in the left-right direction by a partition member,
The heat transfer plate has first raised portions formed by bulging and deforming the heat transfer plate into the shape of a cone so as to protrude into the first heat exchange chamber, and arranged at appropriate intervals in the vertical and horizontal directions. A plurality of the first raised portions are in the shape of a truncated cone having a flat top, and the top flat surfaces are in contact with each other in the first heat exchange chamber. The heat transfer plate has a second raised portion formed by bulging and deforming a portion between the first raised portions of the heat transfer plate into a cone shape so as to protrude into the second heat exchange chamber, A plurality of second ridges are provided in the vertical and horizontal directions at appropriate intervals. The second ridges are in the shape of truncated cones with the tops being flat, and the top planes are mutually connected in the second heat exchange chamber. Plate type used as an evaporator, characterized by contact structure Exchange equipment.
A plurality of rectangular heat transfer plates are laminated so that a plurality of first heat exchange chambers and a plurality of second heat exchange chambers are alternately formed between the heat transfer plates. A vapor inlet to the first heat exchange chamber is provided in a horizontally long shape along the upper side, and a condensed liquid outlet communicating with the first heat exchange chamber is provided at least at one corner of the lower side of the heat transfer plate. On the other hand, a cooling fluid inlet and a cooling fluid outlet communicating with the second heat exchange chamber are arranged vertically on one of the left and right sides of the heat transfer plate. In the exchange chamber, a fluid passage from the cooling fluid inlet to the cooling fluid outlet is formed in a folded shape in the left-right direction by a partition member,
The heat transfer plate has first raised portions formed by bulging and deforming the heat transfer plate into the shape of a cone so as to protrude into the first heat exchange chamber, and arranged at appropriate intervals in the vertical and horizontal directions. A plurality of the first raised portions are in the shape of a truncated cone having a flat top, and the top flat surfaces are in contact with each other in the first heat exchange chamber. The heat transfer plate has a second raised portion formed by bulging and deforming a portion between the first raised portions of the heat transfer plate into a cone shape so as to protrude into the second heat exchange chamber, A plurality of second ridges are provided in the vertical and horizontal directions at appropriate intervals. The second ridges are in the shape of truncated cones with the tops being flat, and the top planes are mutually connected in the second heat exchange chamber. Plate type used as a condenser characterized by a contact structure Exchange equipment.
2. The plate type heat exchange used as an evaporator according to claim 1, wherein the communication with the first heat exchange chamber at the inlet of the liquid to be evaporated is communicated through a small hole. apparatus.
3. The first and second raised portions according to claim 1 or 2, wherein the first raised portion and the second raised portion are arranged in a regular quadrangle or substantially close to a regular quadrangle, and the regular quadrilateral has a diagonal direction in the vertical direction. And a plate-type heat exchange device used as an evaporator or a condenser, wherein the plate-type heat exchanger has a regular quadrilateral shape in the left-right direction.
The partition member according to any one of claims 1 to 4, wherein the partition member is formed by a string-like body made of a soft elastic body and is sandwiched between the heat transfer plates. A plate-type heat used as an evaporator or a condenser, wherein a plate-like piece bonded to one of the heat transfer plates is integrally provided at a plurality of locations along the longitudinal direction. Exchange device.
6. The evaporator according to claim 5, wherein a part of the string-like body in the diametrical direction is fitted in a recessed groove provided in one of the heat transfer plates. Plate type heat exchange device.