JP4848718B2 - Heat exchanger - Google Patents

Description

  The present invention relates to a heat exchanger that is used in a heat exchange ventilator or other air conditioning apparatus and that alternately stacks a plurality of heat transfer plates to alternately form an air path A and an air path B.

  The present applicant has proposed a heat exchanger in which heat transfer plates A101 and heat transfer plates B102 processed by vacuum forming a polystyrene sheet are alternately laminated as a conventional heat exchanger of this type of counter flow ( Patent Document 1).

  Hereinafter, the heat exchanger will be described with reference to FIG.

  The heat transfer plate A101 and the heat transfer plate B102 are square in plan shape, and are obtained by forming a polystyrene sheet by vacuum forming, and then cutting the excess sheet with a Thomson mold or the like. The heat transfer plate A101 is hollow. The substantially L-shaped air passage ribs 103 formed in a convex shape are provided substantially parallel and at substantially equal intervals, and the air passage rib 103 forms a substantially L-shaped air passage A 104 and a heat transfer surface 105.

  At the entrance / exit portion of the air passage A 104, an air passage end surface 106 is provided by bending the edge of the heat transfer plate A 101 in the direction opposite to the convex direction of the air passage rib 103, and the air passage rib 103 has both ends of the air passage rib 103. A plurality of hollow convex protrusions A107 are provided in the same direction as the convex direction.

  The outer peripheral edge portion of the heat transfer plate A101 other than the inlet and outlet of the air passage A104, which is sandwiched between the inlet and outlet of the air passage A104, and is substantially parallel to the air passage portion that is opposed to the air passage. An outer peripheral rib A (not shown) formed in a hollow convex shape in the same direction as the convex direction of the rib 103 is provided, and an outer peripheral rib A 108 b having the same shape is provided at a diagonal of the outer peripheral rib A.

  The outer side surface of the outer peripheral rib A 108 b is bent to the same position as the air passage end surface 106.

An outer peripheral rib B109 having the same shape is provided at the outer peripheral edge of the heat transfer plate A101 other than the entrance and exit of the air passage A104 and the outer peripheral rib A108b. Is substantially orthogonal to the outer peripheral rib A108.

  Note that subscripts at the end of the code have the same functions as the same numbers, but are for distinction due to differences in arrangement, etc.

  The shape of the outer peripheral rib B109 is a hollow convex shape in the same direction as the convex direction of the air passage rib 103, and the central portion of the outer side surface of the outer peripheral rib B 109b is bent to the same position as the heat transfer surface 105 to form the air passage opening 110. Then, both end portions are bent to the same position as the air passage end face 106 to form the air passage end face cover 111.

  On the air path end face 106 side of the outer peripheral rib B109a, there is provided a hollow convex protrusion B112a in the same direction as the convex direction of the airflow rib 103, and a protrusion B112a and a protrusion B112b provided on the heat transfer plate B102 located above the protrusion B112a. Are substantially orthogonal to each other, and the upper surface of the protrusion B112a is in contact with the lower surfaces of the outer peripheral ribs B109a and 109b provided on the heat transfer plate B102 located thereabove.

  The heat transfer plate B102 has a similar relationship with the heat transfer plate A101, and the height of the outer peripheral ribs A108c and 108d of the heat transfer plate B102 in the shape of the heat transfer plate B102 is set equal to the height of the air passage rib 103. Further, the width of the outer peripheral ribs A108c and 108d of the heat transfer plate B102 is formed to be wider than the width of the outer peripheral rib A108b of the heat transfer plate A101.

  In the air passage rib 103 substantially parallel to the outer peripheral rib A 108b of the heat transfer plate A101 and the heat transfer plate B102, a plurality of projections C113 formed in a hollow convex shape in the same direction as the convex direction of the air passage rib 103 are provided, or the air passage An air passage rib laminated portion 114 in which the width of the rib 103 is intermittently widened is provided, and the upper surface of the protrusion C 113 and the lower surface of the air passage rib 103 of the heat transfer plate B 102 located above or the upper surface of the air passage rib laminated portion 114 The protrusion C113 of the heat transfer plate A101 and the heat transfer plate B102 and the air channel rib stacking portion 114 are shifted with respect to the stacking direction so that the lower surface of the heat transfer plate A101 positioned above abuts.

The heat exchanger plate A101 and the heat transfer plate B102 molded as described above are alternately laminated, the air passage A104 and the air passage B115 are alternately formed, and the heat exchanger is configured by heat-welding the outer peripheral side surface, etc. Heat exchange is performed between the fluid flowing through the air passage A104 and the fluid flowing through the air passage B115.
JP 2004-286419 A

  In such a conventional heat exchanger, when the area of the heat transfer plate increases, it becomes easy to bend, and when the pressure received from the fluid flowing through the air passage increases, the adjacent air passage ribs fit together, and the wind There is a problem that the passage height is lowered and the ventilation resistance may increase, and it is required to secure the air passage height and suppress the increase in the ventilation resistance.

  In addition, since the air channel rib laminated portion is wider than the air channel rib, there is a problem that the air passage width is narrowed at the air channel rib laminated portion and the ventilation resistance is increased, and the air resistance is reduced without reducing the air path width. It is required to suppress the increase in

  In addition, since a plurality of L-shaped air passages formed on the square heat transfer plate can have different air passage lengths, there is a difference in the amount of air flowing through each air passage, and after heat exchange of each air passage at the outflow portion There is a problem that a so-called temperature distribution is generated, and improvement of the temperature distribution is required.

Especially when the outlet of a device equipped with a heat exchanger and the outflow part of the heat exchanger are close to each other, there is a possibility that low-temperature air generated by the temperature distribution may be blown out at low outside air temperature, low air flow, etc. .

  In addition, when heat-sealing the outer peripheral side surfaces of the laminated heat transfer plates, there is a problem that the opening height and the air passage height on the outer peripheral side may decrease due to heat shrinkage. It is required to secure the road height and suppress the increase in ventilation resistance.

  Further, there is a problem that man-hours are required for welding work in order to prevent poor welding during heat welding, and it is required to reduce the man-hours for welding work and improve productivity.

  Also, when cutting excess sheets from the heat transfer plate, burrs remain at the inlet or outlet of the air passage, and during heat welding, the opening height of the inlet or outlet can be reduced by the burrs and the ventilation resistance can be increased. Therefore, there is a demand for preventing a decrease in opening height due to burrs and suppressing an increase in ventilation resistance.

  The present invention solves such a conventional problem, and can ensure the air passage height and suppress an increase in ventilation resistance, can improve the temperature distribution, the opening height on the outer peripheral side and the air passage. The height can be secured and the increase in ventilation resistance can be reduced, the number of welding work can be reduced and the productivity can be improved, the decrease in opening height due to burrs can be prevented and the increase in ventilation resistance can be suppressed. It aims to provide a heat exchanger that can be used.

In order to achieve the above object, the heat exchanger according to the present invention includes a plurality of substantially rectangular heat transfer plates A and B, and an air passage A and an air passage formed alternately between the heat transfer plates. In the heat exchanger for exchanging heat between the air flowing through B, the heat transfer plate is substantially L-shaped, and is provided with a plurality of air path holding means formed in a hollow convex shape on one surface of the heat transfer plate. The sheet is integrally molded as a raw material, and a plurality of substantially L-shaped air paths and heat transfer surfaces and inflow and outflow parts are formed at both ends of the air path by the plurality of air path holding means, The heat transfer plate A and the heat transfer plate B have substantially the same shape, and the inflow portion and the outflow portion of the heat transfer plate A face the inflow portion and the outflow portion of the heat transfer plate B. The heat transfer plate A and the heat transfer plate B are alternately rotated by 180 ° so as to be in a positional relationship, and at this time, the heat transfer plate A is substantially parallel to the short side of the heat transfer plate. The air passage portion formed by the passage holding means is an orthogonal flow region, and both the heat transfer plate A and the heat transfer plate B are air passage portions formed by the air passage holding means substantially parallel to the long side of the heat transfer plate. Te, wherein the area other than the cross-flow region and a counter-flow area, by the shape of the air path holding means for forming the counterflow region curvilinear, the in opposing flow region, one of the heat transfer of the heat transfer plate The top of the air path holding means of the other heat transfer plate is brought into contact with the lower surface of the surface.

  By this means, it is possible to obtain a heat exchanger that can secure the air passage height and suppress the increase of the air flow resistance, and can suppress the increase of the air flow resistance without reducing the air passage width.

  Another means is that air path holding means for forming a portion in which the fluid flowing in the air path A and the air path B becomes an opposing flow are arranged at unequal intervals.

  By this means, a heat exchanger capable of improving the temperature distribution of air after heat exchange at the outflow portion of the heat exchanger is obtained.

  The other means is that, among the plurality of air passages formed in an approximately L shape, the air passage width of the air passage having a short air passage length on the shielding means A side is narrow and the air passage length on the shielding means B side is narrow. The air passage holding means are arranged at unequal intervals so that the air passage width of the long air passage is widened.

By this means, it is possible to decrease the air volume of the air path with a short air path length, increase the air volume of the air path with a long air path length, and improve the temperature distribution of the air after heat exchange at the outflow part of the heat exchanger A heat exchanger that can be obtained is obtained.

  Further, the other means reduces the air volume difference between the plurality of air paths formed in a substantially L shape according to the conveying means for ventilating the heat exchanger or the shape of the air path before and after the heat exchanger. The air path holding means are arranged at unequal intervals.

  By this means, it is possible to reduce the air volume difference between the air passages, and to obtain a heat exchanger that can improve the temperature distribution of air after heat exchange at the outflow portion of the heat exchanger.

  The other means is that the air passage length on the shielding means B side is wide and the air passage length on the shielding means B side is wide. The air path holding means are arranged at unequal intervals so that the air path width of the long air path is narrowed.

  By this means, it is possible to reduce the air volume difference between the air passages, and to obtain a heat exchanger that can improve the temperature distribution of air after heat exchange at the outflow portion of the heat exchanger.

  Another means is that the air passage width of the central portion of the plurality of air passages formed in a substantially L shape is narrow and the air passage length on the shielding means A side is short and the shielding means B The air passage holding means are arranged at unequal intervals so that the air passage width of the air passage having a longer air passage length is wide.

  By this means, it is possible to reduce the air volume difference between the air passages, and to obtain a heat exchanger that can improve the temperature distribution of air after heat exchange at the outflow portion of the heat exchanger.

  According to the present invention, the height of the air passage holding means in the portion where the fluid flowing in the air passage A and the air passage B becomes a counter flow is curved, thereby ensuring the air passage height and suppressing an increase in ventilation resistance. It is possible to provide a heat exchanger that has the effect of

  Moreover, the heat exchanger with the effect of suppressing the increase in ventilation resistance can be provided by ensuring the height of the air passage without reducing the air passage width.

  Moreover, the heat exchanger which has the effect of improving temperature distribution can be provided by arrange | positioning the air path holding | maintenance means which forms the part into which the fluid which flows through the air path A and the air path B turns into a counterflow at unequal intervals. .

  Of the plurality of air passages formed in a substantially L shape, the air passage width of the air passage having a short air passage length on the shielding means A side is narrow and the air passage length of the air passage having a long air passage length on the shielding means B side is long. By arranging the air passage holding means at unequal intervals so that the passage width is widened, it is possible to provide a heat exchanger having an effect of improving the temperature distribution.

  Of the plurality of air passages formed in a substantially L shape, the air passage width of the short air passage on the shielding means A side is wide and the air passage length on the shielding means B side is long. By arranging the air passage holding means at unequal intervals so that the passage width becomes narrow, a heat exchanger having an effect of improving the temperature distribution can be provided.

  Of the plurality of air passages formed in a substantially L shape, the air passage width of the air passage in the central portion is narrow, the air passage length on the shielding means A side is short, and the air passage length on the shielding means B side. By disposing the air passage holding means at unequal intervals so that the air passage width of the long air passage becomes wider, a heat exchanger having an effect of improving the temperature distribution can be provided.

In the heat exchanger according to claim 1 of the present invention, a plurality of substantially rectangular heat transfer plates A and B are laminated, and air paths A and B formed alternately between the heat transfer plates are arranged. In the heat exchanger for exchanging heat between flowing air, the heat transfer plate is substantially L-shaped, and is provided with a plurality of air path holding means formed in a hollow convex shape on one surface of the heat transfer plate. The sheet is integrally molded as a raw material, and a plurality of substantially L-shaped air paths, heat transfer surfaces, and inflow portions and outflow portions are formed at both ends of the air paths by the plurality of air path holding means. The plate A and the heat transfer plate B have substantially the same shape, and the positional relationship in which the inflow portion and the outflow portion of the heat transfer plate A oppose the inflow portion and the outflow portion of the heat transfer plate B. The heat transfer plate A and the heat transfer plate B are rotated by 180 ° so as to be alternately stacked, and at this time, the air path holding hand substantially parallel to the short side of the heat transfer plate The air flow path portion formed by the cross flow region, and the heat transfer plate A and the heat transfer plate B are both air flow path portions formed by air path holding means substantially parallel to the long side of the heat transfer plate, A region other than the cross flow region is defined as a counter flow region, and the shape of the airflow path holding means forming the counter flow region is curved, so that the lower surface of the heat transfer surface of one heat transfer plate in the counter flow region. The top of the air flow path holding means of the other heat transfer plate is brought into contact with the air flow path holding means, and the heat flow plate A and the heat transfer plate B are alternately arranged because the air flow path holding means in the counterflow portion is curved. The air path holding means of the adjacent heat transfer plates are bent in opposite directions, and the air path holding means of the adjacent heat transfer plates are arranged at the same position in the stacking direction. The upper surface of the air passage holding means is in contact with the lower surface of the heat transfer plate located above to secure the air passage height. For use.

Of the plurality of air passages formed in a substantially L shape, the air passage width of the air passage having a short air passage length on the shielding means A side is narrow and the air passage length of the air passage having a long air passage length on the shielding means B side is long. The air passage holding means are arranged at unequal intervals so that the road width is wide, and the width of the air passage with a short air passage length is narrower than when the air passage holding means are arranged at substantially equal intervals. As a result, the air volume of the fluid flowing through the short air path is reduced, and the air flow through the long air path is increased by widening the width of the long air path. Since the air flow increases, there is no variation in the air volume in each air passage, and the temperature difference after heat exchange of each air passage is reduced.

Of the plurality of air passages formed in a substantially L shape, the air passage width of the short air passage on the shielding means A side is wide and the air passage length on the shielding means B side is long. The air passage holding means are arranged at unequal intervals so that the passage width is narrow, and the positional relationship with the air blowing means for blowing air to the heat exchanger, the air passage at the inlet or outlet portion of the heat exchanger The width of the short air passage is widened when there is a large amount of air flowing through the air passage on the long air passage side of the heat exchanger in which the air passage holding means are arranged at substantially equal intervals depending on the shape or the like. As a result, the air volume of the fluid flowing through the air path having the short air path length increases, and the air volume flowing through the air path having the long air path length is reduced by narrowing the width of the air path having the long air path length. Therefore, there is no variation in the air volume in each air passage, and it has the effect of reducing the temperature difference after heat exchange in each air passage .

Of the plurality of air passages formed in a substantially L shape, the air passage width of the air passage in the central portion is narrow, the air passage length on the shielding means A side is short, and the air passage length on the shielding means B side. The air passage holding means are arranged at unequal intervals so that the air passage width of the long air passage is wide, and the positional relationship with the air blowing means for blowing air to the heat exchanger, the inlet of the heat exchanger Or, depending on the shape of the air passage at the outlet portion, etc., when there is a large amount of air flowing through the air passage in the central portion of the heat exchanger in which the air passage holding means are arranged at substantially equal intervals, the width of the air passage in the central portion is Narrowing increases the air volume of the fluid flowing through the air passage in the central portion, and the air passage width of the air passage having a short air passage length on the shielding means A side and the air passage length having a long air passage length on the shielding means B side. Since the amount of air flowing through the air passage having a long air passage length and the air passage having a short air passage length is reduced by widening the air passage length, Has the effect of reducing the temperature difference between the air volume of the variation is eliminated after the heat exchange of the air path in the air duct respectively.

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

(Embodiment 1)
1 is a schematic exploded perspective view of a heat exchanger used in the present embodiment, FIG. 2 is a schematic perspective view when the heat transfer plates are stacked, and FIG. 3 is a schematic perspective view from the stacking direction when the heat transfer plates are stacked. 4 is a schematic cross-sectional view of the laminated state of the shielding rib A and the shielding rib B near the opening, FIG. 5 is a schematic cross-sectional view of the inlet before thermal welding, and FIG. 6 is a schematic sectional view of the inlet after thermal welding. .

  1 and 2, the heat exchanger configured by alternately stacking the heat transfer plate A101 and the heat transfer plate B102 includes an air path A1 and an air path B2 above and below each heat transfer plate, The fluids flowing through the air passage A1 and the air passage B2 exchange heat through the respective heat transfer plates, and flow in directions opposite to each other at the entrance / exit portion of each air passage, and flow in directions opposite to each other at the central portion. It is a flow type and is integrated by thermal welding of the outer peripheral side surface.

  Actually, a large number of heat transfer plates A101 and heat transfer plates B102 are alternately stacked, but four heat transfer plates are shown for simplicity.

  The heat transfer plate A101 and the heat transfer plate B102 have a square planar shape and are formed by vacuum forming a high impact polystyrene sheet having a thickness of, for example, 0.2 mm. The heat transfer plate A101 has a hollow convex shape, for example, The curved air passage ribs 3 are formed to have a convex height of 2.6 mm and a width of 2 mm with respect to the surface of the heat transfer surface 105, and the counterflow portion is a substantially L-shaped air passage holding means having a curved shape. Nine air gaps A1 and a substantially L-shaped air passage A1 and a heat transfer surface 105 are formed by the curved air passage rib 3.

  The inlet 4 and outlet 5 of the air passage A1 are bent at the edge of the heat transfer plate A101 in a direction opposite to the convex direction of the curved air passage rib 3, for example, to a position of 2.4 mm with respect to the surface of the heat transfer surface 105. An air passage end face 106 is provided as an airtight means, and both ends of the air passage end face 106, for example, a portion 10 mm from the end are longer than the air passage end face 106, for example, to a position of 5.2 mm with respect to the surface of the heat transfer surface 105. The air path end face cover 111a as the airtight means is provided, and the air path end face 106 and the air path end face cover 111a form the air path opening 6a.

  Note that subscripts at the end of the code are the same code and have the same function, but are for distinction due to differences in arrangement, etc.

  A plurality of protrusions A107 that are hollow and convex in the same direction as the convex direction of the curved air passage rib 3 at both ends of the curved air passage rib 3 and whose height is higher than the height of the curved air passage rib 3, for example, the height is heat transfer. Eighteen pieces of 5.2 mm are provided for the surface 105.

  The outer peripheral edge of the heat transfer plate A101 other than the inlet and outlet of the air passage A1, and the same direction as the convex direction of the curved air passage rib 3 in the straight portion sandwiched between the inlet 4 and outlet 5 of the air passage A1 The outer peripheral rib A7a as a shielding means having a hollow convex shape and formed at the same height as the protrusion A107 is provided so that the width thereof is, for example, 10 mm, the upper surface of the outer peripheral rib A7a is parallel to the heat transfer surface 105, and The side surface is bent to the same position as the air path end surface cover 111a.

  An outer peripheral rib B8 as an L-shaped shielding means B is formed at the same width as the outer peripheral rib A7a on the outer peripheral edge of the heat transfer plate A101 other than the inlet 4, outlet 5 and outer peripheral rib A7a. Out of the ribs B8, the outer peripheral rib B8a that is opposite to the outer peripheral rib A7a is formed at the same height as the outer peripheral rib A7a, and the other outer peripheral ribs B8b and 8c are formed at the same height as the curved air passage rib 3.

The outer peripheral side surface of the outer peripheral rib B8a is bent to the same position as the air path end surface cover 111a to form a side cover 9 as an airtight means, from the corner portion of the outer peripheral side surface of the outer peripheral ribs B8b and 8c to the position of the same size as the outer peripheral rib A7. Is bent to the same position as the air path end cover 111a to form the air path end cover 111b, and other portions are bent from the upper surface of the outer peripheral ribs B8b and 8c to a position of, for example, 2.2 mm, and the air path opening 6b is formed. It is formed.

  The corner portions of the outer peripheral ribs B8b and 8c adjacent to the inflow port 4 and the outflow port 5 are provided with projections B112 which are hollow and convex in the same direction as the convex direction of the curved air passage rib 3 and are formed at the same height as the projection A107. .

  On the air path side of the outer peripheral rib A7a and the outer peripheral rib B8a, four semicircular recesses 10 as outer peripheral air path holding means are provided in a shape having the same surface as the heat transfer surface 105, respectively.

  The heat transfer plate B102 is similar to the heat transfer plate A101, and the height of the outer peripheral rib A7b and the outer peripheral ribs B8d, 8e, and 8f of the heat transfer plate B102 is equal to the height of the curved air passage rib 3. The same width as the outer peripheral rib A7a of the heat transfer plate A is formed.

  The outer peripheral rib A7b and the outer peripheral rib B8d of the heat transfer plate B102 have a width of, for example, 5 mm, which is half the width of the outer peripheral rib A7b, and in the same direction as the convex direction of the curved air passage rib 3 with respect to the heat transfer surface 105, for example. Four side reinforcing portions 11 as side surface holding means formed at a height of 8 mm are provided at positions adjacent to the semicircular concave portions 10 provided in the heat transfer plate A101 during lamination, and the side reinforcing portions 11 at both ends are It coincides with the ends of the outer peripheral rib A7b and the outer peripheral rib B8d.

  In the above configuration, when the heat transfer plates A101 and the heat transfer plates B102 are alternately laminated, the curved air passage ribs 3 and the curved air passage ribs 3 formed on the adjacent heat transfer plates as shown in FIG. Therefore, the upper surfaces of the curved air passage ribs 3 always come into contact with the lower surface of the heat transfer plate disposed above without securing the adjacent curved air passage ribs 3 to each other, thereby ensuring the air passage height. it can.

  This air path height is designed from the viewpoint of the performance of the heat exchanger such as ventilation resistance and molding processability.

  Further, as shown in FIG. 4, the upper surface of the side reinforcing portion 11 contacts the lower surface of the outer peripheral rib A7a of the heat transfer plate A101, and the lower surface of the semicircular recess 10 contacts the upper surface of the outer peripheral rib B8d of the heat transfer plate B102. In addition, it is possible to suppress a decrease in the opening height and a decrease in the height of the air passage on the outer peripheral side due to the heat shrinkage at the time of heat welding.

  Moreover, since the welding area of the outer peripheral side surface of outer peripheral rib A7a of the adjacent heat exchanger plate and the outer peripheral side surface of outer peripheral rib B8d can be taken large, generation | occurrence | production of the unwelded part by heat contraction can be prevented in the case of heat welding. , Productivity can be improved.

  Further, as shown in FIG. 5, the air passage opening 6a and the air passage opening 6b of the inlet 4 have an opening height h2 from the heat transfer surface higher than the air passage height h1, for example, h2 = 3 mm. > H1 = 2.6 mm, and burrs 12 remain at the cut portions of the air passage opening 6a and the air passage opening 6b at the time of cutting, and as shown in FIG. Is designed to ensure an opening height equal to or higher than the airway height, that is, h3 ≧ h1 = 2.6 mm, even when it falls down so as to block the opening height of the inlet 4. A decrease in opening height due to the burr 12 can be suppressed.

  Further, since the burr 12 can be left on the heat transfer plate A101 and the heat transfer plate B102 within an allowable range, productivity is also improved.

In the first embodiment, a high-impact polystyrene sheet is used as the material for the heat transfer plate, and it is integrally formed by vacuum forming. However, as the material, other thermoplastic resins such as polystyrene, polypropylene, polyethylene, polyethylene terephthalate, etc. Films, thin metal plates such as aluminum, or paper materials having heat and moisture permeability, microporous resin films, paper materials mixed with resin, etc. may be used. Even if the heat transfer plate is integrally formed by another method such as vacuum forming or press forming, the same effect can be obtained.

  Moreover, although the thickness of the sheet is 0.2 mm, it is preferable to use a sheet having a thickness of 0.05 to 0.5 mm.

  The reason for this is that when the thickness is 0.05 mm or less, the sheet material is likely to be broken when the uneven shape is formed and when the heat transfer plate after the forming is handled, and the molded heat transfer plate is not easily damaged. However, the handleability is deteriorated, and if it exceeds 0.5 mm, the heat conductivity is lowered.

  As the sheet thickness decreases, the heat transfer property tends to increase and the moldability tends to decrease. Conversely, as the sheet thickness increases, the heat transfer property tends to decrease.

  Therefore, in order to satisfy the formability and heat transfer, it is preferable to use a sheet having a thickness of 0.05 to 0.5 mm, more preferably 0.15 to 0.25 mm. Is most desirable.

  Moreover, although the shape of the curved air path rib 3 was made into the shape which has a curve of one mountain, if the shape where the curved air path rib 3 of the adjacent heat exchanger plate does not fit at the time of lamination | stacking, it is the same also as a several mountain number A working effect can be obtained.

  Further, although the semicircular concave portion 10 is used as the outer peripheral air path holding means, other shapes can be used as long as they are in contact with the upper surface of the outer peripheral rib B8 of the heat transfer plate B102 positioned below during lamination. An effect can be obtained.

  In addition, the dimensional value and the number of each part are only examples, and are not particularly limited to those values, even when appropriately designed from the aspect of heat exchanger performance such as ventilation resistance and heat exchange efficiency and molding processability. Similar effects can be obtained.

(Embodiment 2)
FIG. 7 is a plan view of the heat transfer plate A. FIG. Note that the same parts as those in the first embodiment are denoted by the same reference numerals and have the same operational effects, and detailed description thereof will be omitted.

  As shown in FIG. 7, the substantially L-shaped air passages A1a to 1j formed in the heat transfer plate A101 have the shortest air passage length of the air passage A1a on the outer peripheral rib A7a side, and the air passage A1j on the outer peripheral rib B8 side. Is the longest.

  The air passage width is arranged so that the air passage A1a having the shortest air passage length is narrow and the air passage A1j is wide. The width of each air passage is such that the width of the air passage A1a <the air passage A1b. Width <width of air passage A1c <width of air passage A1d <width of air passage A1e <width of air passage A1f <width of air passage A1g <width of air passage A1h <width of air passage A1i <width of air passage A1j The width of each air passage is appropriately designed based on the size of the heat transfer plate, the air volume, the formability, and the like.

  The heat transfer plate B102 is designed in the same manner, but only the heat transfer plate A101 is shown for simplicity.

  In the above configuration, the fluid flowing from the direction of the arrow A in the drawing flows into each of the air passages A1a to 1j, is heat-exchanged and flows out from the outlet 5, but the width of the air passage having a short air passage length. Since the width of the air passages is narrow and the air passage length is wide, the difference in the amount of air flowing through each air passage is reduced, so the temperature difference of each air passage at the outlet is reduced compared to the case where the air passage width is uniform. Can be made.

  Even when the positional relationship between the curved air passage ribs 3 at the inlet 4a of the air passage A1a and the inflow portion of the air passage B2 (not shown) is on the same line, the curved air passage of the adjacent heat transfer plate in the counterflow portion. Since the rib 3 is not fitted, each air passage width can be designed arbitrarily.

  In the second embodiment, the widths of the air paths are all different from each other. However, the air path width may be partially equal, for example, the width of the air path A1d = the width of the air path A1e.

( Reference example )
The matters described above are useful when the fluid (air) flowing into the heat exchanger has uniform wind speed and static pressure, and there is no structure that prevents the blowout near the outlet of the heat exchanger. In terms of device design, it is difficult to provide an air passage shape that allows such ideal air to flow through the heat exchanger. For example, the size of the blower outlet and the inlet of the heat exchanger do not match, so if the distance from the blower outlet to the inlet of the heat exchanger is not enough, a uniform inflow airflow will not be obtained. Therefore, it is difficult to select such a wind path shape. Next, it is also useful in such a situation, and will be described with reference to FIGS.

  8 and 9 are schematic layout diagrams showing the positional relationship between the heat transfer plate A101 and the outlet 14 of the blower 13. FIG.

  The same parts as those in the first and second embodiments are denoted by the same reference numerals and have the same operational effects, and detailed description thereof is omitted.

  In FIG. 8, the outlet 14 of the blower 13 that conveys air to the air passages A1a to 1j is arranged on the air passage side where the air passage length of the air passage A1 is long, and the air passage width of the air passages A1a to 1j is the blower 13. The curved air passage ribs 3 are arranged so that the width of the air passage A1j having the longest air passage length is narrow and the width of the air passage A1a is wide. The width of the air passage A1a> the width of the air passage A1b> the width of the air passage A1c> the width of the air passage A1d> the width of the air passage A1e> the width of the air passage A1f> the width of the air passage A1g> the width of the air passage A1h. > The width of the air passage A1i> The width of the air passage A1j is designed, and the width dimension of each air passage is appropriately designed from the dimensions of the heat transfer plate, the air volume, the moldability, and the like.

  The heat transfer plate B102 is designed in the same manner, but only the heat transfer plate A101 is shown for simplicity.

  In the above configuration, the fluid blown out from the blowout port 14 of the blower 13 flows into each of the wind passages A1a to 1j and is heat-exchanged and flows out from the outflow port 5, but is disposed directly above the blowout port 14. Since the width of the long air passage is narrow and the width of the air passage short at the position far from the air outlet 14 is wide, the amount of air flowing in is large due to the positional relationship with the air outlet 14 of the blower 13. The difference in the amount of air flowing through each air passage on the side of the path A1j is reduced, and the temperature difference of each air passage at the outlet can be reduced as compared with the case where the air passage width is uniform.

  Even when the positional relationship between the curved air passage ribs 3 at the inlet 4a of the air passage A1a and the inflow portion of the air passage B2 (not shown) is on the same line, the curved air passage of the adjacent heat transfer plate in the counterflow portion. Since the rib 3 is not fitted, each air passage width can be designed arbitrarily.

In this example , the width of each air passage is different from each other. However, in a place where the air volume difference between each air passage is small due to the arrangement relationship between the blower and the heat exchanger, for example, the width of the air passage A1h = wind It is good also as a partially equal wind path width like the width | variety of path A1i.

  Next, in FIG. 9, the air outlet 14 of the blower 13 that conveys air to the air passages A <b> 1 a to 1 j is disposed in the central air passage portion of the air passage A <b> 1, and the air passage width of the air passages A <b> 1 a to 1 j is The curved air passage rib 3 is arranged so that the width of the air passage A1e of the central air passage portion where the air outlet 14 is disposed below is narrow and the width of the air passage A1a and air passage A1j at both ends is widened. The width of each air passage is the width of the air passage A1a> the width of the air passage A1b> the width of the air passage A1c> the width of the air passage A1d> the width of the air passage A1e <the width of the air passage A1f <the width of the air passage A1g <the air passage. The width of A1h <the width of air path A1i <the width of air path A1j is designed so that the width dimension of each air path is appropriately designed from the dimensions of the heat transfer plate, the air volume, and the formability. The

  The heat transfer plate B102 is designed in the same manner, but only the heat transfer plate A101 is shown for simplicity.

  In the above configuration, the fluid blown out from the blowout port 14 of the blower 13 flows into each of the wind passages A1a to 1j and is heat-exchanged and flows out from the outflow port 5, but is disposed directly above the blowout port 14. Since the width of the air passage in the central portion is narrow and the width of the air passages at both ends far from the air outlet 14 is wide, each air passage in the central portion where the amount of air flowing in is large due to the positional relationship with the air outlet 14 of the blower 13. As compared with the case where the air flow difference flowing through the air flow is reduced and the air passage width is uniform, the temperature difference between the air passages at the outlet can be reduced.

  Even when the positional relationship between the curved air passage ribs 3 at the inlet 4a of the air passage A1a and the inflow portion of the air passage B2 (not shown) is on the same line, the curved air passage of the adjacent heat transfer plate in the counterflow portion. Since the rib 3 is not fitted, each air passage width can be designed arbitrarily.

In this example , the widths of the air paths are all different dimensions. However, in places where the air volume difference between the air paths is small due to the arrangement relationship between the blower and the heat exchanger, for example, the width of the air path A1e = wind It is good also as a partially equal wind path width like the width | variety of path A1f.

  The present invention can also be applied to a heat exchange ventilator or a cooling device attached to a housing having a heating element inside a mobile telephone base station, a simple radio station, or the like.

1 is a schematic exploded perspective view of a heat exchanger according to Embodiment 1 of the present invention. Schematic perspective view when the heat transfer plates are stacked Schematic perspective view from the stacking direction when the heat transfer plates are stacked Schematic sectional view of the laminated state of the outer peripheral rib A and the outer peripheral rib B near the opening Schematic cross-sectional view of the inlet before heat welding Schematic cross-sectional view of the inlet after heat welding The top view of the heat exchanger plate A by Embodiment 2 of this invention Schematic layout diagram showing the positional relationship between the heat transfer plate A and the blower according to the reference example Schematic layout diagram showing the positional relationship between the heat transfer plate A and the blower Schematic exploded perspective view showing a conventional heat exchanger

1 Airway A
1a Airway A
1b Airway A
1c Airway A
1d Airway A
1e Airway A
1f Airway A
1g Airway A
1h Airway A
1i Airway A
1j Airway A
2 Wind B
3 Curved air passage rib 4 Inlet 4a Inlet 5 Outlet 6 Air passage opening 6a Air passage opening 6b Air passage opening 7 Outer peripheral rib A
7a Outer peripheral rib A
7b Outer peripheral rib A
8 Outer peripheral rib B
8a Outer peripheral rib B
8b Outer peripheral rib B
8c Outer peripheral rib B
8d Outer peripheral rib B
8e Outer peripheral rib B
8f Outer peripheral rib B
DESCRIPTION OF SYMBOLS 9 Side cover 10 Semicircular recessed part 11 Side reinforcement part 12 Burr 13 Blower 14 Outlet 101 Heat-transfer plate A
102 Heat transfer plate B
105 Heat transfer surface 106 Air passage end surface 107 Projection A
112 Protrusion B

Claims (6)

In a heat exchanger in which a plurality of substantially rectangular heat transfer plates A and B are stacked and heat exchange is performed between air flowing in the air passage A and air passage B formed alternately between the heat transfer plates. ,
The heat transfer plate is substantially L-shaped, and is provided with a plurality of air path holding means formed in a hollow convex shape on one surface of the heat transfer plate and integrally molded as a single sheet,
An inflow portion and an outflow portion are formed at both ends of the plurality of substantially L-shaped air passages and the heat transfer surface and the air passage by the air passage holding means,
The heat transfer plate A and the heat transfer plate B have substantially the same shape,
The heat transfer plate A and the heat transfer plate B are 180 ° so that the inflow portion and the outflow portion of the heat transfer plate A face the inflow portion and the outflow portion of the heat transfer plate B. Rotate and stack alternately
At this time, the air flow path portion formed by the air flow path holding means substantially parallel to the short side of the heat transfer plate is a cross flow region,
Both the heat transfer plate A and the heat transfer plate B are air passage portions formed by the air passage holding means substantially parallel to the long side of the heat transfer plate, and the region other than the cross flow region is a counter flow region,
By the shape of the air path holding means for forming the counterflow region curvilinear,
In the counterflow region, the top of the air path holding means of the other heat transfer plate is brought into contact with the lower surface of the heat transfer surface of one heat transfer plate. 2. The heat exchanger according to claim 1, wherein the air passage holding means for forming a portion in which the fluid flowing through the air passage A and the air passage B becomes a counter flow is arranged at unequal intervals. The heat transfer plate includes a linear shielding means A provided on one long side outer peripheral portion, and a substantially L-shaped shielding means B provided over the other long side and one short side,
Of the plurality of air passages formed in a substantially L shape, the air passage width of the air passage having a short air passage length on the shielding means A side is narrow, and the air flow of the air passage having a long air passage length on the shielding means B side is long. 3. The heat exchanger according to claim 2, wherein the air passage holding means are arranged at unequal intervals so that the passage width is widened. Depending on the conveying means for ventilating the heat exchanger or the shape of the air path before and after the heat exchanger, the air path holding means is not used so as to reduce the difference in air volume between the plurality of substantially L-shaped air paths. The heat exchanger according to claim 2, wherein the heat exchangers are arranged at equal intervals. The heat transfer plate includes a linear shielding means A provided on one long side outer peripheral portion, and a substantially L-shaped shielding means B provided over the other long side and one short side,
Among the plurality of air passages formed in a substantially L shape, the air passage width of the air passage having a short air passage length on the shielding means A side is wide and the air passage width of the air passage having a long air passage length on the shielding means B side. The heat exchanger according to claim 4, wherein the air path holding means are arranged at unequal intervals so as to be narrow. The heat transfer plate includes a linear shielding means A provided on one long side outer peripheral portion, and a substantially L-shaped shielding means B provided over the other long side and one short side,
Of the plurality of air passages formed in a substantially L shape, the air passage width of the air passage in the central portion is narrow, the air passage length on the shielding means A side is short, and the air passage length on the shielding means B side is long. The heat exchanger according to claim 4, wherein the air passage holding means are arranged at unequal intervals so that the air passage width of the air passage is widened.

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