JP2012132606A - Plate-stacked heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a plate-stacked heat exchanger that does not bring about a pressure loss due to area reduction of an inlet or an outlet when making each core plate of a stacked core part rectangular and miniaturizing a width edge side.SOLUTION: A stacked core part is made by alternatively stacking a first core plate 2 and a second core plate 3 in multi-stage. A channel 8 of cooling water is formed on the first core plate 2 on which the inlet 6 and the outlet 7 are diagonally formed. A channel 17 of oil is formed on the second core plate 3 on which an inlet 15 and an outlet 16 are formed on the diagonal line intersecting the diagonal line made by binding the inlet 6 and the outlet 7. The respective inlets 6, 15 and outlets 7, 16 are formed in trapezoids having bases and upper edges parallel to the width edge of respective plates 2, 3 themselves and the edges closest to each other with respect to the inlet 15 and the outlet 16 are made to be the bases of the trapezoids.

Description

  The present invention relates to an improvement in a plate stack type heat exchanger represented by an oil cooler for cooling, for example, lubricating oil of an internal combustion engine or hydraulic oil for an automatic transmission.

  Patent Documents 1 to 3 propose the structure of a heat exchanger used in an oil cooler for an internal combustion engine.

  In these conventional heat exchanger structures, what is called a multi-plate type laminated core part is formed by laminating a plurality of types of quadrilateral and shallow plate-like core plates over a plurality of stages, and adjoining each other in this laminated core part. Each of the spaces formed between the core plates is used as a cooling water passage and an oil passage for heat dissipation and heat reception. In many cases, the cooling water passage and the oil passage are arranged in the stacking direction of the core plates. Alternatingly arranged. In addition, an inlet on the inlet side of the cooling water passage or the oil passage and an outlet on the outlet side form a pair at the diagonal of each plate, and the inlet and outlet of the cooling water passage are formed. For example, when each core plate is square, the diagonal line connecting the diagonal line connecting the inlet and the outlet of the oil passage intersects each other in plan view. is there. A fin plate may be accommodated in the oil passage for the purpose of increasing the heat radiation area.

JP 2002-332818 A JP 2006-183903 A JP 2008-116151 A

  In such a heat exchanger having a multi-plate laminated core part as a main part, when the heat exchange performance between the cooling water and the oil in the laminated core part having a limited volume is insufficient, for example, cooling water or In order to improve the flow rate of the oil and to improve the performance by increasing the length of the cooling water passage or the oil passage, the projected shape (planar shape) of the laminated core portion is rectangular as described in Patent Document 3, for example. It may be.

  In this case, assuming that the area of each inlet and outlet is constant in consideration of the pressure loss of cooling water and oil, in the plan view of the two upper and lower core plates superimposed on each other, the short plate Since the inlet of one core plate and the outlet of the other core plate are close to each other on the side, the short side of the upper and lower core plates, and hence the short side of the laminated core part There is a limit to reducing the size. On the other hand, priority is given to the reduction of the dimension on the short side of each rectangular core plate, conversely, at the expense of the area of each inlet and outlet, the dimension on the short side of each core plate As a result, when the dimension of the short side of the laminated core portion is reduced, it is a matter of course that the pressure loss of the cooling water or oil is increased due to the reduction of the area of each inlet and outlet. As a result, there is a problem that the performance cannot be sufficiently improved by making the projected shape of the laminated core portion rectangular. In particular, as described in Patent Documents 1 and 3, when each inflow hole and outflow hole are circular, the above-described tendency becomes remarkable due to an increase in so-called dead space.

  The present invention has been made paying attention to such problems, and in order to reduce the size of the short side of each plate, which is a component of the laminated core portion, in particular, the respective inlets and It is an object of the present invention to provide a structure of a plate stacked heat exchanger that improves the heat exchange performance, which is the intended purpose, without incurring pressure loss due to the reduction in the area of the outlet.

  The invention according to claim 1 is a laminated core portion in which first and second plates, both of which are rectangular and shallow, are alternately laminated in multiple stages and joined together. In this case, there is a space between the first plate and the second plate thereabove to provide a space for the cold medium, and between the second plate and the first plate thereabove, there is a gap between the two. It is premised on a plate stacked heat exchanger in which a passage for a high temperature medium is formed in each space.

  In addition, the passage of the low-temperature medium has an inlet formed at one corner of the opposite corners of the first plate and an outlet formed at the other corner. In the high-temperature medium passage, the inlet formed in one corner of the opposite corners of the second plate and the other corner are formed in the high-temperature medium passage. The diagonal line connecting the inlet and the outlet on the first plate side and the diagonal line connecting the inlet and the outlet on the second plate side in the plan view with the outlets opened respectively. It is set to intersect. Further, each of the inlet and outlet on the first and second plate sides is formed as a quadrilateral, and each of the quadrilateral inlet and outlet is on the corresponding diagonal line. One side that takes the shortest distance between the outlet and the outlet is parallel to the short side of each plate itself, and the length of this one side is longer than that of the inlet and outlet on the first plate side. Is characterized in that the inlet and outlet of the second plate are set larger.

  Here, the quadrilaterals that are the shapes of the respective inlets and outlets include not only rectangles and squares but also trapezoids, parallelograms, rhombuses, and the like. In addition, a fin plate may be accommodated in one or both of the low-temperature medium passage and the high-temperature medium passage formed in each plate, if necessary.

  In this case, in order to improve the space efficiency by reducing the dead space on the short side of each plate, each of the quadrilateral inlet and the outlet is trapezoidal as described in claim 2. One side that takes the shortest distance between the inlet and outlet on the corresponding diagonal on the first plate side is the upper side of the trapezoid, and on the corresponding diagonal on the second plate side. It is desirable that one side that takes the shortest distance between the inflow port and the outflow port is the bottom side of the trapezoid.

  Therefore, in at least the first aspect of the invention, the shape of each inlet and outlet is a quadrilateral, thereby reducing the dead space on the short side of each rectangular plate and reducing the inlet and outlet. The area necessary for the exit can be secured, and as a result, the size of the short side can be further reduced.

  According to the first aspect of the present invention, each plate, which is a component of the laminated core portion, is made rectangular without incurring pressure loss due to the reduction in the area of each inlet and outlet, and particularly the shortness thereof. Since the dimensions on the side can be reduced, the heat exchange performance is further improved by the effect of increasing the flow path length by making each plate rectangular.

  In addition, according to the invention described in claim 2, by making the shape of the respective inlet and outlet into a trapezoidal shape, the dead space on the short side of each plate is reduced and the space efficiency is improved. Therefore, the effect of improving the heat exchange performance becomes more remarkable by further reducing the size of the short side.

The exploded perspective view which shows the structure of the principal part of the lamination | stacking core part in an oil cooler as a more concrete form for implementing this invention. Plane explanatory drawing of each of the 1st core plate in FIG. 1, a 2nd core plate, and a fin plate. The principal part expansion explanatory drawing which shows the detail of a 1st core plate. The principal part expansion explanatory drawing which shows the detail of a fin plate.

  1 to 4 show a more specific form for carrying out the present invention. In particular, FIG. 1 is an exploded view of a laminated core portion 1 that functions as a main element of an oil cooler that is a plate laminated heat exchanger. FIG. 2 shows a schematic plan view of each of the core plates 2 and 3 in FIG.

  As shown in FIG. 1, a first core plate 2 that is rectangular and has a shallow dish shape, a second core plate 3 that is overlaid on the first core plate 2, and a fin plate 4 that is accommodated in the second core plate 3. A flange portion 5 which is a peripheral portion of the first core plate 2 and the second core plate 3 after the three plates are set as a set, and the plates 2, 3 and 4 are stacked in multiple stages. , 14 and the like are joined and integrated to form a laminated core portion 1 of the oil cooler. A thick and rigid bottom plate serving as a cooling water and oil inflow side is mounted on the lower surface side of the laminated core portion 1, and a top plate serving as a cooling water and oil outflow side is mounted on the upper surface side of the laminated core portion 1. The bottom plate and the top plate are not shown in FIG. 1 though they are assembled as an oil cooler.

  In FIG. 1, the flow of cooling water that is a cooling medium or a low-temperature medium is indicated by a broken line, and similarly, the flow of oil that is a cooling medium or a high-temperature medium is indicated by a solid line.

  An inclined flange portion 5 is erected over the entire circumference at the peripheral edge of the first core plate 2, and an inlet 6 and an outlet 7 are formed diagonally on the bottom wall for cooling water. It is. A space corresponding to the height of embossed portions 9 and 10 to be described later is formed between the first core plate 2 and the second core plate 3 on the first core plate 2 to be laminated with each other. Therefore, this space forms a cooling water passage 8 as a low-temperature medium (cooling medium) passage having the inlet 6 as a cooling water inlet and the outlet 7 as a cooling water outlet.

  More specifically, in the bottom wall portion of the first plate 2 having a rectangular shape, the inflow port 6 is formed in one of the opposite corner portions on one diagonal line, and the other corner portion is opened. An outlet 7 is formed as an opening, the inlet 6 is a cooling water inlet, the outlet 7 is a cooling water outlet, and the inlet 6 and the outlet 7 face the cooling water passage 8 respectively.

  Similarly, in the bottom wall portion of the first plate 2 having a rectangular shape, the embossed portion 9 is provided at one of the opposite corners on the other diagonal line, and the embossed portion 10 is provided at the other corner. Each of the embossed portions 9 and 10 is formed with a communication hole 11 or 12 at the top.

  As is apparent from FIG. 2 in addition to FIG. 1, each of the communication holes 11 and 12 in addition to the inlet 6 and the outlet 7 formed in the bottom wall portion of the rectangular first plate 2 is a quadrilateral. The shape of the embossed portions 9 and 10 in which each communication hole 11 or 12 is formed is also similar to that of the communication holes 11 and 12. It is bulged and formed as a trapezoidal shape.

  Further, each of the trapezoidal inlet 6 and outlet 7 formed on the bottom wall portion of the rectangular first plate 2 has both the bottom and upper sides of the trapezoidal shape of the first core plate 2 itself. It is parallel to the short side. This relationship is the same for the embossed portions 9 and 10 and the communication holes 11 and 12 formed at the top thereof, but the embossed portions 9 and 10 and the communication holes 11 and 12 formed at the top thereof are trapezoidal bottoms. The relative positional relationship between the part and the upper side is opposite to that of the inlet 6 and the outlet 7.

  The relative positional relationship between the inflow port 6 and the outflow port 7 formed in the bottom wall portion of the first plate 2 is that the trapezoidal inflow port 6 is closest to the outflow port 7 and has an inlet width equivalent portion 6a. Is the upper side of the trapezoid (the length of the bottom side> the length of the upper side), and the outlet width equivalent part 7a closest to the inlet 6 among the trapezoidal outlets 7 is also the upper side of the trapezoid. (The length of the bottom side> the length of the top side).

  In other words, each of the trapezoidal inlet 6 and outlet 7 formed on the bottom wall portion of the rectangular first plate 2 is formed between the inlet 6 and the outlet 7 on a corresponding diagonal line. At least the bottom of the trapezoid as one side that takes the shortest distance (distance between each other) (the inlet width equivalent part 6a of the inlet 6 and the outlet width equivalent part 7a of the outlet 7) of the first core plate 2 itself. It is parallel to the short side. Note that the opening areas of the inflow port 6 and the outflow port 7 are substantially equal.

  Here, although not shown in FIGS. 1 and 2, the bottom wall portion of the first core plate 2 has a large number of round or oval shapes as shown in FIG. The fine embossed portions 13a and 13b are bulged, and the bulged height of these fine embossed portions 13a and 13b is smaller than the bulged height of the embossed portions 9 and 10 in which the communication holes 11 and 12 are formed. It has become a thing.

  On the other hand, the second core plate 3 has substantially the same structure as the first core plate 2, and an inclined flange portion 14 is erected on the entire periphery of the second core plate 3. The fin plate 4 is accommodated therein, and the inlet 15 and the outlet 16 are diagonally formed on the bottom wall portion of the second core plate 3 for oil as a medium to be cooled. An opening is formed. A space corresponding to the height is formed in the embossed portions 18 and 19 to be described later between the second core plate 3 and the first core plate 2 thereon. Therefore, this space forms an oil passage 17 as a passage for a high-temperature medium (cooled medium) having the inlet 15 as an oil inlet and the outlet 16 as an oil outlet.

  More specifically, in the bottom wall portion of the second core plate 3 having a rectangular shape, the inflow port 15 is formed in one of the opposite corner portions on one diagonal line, and the other corner portion is formed. The outlet 16 is opened, the inlet 15 is an oil inlet, the outlet 16 is an oil outlet, and the inlet 15 and the outlet 16 face the oil passage 17 respectively.

  Similarly, in the bottom wall portion of the second core plate 3 having a rectangular shape, the embossed portion 18 is provided at one corner portion of the opposite corner portions on the other diagonal line, and the embossed portion 19 is also provided at the other corner portion. Are formed so as to bulge, and communication holes 20 or 21 are formed at the tops of the embossed portions 18 and 19, respectively.

  As is apparent from FIG. 2 in addition to FIG. 1, each of the communication holes 20 and 21 in addition to the inflow port 15 and the outflow port 16 formed in the bottom wall portion of the rectangular second core plate 3 is rectangular. The shape, more specifically, a trapezoidal shape. Similarly, the embossed portions 18 and 19 in which the communication holes 20 and 21 are formed have a similar shape that is slightly larger than the communication holes 20 and 21. It bulges out as a trapezoidal one.

  Further, each of the trapezoidal inlet 15 and outlet 16 formed in the bottom wall portion of the rectangular second core plate 3 includes the second core plate 3 itself in both the trapezoidal bottom and top sides. It is parallel to the short side. This relationship is the same for the embossed portions 18 and 19 and the communication holes 20 and 21 formed at the top thereof, but the embossed portions 18 and 19 and the communication holes 20 and 21 formed at the top thereof are connected to the bottom of the trapezoid. The relative positional relationship between the portion and the upper side is opposite to that of the inflow port 15 and the outflow port 16.

  And the inflow port 15 formed in the bottom wall part of the 2nd core plate 3 contrary to the relative positional relationship of the inflow port 6 formed in the bottom wall part of the 1st core plate 2, and the outflow port 7. FIG. As for the relative positional relationship between the outlet 16 and the trapezoidal inlet 15, the inlet width equivalent portion 15 a closest to the outlet 16 is the trapezoidal bottom side (length of the bottom side> length of the top side) Similarly, among the trapezoidal outlets 16, the outlet width equivalent part 16 a closest to the inlet 15 is the bottom side of the trapezoid (the length of the bottom side> the length of the upper side).

  In other words, each of the trapezoidal inlet 15 and outlet 16 formed in the bottom wall portion of the rectangular second core plate 3 has a corresponding diagonal line between the inlet 15 and the outlet 16. At least the bottom of the trapezoid as one side that takes the shortest distance (distance between each other) (the inlet width equivalent portion 15a of the inlet 15 and the outlet width equivalent portion 16a of the outlet 16) is the second core plate 3. It is parallel to the short side of itself. The opening areas of the inflow port 15 and the outflow port 16 are both substantially equal, and the opening areas of the inflow port 6 and the outflow port 7 on the first core plate 2 side are also approximately equal.

  The fin plate 4 to be accommodated in the second core plate 3 does not have the flange portions 5 and 14 like the first and second core plates 2 and 3, and therefore, It is slightly smaller than the shape of the second core plates 2 and 3 and has the same size as the bottom wall portions of the first and second core plates 2 and 3 and, for example, as shown in FIG. And formed into a rectangular wave shape with regularity. The fin plate 4 has the same shape as the inlet 15 and outlet 16 on the second core plate 3 side, and is formed with a flow hole 22 and a flow hole 23 corresponding thereto, respectively, and the second core plate 3 Relief holes 24 and 25 that are slightly larger than the embossed portions 18 and 19 on the side and are fitted on the embossed portions 18 and 19 are formed.

  As shown in FIG. 1, in the state where the first core plate 2 described above and the second core plate 3 that accommodates the fin plate 4 are stacked as a set in multiple stages, The flange portions 5 and 14 at the peripheral portions of the first and second core plates 2 and 3 are in close contact with each other, and the first and second core plates 2 and 3 are laminated core portions by brazing the portions. As a result, the inner space of each of the core plates 2 and 3 is sealed. Further, the peripheral edge portions of the inlet 15 and the outlet 16 on the second core plate 3 side are closely brazed to the embossed portions 9 and 10 of the first core plate 2. . Similarly, the peripheral edge portions of the inlet 6 on the first core plate 2 side and the outlet 7 on the embossed portions 18 and 19 of the second core plate 3 are brazed in close contact with each other. become.

  Thus, as described above, the height of the embossed portions 9 and 10 on the first core plate 2 side is between the first core plate 2 and the second core plate 3 on the first core plate 2. Corresponding cooling water passages 8 are formed, and between the second core plate 3 containing the fin plate 4 and the first core plate 2 thereon, the second core plate 3 side is provided. An oil passage 17 corresponding to the height of the embossed portions 18 and 19 is formed. That is, in the laminated core 1 formed by laminating the first and second core plates 2 and 3 in multiple stages, as shown in FIGS. The passages 17 are alternately formed in the plate stacking direction.

  In addition, as shown in FIG. 2, the first core plate 2 and the second core plate 3 that are to be overlapped with each other form the first core that forms the cooling water passage 8. A diagonal line connecting the inlet 6 and the outlet 7 on the plate 2 side, and a diagonal line connecting the inlet 15 and the outlet 16 on the second core plate 3 side that will form the oil passage 17. They are set to intersect in plan view.

  As a result, on the short side of the first and second core plates 2 and 3 themselves, the relative positional relationship between the inlet 6 of the first core plate 2 and the embossed portion 9 adjacent thereto, and the first core The relative positional relationship between the outlet 7 of the plate 2 and the embossed portion 10 adjacent thereto is opposite to that on the second plate 3 side. These are the reasons for the cooling water passage 8 and the oil passage 17 formed between the first and second core plates 2 and 3 stacked in multiple stages in the cooling water shown by broken lines in FIGS. This means that the flow direction and the oil flow direction indicated by a solid line are opposite to each other and intersect each other in plan view.

  Therefore, according to the laminated core portion 1 configured in this way, as shown in FIGS. 1 and 2, the cooling water is provided between the first core plate 2 and the second core plate 3 laminated thereon. As described above, the oil passage 17 is formed between the second core plate 3 and the first core plate 2 laminated thereon.

  In addition to the embossed portions 18 and 19 formed in the second core plate 3 and the communication holes 20 and 21 formed in the embossed portions 18 and 19, the first core plate 2 on the upper side is formed. The inflow port 6 and the outflow port 7 to be joined to the embossed portions 18 and 19 form a communication path for communicating the plurality of cooling water paths 8 and 8 in the vertical direction.

  Similarly, in addition to the embossed portions 9, 10 formed in the first core plate 2 and the communication holes 11, 12 formed in the embossed portions 9, 10, the second core plate 3 is formed on the upper side. The inflow port 15 and the outflow port 16 to be joined to the embossed portions 9 and 10 form a communication passage for communicating the plurality of oil passages 17 and 17 in the vertical direction.

  Therefore, in the laminated core part 1, the flow of the cooling water indicated by the broken line in FIG. 1 and the flow of the oil indicated by the solid line are respectively formed, and the mutual heat exchange action in these flow processes causes the oil flow from the oil side. The oil is cooled by releasing heat to the cooling water side through the first and second core plates 2 and 3. The fin plate 4 disposed in the second core plate 3 (oil passage 17) is slightly disadvantageous in terms of oil pressure loss, but greatly contributes to an increase in heat radiation area. It will be.

  In this case, as is clear from FIG. 2, the inlet 15 and the outlet 16 on the second core plate 3 side as well as the inlet 6 and the outlet 7 on the first core plate 2 side have the same shape. Since the opening area is substantially the same quadrangular shape, more specifically, a trapezoidal shape, the rectangular shape in the state where the first core plate 2 and the second core plate 3 are overlapped. Since the dead space is reduced on the short side of each core plate 2, 3, the inlet 6 and the outlet 7 or the inlet 15 and the outlet 16 can coexist. By reducing the length of the short side portion, the difference in length between the short side portion and the long side portion can be further increased. As a result, the flow path lengths of the cooling water passage 8 and the oil passage 17 can be ensured as large as possible to contribute to the improvement of heat dissipation or heat exchange performance.

  For example, when it is assumed that there is a margin in the heat exchange action on the cooling water side, in the above embodiment, the inlet formed in the bottom wall portion of the second core plate 3 that forms the oil passage 17 is formed. 15 and the outlet 16, the inlet width equivalent portion 15 a closest to the outlet 16 among the trapezoidal inlets 15 is a trapezoidal bottom portion, and similarly, the inlet 15 of the trapezoidal outlets 16. Since the exit width equivalent portion 16a closest to the trapezoidal bottom side portion is formed wider than the equivalent portion of the trapezoidal top side portion on the first core plate 2 side, Even though the opening area is equivalent to the inlet 6 and outlet 7 on the first core plate 2 side that forms the cooling water passage 8, the pressure loss of the oil in the oil passage 17 is suppressed. This can also be released It can contribute to the improvement of sexual or heat exchange performance.

  Here, in the above embodiment, each of the inlet 15 and the outlet 16 on the second core plate 3 side as well as the inlet 6 and the outlet 7 on the first core plate 2 side are trapezoidal. As long as it has a quadrilateral shape, for example, a rectangular shape, a square shape, a parallelogram shape, a rhombus shape, or the like may be used.

DESCRIPTION OF SYMBOLS 1 ... Laminated core part 2 ... 1st core plate 3 ... 2nd core plate 4 ... Fin plate 6 ... Inlet 6a ... Inlet width equivalent part 7 ... Outlet 7a ... Outlet width equivalent part 9 ... Embossed part 10 ... Embossed Portion 11 ... Communication hole 12 ... Communication hole 8 ... Cooling water passage 15 ... Inflow hole 15a ... Inlet width equivalent portion 16 ... Outflow hole 16a ... Outlet width equivalent portion 17 ... Oil passage 18 ... Embossed portion 19 ... Embossed portion 20 ... Communication hole 21 ... Communication hole

Claims (2)

Both the first plate and the second plate that are both rectangular and shallow plate-like are laminated in multiple layers and joined together to form a laminated core portion.
There is a space between the first plate and the second plate above the first plate in the laminated core portion, and a passage of a low-temperature medium is provided between the second plate and the first plate thereabove. Is a heat exchanger in which a passage of a high-temperature medium is formed in each with a space between them,
In the passage of the low-temperature medium, an inlet formed at one corner of the opposite corners of the first plate and an outlet formed at the other corner are respectively opened. While letting
The high-temperature medium passage has an inlet formed at one of the opposite corners of the second plate and an outlet formed at the other corner, respectively. Let me
The diagonal line connecting the inlet and outlet on the first plate side and the diagonal line connecting the inlet and outlet on the second plate side are set to intersect in plan view,
Each of the inlet and outlet on the first and second plates is formed as a quadrilateral,
Each of the quadrilateral inlet and outlet is parallel to the short side of each plate itself, with one side taking the shortest distance between the inlet and outlet on the corresponding diagonal line, and The length of one side is set to be larger for the inlet and outlet of the second plate than for the inlet and outlet of the first plate. Heat exchanger. Each of the quadrilateral inlet and outlet is trapezoidal,
On the first plate side, one side that takes the shortest distance between the inlet and the outlet on the corresponding diagonal line is the upper side of the trapezoid, and on the second plate side, the inlet and the inlet on the corresponding diagonal line. 2. The plate laminated heat exchanger according to claim 1, wherein one side portion taking the shortest distance from the outlet is a trapezoidal bottom side portion.

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