JP2016090123A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger which has no risk of the deterioration of heat exchanging performance and the generation of erosion-corrosion, and can equalize a flow of cooling water.SOLUTION: A heat exchanger 100 alternately forms a flow passage for making different fluids flow by alternately laminating a plurality of a first plate 11 and a second plate 12 at an interval, and performs heat exchange between the different fluids via the first plate 11 and the second plate 12. Either of the first plate 11 and the second plate 12 has a rib 11e which abuts on the other plate, blocks a part of the flow passage between the first plate 11 and the second plate 12, and extends to a flow direction.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a heat exchanger attached to a vehicle.

  Patent Document 1 discloses an oil cooler (heat exchanger) in which a large number of a pair of upper and lower core plates are stacked. Between the laminated core plates, a fluid passage through which a fluid can flow is formed. One of the pair of upper and lower core plates of Patent Document 1 is provided with a plurality of protrusions that protrude toward the other core plate. The plurality of protrusions are arranged with a coarse and dense distribution in the fluid channel so that the fluid flow is uniform throughout the fluid channel.

  Patent Document 2 discloses a heat exchanger in which a bulging portion that bulges outward is formed on a side wall portion of a casing. By forming a bulging part in the side wall part located outside the inlet side oil passage in the fluid flow path, it is possible to avoid an increase in size, a decrease in heat exchange efficiency, and cavitation in the vicinity of the inlet side oil passage. And the occurrence of erosion (erosion) of the casing.

JP 2006-183945 A JP 2009-52849 A

  However, in the heat exchanger of Patent Document 1, when a plurality of projections are formed close to the vicinity of the cooling water inlet where the cooling water flows strongly, a water stop area that is a shadow of the flow is generated in a wide range, and the heat exchange efficiency is increased. There is a concern that will decrease. Further, since the plurality of protrusions are formed densely, the water flow resistance is increased, and there is a concern that the coolant leaks from the fluid flow path due to erosion of the protrusions.

  Moreover, in the heat exchanger of patent document 2, since there is no structure of the protrusion etc. which control the flow of a cooling water, there exists a possibility that more cooling water may flow into the shortest path | route vicinity which connects a cooling water inlet and a cooling water outlet. For this reason, the flow rate difference of the cooling water tends to increase between the center and the outside of the fluid flow path, and it is difficult to make the flow of the cooling water uniform.

  The present invention was invented to solve such a problem, and reduced the water stop area to suppress the decrease in heat exchange efficiency and lower the water flow resistance to eliminate the concern of erosion, and An object of the present invention is to provide a heat exchanger that can make the flow of cooling water uniform.

  In the heat exchanger according to an aspect of the present invention, a plurality of first plates and second plates are alternately stacked at intervals to alternately form flow paths for flowing different fluids. Heat exchange is performed between different fluids via the second plate. One of the first plate and the second plate has a rib that abuts the other plate, blocks a part of the flow path between the first plate and the second plate, and extends in the flow direction.

  According to such an aspect, since the rib extends along the fluid flow direction so as to abut against the adjacent plate and block a part of the fluid path, the fluid flow is guided by the rib, and the water stop area is reduced. It is possible to reduce the water resistance. For this reason, in the heat exchanger of the present invention, it is possible to suppress a decrease in heat exchange efficiency, to eliminate the concern of causing erosion, and to make the flow of cooling water uniform.

It is a perspective view when the heat exchanger of 1st Embodiment of this invention is seen from diagonally upward. It is a perspective view when the heat exchanger of 1st Embodiment of this invention is seen from diagonally downward. It is a longitudinal cross-sectional view of the heat exchanger of 1st Embodiment. It is a top view of the 1st plate of a 1st embodiment. It is the top view to which the cooling water inlet side circulation hole vicinity of the 1st plate of 2nd Embodiment of this invention was expanded. It is a top view of the 1st plate of a comparative example.

  Embodiments of the present invention will be described below with reference to the drawings.

(First embodiment)
FIG. 1A is a perspective view when the heat exchanger 100 of the present embodiment is viewed obliquely from above, and FIG. 1B is a perspective view when the heat exchanger 100 is viewed from obliquely below.

  The heat exchanger 100 is attached to a vehicle, for example, and warms up or cools the ATF using heat of engine coolant. As shown in FIG. 1A, the heat exchanger 100 includes a core portion 10 that exchanges heat between different fluids, a lid member 20 that is attached to the upper surface of the core portion 10, and a bottom plate 30 that is attached to the lower surface of the core portion 10. And comprising. For example, cooling water and ATF are selected as the fluid.

  The lid member 20 fixes the core part 10 from the upper surface. A cooling water inlet 21 through which cooling water flows into the core portion 10 and a cooling water outlet 22 through which cooling water flows out from the core portion 10 are connected to the lid member 20. Further, the lid member 20 has an ATF passage pipe 23 protruding upward so that ATF flows inside.

  The bottom plate 30 serves as a base for installing the core unit 10. As shown in FIG. 1B, the bottom plate 30 is formed with flanges 33 having through holes for fixing at the four corners. The bottom plate 30 has an ATF inlet 31 for allowing ATF to flow into the core part 10, and an ATF outlet 32 for allowing ATF to flow out of the core part 10.

  Next, the internal structure of the core unit 10 will be described with reference to FIG. FIG. 2 is a longitudinal sectional view of the heat exchanger 100.

  The core unit 10 is configured by alternately laminating a plurality of first plates 11 and second plates 12 at intervals. The 1st plate 11 and the 2nd plate 12 are formed so that an outer periphery may become the same square shape using the metal flat plate member (plate) which is easy to transmit heat. The corners of the first plate 11 and the second plate 12 have a slightly rounded shape as shown in FIG. 1A in order to guide the flow of cooling water and ATF.

  As shown in FIG. 2, between the adjacent first plate 11 and second plate 12, a cooling water passage 13 through which a plurality of cooling water flows and an ATF passage 14 through which a plurality of ATFs flow alternately It is formed.

  The cooling water flowing from the cooling water inlet 21 connected to the lid member 20 branches and flows into each of the plurality of cooling water flow paths 13, and the cooling water that has passed through the plurality of cooling water flow paths 13 merges. It flows from the cooling water outlet 22 to the outside of the heat exchanger 100.

  ATF branches and flows into each of the plurality of ATF channels 14 from an ATF inlet 31 provided in the bottom plate 30 shown in FIG. 1B, and the ATFs that have passed through the plurality of ATF channels 14 merge to form an ATF outlet. 32 is flowed out of the heat exchanger 100. As shown in FIG. 2, an inner fin 14 a is attached to each of the plurality of ATF channels 14.

  The inner fin 14 a is a fin for increasing the heat transfer area of the first plate 11 and the second plate 12 and facilitating heat exchange of the ATF flowing through the ATF flow path 14. The ATF flowing through each ATF channel 14 exchanges heat with the cooling water flowing through the adjacent cooling water channel 13 via the first plate 11 and the second plate 12.

  The plurality of first plates 11 and second plates 12 are formed with cooling water inlet side circulation holes 11a, cooling water outlet side circulation holes 11b, and ATF circulation holes 11c at the same positions. By laminating the first plate 11 and the second plate 12, the cooling water inlet side circulation hole 11a, the cooling water outlet side circulation hole 11b, and the ATF circulation hole 11c are the first plate 11 and the second plate. 12 are arranged so as to penetrate through from the stacking direction.

  The cooling water inlet side circulation hole 11 a is a hole for introducing cooling water into the cooling water flow path 13 of the core portion 10. The cooling water inlet side circulation hole 11 a is connected to a cooling water inlet 21 connected to the lid member 20, and allows the cooling water flowing from the cooling water inlet 21 to flow into the cooling water flow path 13. The cooling water that has flowed into the cooling water channel 13 flows so as to spread over the entire cooling water channel 13.

  The cooling water outlet side circulation hole 11 b is a hole for discharging cooling water from the cooling water flow path 13. The cooling water outlet side circulation hole 11 b is connected to the cooling water outlet 22 connected to the lid member 20, and allows the cooling water flowing from the cooling water flow path 13 to flow out to the cooling water outlet 22.

  The ATF circulation hole 11 c is a hole for circulating ATF in the ATF flow path 14 of the core portion 10. The ATF that has flowed through the ATF flow path 14 is discharged from the ATF outlet 32 of the bottom plate 30 through the ATF flow hole 11c.

  Note that the cooling water channel 13 and the ATF channel 14 are formed as independent channel systems, and the cooling water and the ATF are not mixed. Further, the cooling water does not leak from the cooling water inlet side circulation hole 11a and the cooling water outlet side circulation hole 11b to the ATF flow path 14, and the ATF does not leak from the ATF flow hole 11c to the cooling water flow path 13.

  Next, with reference to FIG.3 and FIG.5, the 1st plate 11 of this embodiment and the 1st plate 11 of a comparative example are demonstrated. FIG. 3 is a plan view of the first plate 11 of the present embodiment, and FIG. 5 is a plan view of the first plate 11 of the comparative example.

  First, the first plate 11 of the comparative example will be described with reference to FIG. In the following comparative examples, the same reference numerals are used for configurations that perform the same functions as in the present embodiment, and in the present embodiment described later, descriptions that overlap with the comparative examples are omitted as appropriate.

  As shown in FIG. 5, the first plate 11 of the comparative example is in contact with the cooling water inlet side circulation hole 11a, the cooling water outlet side circulation hole 11b, the ATF circulation hole 11c, and the adjacent second plate 12. Thus, a protrusion 11d that blocks a part of the cooling water flow path 13 is formed.

  The cooling water inlet side circulation hole 11 a is formed in the vicinity of one corner of the first plate 11.

  The cooling water outlet side circulation hole 11 b is formed in the vicinity of the diagonal corner of the first plate 11 so as to face the cooling water inlet side circulation hole 11 a across the center of the first plate 11.

  Three ATF circulation holes 11c are formed between the cooling water inlet side circulation hole 11a and the cooling water outlet side circulation hole 11b.

  In the case of the comparative example, a plurality of protrusions 11d are provided over the entire first plate 11. Since a part of the cooling water flow path 13 is blocked by the plurality of protrusions 11d, the cooling water is guided to flow on both sides of each protrusion 11d. Here, in FIG. 5, a portion where the flow of the cooling water in the cooling water flow path 13 is strong is represented by a light tone, and a portion where the flowing force is weak is represented by a dark tone. Therefore, for example, the water stop area which is the shadow of the flow is represented by a dark tone close to black. The cooling water flowing through the cooling water channel 13 repeats the flow division and merging by the plurality of protrusions 11d. For this reason, when the cooling water merges downstream of each of the protrusions 11d, turbulent flow is generated and an unstable flow is likely to occur, pressure loss is likely to occur in the cooling water flow path 13, and the water flow resistance is increased. As a result, the flow rate decreases in the entire cooling water flow path 13.

  In addition, the pressure is lowered in the vicinity of the cooling water outlet side circulation hole 11b as the cooling water flows out. For this reason, the cooling water that has flowed in from the cooling water inlet-side circulation hole 11a tends to flow vigorously toward the cooling water outlet-side circulation hole 11b, that is, toward the center of the cooling water channel 13, as shown in FIG. On the other hand, due to the reaction that a lot of cooling water flows in the center of the cooling water flow path 13, the cooling water hardly flows near the outer periphery of the cooling water flow path 13, and the flow rate is likely to decrease. As a result, the flow rate difference between the cooling water near the center and the outer periphery of the cooling water flow path 13 becomes large, and the flow of the cooling water becomes uneven.

  Furthermore, as shown in FIG. 5, a water stop area that is a shadow of the flow is generated in a wide area downstream of the protrusion 11d. In particular, in the vicinity of the cooling water inlet-side circulation hole 11a and downstream of the protrusion 11d formed on the cooling water outlet-side circulation hole 11b side, there is a tendency that a large water stop area is generated because the momentum of the cooling water is strong.

  Next, the first plate 11 of the present embodiment will be described with reference to FIG.

  As shown in FIG. 3, the first plate 11 of the present embodiment is adjacent to the cooling water inlet side circulation hole 11a, the cooling water outlet side circulation hole 11b, and the ATF circulation hole 11c, as in the comparative example. A protrusion 11d that abuts the second plate 12 and blocks a part of the cooling water flow path 13 is formed. Further, the first plate 11 of the present embodiment is further formed with ribs 11e that contact the adjacent second plates 12 to block a part of the cooling water flow path 13 and extend in the flow direction.

  The cooling water inlet side circulation hole 11a, the cooling water outlet side circulation hole 11b, and the ATF circulation hole 11c of the present embodiment are formed in the first plate 11 as in the comparative example.

  In the case of the present embodiment, the plurality of protrusions 11d are provided only near the corners of the outer periphery of the first plate 11. Since a part of the cooling water flow path 13 is blocked by the protrusion 11d, the cooling water is guided to flow on both sides of the protrusion 11d. Here, as in FIG. 5, FIG. 3 also shows the portion where the cooling water flowing through the cooling water passage 13 is strong with a light tone and the portion where the flowing force is weak with a dark tone. In the vicinity of the corner of the outer periphery of the first plate 11, the cooling water flows so as to go around the protrusion 11d.

  A plurality of ribs 11e are provided on the first plate 11 so as to extend along the flow direction of the cooling water. The rib 11e has a shape in which the upstream side and the downstream side are rounded so as not to disturb the flow of the cooling water. Since a part of the cooling water flow path 13 is blocked by the rib 11e similarly to the protrusion 11d, the cooling water is guided to flow on both sides of the rib 11e, and flows along the side shape of the rib 11e. For this reason, in the first plate 11 of the present embodiment, the flow resistance can be lowered by guiding the flow of the cooling water by the ribs 11e, so that the flow rate of the entire cooling water flow path 13 is kept large compared to the comparative example. Be drunk.

  The rib 11e is formed so that the width gradually decreases from the central portion of the rib 11e toward the upstream side or the downstream side. For example, the rib 11e is formed so that the central portion of the rib 11e has a certain width and the upstream and downstream ends of the rib 11e are rounded.

  Moreover, the rib 11e is formed in the center vicinity of the 1st plate 11 of this embodiment so that cooling water may flow into the center of the cooling water flow path 13 vigorously. On the other hand, a protrusion 11d is formed near the outer periphery of the first plate 11 so as not to disturb the flow of the cooling water. By forming the ribs 11e and the protrusions 11d in this manner, a large amount of cooling water is prevented from flowing into the center of the cooling water flow path 13 and is guided to the outer periphery, so that a flow rate of the cooling water flowing near the outer periphery is ensured. .

  Furthermore, in the first plate 11 of the present embodiment, the rib 11e is formed longer toward the central side where the cooling water flows more strongly, so the water stop area that is the shadow of the flow is smaller than in the comparative example. Further, the total number of the ribs 11e and the protrusions 11d of the first plate 11 of the present embodiment is smaller than the number of the protrusions 11d of the comparative example. For this reason, in the 1st plate 11 of this embodiment, the location which a water stop area generate | occur | produces decreases compared with the case of a comparative example.

  According to the heat exchanger 100 according to the first embodiment described above, the following effects can be obtained.

  In the heat exchanger 100 according to the present embodiment, a plurality of first plates 11 and second plates 12 are alternately stacked at intervals, whereby a cooling water passage 13 and an ATF passage 14 are provided as passages through which different fluids flow. Are alternately formed, and heat exchange is performed between the cooling water and the ATF via the first plate 11 and the second plate 12. The first plate 11 has a rib 11e that abuts against the second plate 12, blocks a part of the cooling water flow path 13 between the first plate 11 and the second plate 12, and extends in the flow direction.

  By setting it as such a structure, since the flow of a cooling water is guided to the rib 11e extended in the flow direction of the cooling water of the cooling water flow path 13, a water stop area decreases and the fall of heat exchange efficiency can be suppressed. . Further, by forming the rib 11e, it is not necessary to form a plurality of projections 11d close to the circulating water inlet side circulation hole 11a where the flowing force is strong. It is possible to eliminate the concern that erosion occurs at 11e and protrusion 11d.

  Further, since the cooling water is prevented from flowing much into the center of the cooling water flow path 13 by the rib 11e and is guided to the outer periphery, a difference in flow rate between the center of the cooling water flow path 13 and the vicinity of the outer periphery is unlikely to occur. The cooling water can be made to flow evenly and uniformly over the entire 13.

  In the heat exchanger 100 according to the present embodiment, the rib 11e of the first plate 11 is formed so that the width becomes narrower from the central portion of the rib 11e toward the downstream side.

  By configuring in this way, the cooling water flowing along the side shapes on both sides of the rib 11e can smoothly merge downstream of the rib 11e, so that a water stop area is further generated downstream of the rib 11e. It becomes difficult to suppress a decrease in heat exchange efficiency.

(Second Embodiment)
With reference to FIG. 4, the 1st plate 11 of 2nd Embodiment of this invention is demonstrated. FIG. 4 is an enlarged plan view of the vicinity of the cooling water inlet side circulation hole 11 a of the first plate 11.

  In the heat exchanger 100 by 2nd Embodiment, the aspect of the rib 11e formed in the 1st plate 11 differs from 1st Embodiment. In the following embodiments, the same reference numerals are used for configurations that perform the same functions as those in the first embodiment, and redundant descriptions are omitted as appropriate.

  In the first plate 11 of the present embodiment, as shown in FIG. 4, the shapes of the upstream side and the downstream side of the rib 11e formed in the vicinity of the cooling water inlet side circulation hole 11a are different.

  The rib 11e formed in the vicinity of the cooling water inlet side circulation hole 11a is formed such that the upstream radius of curvature r1 is larger than the downstream radius of curvature r2.

  According to the heat exchanger 100 according to the second embodiment described above, the following effects can be obtained.

  In the heat exchanger 100 according to the second embodiment, the rib 11e of the first plate 11 has a shape in which the curvature radius r1 on the upstream side of the cooling water flow path 13 is larger than the curvature radius r2 on the downstream side.

  By adopting such a configuration, the cooling water passing through both ends of the rib 11e can smoothly merge downstream of the rib 11e, so that a water stop area is less likely to occur downstream of the rib 11e, and heat exchange efficiency is reduced. Can be suppressed. In addition, since the upstream radius of curvature r1 of the rib 11e is larger than the downstream radius of curvature r2, the cooling water is suppressed from flowing into the center of the cooling water flow path 13 and guided to the outer periphery. Can be made uniform.

  The embodiment of the present invention has been described above. However, the above embodiment only shows a part of application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.

  For example, the first plate 11 may be formed point-symmetrically as shown in FIG. By doing in this way, even if the 1st plate 11 is rotated 180 degrees, the rib 11e, protrusion 11d, and ATF circulation hole 11c will be formed in the same position. Moreover, since the cooling water inlet side circulation hole 11a and the cooling water outlet side circulation hole 11b are formed in the same shape, even when rotated, the roles can be exchanged and functions can be exhibited. For this reason, since it can laminate | stack without considering the direction of the rib 11e etc. of the 1st plate 11, the core part 10 can be assembled easily.

  In the embodiment of the present invention, the rib 11e and the protrusion 11d are formed on the first plate 11, but the rib 11e and the protrusion 11d are formed on the second plate 12 instead of the first plate 11. Also good.

DESCRIPTION OF SYMBOLS 100 Heat exchanger 10 Core part 11 1st plate 11a Cooling water inlet side flow hole 11b Cooling water outlet side flow hole 11c ATF flow hole 11d Protrusion 11e Rib 12 2nd plate 13 Cooling water flow path 20 Lid member 30 Bottom plate

Claims (3)

By alternately laminating a plurality of first plates and second plates at intervals, flow paths through which different fluids flow are alternately formed, and between the different fluids via the first plate or the second plate. A heat exchanger for exchanging heat at
One of the first plate and the second plate has a rib that abuts against the other plate, blocks a part of the flow path between the first plate and the second plate, and extends in the flow direction. A heat exchanger characterized by that. The heat exchanger according to claim 1,
The rib is formed so that the width becomes narrower from the central portion of the rib toward the downstream side.
A heat exchanger characterized by that. The heat exchanger according to claim 2,
The rib has a shape in which the curvature radius on the upstream side of the flow path is larger than the curvature radius on the downstream side.
A heat exchanger characterized by that.