JP2017223397A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger capable of promptly increasing the temperature of heat-transfer fluid by accelerating the circulation of the heat-transfer fluid even in a very low temperature state.SOLUTION: With a heat exchanger 1, a plurality of core units 10 forming a channel A through which heat-transfer fluid L flows and a plurality of outer fins 20 for discharging the heat of the heat-transfer fluid L are alternately laminated, both ends of the core unit 10 communicate with each other in a laminating direction. At least one core unit 10 includes: a first plate 11; a second plate 12; a barrier plate 13; and an inner fin 14. The barrier plate 13 is disposed between the first plate 11 and the second plate 12 so as to partition the channel A into a first channel A1 and a second channel A2 and having communication parts 132 for communicating a first channel 11 with a second channel 12 at both ends. The inner fin 14 is disposed in the interior of the first channel A1.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a drone cup type heat exchanger.

  There is an oil cooler configured by alternately laminating a plurality of core units that form a flat flow path and fins bent in a waveform. For example, the oil cooler shown in Patent Document 1 also has fins (inner fins) inside the tube (core unit). The inner fin is formed into a rectangular corrugated shape having crank-like irregularities, and promotes the oil flow into a turbulent flow.

JP 2002-267384 A

  By the way, when an oil cooler is mounted on a vehicle, the oil is circulated when the internal combustion engine is started. However, the oil flowing through the core unit increases in viscosity due to a drastic decrease in temperature and has a flow resistance. Increase. In particular, the oil cooler is configured to discharge the heat of the oil by exchanging heat with the outside air. Therefore, the oil cooler is exposed to extremely low temperatures in the cold and extremely cold winter seasons. As the part freezes and becomes spilled, the fluidity is further deteriorated, such as blocking a part of the flow path, and the performance of the oil cooler is remarkably deteriorated.

  Therefore, the present invention provides a heat exchanger capable of promptly raising the temperature of the heat transfer fluid by promoting circulation of the heat transfer fluid even in an extremely low temperature state.

  In the heat exchanger according to an embodiment of the present invention, a plurality of core units each having a flow path through which a heat transfer fluid flows and outer fins that release heat from the heat transfer fluid are alternately stacked, and both ends of the core unit are stacked in the stacking direction. It is communicated to. The at least one core unit includes a first plate, a second plate, a partition wall, and an inner fin. The first plate has a shape that bulges to the first side in the stacking direction. The second plate has a shape that bulges to the second side opposite to the first side in the stacking direction. The partition wall is disposed between the first plate and the second plate so as to partition the flow path into the first flow path and the second flow path along the direction in which the heat transfer fluid flows. Has a communicating portion at both ends for communicating with the second flow path. The inner fin is disposed inside the first flow path.

  At this time, in the heat exchanger, the ratio of the flow resistance of the second flow path to the flow resistance of the first flow path in a low temperature state where a part of the heat transfer fluid is in a solid state indicates that the heat transfer fluid is liquid. The ratio of the flow resistance of the second flow path to the flow resistance of the first flow path in a high temperature state is small.

  Moreover, it is preferable that the first channel has a channel cross-sectional area larger than the channel cross-sectional area of the second channel. Alternatively, it is also preferable that the communication portion has a protrusion that extends toward the second flow path.

  The partition wall is disposed along the joining surface of the first plate and the second plate, and both the first plate and the second plate are joined at the outer peripheral edge. Alternatively, the partition wall has the same shape as the second plate, and is joined to the first plate at the outer peripheral edge and joined to the second plate at a portion bulging to the second side.

  According to the heat exchanger of one embodiment of the present invention, the partition wall is arranged between the first plate and the second plate of at least one core unit among the plurality of stacked core units, and the flow path is formed. The first flow path and the second flow path are divided into inner fins. Since the first flow path and the second flow path are arranged across the partition wall, heat is transferred from the second flow path to the first flow path via the partition wall. Even if the flow resistance of the first flow path is increased in a low temperature state where a part of the heat transfer fluid is in a solid state, the warmed heat transfer fluid flows to the second flow path to the first flow path. The heat is transmitted. As a result, the heat transfer fluid that has become solid in the first flow path is melted, and the heat transfer fluid easily flows through the first flow path.

  The ratio of the flow resistance of the second flow path to the flow resistance of the first flow path in a low temperature state where a part of the heat transfer fluid flowing inside the core unit is in a solid state indicates that the heat transfer fluid is liquid. According to the heat exchanger of the present invention configured to be smaller than the ratio of the flow resistance of the second flow path to the flow resistance of the first flow path in the high temperature state, the first flow in the low temperature state When a part of the heat transfer fluid in the path becomes solid and it is difficult for the heat transfer fluid to flow, the heat transfer fluid flows in the second flow path, and in a high temperature state, the heat transfer fluid flowing in the first flow path increases. Inner fins are arranged in the first flow path, and the heat of the heat transfer fluid can be efficiently radiated from the outer surface of the core unit through the outer fins, so that the performance as a heat exchanger is improved. That is, circulation of the heat transfer fluid is promoted, and the temperature of the heat transfer fluid rises quickly. And since a heat-transfer fluid warms and becomes a liquid state, a heat-transfer fluid will flow stably also to another core unit, and the performance as a heat exchanger will be stabilized.

  According to the heat exchanger of the present invention in which the channel cross-sectional area of the first channel is larger than the channel cross-sectional area of the second channel, the heat transfer fluid flowing in the first channel in a high temperature state The flow rate increases. Since the inner fin is provided in the first flow path, the performance of the heat exchanger is further improved by increasing the flow rate of the heat transfer fluid that contributes to heat transfer.

  According to the heat exchanger of the present invention having the protruding portion extending to the second flow path side in the communicating portion, the heat transfer fluid is guided by the protruding portion to flow into the first flow path at the high temperature state, and the first The ratio of the heat transfer fluid flowing through the flow path increases. Since the inner channel is provided in the first flow path, the performance as a heat exchanger is improved.

  According to the heat exchanger of the present invention, the partition is arranged along the joining surface of the first plate and the second plate, and the partition is joined at the outer peripheral edge together with the first plate and the second plate. The assembly structure is simple and the manufacturing cost can be kept low.

  Further, the partition wall has the same shape as the first plate, the partition wall is joined to the first plate at the outer peripheral edge, and the second plate is joined at the portion bulged to the second side. According to the heat exchanger, since it can be made without increasing the types of parts, the manufacturing cost can be reduced.

The front view of the heat exchanger of 1st Embodiment which concerns on this invention. The disassembled perspective view of a part of heat exchanger of FIG. Sectional drawing which expanded a part of heat exchanger of FIG. Sectional drawing which expanded a part of heat exchanger of 2nd Embodiment which concerns on this invention. Sectional drawing which expanded a part of heat exchanger of 3rd Embodiment which concerns on this invention. Sectional drawing which expanded a part of heat exchanger of 4th Embodiment which concerns on this invention. Sectional drawing which expanded a part of heat exchanger of 5th Embodiment which concerns on this invention. Sectional drawing which expanded a part of heat exchanger of 6th Embodiment which concerns on this invention.

  A heat exchanger 1 according to a first embodiment of the present invention will be described with reference to FIGS. 1 to 3 by taking an oil cooler mounted on a vehicle as an example. A heat exchanger 1 shown in FIG. 1 includes a core unit 10 that forms a flat flow path A through which oil L that is a heat transfer fluid flows, and an outer fin 20 that releases heat of the oil L to the outside of the core unit 10. A structure in which a plurality of layers are alternately stacked. Both ends of the core unit 10 and the outer fin 20 communicate with each other in the stacking direction. The oil L inflow port 2 is provided at one end, and the oil L outflow port 3 is provided at the other end.

  In FIG. 1, the inflow port 2 and the outflow port 3 are attached on the same side in the stacking direction, but may be arranged on the opposite side in the stacking direction. The oil L supplied from the inflow port 2 flows in parallel to each of the stacked core units 10 and is recovered from the outflow port 3.

  As shown in FIGS. 2 and 3, at least one core unit 10 among the plurality of core units 10 includes a first plate 11, a second plate 12, a partition wall 13, and an inner fin 14. In the first embodiment, the core units 10 positioned at both ends in the stacking direction have different external shapes, but all the core units 10 have the same internal structure.

  FIG. 2 shows an exploded perspective view of one end of the intermediate three layers of the stacked core units 10. In FIG. 2, the core unit 10 described at the bottom of the figure is in a combined state, and the core unit 10 in the middle stage shows a cross section cut along a plane along the direction in which the oil L flows and the laminating direction. The upper core unit 10 is further disassembled in the stacking direction in a cross-sectional view at the same position as the middle core unit 10. FIG. 3 is a cross-sectional view of one end of the intermediate three-layer core unit 10 cut along a plane along the direction in which the oil L flows and the stacking direction.

  As shown in FIGS. 2 and 3, the first plate 11 has a shape bulging in the first direction X1 (downward in FIGS. 2 and 3) in the stacking direction, and is disposed on the lower side in each figure. Has been. The second plate 12 has a shape that bulges in a second direction X2 (upward in FIGS. 2 and 3) opposite to the first direction in the stacking direction, and is disposed on the upper side in each figure. Yes.

  In this embodiment, the 1st plate 11 and the 2nd plate 12 are the same shapes, and are arrange | positioned so that the outer periphery 111,121 may face each other. The manufacturing cost is reduced because the first plate 11 and the second plate 12 have the same shape.

  As shown in FIGS. 1 to 3, the first plate 11 and the second plate 12 have flange-shaped outer peripheral edges 111 and 121 having a certain width. Both end portions of the first plate 11 and the second plate 12 bulge larger than the intermediate portion. Both end portions of the first plate 11 are in contact with both end portions of the second plate 12 of the adjacent core unit 10 to be laminated on the outer surface. Similarly, both end portions of the second plate 12 are in contact with both end portions of the first plate 11 of the adjacent core unit 10 to be laminated on the outer surface. At both ends of the first plate 11 and the second plate 12, there are through holes 112 and 122 communicating with the adjacent core unit 10, respectively. FIG. 3 shows a cross section passing through these through holes 112 and 122.

  Further, the end portions of the outer peripheral edges 111 and 121 have hem-like ribs 113 and 123 that are warped away from each other in the combined state as shown in FIGS. In addition, the second plate 12 is reinforced so that the second plate 12 is not entirely curved and the outer peripheral edges 111 and 121 are not waved. In addition, since the outer peripheral edges 111 and 121 have a certain width, they have a role of facilitating alignment during assembly and absorbing assembly tolerances.

  In the present embodiment, as shown in FIG. 2, the core unit 10 has a width in the direction in which the oil L flows along the flow path A and in the direction crossing the stacking direction, so two through holes 112 and 122 are provided. Have one by one. If the width of the core unit 10 is small, the number of through holes 112 and 122 may be one, and if the width is larger, the through holes 112 and 122 may be divided into two or more. By dividing the through holes 112 and 122 into a plurality and providing a ligament part (connecting part) between them, the end of the core unit 10 can be prevented from being deformed by the operating pressure of the oil L. When a plurality of through holes 112 and 122 are provided, a rectifying plate, a distribution plate, or the like is provided at the connection portion between the inlet 2 and the core unit 10 so that the oil L is evenly distributed to the through holes 112 and 122. Good.

  The partition wall 13 is disposed between the first plate 11 and the second plate 12 so as to partition the flow path A into the first flow path A1 and the second flow path A2 along the direction in which the heat transfer fluid flows. The In this embodiment, it arrange | positions along the joining surface of the 1st plate 11 and the 2nd plate 12, and the outer periphery 131 with the 1st plate 11 and the 2nd plate 12 is piled up and joined by 3 sheets. The The partition wall 13 has a communication portion 132 having the same shape as the through holes 112 and 122 of the first plate 11 and the second plate 12 in the stacking direction.

  The inner fins 14 are arranged in the first flow path A1, that is, between the first plate 11 and the partition wall 13, increase the heat transfer area in contact with the oil L passing through the first flow path A1, and the oil L The efficiency of transferring the heat of the oil L to the outside of the core unit 10 through the first plate 11 is improved. As shown in FIG. 2, the inner fin 14 has a structure in which a plurality of fins 141 arranged in a direction crossing the flow of the oil L are alternately arranged at regular intervals in a so-called “staggered arrangement”. It is made by bending the following material in three dimensions by press molding. The oil L, which is a heat transfer fluid, is stirred by flowing so as to be detoured to the side whenever it hits the fin 141. The shape of the inner fin 14 is not limited to the shape shown in FIG. 2 as long as the shape is agitated by the flow of the heat transfer fluid. The fins 141 may be provided along the direction in which the heat transfer fluid flows.

  The outer fin 20 is inserted between the intermediate portion of the first plate 11 and the intermediate portion of the second plate 12 of the adjacent core unit 10. The outer fin 20 is formed into a corrugated shape that is folded in a bellows shape so as to be controlled by the size, and the outside air passes between the core units 10 in a direction crossing the flow of the oil L.

  In the heat exchanger 1 of the present embodiment, the first plate 11 and the second plate 12 of the core unit 10 employ a so-called “brazing sheet” material in which a brazing material is clad on the outer surface. Each member of the core unit 10 (the first plate 11, the second plate 12, the partition wall 13 and the inner fin 14) and the outer fin 20 are all superposed and temporarily assembled in a heat treatment furnace to be heated, and the first plate 11, outer peripheral edge 131 of the partition wall 13, outer peripheral edge 121 of the second plate 12 and outer peripheral edge 131 of the partition wall 13, first plate 11 and outer fin 20, second plate 12 and outer fin 20, first The plate 11 and the inner fin 14, and the partition wall 13 and the inner fin 14 are brazed at once. The inner fin 14 may be attached to the partition wall 13 by other joining methods such as spot welding, laser welding, riveting or the like before temporary assembly so that the inner fin 14 does not move when brazed.

  In the heat exchanger 1 of the first embodiment configured as described above, the flow path A in the core unit 10 is divided into the first flow path A1 and the second flow path A2 by the partition wall 13, The inner fins 14 are arranged in the first flow path A1, and the inner fins are not arranged in the second flow path A2. The oil L supplied from the inflow port 2 is supplied to the flow path A of each core unit 10 through the through holes 112 and 122 and the communication portion 132 as indicated by arrows in FIG.

  In the present embodiment, since the flow path A is divided into the first flow path A1 and the second flow path A2 by the partition wall 13, the oil L is divided according to the flow path cross-sectional area and the flow resistance. . The heat of the oil L flowing through the first flow path A1 is released from the outer fin 20 to the outside through the first plate 11, and the heat of the oil L flowing through the second flow path A2 is passed through the second plate 12 to the outer fin 20 To the outside.

  As shown in FIG. 3, the first flow path A1 and the second flow path A2 have almost the same size in the stacking direction, and therefore the first flow path A1 in which the inner fins 14 are arranged flows. The resistance is large, and the oil L tends to flow toward the second flow path A2. Further, since the inner fin 14 is provided in the first flow path A1, the oil L flowing through the first flow path A1 releases more heat than the oil L flowing through the second flow path A2. be able to. Therefore, the difference between the amount of heat released from the first channel A1 and the amount of heat released from the second channel A2 per unit time is not so large.

  Further, in a low temperature state where a part of the oil L of the heat transfer fluid becomes solid, for example, around −30 ° C., the solidified oil L adheres to the inner fin 14 and the flow of the first flow path A1 becomes worse. In this case, that is, even when the flow resistance of the first flow path A1 is further increased, the oil L flows through the second flow path A2 where no inner fin is provided. That is, in the heat exchanger 1, the oil L is circulated through the individual core units 10, and the cooling function can be maintained.

  Further, the first flow path A1 and the second flow path A2 are only partitioned by the partition wall 13, and the heat of the oil L inside each flow path is transmitted through the partition wall 13. When the warmed oil L flows through the second flow path A2, the oil L that has become solid in the first flow path A1 is quickly warmed and melted. Since the oil L is circulated through both the first flow path A1 and the second flow path A2, the cooling performance of the heat exchanger 1 of the present embodiment used as an oil cooler is recovered.

  Below, the heat exchanger 1 of 2nd to 6th embodiment is demonstrated with reference to drawings. In each embodiment, a configuration having the same function as the configuration of the heat exchanger 1 of the first embodiment is denoted by the same reference numeral as the configuration of the heat exchanger 1 of the first embodiment. The corresponding description of the embodiment is taken into consideration.

  The heat exchanger 1 of 2nd Embodiment is demonstrated with reference to FIG. FIG. 4 is a cross-sectional view in which one end of the middle three-layer core unit 10 among a plurality of core units 10 stacked in the heat exchanger 1 is cut along the same plane as FIG. 3 of the first embodiment. It is.

  As shown in FIG. 4, the heat exchanger 1 of the second embodiment is different from the heat exchanger 1 of the first embodiment in the shape of the partition wall 13 and the configuration associated therewith. The partition wall 13 of the present embodiment is arranged to be biased toward the second plate 12, and thereby the channel cross-sectional area of the first channel A <b> 1 formed between the first plate 11 and the partition wall 13. Is larger than the flow path cross-sectional area of the second flow path A2 formed between the second plate 12 and the partition wall 13. Further, the dimensions of the inner fins 14 arranged in the first flow path A1 are also enlarged in the stacking direction of the core units 10.

  Further, in the heat exchanger 1, the second flow path A2 with respect to the flow resistance of the first flow path A1 in a low temperature state (for example, about −30 ° C.) in which a part of the oil L that is a heat transfer fluid is solid. The flow resistance of the second flow path A2 with respect to the flow resistance of the first flow path A1 in a high temperature state where the oil L as the heat transfer fluid is in a liquid state (for example, about 20 ° C., which is normal temperature). Smaller than the ratio of Specifically, as shown in FIG. 4, the flow path cross-sectional area of the first flow path A1 is set larger than the flow path cross-sectional area of the second flow path A2. The flow resistance of the second flow path A2 is smaller than the flow resistance of the first flow path A1 in the low temperature state, and the second flow is lower than the flow resistance of the first flow path A1 in the high temperature state. You may be comprised so that the flow resistance of path A2 may become large.

  Even if the flow path cross-sectional area of the second flow path A2 is smaller than the flow path cross-sectional area of the first flow path A1, the inner fin is not disposed, so that the flow resistance of the second flow path A2 is small and the temperature is low. Even in the state, the oil L can flow through the second flow path A2. Further, when the temperature becomes high, the solid oil L is also melted and the ratio (flow rate) of the oil L flowing through the first flow path A1 having a large flow path cross-sectional area is increased. As a result, in the heat exchanger 1 of the present embodiment, the oil L flows through the second flow path A2 at a low temperature state and mainly flows through the first flow path A1 at a high temperature state.

  That is, when the oil L flows through the second flow path A2 in the low temperature state, the oil L that has become solid in the first flow path A1 adjacent via the partition wall 13 can be melted. Further, in a high temperature state, mainly the oil L flows through the first flow path A1 and comes into contact with the inner fin 14, whereby the heat of the oil L is transmitted to the first plate 11 through the inner fin 14, and the inner fin 14 The heat transfer efficiency between the oil L and the first plate 11 and between the oil L and the inner fins 14 is improved by disturbing the flow in the flow path A1. Thereby, while ensuring the cooling performance as the heat exchanger 1 in a low temperature state, the cooling performance in a high temperature state can also be improved.

  A heat exchanger 1 according to a third embodiment will be described with reference to FIG. FIG. 5 is a cross-sectional view of the first embodiment with respect to an end including one intermediate layer of the plurality of core units 10 stacked in the heat exchanger 1 and half of the core units 10 adjacent to each other in the stacking direction. It is sectional drawing cut | disconnected by the same plane as FIG.

  As shown in FIG. 5, the heat exchanger 1 of the third embodiment is different from the heat exchanger 1 of the first embodiment in the shape of the second plate 12 and the configuration associated therewith. In the second plate 12 of the present embodiment, the intermediate portion is disposed so as to be biased toward the partition wall 13, whereby the flow path of the first flow path A 1 formed between the first plate 11 and the partition wall 13. The cross-sectional area is larger than the cross-sectional area of the second flow path A2 formed between the second plate 12 and the partition wall 13. Further, as the second plate 12 is biased toward the partition wall 13, the outer fin 20 is expanded in the stacking direction of the core units 10.

  Similarly to the heat exchanger 1 of the second embodiment, the heat exchanger 1 of the third embodiment is a first flow path A1 in a low temperature state in which a part of the oil L that is a heat transfer fluid is solid. The ratio of the flow resistance of the second flow path A2 to the flow resistance of the second flow path A2 with respect to the flow resistance of the first flow path A1 in a high temperature state where the oil L as the heat transfer fluid is in a liquid state. By bringing the intermediate portion of the second plate 12 closer to the partition wall 13 than in the case of the first embodiment so that the resistance ratio becomes smaller, the flow passage cross-sectional area of the first flow passage A1 is the second. It is set larger than the channel cross-sectional area of the channel A2. Similarly to the second embodiment, in the third embodiment, even if the flow path cross-sectional area of the second flow path A2 is smaller than the flow path cross-sectional area of the first flow path A1, the second flow path Since the inner fin is not disposed at A2, the oil L easily flows through the second flow path A2 even in a low temperature state. That is, in the heat exchanger 1, the oil L flows through the second flow path A2 at a low temperature and mainly flows through the first flow path A1 at a high temperature.

  In the low temperature state, the oil L flows through the second flow path A2, so that the oil L that has become solid in the first flow path A1 adjacent via the partition wall 13 can be melted and the high temperature state. In this case, the oil L mainly flows through the first flow path A1 and comes into contact with the inner fin 14, whereby the heat of the oil L is transmitted to the first plate 11 through the inner fin 14 and in the first flow path A1. The heat transfer efficiency between the oil L and the first plate 11 and between the oil L and the inner fins 14 is improved. As a result, similarly to the second embodiment, the heat exchanger 1 of the third embodiment can improve the cooling performance in the high temperature state while ensuring the cooling performance in the low temperature state.

  A heat exchanger 1 according to a fourth embodiment will be described with reference to FIG. FIG. 6 shows a first embodiment of an end portion including one half of a plurality of core units 10 stacked in the heat exchanger 1 and half of each of the core units 10 adjacent thereto in the stacking direction. It is sectional drawing cut | disconnected by the same plane as FIG. 3, and has shown the same range as FIG. 5 of 3rd Embodiment.

  As shown in FIG. 6, in the heat exchanger 1 of the fourth embodiment, the core unit 10 includes inner fins 14 disposed in the first flow path A1 and inner fins 15 disposed in the second flow path A2. And have. The inner fins 14 of the first flow path A1 have the same shape as the inner fins 14 in the heat exchanger 1 of the first embodiment. The inner fins 15 of the second flow path A2 are set to have a larger interval in which the fins 151 are arranged than the interval in which the fins 141 of the inner fins 14 of the first flow path A1 are arranged in the direction in which the oil L flows. Is different from the heat exchanger 1 of the first embodiment. In addition, the space | interval of the fin 151 and the structure of the inner fin 15 are made so that the oil L may fully flow even in the low temperature state where a part of the oil L of the heat transfer fluid is solid. In the heat exchanger 1 of the present embodiment, as shown in FIG. 6, the interval between the fins 151 is set to be approximately twice as large as the interval between the fins 141 in the direction in which the oil L flows.

  And in the heat exchanger 1 of this embodiment, ratio of the flow resistance of 2nd flow path A2 with respect to the flow resistance of 1st flow path A1 in a low temperature state is the flow resistance of 1st flow path A1 in a high temperature state. The distance between the fins 141 of the inner fins 14 of the first flow path A1 and the distance of the fins 151 of the inner fins 15 of the second flow path A2 is smaller than the ratio of the flow resistance of the second flow path A2 to the second flow path A2. It has been adjusted.

  In a low temperature state, the fluidity is lowered (the flow resistance is increased) by the oil L solidified on the inner wall of the flow path. Since the distance between the fins 151 of the inner fins 15 of the second flow path A2 is larger than the distance of the fins 14 of the inner fins 14 of the first flow path A1, the oil L flows through the second flow path A2. In addition, since the oil L is in a liquid state at a high temperature, the difference between the flow resistance of the first flow path A1 and the flow resistance of the second flow path A2 becomes small, and the oil L flows almost equally.

  At this time, since the inner fins 14 of the first flow path A1 have more fins 141, the flow speed of the first flow path A1 is slower, but the surface area where the oil L is in contact with the inner fins 14 is larger. This heat is also easily transmitted to the first plate 11 through the inner fins 14. In the fourth embodiment, the number of fins 151 is smaller than that of the inner fins 14 in the first flow path A1, but the second flow path A2 also has the inner fins 15; The heat of the oil L is also transmitted to the second plate 12. The flow rate of the second channel A2 is faster than the flow rate of the first channel A1, and the flow rate of the oil L per unit time is large. As a result, the amount of heat discharged from the first flow path A1 to the first plate 11 side and the amount of heat discharged from the second flow path A2 to the second plate 12 side are approximately the same in a high temperature state. It can also be set as follows. Since both the first flow path A1 and the second flow path A2 contribute to heat dissipation, the cooling performance of the heat exchanger 1 is improved.

  A heat exchanger 1 according to a fifth embodiment will be described with reference to FIG. FIG. 7 shows the first embodiment of the end portion including one intermediate layer of the plurality of core units 10 stacked in the heat exchanger 1 and half of the core units 10 adjacent to each other in the stacking direction. It is sectional drawing cut | disconnected by the same plane as FIG. 3, and has shown the same range as FIG. 5 of 3rd Embodiment, and FIG. 6 of 4th Embodiment.

  As shown in FIG. 7, the heat exchanger 1 of the fifth embodiment is different from the heat exchanger 1 of the first embodiment in the shape of the partition wall 13 and the configuration associated therewith. The partition wall 13 of the present embodiment has a projecting portion 133 extending to the second flow path A2 side in the communication portion 132. The protruding portion 133 has the same opening shape as the communication portion 132 as in the first embodiment, that is, the same size as the through holes 112 and 122 of the first plate 11 and the second plate 12. , Are arranged at a position that overlaps in the stacking direction.

  As shown in FIG. 7, by providing the protruding portion 133, the communication portion 132 of the partition wall 13 of the fifth embodiment has a second plate 12 compared to the communication portion 132 of the partition wall 13 of the first embodiment. It is arranged close to the through hole 122. As a result, the cross-sectional area of the second flow path A2 formed between the second plate 12 and the partition wall 13 is the same as that of the first flow path A1 formed between the first plate 11 and the partition wall 13. Even if it is the same as the cross-sectional area of the flow path, the flow rate of the oil L flowing to the second flow path A2 is less than the flow rate of the oil L flowing to the first flow path A1 in a high temperature state where the oil L is in a liquid state. Become. Moreover, even if the oil L is difficult to flow to the first flow path A1 where the inner fins 14 are arranged in a low temperature state where a part of the oil L is in a solid state, the second flow path A2 where no inner fins are arranged is provided. Oil L flows.

  In the heat exchanger 1 of the fifth embodiment, the ratio of the flow resistance of the second flow path A2 to the flow resistance of the first flow path A1 in the low temperature state is the flow resistance of the first flow path A1 in the high temperature state. It is comprised so that it may become smaller than ratio of the flow resistance of 2nd flow path A2 with respect to. That is, the flow resistance of the second flow path A2 is smaller than the flow resistance of the first flow path A1 in the low temperature state, and the second flow path A2 is lower than the flow resistance of the first flow path A1 in the high temperature state. It has the same function as the structure of the heat exchanger 1 of 2nd and 3rd embodiment so that the flow resistance of this may become larger.

  As a result, in a low temperature state, the oil L that has become solid in the adjacent first flow path A1 through the partition wall 13 can be melted. Further, in a high temperature state, the oil L flows through the first flow path A1 more than the second flow path A2, and the heat of the oil L is transmitted to the first plate 11 through the inner fin 14 by contacting the inner fin 14. The heat transfer efficiency between the oil L and the first plate 11 and between the oil L and the inner fin 14 is improved by disturbing the flow of the oil L in the first flow path A1 by the inner fin 14.

  The heat exchanger 1 of 6th Embodiment is demonstrated with reference to FIG. FIG. 8 is a cross-sectional view in which one end of the core unit 10 of the middle two layers among the plurality of core units 10 stacked in the heat exchanger is cut along the same plane as FIG. 3 of the first embodiment. is there.

  As shown in FIG. 8, the heat exchanger 1 of the sixth embodiment is different from the heat exchanger 1 of the first embodiment in the shape of the partition wall 13 and the configuration associated therewith. The partition wall 13 of the present embodiment has the same shape as the second plate 12, is disposed between the first plate 11 and the second plate 12 in the stacking direction, and is joined to the first plate 11 at the outer peripheral edge 131. At the same time, it is joined to the second plate 12 at a portion that bulges to the second side.

  Since the partition wall 13 has the same shape as the second plate 12, the second plate 12 and the partition wall 13 have a larger cross-sectional area than the first channel A 1 formed between the first plate 11 and the partition wall 13. The channel cross-sectional area of the second channel A2 formed in between is smaller. Further, the communication portions 132 provided at both ends of the partition wall 13 are close to the through hole 122 of the second plate 12. Furthermore, since the displacement portion 124 having a step in the stacking direction between the both end portions and the intermediate portion of the second plate 12 and the corresponding displacement portion 134 of the partition wall 13 have the same shape, a certain distance in the stacking direction. It is closer than both ends and the middle part. And the inner fin 14 arrange | positioned in 1st flow path A1 is provided in the inner surface of 1st flow path A1 in the lamination direction.

  By configuring each core unit 10 as described above, in the heat exchanger 1 of the present embodiment, the first resistance against the flow resistance of the first flow path A1 in a low temperature state where a part of the oil L is solid. The flow resistance ratio of the second flow path A2 is smaller than the ratio of the flow resistance of the second flow path A2 to the flow resistance of the first flow path A1 in a high temperature state where the oil L is in a liquid state.

  Therefore, as in the other embodiments, the heat exchanger 1 of the present embodiment rapidly melts the solid oil L by flowing the oil L through the second flow path A2 in a low temperature state. Can do. In addition, the oil L mainly flows through the first flow path A1 in a high temperature state, so that the heat of the oil L is transmitted to the first plate 11 through the inner fin 14 in contact with the inner fin 14, and the first The flow of the oil L in the flow path A1 is disturbed, and the heat transfer efficiency between the oil L and the first plate 11 and between the oil L and the inner fin 14 is improved.

  The heat exchanger 1 according to the present invention has been described based on the first to sixth embodiments. These embodiments are merely examples for ease of understanding in carrying out the present invention. Therefore, in implementing the present invention, it is possible to replace the components with those having equivalent functions without departing from the spirit thereof, and these are also included in the present invention. In addition, it is also included in the present invention that some of the configurations described in each embodiment are combined with each other or replaced.

  For example, the partition wall 13 in the heat exchanger 1 of the second embodiment may be adopted in the fourth and fifth embodiments, or the protrusion of the partition wall 13 in the heat exchanger 1 of the fifth embodiment may be You may provide in the communication part 132 of the partition 13 of the heat exchanger 1 of 2nd-4th embodiment. In the fourth embodiment, the inner fins 15 arranged in the second flow path A2 are not limited to the similar shape of the inner fins 14 arranged in the first flow path A1, and are parallel to the direction in which the oil L flows. It may be arranged at an angle or may be arranged at an angle.

  Furthermore, in each embodiment, the partition 13 was provided in all the core units 10, and it was set as the structure by which the flow path A was divided into 1st flow path A1 and 2nd flow path A2. At least one core unit 10 may be included in the heat exchanger 1. In a low temperature state where a part of the heat transfer fluid (oil L) is in a solid state, the heat transfer fluid is circulated through the second flow path A2 of the core unit 10 having the partition wall 13, thereby heat of the heat transfer fluid. However, the heat transfer fluid that has become solid in the flow path A, particularly in the first flow path A1, is rapidly melted through each member, and functions as the heat exchanger 1.

  In each embodiment, the oil L has been described as an example of the heat transfer fluid. However, the heat transfer fluid is not limited to the oil L, but may be other water such as pure water depending on the specifications of the heat exchanger such as a use temperature and a heat transfer amount. It may be a liquid or an inert gas such as nitrogen, or a refrigerant such as alternative chlorofluorocarbon represented by HFC (hydrofluorocarbon).

  DESCRIPTION OF SYMBOLS 1 ... Heat exchanger, 10 ... Core unit, 11 ... 1st plate, 111 ... Outer periphery, 112 ... Through-hole, 12 ... Second plate, 121 ... Outer periphery, 122 ... Through-hole, 13 ... Septum, 131 ... outer peripheral edge, 132 ... communication part, 133 ... projecting part, 14 ... inner fin, 20 ... outer fin, A ... flow path, A1 ... first flow path, A2 ... second flow path, L ... oil (heat transfer fluid) ), X1... First direction, X2... Second direction.

Claims (6)

A heat exchanger in which a plurality of core units each having a flow path through which a heat transfer fluid flows and outer fins that release heat of the heat transfer fluid are alternately stacked, and both ends of the core unit are communicated in the stacking direction,
At least one of the core units is
A first plate shaped to bulge to the first side in the stacking direction;
A second plate shaped to bulge to the second side opposite to the first side in the stacking direction;
Arranged between the first plate and the second plate so as to partition the flow path into a first flow path and a second flow path along a direction in which the heat transfer fluid flows. Partition walls having communication portions at both ends for communicating the flow channel with the second flow channel,
And an inner fin disposed in the first flow path. The ratio of the flow resistance of the second flow path to the flow resistance of the first flow path in a low temperature state where a part of the heat transfer fluid is in a solid state is a high temperature state where the heat transfer fluid is in a liquid state 2. The heat exchanger according to claim 1, wherein a ratio of a flow resistance of the second flow path to a flow resistance of the first flow path is smaller. The heat exchanger according to claim 1 or 2, wherein the first channel has a channel cross-sectional area larger than a channel cross-sectional area of the second channel. . The heat exchanger according to any one of claims 1 to 3, wherein the communication portion has a protruding portion that extends toward the second flow path. The partition is disposed along a joint surface between the first plate and the second plate, and is joined together with the first plate and the second plate at an outer peripheral edge. The heat exchanger according to claim 1. The partition wall has the same shape as the second plate, and is joined to the first plate at an outer peripheral edge and joined to the second plate at a portion bulging to the second side. The heat exchanger according to any one of claims 1 to 4, characterized in that:

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