JP6599121B2 - Heat exchanger and waste heat recovery device - Google Patents

Description

  The present invention relates to a heat exchanger and a waste heat recovery apparatus.

  Conventionally, as a technique related to a heat exchanger, for example, a condenser described in Patent Document 1 is known. The condenser described in Patent Document 1 includes a plurality of tubes for circulating a refrigerant, corrugated fins provided between adjacent tubes, and a pair of headers connected to both ends of the tubes, and the inside of the headers. Is provided with a partition plate. In the condenser described in Patent Document 1, the refrigerant flowing from the refrigerant inlet pipe flows so as to meander in the refrigerant flow path from the refrigerant inlet pipe to the refrigerant outlet pipe.

JP-A-63-161393

  In the prior art, since the refrigerant is circulated in a meandering manner as described above, the flow path length of the refrigerant flow path may increase and the pressure loss may increase. Moreover, in the said prior art, the uneven temperature distribution (temperature nonuniformity) arises in a heat exchanger, and heat exchange performance may become inadequate.

  This invention is made | formed in view of the said situation, and makes it a subject to provide the heat exchanger and waste heat recovery apparatus which can make high heat exchange performance and reduction of pressure loss compatible.

  The heat exchanger according to the present invention includes a first flow path layer and a second flow path layer that are adjacent to each other, and a first fluid that flows through the first flow path layer and a second fluid that flows through the second flow path layer. The first flow path layer is provided with an inflow tank portion provided with an inflow port through which the first fluid flows in and an outflow port through which the first fluid flows out. An inflow tank portion, and an intermediate portion that is provided between the inflow tank portion and the outflow tank portion and distributes the first fluid from the inflow tank portion to the outflow tank portion, and the inflow direction of the first fluid in the inflow tank portion A plurality of first heat exchange fins extending along the at least one of the plurality of second heat exchange fins extending along the outflow direction of the first fluid in the outflow tank portion, and first and second heat exchanges in the intermediate portion. A third extending along a direction intersecting at least one of the fins; And exchange fins, wherein at least one of the first and second heat exchanger fins, the first fluid between adjacent pair of channels among a plurality of channels formed with a possible flow geometry.

  In this heat exchanger, not only the third heat exchange fin but also at least one of the first and second heat exchange fins is provided in the first flow path layer. Therefore, not only the intermediate part but also at least one of the inflow tank part and the outflow tank part, the first fluid can exchange heat with the second fluid flowing through the second flow path layer. In addition, in at least one of the inflow tank portion and the outflow tank portion, the first fluid can flow between a pair of adjacent channels. Therefore, for example, in the inflow tank portion (outflow tank portion), the first fluid can flow in the direction intersecting the flow direction while flowing the first fluid in the inflow direction (outflow direction). . Accordingly, the first fluid is effectively heat exchanged with the second fluid while suppressing an increase in the channel length of the first fluid and reducing the pressure loss, thereby suppressing temperature unevenness in the first channel layer. be able to. That is, it is possible to achieve both high heat exchange performance and reduced pressure loss.

  In the heat exchanger according to the present invention, the second flow path layer includes a facing portion adjacent to an intermediate portion of the first flow path layer, and the facing portion is a flow of the first fluid in the intermediate portion of the first flow path layer. The second fluid may be circulated in a direction opposite to the direction. According to such a configuration, it is possible to realize the flow of the first fluid and the second fluid facing each other (so-called counter flow). Therefore, it is possible to further reduce pressure loss while having high heat exchange performance.

  In the heat exchanger according to the present invention, at least one of the first and second heat exchange fins may be a louver fin or an offset fin.

  A waste heat recovery apparatus according to the present invention includes a Rankine cycle device in which a working fluid is circulated, and is a waste heat recovery device that recovers waste heat from a high-temperature heat source. The Rankine cycle device is an evaporator that evaporates the working fluid. As described above, the heat exchanger includes the heat exchanger, and the heat exchanger evaporates the working fluid by transferring heat from the high-temperature heat source as the second fluid to the working fluid as the first fluid.

  In this waste heat recovery apparatus, by applying the above-described heat exchanger to the evaporator, it is possible to achieve both high heat exchange performance and reduced pressure loss in heat transfer from the high-temperature heat source to the working fluid. As a result, the thermal efficiency of the Rankine cycle device can be improved, and the exhaust heat recovery efficiency of the waste heat recovery device can be improved.

  ADVANTAGE OF THE INVENTION According to this invention, it becomes possible to provide the heat exchanger and waste heat recovery apparatus which can make high heat exchange performance and reduction of pressure loss compatible.

It is a block diagram which shows the waste heat recovery apparatus which has the heat exchanger which concerns on embodiment. (A) is a front view of the heat exchanger of one Embodiment of this invention. FIG. 2B is a cross-sectional view taken along the line IIb-IIb in FIG. (A) is sectional drawing along the IIIa-IIIa line | wire in FIG.2 (b). FIG. 2B is a partial cross-sectional view taken along line IIIb-IIIb in FIG. (A) is a figure showing an example of a louver fin. (B) is a figure which shows an example of an offset fin. (C) is a figure which shows an example of a square fin. (D) is a figure showing an example of a wave type fin. It is a partial cross section figure of the heat exchanger which concerns on a comparative example.

  DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, preferred embodiments of the invention will be described in detail with reference to the drawings. In the following description, the same or equivalent elements are denoted by the same reference numerals, and redundant description is omitted.

  FIG. 1 is a block diagram illustrating a waste heat recovery apparatus having a heat exchanger according to an embodiment. As FIG. 1 shows, the heat exchanger 1 which concerns on embodiment is applied to the waste heat recovery apparatus 100 provided with the Rankine cycle apparatus 10, for example, is mounted in a vehicle. Examples of the vehicle to be applied include commercial vehicles such as trucks and buses. The vehicle is not particularly limited, and may be, for example, a large vehicle, a medium vehicle, a normal passenger vehicle, a small vehicle, a light vehicle, or the like.

  The Rankine cycle apparatus 10 uses, for example, the waste heat of the engine E as heat input, converts the heat energy related to the waste heat into power, and outputs the power. The Rankine cycle device 10 includes a working fluid pump 11, an evaporator 12, an expander 13, and a condenser 14 in the flow path 15. The working fluid M is circulated through the flow path 15 in the Rankine cycle device 10. Various fluids can be used as the working fluid M. Here, R134a which is a low boiling point medium is used.

  The working fluid pump 11 is a pump that pumps and circulates the working fluid M. The evaporator 12 is provided on the downstream side of the working fluid pump 11 and heats and evaporates the working fluid M compressed by the working fluid pump 11. In the evaporator 12, the working fluid M is heated and evaporated by the waste heat of the engine E input through the cooling water (high temperature heat source) W of the engine E. As the evaporator 12, a heat exchanger 1 described later is applied. That is, the heat exchanger 1 evaporates the working fluid M by transferring heat from the cooling water W as the second fluid to the working fluid M as the first fluid.

  The expander 13 is provided on the downstream side of the evaporator 12. The expander 13 rotates by the expansion of the working fluid M and outputs power. For example, a turbine or the like is used as the expander 13. The expander 13 may output a mechanical output, for example, or may be connected to a generator and output an electrical output, for example. The condenser 14 is provided on the downstream side of the expander 13. The condenser 14 is a heat exchanger that cools and condenses (liquefies) the working fluid M. The condenser 14 is cooled by a low-temperature heat source (not shown). The low-temperature heat source includes, for example, a sub-radiator, and cools the condenser 14 with, for example, traveling wind when the vehicle travels.

  The engine E is an internal combustion engine such as a water-cooled diesel engine. The engine E includes an engine main body 20 including a cylinder head, a cylinder block, and the like, an EGR cooler 21 that cools an EGR (Exhaust Gas Recirculation) gas, a cooling water passage 22 that circulates the cooling water W, and heat of, for example, traveling wind And a radiator 23 that cools the cooling water W by replacement. The cooling water W is circulated through the engine main body 20 through the cooling water flow path 22 to cool the engine main body 20. The cooling water W is circulated through the EGR cooler 21 through the cooling water flow path 22 to cool the EGR gas.

  Next, the configuration of the heat exchanger 1 will be described with reference to FIGS. Fig.2 (a) is a front view of the heat exchanger of one Embodiment of this invention. FIG. 2B is a sectional view taken along line IIb-IIb in FIG. FIG. 3A is a cross-sectional view taken along the line IIIa-IIIa in FIG. FIG. 3B is a cross-sectional view taken along line IIIb-IIIb in FIG. In the following description, the X direction is a direction along the inflow direction and the outflow direction of the first fluid, and the Y direction is a direction orthogonal to the inflow direction and the outflow direction of the first fluid.

  As shown in FIGS. 2A and 2B, the heat exchanger 1 includes a housing 2 having a quadrangular prism shape. The illustrated housing 2 is inclined such that the end in the Y direction has a quadrangular frustum shape. The heat exchanger 1 includes a plurality of first flow path layers 4 through which the working fluid M flows and a plurality of second flow path layers 5 through which the cooling water W that is a high-temperature heat source flows. The first flow path layers 4 and the second flow path layers 5 are alternately stacked. That is, the first flow path layer 4 and the second flow path layer 5 are adjacent to each other. The first flow path layer 4 and the second flow path layer 5 are stored in the outer wall 6 of the housing 2. Such a heat exchanger 1 transfers heat between the working fluid M flowing through the first flow path layer 4 and the cooling water W flowing through the second flow path layer 5. In the heat exchanger 1, the working fluid M constitutes the first fluid, and the cooling water W constitutes the second fluid.

  As shown in FIG. 3A, the first flow path layer 4 includes an inflow tank portion 30, an outflow tank portion 31, and an intermediate portion 32. The inflow tank portion 30 is provided with an inflow port 33 through which the working fluid M flows. The inflow port 33 is connected to one end side of the housing 2 in the Y direction so as to communicate with the inside of the inflow tank portion 30. The inflow port 33 extends along the X direction, and is formed of, for example, a pipe member.

  The inflow tank unit 30 includes a plurality of heat exchange fins (first heat exchange fins) 40. The plurality of heat exchange fins 40 extend along the inflow direction (X direction) of the working fluid M in the inflow tank portion 30. The plurality of heat exchange fins 40 form a plurality of channels 41. Accordingly, the plurality of channels 41 extend along the X direction. The channel 41 is a space in which the inside of the inflow tank portion 30 is partitioned by the adjacent heat exchange fins 40 and the working fluid M is circulated. The heat exchange fin 40 has a shape in which the working fluid M can flow between a pair of adjacent channels 41 among a plurality of channels 41 to be formed (details will be described later). The inflow tank portion 30 communicates with the intermediate portion 32. The inflow tank unit 30 sends the working fluid M that has flowed into the first flow path layer 4 through the inflow port 33 to the intermediate unit 32.

  The intermediate part 32 is provided between the inflow tank part 30 and the outflow tank part 31. The intermediate part 32 circulates the working fluid M from the inflow tank part 30 to the outflow tank part 31. The intermediate part 32 includes a plurality of heat exchange fins (third heat exchange fins) 42. The plurality of heat exchange fins 42 extend along a direction (Y direction) orthogonal to (intersect) the heat exchange fins 40 and a heat exchange fin 44 described later in the intermediate portion 32. The plurality of heat exchange fins 42 are arranged in parallel. The plurality of heat exchange fins 42 form a plurality of channels 43. The plurality of channels 43 extend along the Y direction. The channel 43 is a space in which the inside 32 is partitioned by the adjacent heat exchange fins 42 and the working fluid M flows therethrough. The heat exchange fins 42 have a shape that allows the working fluid M to flow along a plurality of channels 43 to be formed (details will be described later). The intermediate part 32 communicates with the outflow tank part 31. The intermediate part 32 sends the working fluid M flowing in from the inflow tank part 30 to the outflow tank part 31.

  The outflow tank unit 31 is provided with an outflow port 34 through which the working fluid M flows out. The outflow port 34 is connected to the other end side in the Y direction of the housing 2 so as to communicate with the inside of the outflow tank portion 31. The outflow port 34 extends along the X direction, and is formed of, for example, a pipe member. The outflow tank unit 31 has a plurality of heat exchange fins (second heat exchange fins) 44. The plurality of heat exchange fins 44 extend in the outflow tank portion 31 along the outflow direction (X direction) of the working fluid M. The plurality of heat exchange fins 44 form a plurality of channels 45. Therefore, the plurality of channels 45 extend along the X direction. The channel 45 is a space in which the inside of the outflow tank portion 31 is partitioned by the adjacent heat exchange fins 44 and the working fluid M is circulated. The heat exchange fin 44 has a shape in which the working fluid M can flow between a pair of adjacent channels 45 among a plurality of channels 45 to be formed (details will be described later). The outflow tank unit 31 causes the working fluid M flowing in from the intermediate unit 32 to flow out from the first flow path layer 4 through the outflow port 34.

  As shown in FIG. 3B, the second flow path layer 5 includes an inflow tank portion 35, an outflow tank portion 36, and a facing portion 37. The inflow tank portion 35 is provided with an inflow port 38 through which the cooling water W flows. The inflow port 38 is connected to the other end side of the housing 2 in the Y direction so as to communicate with the inside of the inflow tank portion 35. The inflow port 38 extends along the X direction, and is formed of, for example, a pipe member. The inflow tank portion 35 communicates with the facing portion 37. The inflow tank portion 35 is an empty space in which no heat conducting fin is provided. The inflow tank portion 35 sends the cooling water W that has flowed into the second flow path layer 5 through the inflow port 38 to the facing portion 37.

  The facing portion 37 is provided between the inflow tank portion 35 and the outflow tank portion 36. The facing portion 37 is adjacent to the intermediate portion 32 of the first flow path layer 4. The facing portion 37 circulates the cooling water W in a direction facing the flow direction of the working fluid M in the intermediate portion 32 of the first flow path layer 4. The facing portion 37 includes a plurality of heat exchange fins 46. The plurality of heat exchange fins 46 extend along the direction (Y direction) in which the heat exchange fins 42 of the intermediate portion 32 extend in the facing portion 37. The plurality of heat exchange fins 46 form a plurality of channels 47. The plurality of channels 47 extend along the Y direction. The channel 47 is a space in which the facing portion 37 is partitioned by the adjacent heat exchange fins 46 and allows the working fluid M to flow therethrough. The facing portion 37 communicates with the outflow tank portion 36. The facing portion 37 sends the cooling water W flowing in from the inflow tank portion 35 to the outflow tank portion 36.

  The outflow tank portion 36 is provided with an outflow port 39 through which the cooling water W flows out. The outflow port 39 is connected to one end side of the housing 2 in the Y direction so as to communicate with the inside of the outflow tank portion 36. The outflow port 39 extends along the Y direction, and is formed of, for example, a pipe member. The outflow tank portion 36 is an empty space in which no heat conducting fin is provided. The outflow tank portion 36 causes the cooling water W flowing in from the facing portion 37 to flow out from the second flow path layer 5 via the outflow port 39.

  Here, the shape of the heat exchange fins 40, 42, 44, and 46 will be specifically described with reference to FIGS. 4 (a) to 4 (d). FIG. 4A is a diagram illustrating an example of a louver fin. FIG. 4B is a diagram illustrating an example of the offset fin. FIG.4 (c) is a figure which shows an example of a square fin. FIG. 4D is a diagram illustrating an example of a corrugated fin.

  The heat exchange fin 40 in the inflow tank portion 30 has a shape that allows the working fluid M to flow between a pair of adjacent channels 41 among the plurality of channels 41 to be formed. As the heat exchange fin 40, a louver fin 50 or an offset fin 60 is employed. The heat exchange fin 40 here is a louver fin 50. Further, the heat exchange fins 44 in the outflow tank portion 31 have a shape that allows the working fluid M to flow between a pair of adjacent channels 45 among the plurality of channels 45 to be formed. As the heat exchange fins 44, louver fins 50 or offset fins 60 are employed. The heat exchange fins 44 here are louver fins 50.

  As shown in FIG. 4A, the louver fin 50 has a V-shaped cross section when viewed from the X direction and extends along the X direction. Louver fins 50 are arranged in the Y direction. Adjacent louver fins 50 are connected together and integrated. The plurality of louver fins 50 are configured to be corrugated along the Y direction.

  Louver fin 50 includes a plane portion 51 and a plane portion 52 that intersect at a predetermined angle. Each of the flat part 51 and the flat part 52 is provided with a plurality of through holes 53 having a rectangular cross section. The through-holes 53 are spaced apart from each other in the X direction in each of the planar portion 51 and the planar portion 52. A louver 54 is provided in the through-hole 53. The louver 54 is connected to one edge of the through hole 53 and extends so as to block the through hole 53 with a predetermined gap. The louver 54 inclines away from the flat surface portion 51 or the flat surface portion 52 as it goes from the proximal end side to the distal end side. Such a through-hole 53 with a louver 54 is formed, for example, by providing a U-shaped cut in the flat portion 51 and the flat portion 52 and bending a portion surrounded by the cut by a predetermined amount.

  The plurality of louver fins 50 form a plurality of channels 41. The plurality of channels 41 are defined by the plane portions 51 and the plane portions 52 of the plurality of louver fins 50. One channel 41 a of the pair of adjacent channels 41 is connected to the other channel 41 b by a through-hole 53. In other words, the plurality of channels 41 formed by the plurality of louver fins 50 are used to distribute the working fluid M between the adjacent channels 41a and 41b through the through-hole 53 having the louver 54, while the working fluid M is channeled. It distribute | circulates along 41 (along X direction).

  As shown in FIG. 4B, the offset fin 60 has a cross-sectional hat shape when viewed from the X direction. The offset fins 60 are arranged in the Y direction. The offset fins 60 are arranged so as to be aligned in the X direction while being shifted (offset) in the Y direction. The offset fin 60 includes a plane portion 61, a plane portion 62, and a plane portion 63 that are orthogonal to each other.

  The plurality of offset fins 60 form a plurality of channels 41. The plurality of channels 41 are defined by the planar portion 61, the planar portion 62, and the planar portion 63 of the plurality of offset fins 60. Since the offset fins 60 are arranged in the X direction while being displaced in the Y direction, one channel 41a of the pair of adjacent channels 41 communicates with the other channel 41b. For example, one channel 41a shown in the figure is a flow channel that flows while being inclined with respect to the X direction (a flow channel surrounded by the flat portions 61 to 63), and a flow that flows from the X direction end of the offset fin 60 into the other channel 41b. Road. That is, the plurality of channels 41 formed by the plurality of offset fins 60 allows the working fluid M to flow along the channels 41 (along the X direction) while flowing the working fluid M between the adjacent channels 41a and 41b. Circulate.

  The heat exchange fins 46 in the facing portion 37 have a shape that allows the cooling water W to flow along the plurality of channels 47 to be formed. The heat exchange fins 46 here are square fins 70.

  As shown in FIG. 4C, the square fin 70 has a cross-sectional hat shape when viewed from the Y direction, and extends along the Y direction. The square fins 70 are arranged in the X direction. Adjacent square fins 70 are connected together and integrated. The plurality of square fins 70 are configured to have a rectangular wave shape along the X direction. The square fin 70 includes a plane portion 71, a plane portion 72, and a plane portion 73 that are orthogonal to each other.

  The plurality of square fins 70 form a plurality of channels 47. Here, the plurality of channels 47 are defined by the planar portion 71, the planar portion 72, and the planar portion 73 of the plurality of square fins 70. The plurality of channels 47 formed by the plurality of square fins 70 circulate the cooling water W along the channels 47 (along the Y direction) without flowing the cooling water W between the adjacent channels 47.

  The heat exchange fins 42 in the intermediate portion 32 have a shape that allows the working fluid M to flow along the plurality of channels 43 to be formed. The heat exchange fins 42 here are corrugated fins 80.

  As shown in FIG. 4D, the corrugated fin 80 has a V-shaped cross section when viewed from the Y direction, and extends along the Y direction. The corrugated fins 80 are arranged in the X direction. Adjacent corrugated fins 80 are connected together and integrated. The plurality of corrugated fins 80 are configured to be corrugated along the X direction. The corrugated fin 80 includes a plane portion 81 and a plane portion 82 that intersect at a predetermined angle.

  The plurality of corrugated fins 80 form a plurality of channels 43. The plurality of channels 43 here are defined by the plane portions 81 and the plane portions 82 of the plurality of corrugated fins 80. The plurality of channels 43 formed by the plurality of corrugated fins 80 distribute the working fluid M along the channels 43 (along the Y direction) without flowing the working fluid M between the adjacent channels 43.

  In the first flow path layer 4 of the heat exchanger 1 configured as described above, the working fluid M that has flowed into the inflow tank portion 30 from the inflow port 33 flows through the heat exchange fins 40 along the X direction while passing through the through-hole. It flows in the Y direction via 53 and flows into the intermediate part 32. The working fluid M flowing into the intermediate portion 32 flows along the Y direction by the heat exchange fins 42 and flows into the outflow tank portion 31. The working fluid M that has flowed into the outflow tank portion 31 flows in the Y direction through the through-hole 53 while flowing along the X direction by the heat exchange fins 44, and then flows in from the outflow port 39 along the X direction. On the other hand, in the second flow path layer 5, the cooling water W flowing into the inflow tank portion 35 from the inlet 38 flows into the facing portion 37 and flows along the Y direction by the heat exchange fins 46 in the facing portion 37. After that, it flows into the outflow tank section 36. And it flows out from the outflow port 39 along a X direction.

  As described above, not only the heat exchange fins 42 but also the heat exchange fins 40 and the heat exchange fins 44 are provided in the first flow path layer 4 of the heat exchanger 1 according to the present embodiment. Therefore, the working fluid M can exchange heat with the cooling water W flowing through the second flow path layer 5 not only in the intermediate portion 32 but also in the inflow tank portion 30 and the outflow tank portion 31.

  In addition, in the inflow tank portion 30, the working fluid M can flow between a pair of adjacent channels 41. In the outflow tank portion 31, the working fluid M can flow between a pair of adjacent channels 45. Thereby, in the inflow tank part 30 (outflow tank part 31), it is possible to flow the working fluid M in a direction perpendicular to the flow direction while flowing the working fluid M in the inflow direction (outflow direction). It becomes. For example, when the heat exchanger 1 is viewed as a whole, the working fluid M flows in one direction from the inflow tank portion 30 side to the outflow tank portion 31 side (the working fluid M flows in one way). Does not meander and circulate, and does not circulate in the heat exchanger 1 many times.

  Therefore, while suppressing the increase in the flow path length of the working fluid M and reducing the pressure loss, the working fluid M is effectively exchanged with the cooling water W, thereby suppressing the temperature unevenness in the first flow path layer 4. can do. In other words, the pressure loss can be reduced by shortening the channel length without reducing the amount of heat that can be transferred between the working fluid M and the cooling water W in the heat exchanger 1. That is, according to the heat exchanger 1, it is possible to achieve both high heat exchange performance and reduced pressure loss.

  For example, as shown in FIG. 5, when the inflow tank unit 30 and the outflow tank unit 31 are empty spaces, the working fluid M and the cooling water W are mixed in the inflow tank unit 30 and the outflow tank unit 31. There is not enough heat exchange between them. In this respect, in the heat exchanger 1 according to the present embodiment, not only the heat exchange fins 42 of the intermediate portion 32 but also the heat exchange fins 40 and the heat exchange fins 44 are provided. Therefore, in the first flow path layer 4, heat exchange is possible not only in the intermediate portion 32 but also in the inflow tank portion 30 and the outflow tank portion 31. In this way, it is possible to achieve both high heat exchange performance and reduced pressure loss. The heat exchange performance here refers to the amount of heat that can be transferred between the working fluid M and the cooling water W when the heat exchangers 1 having the same size are compared, for example.

  In the heat exchanger 1, the second flow path layer 5 includes a facing portion 37 adjacent to the intermediate portion 32 of the first flow path layer 4. In the facing portion 37, the cooling water W is circulated in a direction facing the flow direction of the working fluid M in the intermediate portion 32 of the first flow path layer 4. According to such a configuration, it becomes possible to cause the working fluid M and the cooling water W to circulate facing each other (so-called counter flow). Therefore, it is possible to further reduce pressure loss while having high heat exchange performance.

  In the heat exchanger 1, the heat exchange fins 40 and the heat exchange fins 44 are louver fins 50 or offset fins 60. Thus, the above-described action of circulating the working fluid M between the pair of adjacent channels 41 and the above-described action of flowing the working fluid M between the pair of adjacent channels 45 can be realized specifically and preferably.

  The waste heat recovery apparatus 100 according to this embodiment includes a Rankine cycle apparatus 10 in which the working fluid M is circulated, and recovers waste heat of the cooling water W of the engine E. In the Rankine cycle apparatus 10, the heat exchanger 1 is applied as the evaporator 12 that evaporates the working fluid M. In the heat exchanger 1, heat is transferred from the cooling water W to the working fluid M, and the working fluid M is evaporated.

  In such a waste heat recovery apparatus 100, by applying the heat exchanger 1 described above to the evaporator 12, high heat exchange performance and reduction of pressure loss in heat transfer from the cooling water W to the working fluid M are achieved. Can be compatible. As a result, the thermal efficiency of the Rankine cycle apparatus 10 is improved, and the exhaust heat recovery efficiency of the waste heat recovery apparatus 100 can be improved.

  When the heat exchanger 1 is assumed to be applied to the evaporator 12 in this way, in the heat exchanger 1, heat is transferred from the cooling water W as the second fluid to the working fluid M as the first fluid. Thus, the working fluid M is evaporated. That is, the working fluid M flowing in from the inlet 33 and the cooling water W flowing in from the inlet 38 are both in a liquid phase.

  As mentioned above, although preferred embodiment which concerns on this invention was described, this invention is not limited to the said embodiment, It deform | transforms in the range which does not change the summary described in each claim, or is applied to another thing. May be.

  In the above embodiment, the heat exchange fin 40 for forming the channel 41 is provided in the inflow tank portion 30 and the heat exchange fin 44 for forming the channel 45 is provided in the outflow tank portion 31. Only one may be provided.

  Moreover, although the heat exchange fin 40 in the inflow tank part 30 and the heat exchange fin 44 in the outflow tank part 31 were demonstrated as the louver fin 50 of the same shape, both may employ | adopt the offset fin 60, Alternatively, an offset fin 60 may be employed. The heat exchange fins 40 and 44 may have various shapes as long as the working fluid M can flow between the pair of adjacent channels 41 and 45.

  Moreover, although the heat exchange fin 42 in the intermediate part 32 was demonstrated as the wave type fin 80, the square fin 70 may be employ | adopted and the louver fin 50 or the offset fin 60 may be employ | adopted. The heat exchange fin 42 may have various shapes as long as it has a shape that allows the working fluid M to flow in the Y direction along the channel 43.

  Moreover, although the heat exchange fin 46 in the opposing part 37 was demonstrated as the square fin 70, the wave fin 80 may be employ | adopted and the louver fin 50 or the offset fin 60 may be employ | adopted. The heat exchange fin 46 may have various shapes as long as it has a shape that allows the cooling water W to flow in the Y direction along the channel 47.

  In the facing portion 37 in the second flow path layer 5, the cooling water W is circulated in a direction opposite to the flow direction of the working fluid M in the intermediate portion 32 of the first flow path layer 4. The flow direction of the cooling water W is not limited to this example. The second flow path layer 5 may have a flow path for circulating the cooling water W in the X direction, or may have a flow path for circulating the cooling water W in the Y direction. You may have the combined flow path.

  DESCRIPTION OF SYMBOLS 1 ... Heat exchanger, 4 ... 1st flow path layer, 5 ... 2nd flow path layer, 10 ... Rankine cycle apparatus, 12 ... Evaporator, 30 ... Inflow tank part, 31 ... Outflow tank part, 32 ... Middle part, 33 ... Inlet, 34 ... Outlet, 37 ... Opposite part, 40 ... Heat exchange fin (first heat exchange fin), 41 ... Channel, 42 ... Heat exchange fin (third heat exchange fin), 44 ... Heat exchange fin (Second heat exchange fin), 45 ... channel, 50 ... louver fin, 60 ... offset fin, 100 ... waste heat recovery device, M ... working fluid (first fluid), W ... cooling water (second fluid, high temperature heat source) ).

Claims (6)

A first flow path layer and a second flow path layer that are adjacent to each other are provided, and heat is transferred between the first fluid that flows through the first flow path layer and the second fluid that flows through the second flow path layer. A heat exchanger,
The first flow path layer includes
An inflow tank portion provided with an inflow port through which the first fluid flows;
An outflow tank part provided with an outflow port through which the first fluid flows out;
An intermediate portion that is provided between the inflow tank portion and the outflow tank portion, and circulates the first fluid from the inflow tank portion to the outflow tank portion,
A plurality of first heat exchange fins extending along the inflow direction of the first fluid in the inflow tank portion, and a plurality of second heat exchange fins extending along the outflow direction of the first fluid in the outflow tank portion. A plurality of heat exchange fins that are at least one;
A plurality of third heat exchange fins extending along a direction intersecting the plurality of heat exchange fins in the intermediate portion;
The plurality of heat exchange fins are juxtaposed along the extending direction of the plurality of third heat exchange fins, and the first fluid can flow between a pair of adjacent channels among the plurality of channels to be formed. Have a shape,
Each end portion in the extending direction of the plurality of third heat exchange fins is not joined to each of the plurality of heat exchange fins, and is opposed to a flat portion which is a side surface of the heat exchange fin. Spaced apart from the heat exchange fins ;
The plurality of heat exchange fins connect the inner wall of the inflow tank portion facing the inflow port and the inflow port, or connect the inner wall of the outflow tank portion facing the outflow port and the outflow port. A heat exchanger extending in a direction orthogonal to the extending direction of the plurality of third heat exchange fins so as to tie .   The plurality of heat exchange fins include the first heat exchange fins extending substantially over the entire inflow direction on the intermediate portion side of the inflow tank portion, and the channel formed by the first heat exchange fins and the The heat exchanger according to claim 1, wherein the heat exchanger has a shape allowing the first fluid to flow between the intermediate portion.   The plurality of heat exchange fins include the second heat exchange fins extending substantially over the entire outflow direction on the intermediate side of the outflow tank portion, and the channel formed by the second heat exchange fins and the The heat exchanger according to claim 1 or 2, wherein the first fluid has a shape that allows the first fluid to flow between the intermediate portion. The second flow path layer includes a facing portion adjacent to the intermediate portion of the first flow path layer,
The heat according to any one of claims 1 to 3, wherein the facing portion causes the second fluid to flow in a direction opposite to a flow direction of the first fluid in the intermediate portion of the first flow path layer. Exchanger.   The heat exchanger according to any one of claims 1 to 4, wherein the plurality of heat exchange fins are louver fins or offset fins. A waste heat recovery device that includes a Rankine cycle device in which a working fluid is circulated and recovers waste heat from a high-temperature heat source,
The Rankine cycle device has the heat exchanger according to any one of claims 1 to 5 as an evaporator for evaporating the working fluid,
The waste heat recovery apparatus, wherein the heat exchanger causes the working fluid to evaporate by transferring heat from the high-temperature heat source as the second fluid to the working fluid as the first fluid.

Images