JP2006105464A - Heat exchanger and heat exchange device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a heat exchanger and a heat exchange device having good heat exchange efficiency between a gas and a coolant.
SOLUTION: The heat exchanger 50 passes through a cylindrical shell 52 that houses a plurality of exhaust gas pipes 54 through which gas passes, so that the gas passes through the pipe wall of each exhaust gas pipe 54. And the cooling water exchange heat. The cooling water inlet pipe 64 for introducing the cooling water into the shell 52 is provided through the cylindrical wall on one end side in the axial direction of the shell 52, and the cooling water outlet pipe for cooling to lead out the cooling water from the shell 52. 66 is provided through the cylindrical wall on the other axial end side of the shell 52. Each exhaust gas pipe 54 is arranged in parallel to the axial direction of the shell 52, and is formed on the inner peripheral surface of the shell 52 in a spiral shape from the cooling water inlet pipe 64 to the cooling water outlet pipe 66. A spiral groove 52B is provided.
[Selection] Figure 1

Description

  The present invention relates to a heat exchanger that performs heat exchange between an exhaust gas of an automobile or the like and a coolant, and a heat exchange device including the heat exchanger.

Some vehicles such as automobiles have heat exchange for exchanging heat between the exhaust gas and cooling water in order to recover the heat of the exhaust gas of the engine (see, for example, Patent Document 1). Moreover, although it is not used for automobiles, a heat exchanger for recovering heat from exhaust gas is known in which a spiral water pipe that passes cooling water along an annular flue formed in a container is arranged (for example, , See Patent Document 2).
Japanese Utility Model Publication No. 5-56514 JP 2002-115802 A Japanese Patent Laid-Open No. 2000-240445

  However, the conventional heat exchanger such as the former has room for improvement in the exhaust heat recovery efficiency for recovering heat from the exhaust gas. Moreover, in the latter heat exchanger, in order to improve heat exchange efficiency, it was necessary to provide a spiral water tube.

  In view of the above fact, an object of the present invention is to obtain a heat exchanger and a heat exchange device with good heat exchange efficiency between a gas and a coolant.

  In the heat exchanger according to the first aspect of the present invention, the cooling liquid passes through a cylindrical container containing a plurality of gas pipes through which the gas passes, so that the gas and the cooling are passed through the pipe wall of the gas pipe. A heat exchanger for exchanging heat with the liquid, provided at one end in the axial direction of the cylindrical wall of the cylindrical container, and a cooling liquid inlet for introducing the cooling liquid into the cylindrical container; and the cylindrical container A cooling liquid outlet that is provided on the other end side in the axial direction of the cylindrical wall and that extracts the cooling liquid from the cylindrical container, and the gas pipes are arranged in parallel to the axial direction of the cylindrical container, and A spiral guide portion formed in a spiral shape from the coolant inlet to the coolant outlet is provided on the inner peripheral surface of the cylindrical container.

  In the heat exchanger according to claim 1, the gas passes through the plurality of gas pipes, and the coolant passes through the cylindrical container containing the gas pipes so that the gas passes through the pipe wall of the gas pipe. Heat exchange with the coolant. The cooling liquid is introduced into the cylindrical container through a cooling liquid inlet penetrating the cylindrical wall of the cylindrical container, passes through the cylindrical container from one end side to the other end side in the axial direction, and penetrates the cylindrical wall of the cylindrical container. To the outside of the heat exchanger from the cylindrical container through the coolant outlet.

  Here, since the spiral guide portion is provided on the inner peripheral surface of the cylindrical container, the cooling liquid introduced and led out through the cylindrical wall of the cylindrical container as described above passes through the cylindrical container along the spiral groove. It flows spirally from one end side to the other end side. That is, a strong swirling flow of the coolant is generated by the spiral guide portion and the coolant inlet and outlet. As a result, the contact time (area) between the coolant and the gas pipe is increased, and the heat exchange efficiency is improved as compared with a configuration in which the coolant simply passes straight from one end side to the other end side (with the shortest distance). improves. Further, since the swirl flow prevents the stagnation of the coolant, the amount of the coolant that performs heat exchange does not decrease, and this also improves the heat exchange efficiency between the coolant and the gas.

  Thus, in the heat exchanger according to claim 1, the heat exchange efficiency between the gas and the coolant is good. The cooling liquid may be one that cools the gas or may be one that is cooled by the gas. In order to promote the swirl flow, one or both of the coolant inlet and the outlet can be arranged or formed such that the coolant is introduced or led out along the tangential direction of the spiral guide portion. Further, if the spiral guide part is provided integrally with the cylindrical container and on the outer peripheral surface (the cylindrical wall itself of the cylindrical container is spirally provided to provide the spiral guide part), the cylindrical container is Since the rigidity of the gas pipe is reduced due to the reduced rigidity, the thermal stress can be reduced by absorbing the difference in thermal expansion from each gas pipe.

  In the heat exchanger according to the second aspect of the present invention, the cooling liquid passes through a cylindrical container containing a plurality of gas pipes through which the gas passes, so that the gas and the cooling are passed through the pipe wall of the gas pipe. A heat exchanger for exchanging heat with the liquid, wherein each of the gas pipes is arranged in parallel to the axial direction of the cylindrical container, and the length of some of the plurality of gas pipes is , Different from the length of other gas pipes.

  In the heat exchanger according to claim 2, the gas passes through the plurality of gas pipes, and the coolant passes through the cylindrical container containing the gas pipes, so that the gas passes through the tube wall of the gas pipe. Heat exchange with the coolant. Here, since the lengths of all or some of the gas pipes are made different from each other, the gas flow rates passing through the respective gas pipes can be made different. For this reason, it becomes possible to implement | achieve the structure which increases the gas flow rate of the gas pipe arrange | positioned in the site | part with much coolant flow rate in a cylindrical container. In this configuration, heat exchange between the gas in each gas pipe and the coolant is performed substantially uniformly, and the heat exchange efficiency is improved.

  Thus, in the heat exchanger according to claim 2, the heat exchange efficiency between the gas and the coolant is good. The cooling liquid may be one that cools the gas or may be one that is cooled by the gas.

  A heat exchanger according to a third aspect of the present invention is the heat exchanger according to the second aspect, wherein the length of the gas pipe positioned on the axial center side of the cylindrical container is set to the inner peripheral surface side of the cylindrical container. It was longer than the length of the gas pipe located at.

  In the heat exchanger according to the third aspect, for example, a gas flow having a high flow velocity is branched into the plurality of gas pipes at the central portion of the flow path before being branched into the plurality of gas pipes. Here, since the gas pipe on the axial center side (central part) of the cylindrical container is configured to be longer than the gas pipe in the peripheral part, the gas flow rate in the gas pipe in the peripheral part can be relatively increased. Thereby, the flow volume of each gas pipe can be approached uniformly. For example, if the cylindrical container having the spiral groove on the inner periphery and the coolant inlet and outlet are provided on the coolant side, the coolant becomes a swirl flow as described above, In addition, since the flow rate of the coolant around the cylindrical container increases, it is effective to increase the gas flow rate by making the gas pipe disposed in the peripheral part shorter than the gas pipe at the center.

  For example, the surface on the gas inlet header side of the partition wall that divides the coolant flow path through which the coolant in the cylindrical container passes and the gas inlet header in which the gas inlets of the plurality of gas pipes respectively open are provided on the gas inlet header side. By curving so as to be convex, it is possible to realize a configuration in which the gas pipe on the cylindrical container axis side is longer than the gas pipe in the peripheral portion.

  According to a fourth aspect of the present invention, there is provided a heat exchanger comprising: a cooling liquid passing through a cylindrical container containing a plurality of gas pipes through which gas passes; A heat exchanger for exchanging heat with the liquid, wherein a first liquid partitioning a coolant flow path through which the coolant in the cylindrical container passes and a gas inlet header in which gas inlets of the plurality of gas pipes respectively open. A partition wall, a second partition wall partitioning the coolant flow path in the cylindrical container, a gas outlet header in which gas outlets of the plurality of gas pipes respectively open, and a second wall wall of the cylindrical container. Provided on the partition wall side, for introducing a coolant into the coolant channel, and provided on the first partition side of the cylindrical wall of the cylindrical container, and the coolant is led out from the coolant channel. A coolant outlet, and each gas pipe is provided in front of Arranged parallel to the axial direction of the cylindrical container, and said first surface of said gas inlet header side of the partition wall is formed in a convex curved surface to the gas inlet header side.

  In the heat exchanger according to claim 4, the gas passes through the plurality of gas pipes, and the cooling liquid passes through the cylindrical container containing the gas pipes, so that the gas passes through the pipe wall of the gas pipe. Heat exchange with the coolant. The cooling liquid is introduced into the cylindrical container through a cooling liquid inlet penetrating the cylindrical wall of the cylindrical container, passes through the cylindrical container from one end side to the other end side in the axial direction, and penetrates the cylindrical wall of the cylindrical container. To the outside of the heat exchanger from the cylindrical container through the coolant outlet.

  Here, the second partition wall formed in a curved shape convex to the coolant flow path side (concave to the gas outlet header side) is positioned so as to overlap the coolant inlet in the axial direction of the cylindrical container. The coolant introduced from the liquid inlet is guided by the second partition (flows around the second partition) to generate a swirling flow. As a result, the stagnation of the coolant is prevented on the coolant inlet side in the coolant channel in the cylindrical container, and the heat exchange efficiency between the coolant and the gas is improved. In addition, the contact time (area) between the coolant and the gas pipe is increased, and the heat exchange efficiency is improved, compared to a configuration in which the coolant simply passes from one end to the other in a straight line (with the shortest distance). To do.

  Thus, in the heat exchanger according to claim 4, the heat exchange efficiency between the gas and the coolant is good. The cooling liquid may be one that cools the gas or may be one that is cooled by the gas. Moreover, in order to accelerate | stimulate a swirl | vortex flow, a cooling fluid inlet can be arrange | positioned or formed so that a cooling fluid may be introduce | transduced along the tangential direction of a 2nd partition, for example. Further, the surface shape of the first partition wall on the gas inlet header side is a curved surface that is convex toward the gas inlet header side, or the gas outlet header side surface of the second partition wall is a concave curved surface on the gas outlet header side. By doing so, it becomes possible to make the length of each gas pipe different, or to make it the same length.

  A heat exchanger according to a fifth aspect of the present invention is the heat exchanger according to the fourth aspect, wherein the spiral formed on the inner peripheral surface of the cylindrical container in a spiral shape from the coolant inlet to the coolant outlet. A guide part was provided.

  In the heat exchanger according to claim 5, since the spiral groove is provided on the inner peripheral surface of the cylindrical container, the swirling flow of the cooling liquid generated by being guided by the second partition wall as described above reaches the cooling liquid outlet side. Maintained. In other words, the coolant flows spirally along the spiral groove from the second partition side to the first partition side. Thereby, the contact time (area) between the coolant and the gas pipe is further increased, and the heat exchange efficiency is further improved.

  A heat exchanger according to a sixth aspect of the present invention is the heat exchanger according to any one of the first to fifth aspects, wherein each gas is provided at each gas inlet side end of the plurality of gas pipes. A guide part for guiding gas into the tube was formed.

  In the heat exchanger according to the sixth aspect, the guide portion provided at the gas inlet side end of each gas pipe draws the gas into each gas pipe. For this reason, the gas inflow resistance to each gas pipe is reduced and the introduction efficiency is improved. That is, the pressure loss of the gas due to the heat exchanger is reduced and the gas flow rate is increased, and the heat exchange efficiency between the gas and the coolant is improved. In addition, as a guide part, the flare shape etc. which expanded the gas inlet side edge part of each gas pipe in the taper shape etc. are employable, for example.

  A heat exchange device according to a seventh aspect of the present invention is provided coaxially with the heat exchanger according to any one of the first to sixth aspects and the cylindrical container or the cylindrical container, and the heat exchange device. A gas introduction pipe for introducing gas into a gas inlet of the gas generator; and a gas supply pipe for introducing gas while changing a flow direction in the gas introduction pipe, and the gas introduction pipe is provided on an inner peripheral surface of the gas introduction pipe. A spiral guide portion formed in a spiral shape from the supply pipe toward the heat exchanger was provided.

  In the heat exchange device according to the seventh aspect, the gas is introduced into the heat exchanger through the gas supply pipe and the gas introduction pipe in this order. In the heat exchanger into which the gas is introduced, the gas passes through the plurality of gas pipes, and the cooling liquid passes through the cylindrical container containing the gas pipes, so that the gas passes through the pipe wall of the gas pipe. Heat exchange with the coolant.

  Here, since the spiral groove is provided on the inner peripheral surface of the gas introduction pipe into which the gas flows from the gas supply pipe while changing the flow direction (for example, while bending approximately 90 °), the heat exchanger (gas inlet header or the like) ) Produces a swirl flow. For this reason, in the state before the gas is branched into each gas pipe, the flow velocity of each part in the radial direction of the cylindrical container or the cylindrical container is equalized (considering only the axial direction component of the gas introduction pipe, Close). For this reason, the flow rates of the plurality of gas pipes are made uniform, and the heat exchange efficiency is improved.

  Thus, in the heat exchange device according to the seventh aspect, the heat exchange efficiency between the gas and the coolant is good.

  The heat exchange apparatus according to an eighth aspect of the present invention is the heat exchange apparatus according to the seventh aspect, wherein the gas supply pipe is a branch pipe branched from a main gas pipe, and the gas introduction pipe has a spiral pipe wall. The spiral guide portion is integrally formed on the inner peripheral surface.

  In the heat exchange device according to the eighth aspect, the gas is introduced into the heat exchanger from the gas supply pipe, which is a branch organ branched from the main gas pipe, via the gas introduction pipe. Since the gas inlet pipe is formed in a spiral shape and the spiral guide portion is integrally formed, the gas introduction pipe is less rigid than the cylindrical pipe or the like and easily deforms. For this reason, even if the gas introduction pipe has a temperature difference with the main gas pipe due to, for example, switching of the gas flow with the main gas pipe, the thermal expansion difference based on the temperature difference is deformed by itself. Can be absorbed.

  As described above, the heat exchanger according to the present invention has an excellent effect that heat exchange efficiency from gas is good.

  An automobile exhaust heat recovery system 10 to which a heat exchanger and a heat exchange device according to a first embodiment of the present invention are applied will be described with reference to FIGS. 1 to 6. First, the schematic overall configuration of the exhaust heat recovery system 10 will be described, and then the exhaust heat recovery heat exchanger 50 as a heat exchanger, which is a main part of the present invention, and the periphery of the exhaust heat recovery heat exchanger 50 are included. The heat exchange device will be described.

  FIG. 5 schematically shows the overall configuration of the exhaust heat recovery system 10. As shown in this figure, an exhaust heat recovery system 10 is a device that recovers heat of exhaust gas of an internal combustion engine 12 of an automobile and uses it for heating, warming promotion of the engine 12, or the like.

  An exhaust pipe 14 for leading exhaust gas is connected to the engine 12. A catalyst system 16 and a main muffler 18 are arranged in this order from the upstream side on the exhaust gas discharge path by the exhaust pipe 14. The catalyst system 16 is disposed under the floor of an automobile and is configured to purify exhaust gas that passes through the catalyst accommodated therein. The main muffler 18 is configured to reduce exhaust noise that is generated when exhaust gas is released into the atmosphere outside the automobile.

  A branch pipe 20 as a gas supply pipe and a gas introduction pipe is branched from the catalyst system 16 and the main muffler 18 in the exhaust pipe 14. The branch pipe 20 forms a path for introducing the exhaust gas to the exhaust heat recovery heat exchanger 50 described in detail later. The exhaust gas that has passed through the heat exchanger 50 for exhaust heat recovery passes through the junction pipe 22, and is exhausted between the catalyst system 16 and the main muffler 18 in the exhaust pipe 14 and from the branch portion of the branch pipe 20. It joins the downstream part in the flow direction.

  Further, a flow path switching valve 26 for switching the flow of the exhaust gas is disposed between the branch portion of the branch pipe 20 in the exhaust pipe 14 and the junction portion of the junction pipe 22. The flow path switching valve 26 is in a fully open state in which exhaust gas mainly passes through the exhaust pipe 14 (the exhaust gas hardly flows into the exhaust heat recovery heat exchanger 50 having a large pressure loss compared to the exhaust pipe 14). The fully closed state in which all exhaust gas is introduced into the exhaust heat recovery heat exchanger 50 can be switched to selection. A vacuum path 28 connected to the intake side of the engine 12 is connected to the flow path switching valve 26. In the vacuum path 28, an actuator (negative pressure diaphragm) 30, a vacuum switching valve (VSV) 32, and a vacuum tank 34 are disposed.

  The vacuum switching valve 32 is electrically connected to an engine ECU (not shown) so that its operation is controlled. Specifically, the vacuum switching valve 32 is operated based on an exhaust heat recovery command from the engine ECU to operate the actuator 30. Thereby, the open / closed state of the flow path switching valve 26 is switched by the negative pressure acting.

  The exhaust heat recovery heat exchanger 50 performs heat exchange between the exhaust gas and the engine cooling water, and recovers the heat of the exhaust gas into the engine cooling water. The exhaust heat recovery system 10 includes a front heater core 36 and a rear heater core 38 that recover the heat of the engine coolant for heating, and a heater hot water passage 40 that circulates the engine coolant to the front heater core 36 and the rear heater core 38. The front heater core 36 and the rear heater core 38 are arranged in parallel. An exhaust heat recovery heat exchanger 50 is disposed downstream of the rear heater core 38 in the heater hot water passage 40. In this embodiment, the exhaust heat recovery heat exchanger 50 is arranged in parallel to the front heater core 36 and in series to the rear heater core 38.

  Therefore, in the exhaust heat recovery system 10, the engine cooling water flows as indicated by the arrows on the heater hot water passage 40 in FIG. That is, when hot hot water that has passed through the engine 16 passes through the front heater core 36 and the rear heater core 38, heat is exchanged and used for heating, and engine cooling water that has been cooled at the rear heater core 38 is used as an exhaust heat recovery heat exchanger. 50, the exhaust gas is cooled by exchanging heat with the exhaust gas. The engine coolant passing through the exhaust heat recovery heat exchanger 50 is returned to the engine 12 together with the engine coolant passing through the front heater core 36. Thus, the exhaust heat recovery heat exchanger 50 is configured to function as a preheater that preheats the engine coolant before being heated by the engine 12 from the viewpoint of the heating function, for example.

  Further, as shown in FIG. 6A, a condensate water reservoir 42 between the catalyst system 16 and the main muffler 18 in the exhaust pipe 14 is lower than the other parts. The lowermost portion 44A of the downstream horizontal portion 44 on the main muffler 18 side with respect to the condensed water reservoir 42 in the exhaust pipe 14 is set to a higher position between the lowermost portion 42A and the uppermost portion 42B of the condensed water reservoir 42, and the condensed water The lowermost portion 46 </ b> A of the upstream horizontal portion 46 on the catalyst system 16 side is higher than the lowermost portion 44 </ b> A of the downstream horizontal portion 44 with respect to the reservoir portion 42. Thereby, the highest level of the condensed water accumulated in the condensed water reservoir 42 becomes the lowermost portion 44A of the downstream horizontal portion 44, and a clearance C is secured between the uppermost portion 42B of the condensed water reservoir 42 and the condensed water. This prevents the exhaust pipe 14 from being blocked.

  As a result, troubles in the engine 12 due to blockage of the exhaust pipe 14 (particularly pipeline blockage due to freezing) are prevented. Further, in the exhaust heat recovery system 10, the condensed water is prevented from flowing to the catalyst system 16 side, and the condensed water can be blown downstream of the main muffler 18, that is, into the atmosphere by the exhaust pulsation behind the main muffler 18. It is configured. This prevents the high temperature catalyst from coming into contact with the low temperature condensed water and cracking by heat shock. As shown in FIG. 6B, a drain pipe 48 that discharges the condensed water in the condensed water reservoir 42 by the negative pressure of the main muffler 18 may be provided.

(Configuration of heat exchanger for exhaust heat recovery)
FIG. 2 is a cross-sectional view along the axial direction schematically showing the overall configuration of the exhaust heat recovery heat exchanger 50. The direction of arrow A shown in this figure indicates the macro flow direction of the exhaust gas. In the following description, the side indicated by arrow A is the gas downstream side, and the side opposite to arrow A is the gas upstream side. To do. The same applies to the case where the arrow A is shown in other drawings.

  As shown in FIG. 2, the exhaust heat recovery heat exchanger 50 includes a cylindrical container or a shell 52 as a cylindrical container. The shell 52 is formed in a cylindrical shape having openings at both ends (both gas upstream and downstream). An exhaust gas pipe 54 as a plurality of gas pipes is inserted in the shell 52. Each of the plurality of exhaust gas pipes 54 is fixed to the first partition member 56 through the first partition member 56 at the upstream end of each gas. Further, the plurality of exhaust gas pipes 54 are fixed to the second partition wall member 58 through the second partition wall member 58 at their respective downstream end portions. In this state, the exhaust gas pipes 54 are held parallel to each other.

  The first partition member 56 is fitted in the vicinity of the gas upstream end of the shell 52 in a watertight and airtight state (watertight or airtight for an allowable pressure, the same applies hereinafter), and the second partition member 58 is gas downstream of the shell 52. The end is fitted in a watertight and airtight state. Thereby, each exhaust gas pipe 54 is arranged along the longitudinal direction of the shell 52 (parallel to the axial direction of the shell 52). A space between the first partition member 56 and the second partition member in the shell 52 is a cooling water flow path 52A through which engine cooling water flows. The first partition member 56 and the second partition member 58 fixed to the shell 52 correspond to the first partition and the second partition in the present invention.

  A gas inlet header member 60 is fixed to the gas upstream end of the shell 52. The gas inlet header member 60 is formed in a substantially tapered cylindrical shape (conical shape), and the end portion on the gas downstream side, which is the large diameter side, is watertight to the gas upstream end of the shell 52, that is, the fixed side of the first partition wall member 56. And it is fixed in an airtight state. On the other hand, a gas outlet header member 62 is fixed to the downstream end of the shell 52. The gas outlet header member 62 is formed in a substantially tapered cylindrical shape (conical shape), and the end portion on the gas upstream side, which is the large diameter side, is water-tight and the downstream end of the shell 52, that is, the fixed side of the second partition wall member 58. It is fixed in an airtight state. Thereby, the gas inlet header 60A is formed at the gas upstream end of the exhaust heat recovery heat exchanger 50, and the gas outlet header 62A is formed at the gas downstream end of the exhaust heat recovery heat exchanger 50. The gas inlet header 60A and the gas outlet header 62A communicate with each other through the exhaust gas pipes 54.

  Further, the gas upstream side (small diameter side) opening end of the gas inlet header member 60 is connected to the downstream end of the branch pipe 20, and the gas downstream side (small diameter side) opening end of the gas outlet header member 62 is connected to the joining pipe 22. Connected to the upstream end. As a result, exhaust gas is introduced from the exhaust pipe 14 via the branch pipe 20 to the gas side of the exhaust heat recovery heat exchanger 50, and the exhaust gas that has passed through each exhaust gas pipe 54 is discharged to the junction pipe 22. It is supposed to be configured.

  On the other hand, a cooling water inlet pipe 64 for introducing cooling water into the cooling water flow path 52A is attached to the outer periphery of the shell 52 near the gas downstream end, and the outer periphery of the shell 52 near the gas upstream end is attached to the outer periphery of the shell 52. A cooling water outlet pipe 66 for discharging the cooling water from the cooling water flow path 52 </ b> A to the outside of the apparatus is attached through the cylindrical wall of the shell 52. By connecting the cooling water inlet pipe 64 and the cooling water outlet pipe 66 to the heater hot water passage 40, the exhaust heat recovery heat exchanger 50 is configured so that the rear heater core with respect to the flow of engine cooling water as described above. 38 is arranged in series downstream of 38.

  As described above, the exhaust heat recovery heat exchanger 50 is introduced from the gas upstream side of the shell 52 and discharged to the gas downstream side, and is introduced from the gas downstream side of the shell 52 and discharged from the gas upstream side. It is a multi-tube (shell and tube type) countercurrent heat exchanger that exchanges heat with the engine coolant.

  1, the shell 52 of the exhaust heat recovery heat exchanger 50 has a spiral groove 52B as a spiral guide portion formed on the inner peripheral surface thereof. . The spiral groove 52 </ b> B is formed integrally with the shell 52 by forming the cylindrical wall itself of the shell 52 to be uneven along a single spiral (in a spiral shape). For this reason, the shell 52 has a spiral groove 52C formed on the outer peripheral surface thereof, and the thickness of the shell wall is substantially constant in each part. In addition, in the notch part of the shell 52 in FIG. 1, the exhaust gas pipe 54 is shown with the imaginary line.

  Further, as shown in the schematic diagram of FIG. 3, the cooling water inlet pipe 64 and the cooling water outlet pipe 66 have respective one open ends entering the shell 52. The opening end of the cooling water inlet pipe 64 that introduces engine cooling water substantially along the radial direction of the shell 52 and cut into the shell 52 is cut so as to be inclined with respect to the axial direction, so that the opening surface 64 </ b> A is formed on the shell 52. Both the axial center and the circumferential direction are directed. As a result, the engine coolant introduced into the shell 52 from the coolant inlet pipe 64 and colliding with the plurality of exhaust gas pipes 54 is guided in the circumferential direction of the shell 52 and flows following the spiral groove 52B ( Swirl flow) is generated.

  On the other hand, the cooling water outlet pipe 66 for leading the engine cooling water substantially along the radial direction of the shell 52 enters the shell 52 in a direction for receiving (receiving) the engine cooling water flowing along the spiral groove 52B. The opening surface 64A at the open end is directed. The opening surface 64 </ b> A is formed by cutting the opening end portion of the cooling water outlet pipe 66 entering the shell 52 so as to be inclined with respect to the axial direction.

  As described above, in the heat exchanger 50 for exhaust heat recovery, the engine coolant introduced into the shell 52 from the coolant inlet pipe 64 generates a swirling flow that flows along the spiral groove 52B, and is discharged from the coolant outlet pipe 66. It has become so.

  Further, as shown in FIG. 2, in the heat exchanger 50 for exhaust heat recovery, the surface facing the gas inlet header 60A of the first partition member 56 is formed as a convex curved surface on the gas inlet header 60A side. The curved surface 56A is used. The convex curved surface 56A is a spherical surface in this embodiment. A surface of the first partition member 56 facing the cooling water flow path 52 </ b> A is a substantially flat surface along a plane orthogonal to the axis of the shell 52. On the other hand, the second partition wall member 58 is formed in a substantially disk shape, and both the surface facing the gas outlet header 62A and the surface facing the cooling water flow path 52A are substantially flat surfaces along a plane orthogonal to the axis of the shell 52. ing.

  As a result, the exhaust heat recovery heat exchanger 50 is longer in the exhaust gas pipe 54 nearer to the axial center of the shell 52 among the many exhaust gas pipes 54 and closer to the inner peripheral surface (spiral groove 52B) of the shell 52. The gas pipe 54 has a shorter configuration. For this reason, the exhaust gas introduced from the branch pipe 20 into the gas inlet header 60A has a peripheral portion of the shell 52 as compared with the configuration in which the first partition member 56 is formed in a disk shape similar to the second partition member 58. In the exhaust gas pipe 54 (the difference in the exhaust gas flow rate between the exhaust gas pipe 54 on the axial center side and the exhaust gas pipe 54 in the peripheral portion is reduced).

  As shown in part in FIG. 2, each exhaust gas pipe 54 has a spiral outer peripheral surface, and has a configuration in which the contact area with the cooling water is increased. Instead of forming the outer peripheral surface in a spiral shape, a heat transfer fin or the like may be attached. Further, as shown in FIG. 2, a flare portion 54A as a guide portion for guiding the exhaust gas is formed at each gas inlet side opening end opened in the gas inlet header 60A of each exhaust gas pipe 54. As shown in FIG. 4, in order to effectively draw the exhaust gas into each exhaust gas pipe 54 opened substantially along the convex curved surface 56 </ b> A of the first partition wall member 56 formed in a substantially spherical shape as described above, as shown in FIG. The flare portion 54A of the exhaust gas pipe 54 located on the axial center side of the exhaust gas pipe 54 is formed in an axially symmetrical taper shape, and the flare portion 54A of the exhaust gas pipe 54 disposed in the peripheral portion of the shell 52 is a radially outer portion of the shell 52. Is extended to the upstream side of the gas so that the exhaust gas is surely drawn in.

  Further, as shown in FIG. 1, the branch pipe 20 for leading the exhaust gas from the exhaust pipe 14 to the exhaust heat recovery heat exchanger 50 includes a gas branch pipe 68 as a gas supply pipe branched from the exhaust pipe 14 and a gas branch. The gas inlet pipe 70 is positioned between the pipe 68 and the exhaust heat recovery heat exchanger 50 and extends along the axial direction of the exhaust heat recovery heat exchanger 50 (shell 52). The axial direction of the gas branch pipe 68 is a direction that intersects with the axial direction of the gas introduction pipe 70 (exhaust heat recovery heat exchanger 50). In this embodiment, the axis of the gas branch pipe 68 and the gas introduction pipe The angle formed by the 70 axis is a substantially right angle.

  The gas introduction pipe 70 is formed with a spiral groove 70A as a spiral guide portion on the inner peripheral surface thereof. Accordingly, the exhaust gas flowing into the gas introduction pipe 70 while changing the flow direction at the corner portion 68A between the gas branch pipe 68 and the gas introduction pipe (the flow rate is large on the large diameter side in the corner portion 68A) It is guided by 70 spiral grooves 70A to generate a swirling flow. For this reason, the exhaust gas passing through the gas introduction pipe 70 in the macro direction (considering only the component in the axial direction) has a uniform flow velocity (flow rate) distribution in each radial part of the gas introduction pipe 70. It has become so. Further, since the exhaust gas is introduced into the tapered gas inlet header 60A of the exhaust heat recovery heat exchanger 50 and the flow is expanded, the flow velocity distribution is more uniform in the gas inlet header 60A. It is the composition which is done. In addition, the gas introduction pipe 70 has a spiral pipe wall itself, and a spiral groove 70B is formed on the outer peripheral surface with the groove bottom between the groove bottoms of the spiral groove 70A. That is, the gas introduction pipe 70 is constituted by a spiral pipe having a substantially constant wall thickness at each part of the pipe wall.

  Of the branch pipes 20 constituting the heat exchange device in the present invention together with the exhaust heat recovery heat exchanger 50, the gas introduction pipe 70 is a component on the exhaust heat recovery heat exchanger 50 (heat exchanger in the present invention) side. Needless to say, it is possible to grasp as.

  In the exhaust heat recovery heat exchanger 50 described above, the engine cooling water such as the shell 52, the exhaust gas pipes 54, the first and second partition members 56, 58, the cooling water inlet pipe 64, and the cooling water outlet pipe 66 are provided. The material of the parts and parts that come into contact with the heater is made of austenitic stainless steel together with the material of the heater hot water channel 40. These parts / parts have low stress (98MPa or less) due to vibration and road surface input caused by vehicle running, low temperature (65 ° C or less), stress corrosion cracking and thermal stress load peculiar to austenitic stainless steel. Therefore, austenitic stainless steel with good corrosion resistance at low temperatures is used. On the other hand, the parts such as the gas inlet header member 60, the gas outlet header member 62, the branch pipe 20 (the gas branch pipe 68 and the gas introduction pipe 70) which are in contact with the exhaust gas without touching the engine coolant are made of the exhaust pipe 14. In addition to the above materials, a ferritic stainless steel that does not cause a problem peculiar to the above-described austenitic stainless steel, that is, has good corrosion resistance at high temperatures is employed. Thereby, the durability reliability of the exhaust system including the exhaust heat recovery system 10 is ensured.

  For example, when the use temperature or design temperature of the heat exchanger 50 for exhaust heat recovery becomes high or the design stress becomes high, the parts / parts made of austenitic stainless steel are coated. . As for painting, both normal painting and electrodeposition painting (cationic painting) are applied. These coatings contribute to the prevention of salt corrosion due to the adhesion of chlorine, particularly in the salt spray area. Furthermore, when the environment of use of the vehicle is particularly severe, stress as a post-weld heat treatment is applied to a welded portion of austenitic stainless steel and ferritic stainless steel (welded portion of the shell 52, the inlet header member 60, and the outlet header member 62). Removal annealing is performed to relieve the initial stress (residual stress) of the welded part and the heat affected zone. Thereby, the sensitization of the structure | tissue accompanying the welding (thermal influence) peculiar to austenitic stainless steel is prevented.

  As shown in FIG. 6 (A) or 6 (B), the heat exchanger 50 for exhaust heat recovery has a lowest part 50A of the lowermost part 44A of the downstream horizontal part 44 of the exhaust pipe 14, that is, a condensed water reservoir. It is arranged so as to be higher than the highest level of condensed water accumulated in 42. This prevents the condensed water from being introduced into the exhaust heat recovery heat exchanger 50. This function is performed if the lowest part of the horizontal part of the branch pipe 20 and the junction pipe 22 is higher than the lowest part 44A. In this embodiment, the above arrangement is employed to improve the reliability. .

  Next, the operation of the first embodiment will be described.

  In the exhaust heat recovery system 10 having the above configuration, when the actuator 30 is operated based on an exhaust heat recovery command from the engine ECU, negative pressure acts on the vacuum path 28 to close the flow path switching valve 26 and close the exhaust pipe 14. To do. Then, the exhaust gas is introduced into the exhaust heat recovery heat exchanger 50 via the branch pipe 20, and the exhaust gas passes through the exhaust heat recovery heat exchanger 50 and passes through the junction pipe 22 to the exhaust pipe 14. Returning to step 2, the sound is silenced by the main muffler 18 and then discharged into the atmosphere. That is, a flow is formed in which the exhaust gas passes through each exhaust gas pipe 54 of the exhaust heat recovery heat exchanger 50.

  On the other hand, the engine cooling water circulates in the heater hot water passage 40 by the operation of the water pump. A flow of engine cooling water introduced from the cooling water inlet pipe 64 and led out from the cooling water outlet pipe 66 is formed in the cooling water flow path 52A of the exhaust heat recovery heat exchanger 50 arranged on the heater hot water path. Is done. This engine cooling water exchanges heat with the exhaust gas through the pipe wall on the spiral of each exhaust gas pipe 54, and recovers the heat of the exhaust gas. On the other hand, the temperature of the exhaust gas is lowered. Therefore, the exhaust heat recovery heat exchanger 50 functions as a sub-muffler that reduces exhaust gas exhaust noise and back pressure.

  Here, in the exhaust heat recovery heat exchanger 50, the spiral groove 52B is formed on the inner surface of the shell 52, and the engine coolant flows into the shell 52 from the direction perpendicular to the axial direction by the coolant inlet pipe 64. In the cooling water flow path 52A, a strong swirling flow of engine cooling water is generated following the spiral groove 52B. Thereby, compared with the configuration in which the engine coolant simply passes through the coolant flow path 52A from one end side to the other end side (with the shortest distance), the contact time between the engine coolant and each exhaust gas pipe 54 ( Area) and heat exchange efficiency is improved.

  Further, since the swirl flow prevents stagnation (stagnation) of engine cooling water in the cooling water flow path 52A, the amount of engine cooling water used for heat exchange does not decrease, that is, in the cooling water flow path 52A. Almost all engine cooling water is used for heat exchange with the exhaust gas, which also improves the heat exchange efficiency between the engine cooling water and the exhaust gas. Furthermore, since the cooling water outlet pipe 66 is formed with the opening surface 66A so as to receive the swirling flow, the flow resistance of the engine cooling water discharged in a direction substantially perpendicular to the axial direction of the shell 52 is small. In particular, since the opening surfaces 64A and 66A of the cooling water inlet pipe 64 and the cooling water outlet pipe 66 face the direction along the swirling flow formed by the spiral groove 52B, a strong swirling flow is formed while the flow resistance is reduced. Is done.

  Thus, in the heat exchanger 50 for exhaust heat recovery which concerns on 1st Embodiment, the heat exchange efficiency (heat recovery rate) of exhaust gas and engine cooling water is favorable. Further, the exhaust heat recovery heat exchanger 50 has a configuration in which the spiral groove 52C is also formed on the outer peripheral surface of the shell 52. Therefore, the exhaust heat recovery heat exchanger 50 has a lower rigidity and a bellows than the configuration formed in a simple cylindrical shape. It is easy to deform. For this reason, when high-temperature exhaust gas mainly flows through either the exhaust pipe 14 or the exhaust heat recovery heat exchanger 50, these exhaust gases are interposed between the exhaust pipe 14 and the exhaust heat recovery heat exchanger 50. The thermal expansion difference caused by the temperature difference can be absorbed by the expansion and contraction of the shell 52.

  Here, in the heat exchanger 50 for exhaust heat recovery, since the exhaust gas pipe 54 on the axial center side of the shell 52 is long and the peripheral exhaust gas pipe 54 is short, the flow resistance of the peripheral exhaust gas pipe 54 is low. Reduced. As a result, the exhaust gas flow rate in the peripheral exhaust gas tube 54, which has a lower exhaust gas flow rate than the exhaust gas tube 54 on the normal axial side, increases, and the difference in the exhaust gas flow rates in the exhaust gas tubes 54 decreases. That is, the exhaust gas flow rate of each exhaust gas pipe 54 is made uniform. As described above, the engine coolant that forms the swirl flow has a uniform flow when passing through the coolant flow path 52A (reduction of the flow rate difference in the macro flow direction between the axial center portion and the peripheral portion). In other words, since the exhaust gas and the engine cooling water are made uniform in flow rate (heat quantity) in the axial center portion and the peripheral portion, the exhaust heat recovery heat exchanger 50 cools the inside of the shell 52. Heat exchange is performed in a well-balanced manner in each part of the water flow path 52A. For this reason, in the heat exchanger 50 for exhaust heat recovery, the heat exchange efficiency between the exhaust gas and the engine coolant is greatly improved.

  In particular, the flare 54A is formed in each exhaust gas pipe 54, so that the exhaust gas flow rate is made more uniform and the flow resistance of the exhaust gas is reduced. The former can further improve the heat exchange efficiency, and can reduce the performance loss of the engine 12 by reducing the latter, that is, the back pressure.

  Further, since the spiral groove 70A is formed in the gas introduction pipe 70 for introducing the exhaust gas into the exhaust heat recovery heat exchanger 50, the exhaust gas before being introduced into the exhaust heat recovery heat exchanger 50 is formed. Since the swirl flow is applied and the swirl flow is expanded by the tapered gas inlet header 60A, the flow velocity distribution of the exhaust gas is made uniform. That is, since the flow velocity distribution is made uniform before flowing into each exhaust gas pipe 54, the flow rate of each exhaust gas pipe 54 is made more uniform. Thereby, the heat exchange efficiency is further improved, and the flow resistance of the exhaust gas is further reduced. Further, since the gas introduction pipe 70 is also configured to be easily deformed like a bellows, it contributes to the absorption of the thermal expansion difference between the exhaust pipe 14 and the branch side exhaust heat recovery heat exchanger 50 side.

(Other embodiments)
Next, another embodiment of the present invention will be described. Parts and portions that are basically the same as those of the first embodiment or the previous embodiment are denoted by the same reference numerals as those of the first embodiment or the previous embodiment, and are described or illustrated. May be omitted.

  FIG. 7 shows a schematic perspective view corresponding to FIG. 3 of the heat exchanger 72 for exhaust heat recovery according to the second embodiment. As shown in this figure, the exhaust heat recovery heat exchanger 72 includes a cooling water inlet pipe 74 and a cooling water outlet pipe 76 in place of the cooling water inlet pipe 64 and the cooling water outlet pipe 66. The cooling water inlet pipe 74 is arranged offset from the center line of the shell 52 in plan view so as to introduce engine cooling water into the cooling water flow path 52A from a direction substantially coinciding with the tangential direction of the spiral groove 52B. Yes. In this embodiment, the cooling water inlet pipe 74 is provided in parallel to the radial direction coinciding with the vertical direction of the shell 52, and its opening surface 74A is substantially the same as the inner surface of the shell 52 (the groove bottom of the spiral groove 52B). Match. That is, the cooling water inlet pipe 74 is configured not to protrude into the cooling water flow path 52A.

  The cooling water outlet pipe 76 is disposed offset from the center line of the shell 52 in plan view so as to discharge the engine cooling water in a direction substantially coinciding with the tangential direction of the spiral groove 52B. In this embodiment, the cooling water outlet pipe 76 is provided in parallel to the radial direction coinciding with the vertical direction of the shell 52, and its opening surface 76A is substantially the same as the inner surface of the shell 52 (the groove bottom of the spiral groove 52B). Match. That is, the cooling water outlet pipe 76 is configured not to protrude into the cooling water flow path 52A.

  The exhaust heat recovery heat exchanger 72 and the exhaust heat recovery system 10 including the exhaust heat recovery heat exchanger 72 and the exhaust heat recovery system 10 including the exhaust heat recovery system 10 described above are also used. The same effect can be obtained. Further, since the cooling water inlet pipe 74 and the cooling water outlet pipe 76 do not protrude into the shell 52, a large number of exhaust gas pipes 54 are accommodated (increase the heat exchange area) without forming a dead space in the shell 52. It becomes possible.

  FIG. 8 schematically shows an exhaust heat recovery heat exchanger 78 according to the third embodiment. As shown in this figure, the exhaust heat recovery heat exchanger 78 includes a cooling water inlet pipe 80 and a cooling water outlet pipe 82 instead of the cooling water inlet pipe 64 and the cooling water outlet pipe 66. In the cooling water inlet pipe 80 and the cooling water outlet pipe 82, the ends inserted into the respective shells 52 introduce engine cooling water along the tangential direction of the spiral groove 52B, or in the tangential direction of the spiral groove 52B. It is bent to discharge engine cooling water along. That is, the opening surfaces 80A and 82A of the cooling water inlet pipe 80 and the cooling water outlet pipe 82 face the direction along the circumferential direction of the cooling water flow path 52A. In this figure, the cooling water outlet pipe 82 is shifted from the cooling water inlet pipe 80 by 180 °. The exhaust heat recovery heat exchanger 78 and the exhaust heat recovery system 10 including the exhaust heat recovery heat exchanger 78 described above also provide the exhaust heat recovery heat exchanger 50 and the exhaust heat recovery system 10 including the exhaust heat recovery system 10 according to the first embodiment. The same effect can be obtained.

  FIG. 9 schematically shows an exhaust heat recovery heat exchanger 84 according to the fourth embodiment. As shown in this figure, the exhaust heat recovery heat exchanger 84 includes a cooling water inlet pipe 86 and a cooling water outlet pipe 88 in place of the cooling water inlet pipe 64 and the cooling water outlet pipe 66. The cooling water inlet pipe 86 and the cooling water outlet pipe 88 have opening surfaces 86 </ b> A and 88 </ b> A located in the respective shells 52 opened toward the axial center side of the shell 52. In this figure, the cooling water outlet pipe 88 is shifted from the cooling water inlet pipe 86 by 180 °. The exhaust heat recovery heat exchanger 84 and the exhaust heat recovery system 10 including the exhaust heat recovery heat exchanger 84 and the exhaust heat recovery system 10 including the exhaust heat recovery system described above are also used. The engine cooling water swirling flow is slightly weaker than the above, and the same effects can be obtained.

  FIG. 10 shows an exhaust heat recovery heat exchanger 90 according to the fifth embodiment in a cross-sectional view corresponding to FIG. As shown in this figure, the exhaust heat recovery heat exchanger 90 includes a second partition member 92 instead of the second partition member 58. The second partition wall member 92 has a convex curved surface 92A and a concave curved surface 92B on both sides of the gas so that it is concave with respect to the gas outlet header 62A and convex with respect to the cooling water passage 52A. In the second partition member 92, the curvature of the convex curved surface 92A coincides with the curvature of the convex curved surface 56A, and the thickness of each part (thickness along the radial direction of the convex curved surface 92A and the concave curved surface 92B) is substantially constant. Therefore, in this embodiment, the length of each exhaust gas pipe 54 is constant. The convex curved surface 56 </ b> A protrudes directly below the cooling water inlet pipe 64 (positions overlapping the cooling water inlet pipe 64 in the longitudinal direction of the shell 52), and the flow of the cooling water flowing from the cooling water inlet pipe 64. Are guided along the outer peripheral surface thereof. Accordingly, the convex curved surface 56A is configured to function as a guide that imparts a swirling flow to the engine coolant that has flowed into the coolant flow path 52A.

  The exhaust heat recovery heat exchanger 90 and the exhaust heat recovery system 10 including the exhaust heat recovery system 90 described above also eliminate the effect of the length of the exhaust gas pipe 54 being different between the axial portion of the shell 52 and the peripheral portion. The same effects as those of the heat exchanger 50 for exhaust heat recovery according to the first embodiment and the exhaust heat recovery system 10 including the same can be obtained. In particular, since the convex curved surface 92A of the second partition member 92 promotes the generation of the swirling flow, a stronger swirling flow can be obtained. Note that the length of each exhaust gas pipe 54 is the same as that of the heat exchanger 50 for exhaust heat recovery according to the first embodiment by making the concave curved surface 92B a flat surface along a plane orthogonal to the axis of the shell 52. It is also possible to make them different so that they are longer on the axis side of the shell 52 than on the peripheral side.

  FIG. 11 shows a heat exchanger 94 for exhaust heat recovery according to the sixth embodiment in a cross-sectional view corresponding to FIG. As shown in this figure, the exhaust heat recovery heat exchanger 94 includes a second partition member 96 in place of the second partition member 92. The second partition member 96 has a convex curved surface 96A and a concave curved surface 96B on both the upstream and downstream sides so as to be concave with respect to the gas outlet header 62A and convex with respect to the cooling water flow path 52A. 96A and the thickness along the radial direction of the concave curved surface 96B) are substantially constant. The curvature of the convex curved surface 96A is smaller than the curvature of the convex curved surface 56A (the radius of curvature is large). Therefore, in this embodiment, the length of the exhaust gas pipe 54 positioned at the axial center of the shell 52 is the periphery. The configuration is the same as that of the first embodiment, which is longer than the exhaust gas pipe 54 located in the section. On the other hand, since the protruding amount of the convex curved surface 96 </ b> A into the cooling water flow path 52 </ b> A is small compared to the second partition wall member 92, the effect of promoting the swirling flow generation is small compared to the second partition wall member 92. The exhaust heat recovery heat exchanger 94 and the exhaust heat recovery system 10 including the exhaust heat recovery heat exchanger 94 described above also provide the exhaust heat recovery heat exchanger 50 and the exhaust heat recovery system 10 including the exhaust heat recovery system 10 according to the first embodiment. The same effect can be obtained.

  In each of the above embodiments, both the shell 52 and the gas introduction pipe 70 are provided with the spiral grooves 52B and 70A. However, the present invention is not limited to this, and either the shell 52 or the gas introduction pipe 70 is provided. May be provided with a spiral guide portion on the inner peripheral surface. In particular, the gas introduction pipe 70 preferably includes a spiral groove 70A when the exhaust gas pipes 54 have the same length. Further, when there is a spiral groove 70A or when the lengths of the exhaust gas pipes 54 are different, the flare portions 54A may not be provided in the exhaust gas pipes 54 regardless of the configuration of the shell 52.

  In each of the above embodiments, the spiral grooves 52B and 70A are single spirals. However, the present invention is not limited to this, and for example, the spiral grooves 52B and the like are formed along two or more spirals. You may do it. Further, the spiral guide portion in the present invention is not limited to the spiral groove 52B formed integrally with the shell 52. For example, a spiral protrusion is attached to the inner surface of the shell 52 and a coolant is provided between the protrusions. You may comprise the spiral guide part which lets it pass.

  In addition, the heat exchanger and heat exchange device according to the present invention have a configuration in which the coolant is passed through the shell 52 side and the gas is passed through the exhaust gas pipe 54 side to perform heat exchange between the coolant and the gas. In addition, the application is not limited to the heat exchanger 50 for exhaust heat recovery and the exhaust heat recovery system 10.

1 is a partially cutaway side view showing a schematic overall configuration of an exhaust heat recovery heat exchanger according to a first embodiment of the present invention. It is sectional drawing of the heat exchanger for exhaust heat recovery which concerns on the 1st Embodiment of this invention. It is a typical perspective view which shows the cooling water inlet / outlet which comprises the heat exchanger for exhaust heat recovery which concerns on the 1st Embodiment of this invention. It is a sectional side view which shows the shape of the exhaust-gas inlet part of the exhaust-gas pipe | tube which comprises the heat exchanger for exhaust heat recovery which concerns on the 1st Embodiment of this invention. 1 is an overall configuration diagram of an exhaust heat recovery apparatus to which an exhaust heat recovery heat exchanger according to a first embodiment of the present invention is applied. It is a figure which shows the arrangement | positioning relationship between the heat exchanger for exhaust heat recovery which concerns on the 1st Embodiment of this invention, and an exhaust pipe, Comprising: (A) is a sectional side view which shows an example, (B) shows another example. It is a sectional side view. It is a typical perspective view corresponding to FIG. 3 which shows the principal part of the heat exchanger for exhaust heat recovery which concerns on the 2nd Embodiment of this invention. It is typical sectional drawing which shows the principal part of the heat exchanger for exhaust heat recovery which concerns on the 3rd Embodiment of this invention. It is typical sectional drawing which shows the principal part of the heat exchanger for exhaust heat recovery which concerns on the 4th Embodiment of this invention. It is sectional drawing of the heat exchanger for exhaust heat recovery which concerns on the 5th Embodiment of this invention. It is sectional drawing of the heat exchanger for exhaust heat recovery which concerns on the 6th Embodiment of this invention.

Explanation of symbols

50 Exhaust heat recovery heat exchanger (heat exchanger)
52 Shell (cylindrical container, cylindrical container)
52A Cooling water flow path 52B Spiral groove (spiral guide part)
54 Exhaust gas pipe (gas pipe)
54A Flare part (guide part)
56 First partition member (first partition)
58 Second partition member (second partition member)
60A Gas inlet header 62A Gas outlet header 64 Cooling water inlet pipe (coolant inlet)
66 Cooling water outlet pipe (cooling liquid outlet)
68 Gas branch pipe (gas supply pipe)
70 Gas introduction pipe 70A Spiral groove (spiral guide part)
72 Exhaust heat recovery heat exchanger (heat exchanger)
74 Cooling water inlet pipe (coolant inlet)
76 Cooling water outlet pipe (cooling liquid outlet)
78 Heat exchanger for exhaust heat recovery (heat exchanger)
80 Cooling water inlet pipe (coolant inlet)
82 Cooling water outlet pipe (cooling liquid outlet)
84 Heat exchanger for exhaust heat recovery (heat exchanger)
86 Cooling water inlet pipe (coolant inlet)
88 Cooling water outlet pipe (cooling liquid outlet)
90 Heat exchanger for exhaust heat recovery (heat exchanger)
92 Second partition member (second partition)
92A Convex curved surface (curved curved surface on the coolant flow path side)
94 Heat exchanger for exhaust heat recovery (heat exchanger)
96 Second partition member (second partition)
96A Convex curved surface (curved curved surface on the coolant flow path side)

Claims (8)

A heat exchanger for exchanging heat between the gas and the cooling liquid through the tube wall of the gas pipe by passing the cooling liquid through a cylindrical container containing a plurality of gas pipes through which the gas passes. ,
A cooling liquid inlet provided on one end side in the axial direction of the cylindrical wall of the cylindrical container, for introducing a cooling liquid into the cylindrical container;
A cooling liquid outlet that is provided on the other axial end of the cylindrical wall of the cylindrical container, and that discharges the cooling liquid from the cylindrical container;
Each gas pipe is arranged parallel to the axial direction of the cylindrical container,
And the heat exchanger which provided in the inner peripheral surface of the said cylindrical container the spiral guide part formed in the spiral from the said coolant inlet toward a coolant outlet. A heat exchanger for exchanging heat between the gas and the cooling liquid through the tube wall of the gas pipe by passing the cooling liquid through a cylindrical container containing a plurality of gas pipes through which the gas passes. ,
The gas pipes are arranged in parallel with the axial direction of the cylindrical container,
And the heat exchanger which made the length of some gas pipes different from the length of another gas pipe among these gas pipes.   The heat exchanger according to claim 2, wherein the length of the gas pipe positioned on the axial center side of the cylindrical container is longer than the length of the gas pipe positioned on the inner peripheral surface side of the cylindrical container. A heat exchanger for exchanging heat between the gas and the cooling liquid through the tube wall of the gas pipe by passing the cooling liquid through a cylindrical container containing a plurality of gas pipes through which the gas passes. ,
A first partition partitioning a coolant flow path through which the coolant in the cylindrical container passes and a gas inlet header in which gas inlets of the plurality of gas pipes respectively open;
A second partition partitioning the coolant flow path in the cylindrical container and a gas outlet header in which gas outlets of the plurality of gas pipes respectively open;
A cooling liquid inlet provided on the second partition side of the cylindrical wall of the cylindrical container and introducing a cooling liquid into the cooling liquid flow path;
A cooling liquid outlet provided on the first partition wall side of the cylindrical wall of the cylindrical container and leading out the cooling liquid from the cooling liquid flow path;
Each gas pipe is arranged parallel to the axial direction of the cylindrical container,
In addition, heat exchange formed on the surface of the second partition wall on the side of the coolant flow path is formed in a curved surface convex toward the coolant flow path side so as to overlap the coolant inlet in the axial direction of the cylindrical container. vessel.   The heat exchanger according to claim 4, wherein a spiral guide portion formed in a spiral shape from the coolant inlet to the coolant outlet is provided on the inner peripheral surface of the cylindrical container.   The heat exchanger according to any one of claims 1 to 5, wherein a guide portion for guiding gas into each gas pipe is formed at each gas inlet side end of the plurality of gas pipes. The heat exchanger according to any one of claims 1 to 6,
A gas introduction pipe which is provided coaxially with the cylindrical container or the cylindrical container and introduces gas into a gas inlet in the heat exchanger;
A gas supply pipe for introducing gas into the gas introduction pipe while changing the flow direction;
The heat exchange apparatus is provided with a spiral guide portion formed in a spiral shape from the gas supply pipe toward the heat exchanger on the inner peripheral surface of the gas introduction pipe. The gas supply pipe is a branch pipe branched from the main gas pipe,
The heat exchange apparatus according to claim 7, wherein the gas introduction pipe has a pipe wall formed in a spiral shape so that the spiral guide portion is integrally formed on an inner peripheral surface.

Images