US20110180242A1

US20110180242A1 - Stack type heat exchanger

Info

Publication number: US20110180242A1
Application number: US13/012,338
Authority: US
Inventors: Kazunori Urata; Susumu Tomida; Kouji Narita; Takeshi Sakamoto
Original assignee: Sumitomo Precision Products Co Ltd
Current assignee: Sumitomo Precision Products Co Ltd
Priority date: 2010-01-27
Filing date: 2011-01-24
Publication date: 2011-07-28
Also published as: JP2011153752A; JP5506428B2; EP2357329A2

Abstract

The heat exchanger performance of a stack type heat exchanger used as an aircraft engine oil cooler or the like is increased. U-turn type layered hot fluid passages having corrugated fins and U-turn type layered cold fluid passages having corrugated fins are alternately stacked to configure a stacked core. Mixing headers are provided to both side surfaces of the stacked core so as to pass a hot fluid which circulates on a first half side and a return path side through the mixing headers outside of the stacked core. The mixing headers mix the hot fluid which circulates in the inside portion of the U-turn passage and the hot fluid which circulates in the outside portion thereof. The hot fluids are mixed between the plural stacked hot fluid passages. The temperature distribution of the hot fluid in the first half and in the passage width direction is made uniform.

Description

BACKGROUND OF THE INVENTION

(1) Field of the Invention
The present invention relates to a heat exchanger suitable for an aircraft engine oil cooler. More specifically, the present invention relates to a stack type heat exchanger in which U-turn type layered hot fluid passages through which a hot fluid circulates and U-turn type layered cold fluid passages through which a cold fluid circulates are alternately stacked.
(2) Description of Related Art
In terms of difference between media which cools an engine oil, as aircraft engine oil coolers, two types, that is, a fuel cooled type and an air cooled type, are typical. In addition, in terms of difference in configuration between heat exchangers used, two types, that is, a plate-fin type and a shell-and-tube type, are typical. Used relatively frequently among these combinations is the fuel cooled type oil cooler using the plate-fin type heat exchanger. In the fuel cooled type oil cooler, with cooling of a hot engine oil by a cold fuel, the fuel temperature is increased, so that the fuel cooled type oil cooler can serve as a fuel preheater. The basic configuration of the plate-fin type heat exchanger used in the fuel cooled type oil cooler will be described with reference to FIG. 8 by taking the plate-fin type heat exchanger used in the fuel preheater described in Japanese Patent Application Laid-Open No. 2000-097582 as an example.
The plate-fin type heat exchanger is a kind of a stack type heat exchanger including, as a main configuration member, a stacked core 10 in which layered hot fluid passages 11 having plate-like fins called corrugated fins and layered cold fluid passages 12 having plate-like fins called corrugated fins are alternately stacked, and partition plates 13 called tube plates are provided between the hot fluid passages 11 and the cold fluid passages 12. In addition, tube plates are joined as end plates 14 on both sides in the stacking direction of the stacked core 10.
Each of the hot fluid passages 11 and each of the cold fluid passages 12 of the stacked core 10 are both of a U-turn type in which a fluid makes a U-turn and circulates in a plane perpendicular to the layer thickness direction, and a partitioning member 15 is provided in the center portion in the width direction perpendicular to the fluid circulation direction to form its first half and its return path. In addition, to avoid the interference between the entrance and outlet ports of a hot fluid and a cold fluid, an inlet port 12 a and an outlet port 12 b of the cold fluid passage 12 are opened to one end face of the stacked core 10, and an inlet port 11 a and an outlet port 11 b of the hot fluid passage 11 are opened to the ends on the entrance and outlet ports side of the cold fluid passage 12 on both side surfaces of the stacked core 10. Further, an engine oil circulates in the hot fluid passage 11, and at the same time, a fuel circulates in the cold fluid passage 12, so that heat exchange is performed between the cold fuel and the hot engine oil to cool the hot engine oil. At the same time, since the cold fuel is preheated, the oil cooler can serve as a fuel preheater.
In this connection, the temperature of the engine oil before heat exchange is typically approximately −50 to 200° C., and likewise, the fuel temperature before heat exchange is typically approximately −75 to 150° C. depending on a flight altitude or the like. In addition, the circulation directions of the engine oil and the fuel herein are the same. In other words, the plate-fin type heat exchanger described in Japanese Patent Application Laid-Open No. 2000-097582 is of a stacked parallel flow type. Conversely, the circulation directions of the fuel and the engine oil can be counter, which in this case, is called a stacked counterflow type.
As one of the problems of the plate-fin type heat exchanger used as such aircraft engine oil cooler, there is the degradation of the heat exchanging performance due to the abnormal temperature distribution of the engine oil circulating in the hot fluid passage 11. In other words, it is ideal that the temperature of the engine oil circulating in the layered hot fluid passage 11 is gradually decreased from the inlet port 11 a to the outlet port 11 b so that the temperature distribution in the passage width direction perpendicular to the fluid circulation direction and perpendicular to the layer thickness direction is uniform, but actually, the tendency of the temperature to be decreased is stronger toward the inside of the U-turn passage, that is, toward the vicinity of the partitioning member 15 which partitions the first half and the return path. Consequently, the flowability of the oil whose viscosity is dominated by the temperature becomes worse toward the inside of the U-turn passage, and only the oil circulating in the outside of the U-turn passage substantially contributes to heat exchange, with the result that the effective heat transfer area is reduced to degrade the heat exchanging performance. This tendency is more significant as the atmosphere temperature and the fuel temperature are lower, causing the cold ability of the oil cooler to be degraded.
As a means for solving this problem, the plate-fin type heat exchanger described in Japanese Patent Application Laid-Open No. 2000-097582 degrades the thermal conductivity of the partitioning member 15 which partitions the first half and the return path of the U-turn type hot fluid passage. The grounds are as follows. The relatively hot oil circulating in the first half of the hot fluid passage 11 is cooled by the relatively cold oil circulating in the return path across the partitioning member 15, which causes the temperature in the vicinity of the partitioning member 15 to be decreased. Therefore, the configuring material of the partitioning member 15 is replaced with a material with low thermal conductivity, such as ceramics, to inhibit heat conduction from the first half to the return path across the partitioning member 15, so that the temperature distribution in the passage width direction perpendicular to the fluid circulation direction is made uniform.
However, the effect of this means is limitative, and in an aircraft such as a large jet plane which flies at a high altitude, the temperature distribution in the passage width direction perpendicular to the fluid circulation direction in the first half and the return path of the hot fluid passage 11 is still non-uniform, so that the heat conduction ability is found to be degraded due to the reduction of the heat transmission surface.
Further, the aircraft engine oil cooler is often equipped with a bypass mechanism to rapidly increase the temperature of the engine oil at engine start. The bypass mechanism is described in Japanese Utility Model Application Laid-Open No. 01-067479 or the like. The configuration of the plate-fin type heat exchanger for the oil cooler equipped with the bypass mechanism will be described with reference to FIG. 9. The bypass mechanism has an entrance/outlet port 11 c provided to the side surface on the first half side of the hot fluid passage 11 of the stacked core 10, a bypass header 20 which communicates with the entrance/outlet port 11 c in the stacking direction, a bypass pipe 21 which directly connects the bypass header 20 to the outlet port 11 b of the hot fluid passage 11, and an opening and closing mechanism of the bypass pipe 21.
The bypass pipe 21 is typically brought into the closed state so that the oil circulating in the first half of the hot fluid passage 11 once flows out to the bypass header 20 and returns into the first half again. When the engine oil is required to be immediately heated, e.g., at engine start in a cold area, the bypass pipe 21 is brought into the opened state. Accordingly, the oil drawn into the first half of the hot fluid passage 11 is once drawn out from the middle of the first half to the outside of the stacked core 10 and passes around the stacked core 10 so as to be discharged to the outside of the heat exchanger. As a result, the cooling of the engine oil by the fuel can be avoided to enable the rapid temperature increase of the engine oil. In addition, with the temperature increase of the engine oil, the cold engine oil initially present in the heat exchanger is also gradually heated to decrease the viscosity.

SUMMARY OF THE INVENTION

An object of the present invention is to provide a stack type heat exchanger which can eliminate the abnormal temperature distribution in the passage width direction of a hot fluid circulating in a U-turn type layered hot fluid passage, and can increase the heat transmission ability, in particular, can significantly increase the cold ability.
Meanwhile, the present applicant has manufactured the plate-fin type heat exchanger used as the aircraft engine oil cooler which is equipped with the bypass mechanism shown in FIG. 9, more specifically, the counterflow type heat exchanger in which the circulation directions of the engine oil and the fuel are counter. The present inventors have initially considered that the abnormal temperature distribution in the width direction of the hot fluid circulating in the U-turn type layered hot fluid passage 11 is caused by the bypass mechanism, have experimentally manufactured the plate-fin type heat exchanger without the mechanism, and have examined in detail the effect of bypass mechanism on the non uniform oil temperature distribution. Consequently, contrary to expectations of the present inventors, by removing the bypass mechanism, the non-uniformity of the temperature distribution becomes more significant to degrade the heat exchanging performance.
In other words, in the aircraft engine oil cooler, the bypass mechanism is used only at engine start, is brought into the off state at the time of the typical engine operation, and becomes a header bypass passage which only passes the oil circulating in the first half of the U-turn passage on the hot side through the bypass header 20. At this time, not only the oil circulating in the outside portion of the first half (the portion far from the partitioning member 15 which partitions the first half and the return path of the U-turn passage), but also the oil circulating in the inside portion of the first half (the portion near the partitioning member 15), once pass through the bypass header 20 so that both of the oils are forcibly mixed in the bypass header 20 and then the forcible mixing of the oils is performed in the stacking direction of the U-turn passage on the hot side. The present inventors have considered that such oil mixing in the bypass header 20 causes the abnormal temperature distribution in the passage width direction of the hot fluid circulating in the hot fluid passage 11, but actually, has found to be an effective means for eliminating the abnormal temperature distribution.
In the specific description, when the bypass header 20 is provided in the first half of the U-turn passage on the hot side, contrary to when there is not the bypass mechanism, on the return path side, the oil temperature in the outside portion (the portion far from the partitioning member 15) is lower than that of the inside portion (the portion near the partitioning member 15 which partitions the first half and the return path of the U-turn passage), so that the switching of the temperature distributions in the return path without the stacked core 10 completely functioning increases the heat exchanging performance, as compared with when there is not the bypass mechanism.
With such circumstances as a background, as one attempt, the present inventors have provided the header bypass passages having the same function as the normal bypass mechanism in both the first half and the return path of the U-turn passage on the hot side. As a result, we have found that the abnormal temperature distribution in the hot fluid passage which has been the problem in the plate-fin type heat exchanger used as the aircraft engine oil cooler, the drift of the oil due to this, and the degradation of the heat exchanging performance can be effectively eliminated.
The stack type heat exchanger of the present invention has been completed based on such findings, and includes a stacked core in which U-turn type layered hot fluid passages through which a hot fluid circulates and U-turn type layered cold fluid passages through which a cold fluid circulates are alternately stacked, wherein each of the outer surfaces of the stacked core on the first half side and on the return path side has a mixing header which communicates with each of the hot fluid passages in the stacking direction, wherein each of the hot fluid passages has therein a fluid draw-in/draw-out passage that passes the hot fluid circulating in each of the passages through the mixing header.
The fluid draw-in/draw-out passage desirably passes the hot fluid circulating in the entire area in the width direction from the outside to the inside of the U-turn passage through the mixing header. In addition, the configuration in which the mixing header on the first half side serves as the bypass header is desirably reasonable. Further, the counterflow type in which the circulation direction of the hot fluid in the hot fluid passage and the circulation direction of the cold fluid in the cold fluid passage are counter is preferable from the viewpoint of improving the heat exchanging performance.
In the stack type heat exchanger of the present invention, since the U-turn type layered hot fluid passages and the U-turn type layered cold fluid passages are alternately stacked. Accordingly, the hot fluid circulating in the hot fluid passages and the cold fluid circulating in the cold fluid passages exchange heat, so that the temperature of the hot fluid is decreased and thus the temperature of the cold fluid is increased. At this time, the hot fluid circulating in the U-turn passage on the hot side once flows out to the mixing header in the middle of the first half of the U-turn passage, and here, the fluid which flows through the inside portion of the U-turn passage and the fluid which flows through the outside portion thereof are mixed. In addition, the mixing of the hot fluids is performed in the stacking direction of the U-turn passage. These can make the fluid temperature distribution in the passage width direction uniform. Aside from this, the hot fluid once flows out to the mixing header in the middle of the return path of the U-turn passage, and here, the fluid which flows through the inside portion of the U-turn passage and the fluid which flows through the outside portion thereof are mixed. In addition, the mixing of the hot fluids is performed in the stacking direction of the U-turn passage.
From these results, the fluid temperature difference between the inside portion and the outside portion of the U-turn passage on the hot side is reduced, and consequently, the drift is reduced to improve the heat exchanging performance, in particular, the cold ability when the temperature of the cold fluid is low.
In other words, the hot fluid circulating in the inside portion in each of the first half and the return path of the U-turn passage on the hot side is forcibly discharged to the outside of the stacked core and is actively stirred and mixed with the hot fluid circulating in the outside portion, which is the largest characteristic point in the stack type heat exchanger of the present invention.
The heat exchanging performance of the stack type heat exchanger of the present invention is increased particularly when the hot fluid circulating in the entire area in the width direction from the outside to the inside of the U-turn passage passes through the mixing header to perform stirring and mixing. In addition, the heat exchanging performance of the counterflow type heat exchanger in which the circulation directions of the hot fluid and the fluid direction are counter is higher than that of the parallel flow type in which the circulation direction of the hot fluid and the fluid direction of the cold fluid are the same.
When the bypass mechanism is necessary, the mixing header on the advance side is used as the bypass header so that the configuration is simplified.
In the stack type heat exchanger of the present invention, in each of the first half and the return path of the U-turn passage on the hot side in the stacked core in which the U-turn type layered hot fluid passages and the U-turn type layered hot fluid passages are alternately stacked, the mixing header is attached to the outer surface on the advance side and the outer surface on the return path side, and the hot fluid circulating in the first half or the return path is once discharged to the outside of the stacked core for stirring and mixing so as to be returned into the stacked core, so that the abnormal temperature distribution in the passage width direction of the hot fluid circulating in the U-turn passage on the hot side is reduced to enable the significant increase of the heat exchanging performance.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a perspective view of a stack type heat exchanger showing an embodiment of the present invention;

FIG. 2 is a perspective view of a stacked core in the stack type heat exchanger;

FIG. 3 is a plan view of a hot fluid passage in the stacked core;

FIG. 4 is a plan view of a cold fluid passage in the stacked core;

FIG. 5 is a plan view showing the temperature distribution of a hot fluid in the hot fluid passage;

FIG. 6 is a plan view showing the temperature distribution of the hot fluid in the hot fluid passage of a conventional stack counterflow type heat exchanger;

FIG. 7 is a perspective view of the stack type heat exchanger showing another embodiment of the present invention;

FIG. 8 is a perspective view of a conventional stack type heat exchanger; and

FIG. 9 is a perspective view of another conventional stack type heat exchanger.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
A stack type heat exchanger of this embodiment is used as an aircraft engine oil cooler, and as shown in FIGS. 1 and 2, has a rectangular cuboid stacked core 10 including a plate-fin type heat exchanger of a counterflow type. In the stacked core 10, layered hot fluid passages 11 including corrugated fins and layered cold fluid passage 12 including corrugated fins are alternately stacked. Partition plates 13 called tube plates are provided between the hot fluid passages 11 and the cold fluid passages 12, and both end faces in the stacking direction of the stacked core 10 are closed by end plates 14 called tube plates.
As shown in FIGS. 3 and 4, each of the hot fluid passages 11 and each of the cold fluid passages 12 are both of a U-turn type, and a partitioning member 15 which partitions its first half and its return path is provided in the center portion in the width direction of each of the fluid passages except for the end on the passage reversing side (on the opposite side of the entrance and outlet ports side). An inlet port 12 a and an outlet port 12 b of the cold fluid passage 12 are opened side by side in the width direction on the end face on the entrance/exit side of the stacked core 10. An inlet port 11 a of the hot fluid passage 11 is opened to the end on the entrance/exit side on one side surface of the stacked core 10, and an outlet port 11 b of the hot fluid passage 11 is opened to the end on the entrance/exit side on the other side surface of the stacked core 10. Further, a second entrance/outlet port 11 c of the hot fluid passage 11 a is provided to one side surface of the stacked core 10 so as to be located in the middle portion of the first half. Likewise, a third entrance/outlet port 11 d of the hot fluid passage 11 a is provided to the other side surface of the stacked core 10 so as to be located in the middle portion of the return path.
The outer edges of the hot fluid passage 11 and the cold fluid passage 12 except for the fluid entrance and outlet ports are closed by side bars 18 and 19, respectively.
A vertical inlet header 30 a which communicates with the inlet port 12 a of the cold fluid passage 12 in the passage stacking direction and a vertical outlet header 30 b which communicates with the outlet port 12 b of the cold fluid passage 12 in the passage stacking direction are attached side by side in the width direction to the end face on the entrance/exit side of the stacked core 10. To one side surface of the stacked core 10, a vertical inlet header 40 a which communicates with the inlet port 11 a of the hot fluid passage 11 in the passage stacking direction is attached along the entire height, and a first vertical mixing header 50 a which communicates with the second entrance/outlet port 11 c of the hot fluid passage 11 in the passage stacking direction is attached along the entire height. To the other side surface of the stacked core 10, a vertical outlet header 40 b which communicates with the outlet port 11 b of the hot fluid passage 11 in the passage stacking direction is attached in the stacking direction along the entire height, and a second vertical mixing header 50 b which communicates with the third entrance/outlet port 11 d of the hot fluid passage 11 in the passage stack direction is attached in the stacking direction along the entire height.
All of the inlet header 30 a and the outlet header 30 b of the cold fluid, the inlet header 40 a and the outlet header 40 b of the hot fluid, and the first mixing header 50 a and the second mixing header 50 b are covers of a semicircular cross section along the entire length in the longitudinal direction (vertical direction), and both ends in the longitudinal direction of each of the headers are closed. In addition, an inlet 31 a of the cold fluid is provided in the center portion in the longitudinal direction of the inlet header 30 a, an outlet 31 b of the cold fluid is provided in the center portion in the longitudinal direction of the outlet header 30 b, an inlet 41 a of the hot fluid is provided in the center portion in the longitudinal direction of the inlet header 40 a, and an outlet 41 b of the hot fluid is provided in the center portion in the longitudinal direction of the outlet header 40 b.
The fluid circulation direction of a corrugated fin 16 arranged in the hot fluid passage 11 is along the direction of the first half and the return path of the U-turn passage on the hot side except for the following exceptions. To lead the hot fluid flowing from the inlet header 40 a to the hot fluid passage 11, a right triangular corrugated fin 16 a in the different passage direction is arranged at the end of the entrance side of the U-turn passage on the hot side. To lead the hot fluid discharged from the hot fluid passage 11 to the outlet header 40 b, a right triangular corrugated fin 16 b in the different passage direction is arranged at the end on the exit side of the U-turn passage on the hot side. An isosceles triangular corrugated fin 16 c in the different passage direction for reversing the passage is arranged at the end on the passage reversing side (on the opposite side of the entrance/exit side) of the U-turn passage on the hot side.
For the corrugated fin 16, further, to pass the total amount of the hot fluid circulating in the first half of the U-turn passage on the hot side through the first mixing header 50 a, an isosceles triangular corrugated fin 16 d in the different passage direction is arranged as the fluid draw-in/draw-out passage for bypass so as to be located on the back side of the mixing header 50 a. Further, to pass the total amount of the hot fluid circulating in the return path of the U-turn passage on the hot side through the second mixing header 50 b, an isosceles triangular corrugated fin 16 e in the different passage direction is arranged as the fluid draw-in/draw-out passage for bypass so as to be located on the back side of the mixing header 50 b.
The fluid circulation direction of a corrugated fin 17 arranged in the cold fluid passage 12 is along the direction of the first half and the return path of the U-turn passage on the cold side except that an isosceles triangular corrugated fin 17 a in the different passage direction for reversing the passage is arranged at the end on the passage reversing side (on the opposite side of the entrance/exit side) of the U-turn passage on the cold side.
The function of the stack type heat exchanger of this embodiment is as follows.
As described above, the stack type heat exchanger of this embodiment is the plate-fin type heat exchanger of the counterflow type used as the aircraft engine oil cooler. For this reason, the hot fluid circulating in the hot fluid passage 11 is the hot engine oil to be cooled, and the cold fluid circulating in the cold fluid passage 12 is the cold fuel.
The engine oil as the hot fluid flows from the inlet 11 a through the inlet header 40 a provided to one side surface on the entrance/exit side of the stacked core 10 into the first half of the hot fluid passage 11. The engine oil which advances in the first half passes in the fluid draw-in/draw-out passage 16 d in the middle of the first half through the first mixing header 50 a attached to the side surface of the stacked core 10 to return to the first half. The engine oil which has returned to the first half changes the direction on the other end side of the passage to enter the return path parallel with the first half. The engine oil which advances in the return path passes in the fluid draw-in/draw-out passage 16 e in the middle of the return path through the second mixing header 50 b attached to the side surface of the stacked core 10 to return into the return path. Then, the engine oil is discharged from the outlet 11 b provided to the other side surface on the entrance/exit side of the stacked core 10 through the outlet header 40 b to the outside of the stacked core 10.
On the other hand, the fuel as the cold fluid flows from the inlet port 12 a of the cold fluid passage 12 through the inlet header 30 a provided to the end face on the entrance/exit side of the stacked core 10 into the first half of the passage, moves straight forward in the first half, changes the direction on the other end side of the passage, moves straight forward in the return path parallel with the first half, and is discharged from the outlet port 12 b through the outlet header 30 b to the outside.
While the engine oil as the hot fluid is drawn into and is drawn out from the side surface on the entrance/exit side of the stacked core 10, the fuel as the cold fluid is drawn into and is drawn out from the end face on the entrance/exit side of the stacked core 10 to avoid the interference between the headers 40 a and 40 b on the hot side and between the headers 30 a and 30 b on the cold side.
In such stack type counterflow type heat exchanger, the U-turn type hot fluid passages 11 and the U-turn type cold fluid passages 12 are alternately stacked, so that the hot engine oil circulating in the hot fluid passages 11 and the fuel circulating in the cold fluid passages 12 in the reverse direction exchange heat to cool the engine oil.
Here, the total amount of the engine oil circulating in the hot fluid passage 11 once passes through the mixing header 50 a outside of the stacked core 10 in the first half of the U-turn passage on the hot side. In the mixing header 50 a, the engine oil circulating in the outside portion of the first half of the hot fluid passage 11 and the engine oil circulating in the inside portion of the first half are mixed. At the same time, the engine oils are mixed between the stacked hot fluid passages 11. Accordingly, the non-uniform temperature distribution in the passage width direction of the hot fluid passage 11 and the non-uniform temperature distribution between the hot fluid passages 11 in the stacking direction can be eliminated.
In this state, the temperature of the engine oil is decreased in the outside portion of the return path of the hot fluid passage 11, the temperature of the engine oil is increased in the inside portion, the flow in the outside portion becomes worsen, and the engine oil circulates only in the inside portion. For this reason, the designed heat exchange performance is not be achieved. Consequently, in the stack type heat exchanger of this embodiment, the total amount of the engine oil also passes through the mixing header 50 b outside of the stacked core 10 in the return path of the hot fluid passage 11. Further, the engine oil circulating in the outside portion of the return path of the hot fluid passage 11 and the engine oil circulating in the inside portion in the return path are also mixed in the mixing header 50 b. At the same time, the engine oils are mixed between the stacked hot fluid passages 11. From this, the non-uniform temperature distribution in the passage width direction of the hot fluid passage 11 and the non-uniform temperature distribution caused between the hot fluid passages 11 in the stacking direction can be eliminated.
Thus, in the stack type heat exchanger of this embodiment, the temperature distribution in the passage width direction of the engine oil is made significantly uniform in both the first half and the return path of the U-turn passage on the hot side, and substantially the entire surface of the hot fluid passage 11 contributes to heat exchange, so that the heat exchanging performance is increased even at cold temperature, and the heat exchanger performance is achieved as designed.
In the stack type heat exchanger of this embodiment, FIG. 5 shows the analysis of the fluid temperature distribution in the hot fluid passage 11 in the stacked core 10. The temperature at the time of the inflow of the engine oil is 100° C. The temperature distribution in the passage width direction in the first half and the return path is found to be made uniform. In particular, the uniformity of the temperature distribution is significant on the downstream side of the mixing header 50 b in the return path.
For comparison, FIG. 6 shows the temperature distribution of a conventional stack type heat exchanger (FIG. 9) having only the bypass header 20. It is found that the uniformity of the temperature distribution in the width direction is significant on the return path side, the temperature in the outside portion of the passage is low, and only the inside portion substantially functions.
These functions are compared based on the heat exchange performance of the heat exchangers. The length of the stacked core 10 is approximately 400 mm, the width is approximately 200 mm, the height in the stacking direction is approximately 50 mm, the number of the hot fluid passages 11 is 7, the number of the cold fluid passages 12 is 6, and the layer thickness of each of the passages is approximately 3 mm. As the cold fluid, the aircraft fuel at approximately −50° C. circulates in the cold fluid passage 12 at a flow rate of approximately 3 tons/h. As the hot fluid, the engine oil at approximately 100° C. circulates in the hot fluid passage 11 at a flow rate of approximately 2 tons/h.
The heat exchanging performance of the stack type heat exchanger of this embodiment provided with the mixing headers in the first half and the return path of the U-turn passage on the hot side is increased by 10% with respect to the conventional stack type heat exchanger provided with the bypass header on the first half side of the U-turn passage on the hot side. In addition, the heat exchanging performance of the stack type heat exchanger from which the bypass header is removed from the first half side of the U-turn passage on the hot side is decreased by 20% with respect to the conventional stack type heat exchanger provided with the bypass header on the first half side of the U-turn passage on the hot side.
In the stack type heat exchanger of this embodiment, the mixing headers 50 a and 50 b are provided on the first half side and the return path side of the U-turn passage on the hot side, and as shown in FIG. 7, the mixing header 50 a on the first half side can be used as the bypass header. In that case, the outlet port 51 a is provided in the center portion or the like on the back of the mixing header 50 a, and is opened at the time of the use of the bypass function so as to be connected to the outlet port 41 b of the outlet header 40 b. In addition, the total amount of the hot fluid which has flowed from the inlet header 40 a into the hot fluid passage 11 passes from the mixing header 50 a to the outlet header 40 b, so that the rapid temperature increase of the engine oil as the hot fluid is enabled, and the temperature increased engine oil passes through part of the inside of the heat exchanger, so that the temperature increase of the cold engine oil staying in the heat exchanger is enabled while the supply of the hot fluid is kept.

Claims

1. A stack type heat exchanger comprising:

a stacked core in which U-turn type layered hot fluid passages through which a hot fluid circulates and U-turn type layered cold fluid passages through which a cold fluid circulates are alternately stacked,

wherein each of the outer surfaces of the stacked core on the first half side and on the return path side has a mixing header which communicates with each of the hot fluid passages in the stacking direction,

wherein each of the hot fluid passages has therein a fluid draw-in/draw-out passage that passes the hot fluid circulating in each of the passages through the mixing header.

2. The stack type heat exchanger according to claim 1, wherein the fluid draw-in/draw-out passage passes the hot fluid circulating in the entire area in the width direction from the outside to the inside of the U-turn passage through the mixing header.

3. The stack type heat exchanger according to claim 1 or 2, wherein the mixing header on the first half side serves as the bypass header.