Patent Grant
11079182
The present invention relates to a heat exchanger that performs heat exchange between a first fluid and a second fluid.
Recently, there has been a need for improvement of fuel economy of motor vehicles. Particularly, there has been a need for a system that can reduce friction loss by early warming up cooling water, an engine oil, ATF (Automatic Transmission Fluid) or like in order to prevent deterioration of fuel economy when the engine is cold, such as when the engine is started. Further, there has been a need for a system that heats a catalyst in order to activate a catalyst for cleaning an exhaust gas at an early stage.
An example of such a system is a heat exchanger. The heat exchanger is a device including a component (a heat exchange component) that performs heat exchange between a first fluid and a second fluid by allowing the first fluid to flow internally and the second fluid to flow externally. In such a heat exchanger, heat can be effectively utilized by heat exchange from a higher temperature fluid (for example, the exhaust gas or the like) to a lower temperature fluid (for example, the cooling water).
Patent Document 1 as described below discloses a heat exchange member capable of improving fuel economy of a motor vehicle when recovering waste heat from an exhaust gas and using the heat for warming up an engine in the field of the motor vehicle. The heat exchange member disclosed in Patent Document 1 includes: a pillar shaped honeycomb structure having a plurality of cells; and a casing arranged on an outer peripheral side of the honeycomb structure. A first fluid is passed through the cells of the honeycomb structure and a second fluid is passed between the honeycomb structure and the casing. An inlet for the second fluid to the casing and an outlet for the second fluid from the casing are arranged on the same side relative to the honeycomb structure. Therefore, in the heat exchange member disclosed in Patent Document 1, the heat exchange between the first fluid and the second fluid occurs while circulating the second fluid around the outer periphery of the honeycomb structure. Further, Patent Document 1 illustrates an embodiment where a height of a flow path between the honeycomb structure and the casing is uniform in an axial direction of the honeycomb structure.
Patent Document 1: Japanese Patent Application Publication No. 2012-037165 A
When the height of the flow path is uniformly increased in the above conventional heat exchanger, there will be many second fluids that will not be subjected to heat exchange. In this case, a temperature of the second fluid will be difficult to rise, and a heat exchange efficiency will be deteriorated. On the other hand, when the height of the flow path is uniformly decreased, the second fluid that is not subjected to heat exchange can be decreased, but the second fluid may not be thoroughly distributed in a circumferential direction of the honeycomb structure. If the second fluid is not thoroughly distributed in the circumferential direction of the honeycomb structure, the entire circumferential surface of the honeycomb structure cannot be utilized for heat exchange, and the heat exchange efficiency is also deteriorated.
The present invention has been made to solve the above problems. One of objects of the present invention is to provide a heat exchanger that can have an improved heat exchange efficiency.
In one embodiment, a heat exchanger according to the present invention comprises: a pillar shaped honeycomb structure having a plurality of cells, the cells providing first flow paths through which a first fluid is passed; an inner cylinder attached to an outer periphery of the honeycomb structure; and an outer cylinder disposed on an outer periphery of the inner cylinder, the outer cylinder providing a second flow path through which a second fluid is passed, the second flow path being arranged between the outer cylinder and the inner cylinder, wherein the second flow path comprises: an intermediate flow path extending in an axial direction of the honeycomb structure so as to include an outer peripheral position of the honeycomb structure; and side flow paths located on both sides of the intermediate flow path in the axial direction, and wherein the intermediate flow path has a height lower than that of each of the side flow paths.
According to one embodiment of the heat exchanger according to the present invention, the height of the intermediate flow path is lower than that of each side flow paths, so that the second fluid can be thoroughly distributed in the side flow paths in the circumferential direction of the honeycomb structure, and an amount of the second fluid that is not subjected to the heat exchange can be decreased in the intermediate flow path, thereby improving the heat exchange efficiency.
Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings. It should be understood that the present invention is not limited to the embodiments, and it can be embodied by modifying elements without departing from the spirit of the present invention. Further, various inventions may be formed by appropriately combining a plurality of elements disclosed in the respective embodiments. For example, some elements may be deleted from all elements shown in the embodiments. Further, elements of different embodiments may be optionally combined.
The heat exchanger 1 shown in
The heat exchanger 1 according to the present embodiment is provided with the honeycomb structure 10, the inner cylinder 11, an outer cylinder 12, the supply pipe 13, the discharge pipe 14, the intermediate cylinder 15, spacers 16, and covers 17.
<Regarding Honeycomb Structure>
The honeycomb structure 10 according to the present embodiment is a pillar shaped structure. A cross-sectional shape of the honeycomb structure 10 may be a circle, an ellipse, a rectangle, or other polygon. The honeycomb structure 10 according to the present embodiment is a cylindrical structure.
As particularly shown in
The first fluid 2 according to the present embodiment is allowed to flow along the axial direction 10c of the honeycomb structure 10 and passes through the honeycomb structure 10 through the respective cells 101 from the first end face 10a to the second end face 10b. That is, each cell 101 provides a first flow path through which the first fluid 2 passes. It should be noted that
In
Each cell 101 of the honeycomb structure 10 shown in
The cells 101 shown in
It is preferable that the first partition walls 100a that define one cell 101 are longer than the second partition walls 100b that define one cell 101. Since the first partition walls 100a contribute to thermal conductivity in the radial direction, such a configuration can allow efficient transmission of heat of the first fluid 2 flowing through the cells 101 toward a radially outer side of the honeycomb structure 10.
It is preferable that the first partition wall 100a is thicker than the second partition wall 100b. Since the thickness of the partition wall 100 correlates with the thermal conductivity, such a configuration can allow the thermal conductivity of the first partition wall 100a to be higher than the thermal conductivity of the second partition wall 100b. As a result, the heat of the first fluid 2 flowing through the cells 101 can be efficiently transmitted toward the radially outer side of the honeycomb structure 10.
An outer peripheral wall 103 of the honeycomb structure 10 is preferably thicker than the partition walls 100 (the first partition walls 100a and the second partition walls 100b). Such a configuration can allow improvement of strength of the outer peripheral wall 103 which would otherwise tend to generate breakage (for example, cracks, chinks, and the like) due to an impact from the outside or thermal stress based on a temperature difference between the first fluid 2 and the second fluid 3.
The thickness of the partition wall 100 (the first partition walls 100a and the second partition walls 100b) is not particularly limited and may be adjusted as needed according to applications and the like. The thickness of the partition wall 100 is preferably from 0.1 to 1 mm, and more preferably 0.2 to 0.6 mm. The thickness of the partition wall 100 of 0.1 mm or more can lead to sufficient mechanical strength of the honeycomb structure 10. Further, the thickness of the partition wall 100 of 1 mm or less can allow prevention of problems that a pressure loss is increased due to a decrease in an opening area and a heat recovery efficiency is decreased due to a decrease in a contact area with the first fluid 2.
The space between the adjacent first partition walls 100a will be narrower in the circumferential direction as it is a radially inner side of the honeycomb structure 10, which may be difficult to form the cells 101. When the cells 101 are not formed radially inward or when the cross-sectional areas of the cells 101 formed on the inner side in the radial direction is too low, the pressure loss of the heat exchanger 1 will be increased.
From the viewpoint of preventing such problems, in the cross section of the honeycomb structure 10 in the plane orthogonal to the first flow path or the axial direction 10c, the number of the first partition walls 100a on the radially inner side of the honeycomb structure 10 is lower than the number of the first partitions 100a on the radially outer side. Such a configuration can allow the cells 101 to be stably formed even on the radially inner side of the honeycomb structure 10. This can allow suppression of an increase in the pressure loss of the heat exchanger 1 caused by difficulty in forming the cells 101 on the radially inner side of the honeycomb structure 10.
It should be noted that the number of the first partition walls 100a on the radially inner side or the radially outer side of the honeycomb structure 10 refers to the total number of the first partition walls 100a included in each annular region (circumferential region) defined by the second partition walls 100b and the outer peripheral wall 103 adjacent to each other in the radial direction of the honeycomb structure 10, in the cross section of the honeycomb structure 10. It is preferable that the total number of the first partition walls 100a in the annular region located on the innermost side in the radial direction of the honeycomb structure 10 is higher than the total number of the first partition walls 100a in the annular region located on the outermost side in the radial direction of the honeycomb structure 10. It is also preferable that the total number of the first partition walls 100a in each annular region is decreased as it goes inward in the radial direction of the honeycomb structure 10. The total number of the first partition walls 100a may be continuously decreased toward the inner side in the radial direction of the honeycomb structure 10 or may be decreased in a stepwise manner toward the inner side in the radial direction of the honeycomb structure 10 (i.e., the number of the first partitions 100a in the annular region, adjacent to each other in the radial direction of the honeycomb structure 10, may be the same). Since the space between the adjacent first partition walls 100a has to be narrower as it approaches the radially inner side of the honeycomb structure 10, it will be difficult to form the cells 101. However, the structure as described above can allow the space between the adjacent first partition walls 100a to be ensured, so that the cells 101 can be stably formed. Therefore, an increase in the pressure loss of the heat exchanger 1 can be suppressed.
The honeycomb structure 10 shown in
<Regarding Inner Cylinder>
The inner cylinder 11 according to the present embodiment is a cylindrical member attached to the outer periphery of the honeycomb structure 10. The inner cylinder 11 according to the present embodiment is fixed to the outer periphery of the honeycomb structure 10 in a state where an inner peripheral surface of the inner cylinder 11 is in contact with the outer peripheral surface of the honeycomb structure 10. That is, the cross-sectional shape of the inner peripheral surface of the inner cylinder 11 according to the present embodiment agrees with the cross-sectional shape of the outer peripheral surface of the honeycomb structure 10. The axial direction of the inner cylinder 11 of the present embodiment agrees with the axial direction 10c of the honeycomb structure 10. It is preferable that the central axis of the inner cylinder 11 agrees with the central axis of the honeycomb structure 10. The length of the inner cylinder 11 in the axial direction 10c of the honeycomb structure 10 is longer than the length of the honeycomb structure 10 in the axial direction 10c of the honeycomb structure 10. It is preferable that the center positions of the honeycomb structure 10 and the inner cylinder 11 in the axial direction 10c of the honeycomb structure 10 are coincident with each other. The inner diameter of the inner cylinder 11 according to the present embodiment is uniform in the axial direction 10c of the honeycomb structure 10 and the peripheral wall of the inner cylinder 11 extends linearly in the axial direction 10c of the honeycomb structure 10.
The heat of the first fluid 2 passing through the honeycomb structure 10 is transmitted to the inner cylinder 11 through the honeycomb structure 10. A material of the inner cylinder 11 that can be preferably used includes a material having higher thermal conductivity, for example, metals, ceramics or the like. Examples of the metals that can be used include stainless steel, titanium alloys, copper alloys, aluminum alloys, brass and the like. For the reason that the durability and reliability is higher, the material of the inner cylinder 11 is preferably stainless steel.
From the inner peripheral surface of the inner cylinder 11 according to the present embodiment, protruding portions 110 protrude radially inward of the inner cylinder 11. The protruding portions 110 are disposed at positions where they are in contact with the first and second end faces 10a, 10b of the honeycomb structure 10 in the axial direction 10c of the honeycomb structure 10, respectively. By providing such protruding portions 110, displacement of the honeycomb structure 10 in the axial direction 10c is restricted. Each protruding portion 110 according to the present embodiment is configured to fix a stainless steel ring member to the inner peripheral surface of the inner cylinder 11 by welding and extend in the entire circumferential direction of the inner cylinder 11. However, each protruding portion 110 may not extend in the entire circumferential direction of the inner cylinder 11, and may protrude from the inner peripheral surface of the inner cylinder 11 at one or more positions in the circumferential direction of the inner cylinder 11.
<Regarding Outer Cylinder, Supply Pipe and Discharge Pipe>
The outer cylinder 12 according to the present embodiment is a cylindrical member arranged on the outer periphery of the inner cylinder 11. The axial direction of the outer cylinder 12 according to the present embodiment agrees with the axial direction 10c of the honeycomb structure 10. It is preferable that the central axis of the outer cylinder 12 coincides with the central axis of the honeycomb structure 10. The length of the outer cylinder 12 in the axial direction 10c of the honeycomb structure 10 is longer than the length of the honeycomb structure 10 in the axial direction 10c of the honeycomb structure 10. Further, the length of the outer cylinder 12 in the axial direction 10c is equal to the length of the inner cylinder 11 in the axial direction 10c.
The outer cylinder 12 according to the present embodiment includes a central peripheral wall 120, a pair of expanded diameter peripheral walls 121, a pair of connecting peripheral walls 122, and a pair of end walls 123.
The central peripheral wall 120 is an annular wall extending in a center portion of the outer cylinder 12 in the axial direction of the outer cylinder 12 (the axial direction 10c of the honeycomb structure 10). An inner diameter of the central peripheral wall 120 is larger than an outer diameter of the inner cylinder 11. The central peripheral wall 120 is disposed so as to include an outer peripheral position of the honeycomb structure 10. The outer peripheral position of the honeycomb structure 10 refers to a position which is outside the outer peripheral surface of the honeycomb structure 10 and which is between the first end face 10a and the second end face 10b of the honeycomb structure 10 in the axial direction 10c of the honeycomb structure 10. It is preferable that the central positions of the honeycomb structure 10 and the central peripheral wall 120 in the axial direction 10c of the honeycomb structure 10 agree with each other.
Each expanded diameter peripheral wall 121 is an annular wall portion where the honeycomb structure 10 is provided on both sides of the central peripheral wall 120 in the axial direction 10c. The inner diameter of each expanded diameter peripheral wall 121 is larger than the inner diameter of the central peripheral wall 120. In the present embodiment, the inner diameter of one expanded diameter peripheral wall 121 in the axial direction of the outer cylinder 12 and the inner diameter of the other expanded diameter peripheral wall 121 in the axial direction of the outer cylinder 12 are matched with each other. However, these inner diameters may be different from each other.
Each connecting peripheral wall 122 is an annular wall portion connecting the central peripheral wall 120 to the expanded diameter peripheral wall 121. Each connecting peripheral wall 122 according to the present embodiment extends so as to be inclined with respect to the axial direction and the radial direction of the outer cylinder 12. The cross-sectional shape of each connecting peripheral wall 122 may be either a curved shape or a linear shape.
Each end wall 123 is an annular wall portion that protrudes radially inward of the outer cylinder 12 from an end portion of the expanded diameter peripheral wall 121. A tip of each end wall 123 abuts against the outer peripheral surface of the inner cylinder 11. The tip of each end wall 123 is fixed to the outer peripheral surface of the inner cylinder 11 such as by welding or the like, so that the outer cylinder 12 is fixed to the inner cylinder 11.
As described above, the inner diameter of each of the peripheral walls 120 to 122 of the outer cylinder 12 is larger than the outer diameter of the inner cylinder 11, and between the outer peripheral surface of the inner cylinder 11 and the inner peripheral surface of the outer cylinder 12 is a space where the honeycomb structure 10 extends in the axial direction 10c and the circumferential direction.
The supply pipe 13 is connected to one expanded diameter peripheral wall 121 in the axial direction of the outer cylinder 12, and the discharge pipe 14 is connected to the other expanded diameter peripheral wall 121 in the axial direction of the outer cylinder 12. The supply pipe 13 is a pipe for supplying the second fluid 3 to the space between the inner cylinder 11 and the outer cylinder 12. The discharge pipe 14 is a pipe for discharging the second fluid 3 from the space between the inner cylinder 11 and the outer cylinder 12. That is, the outer cylinder 12 according to the present embodiment provides a second flow path 124 through which the second fluid 3 is passed. The second flow path 124 is arranged between the outer cylinder 12 and the inner cylinder 11.
As shown in
As particularly shown in
The second flow path 124 according to the present embodiment includes an intermediate flow path 124a, a supply-side side flow path 124b, and a discharge-side side flow path 124c.
The intermediate flow path 124a is a flow path formed between the inner cylinder 11 and the central peripheral wall 120 of the outer cylinder 12 and extends in the axial direction 10c of the honeycomb structure 10 so as to include the outer peripheral position of the honeycomb structure 10.
The supply-side side flow path 124b is a flow path formed between the expanded diameter peripheral wall 121 of the outer cylinder 12 to which the supply pipe 13 is connected and the inner cylinder 11. The discharge-side side flow path 124c is a flow path formed between the expanded diameter peripheral wall 121 of the outer cylinder 12 to which the discharge pipe 14 is connected and the inner cylinder 11. The supply-side side flow path 124b and the discharge-side side flow path 124c form side flow paths located on both sides of the intermediate flow path 124a in the axial direction 10c of the honeycomb structure 10.
The second fluid 3 from the supply pipe 13 is reserved in the supply-side side flow path 124b and flows into the discharge-side side flow path 124c through the intermediate flow path 124a, and is discharged from the discharge pipe 14 to the outside of the heat exchanger 1. As described above, the heat of the first fluid 2 is transmitted to the inner cylinder 11 through the honeycomb structure 10. When the second fluid 3 mainly passes through the intermediate flow path 124a, heat exchange occurs between the second fluid 3 and the inner cylinder 11 (the first fluid 2).
As described above, in the present embodiment, the inner diameter of the expanded diameter peripheral wall 121 is larger than the inner diameter of the central peripheral wall 120. Therefore, the height of the intermediate flow path 124a is lower than the heights of the supply-side side flow path 12b and the discharge-side side flow path 124c. Therefore, the second fluid 3 can be thoroughly distributed in the supply-side side flow path 124b and the discharge-side side flow path 124c in the circumferential direction of the honeycomb structure 10, and the second fluid 3 that is not subjected to the heat exchange in the intermediate flow path 124a can be reduced to improve a heat exchange efficiency. The reducing of the second fluid 3 that is not subjected to the heat exchange in the intermediate flow path 124a is particularly useful for improving the heat exchange efficiency (heat recovery efficiency) at the time of a lower heat load in which the temperature of the honeycomb structure 10 is lower. The heights of the intermediate flow path 124a, the supply-side side flow path 124b, and the discharge-side side flow path 124c can be defined by a distance between the outer peripheral surface of the inner cylinder 11 and the inner peripheral surface of the outer cylinder 12 in the normal direction of the outer peripheral surface of the inner cylinder 11.
Since the height of the intermediate flow path 124a is lower than the heights of the supply-side side flow path 124b and the discharge-side side flow path 124c, the flow rate of the second fluid 3 at the outer peripheral position of the honeycomb structure 10 can be improved.
That is, a volumetric flow rate [m3/s] is expressed by product of a flow path cross-sectional area [m2] and a flow rate [m/s] as shown in the following equation:
Volumetric flow rate [m3/s]=flow path cross-sectional area [m2]×flow rate [m/s]
In the absence of leakage, the volumetric flow rates [m3/s] flowing through one cross section in the intermediate flow path 124a and one cross section in the supply-side side flow path 124b are the same as each other. When a fluid is to flow through one cross section in the intermediate flow path 124a and one cross section in the supply-side side flow path 124b at the same flow rate, one cross section in the intermediate flow path 124a is smaller than one cross section in the supply-side side flow path 124b, so that the fluid flows more quickly in one cross section in the intermediate flow path 124a. Therefore, as described above, the flow rate of the second fluid 3 at the outer peripheral position of the honeycomb structure 10 is improved.
In the intermediate flow path 124a, the second fluid 3 flows in parallel to the first fluid 2. In other words, the second fluid 3 flows in the axial direction 10c of the honeycomb structure 10 in the intermediate flow path 124a. Although it is preferable that the second fluid 3 linearly flows in the axial direction 10c from the supply-side side flow path 124b toward the discharge-side side flow path 124c, the second fluid 3 may flow in a spiral manner in the axial direction 10c and the circumferential direction of the honeycomb structure 10 from the supply-side side flow path 124b to the discharge-side side flow path. That is, the flowing of the second fluid 3 in parallel to the first fluid 2 include not only the linearly flowing of the second fluid 3 in the axial direction 10c, but also the spiral flowing of the second fluid 3.
The height of the intermediate flow path 124a is set so as to reduce the second fluid 3 that is not subjected to the heat exchange. The height of the intermediate flow path 124a is preferably 0.2 mm or more and 33 mm or less. The height of the intermediate flow path 124a is a total value of the heights of a main flow path 124a1 and a sub flow path 124a2 which will be described below.
The magnification of the heights of the supply-side side flow path 124b and the discharge-side side flow path 124c to the height of the intermediate flow path 124a are set such that the second fluid 3 is allowable to flow in the supply-side side flow path 124b and the discharge-side side flow path 124c in the circumferential direction of the honeycomb structure 10. Further, the magnification is set such that the second fluid 3 flows smoothly in the intermediate flow path 124a from the supply-side side flow path 124b toward the discharge-side side flow path 124c. As the magnification of the heights of the supply-side side flow path 124b and the discharge-side side flow path 124c to the height of the intermediate flow path 124a are larger, the pressure loss of the supply-side side flow path 124b in the circumferential direction is decreased, so that the second fluid 3 can flow uniformly in the supply side-side flow path 124b. As a result, the second fluid 3 can flow uniformly in the intermediate flow path 124a in the circumferential direction. Further, since the pressure loss relating to the flow of the second fluid 3 from the intermediate flow path 124a to the discharge-side flow path 124c is reduced, the warmed second fluid 3 can be discharged in a shorter period of time from the intermediate flow path 124a to the discharge-side side flow path 124c, so that the heat collection efficiency can be improved. The heights of the supply-side side flow path 124b and the discharge-side side flow path 124c are preferably 1.1 times or more the height of the intermediate flow path 124a, and more preferably 3 times or more the height of the intermediate flow path 124a. If the magnification of the heights of the supply-side side flow path 124b and the discharge-side side flow path 124c to the height of the intermediate flow path 124a are too large, the size and weight of the heat exchanger 1 will be increased. The upper limit of the heights of the supply-side side flow path 124b and the discharge-side side flow path 124c can be determined according to an allowable size and weight of the heat exchanger 1.
The supply-side side flow path 124b according to the present embodiment is disposed on a downstream side of the discharge-side side flow path 124c in the flow direction of the first fluid 2 (the direction from the first end face 10a toward the second end face 10b of the honeycomb structure 10). That is, in the present embodiment, the second fluid 3 is reversed to the first fluid 2 in the intermediate flow path 124a. Therefore, as the second fluid 3 moves in the axial direction 10c, the second fluid 3 can exchange the heat to the first fluid 2 having a higher temperature, so that the heat exchange efficiency can be improved.
<Regarding Intermediate Cylinder>
The intermediate cylinder 15 according to the present embodiment is a cylindrical member disposed between the inner cylinder 11 and the outer cylinder 12 on the outer periphery of the honeycomb structure 10. The axial direction of the intermediate cylinder 15 according to this embodiment agrees with the axial direction 10c of the honeycomb structure 10. It is preferable that the central axis of the intermediate cylinder 15 coincides with the central axis of the honeycomb structure 10. In the axial direction 10c of the honeycomb structure 10, the intermediate cylinder 15 is longer than the honeycomb structure 10. It is preferable that the center positions of the honeycomb structure 10 and the intermediate cylinder 15 in the axial direction 10c of the honeycomb structure 10 are coincident with each other.
As particularly shown in
When the second fluid 3 in a liquid phase is filled in the sub flow path 124a2, the heat of the first fluid 2 transmitted to the inner cylinder 11 through the honeycomb structure 10 is transmitted to the second fluid 3 in the main flow path 124a1 through the second fluid 3 in the sub flow path 124a2. On the other hand, when the temperature of the inner cylinder 11 is higher and vapors (bubbles) of the second fluid 3 is generated in the sub flow path 124a2, any heat conduction to the second fluid 3 in the main flow path 124a1 through the second fluid 3 in the sub flow path 124a2 is suppressed. This is because thermal conductivity of a fluid in a gas phase is lower than that of a liquid in a liquid phase. That is, in the heat exchanger 1 according to the present embodiment, a state where the heat exchange is efficiently performed and a state where heat exchange is suppressed are switched depending on whether or not the vapors of the second fluid 3 are generated in the sub flow path 124a2. That state of heat exchange does not require any external control. As the second fluid 3, it is preferable to use a fluid having a boiling point in a temperature range where it is desired to suppress the heat exchange.
The height of the sub flow path 124a2 is lower than the height of the main flow path 124a1. It is preferable that the height of the main flow path 124a1 is 0.15 mm or more and 30 mm or less, the height of the sub flow path 124a2 is 0.05 mm or more and 3 mm or less, and a ratio of the height of the main flow path 124a1 to the height of the sub flow path 124a2 (=the height of the main flow path 124a1/the height of the sub flow path 124a2) is 1.6 or more and 10 or less.
If the height of the main flow path 124a1 is less than 0.15 mm, a heat shielding property is decreased. That is, since the inflow of the second fluid 3 into the sub flow path 124a2 is increased, it is difficult for the second fluid 3 in the gas phase to stay in the sub flow path 124a2, so that the heat exchange cannot be effectively suppressed by the second fluid 3 in the gas phase. Further, the heights of the main flow path 124a1 and the sub flow path 124a2 become close to each other, which will tend to be affected by eccentricity or the like of the intermediate cylinder 15.
On the other hand, if the height of the main flow path 124a1 is more than 30 mm, the heat recovery performance is lowered. That is, an amount of the second fluid 3 that is not subjected to the heat exchange is increased, so that the temperature of the second fluid 3 is hardly increased.
Further, if the height of the sub flow path 124a2 is less than 0.05 mm, the heat shielding property is lowered. That is, if the inner cylinder 11 and the intermediate tube 15 are too close to each other, the heat of the inner cylinder 11 is transferred to the intermediate cylinder 15, so that the heat conduction cannot effectively suppressed by the second fluid 3 in the gas phase in the sub flow path 124a2.
On the other hand, if the height of the sub flow path 124a2 is more than 3 mm, the heat recovery performance is lowered. That is, if the space between the inner cylinder 11 and the intermediate cylinder 15 is too wide, the temperature of the second fluid 3 in the sub flow path 124a2 is hardly increased, so than it is also difficult to increase the temperature of the second fluid 3 in the main flow path 124a1.
The heat shielding performance on the vertical axis in
On the other hand, when the ratio of the height of the main flow path 124a1 to the height of the sub flow path 124a2 is more than 10, the heat recovery performance is deteriorated as shown in
As particularly shown in
The heat exchanger 1 according to the present embodiment is configured such that the second fluid 3 flows in and out of the sub flow path 124a2 through the opening portions 150 between the end portion of the intermediate cylinder 15 and the inner cylinder 11. In other words, in the heat exchanger 1 according to the present embodiment, no opening portion is provided in the peripheral wall of the intermediate cylinder 15. However, the heat exchanger 1 may be configured such that the second fluid 3 flows in the sub flow path 124a2 through the opening portion provided in the peripheral wall of the intermediate cylinder 15.
As particularly shown in
It is preferable that an area of the opening portion 150 to the entire area between the end portion of the intermediate cylinder 15 and the inner cylinder 11 in the plane orthogonal to the axial direction 10c of the honeycomb structure 10 is 1% or more and 50% or less.
If the area ratio is less than 1%, the heat recovery performance is lowered. That is, the inflow of the second fluid 3 into the sub flow path 124a2 is decreased, and the second fluid 3 in the gas phase tends to be generated in the sub flow path 124a2. Therefore, it tends to be in a state of suppressing the heat exchange, so that the temperature rise of the second fluid 3 in the main flow path 124a1 is easily hindered.
On the other hand, if the area ratio is more than 50%, the heat shielding performance is deteriorated. That is, the inflow of the second fluid 3 into the sub flow path 124a2 is increased, so that even if the second fluid 3 in the gas phase is generated in the sub flow path 124a2, it is difficult for the fluid 3 in the gas phase to stay in the sub flow path 124a2. Therefore, the heat exchange cannot be effectively suppressed by the second fluid 3 in the gas phase.
It is more preferable that the area of the opening portions 150 to the entire area between the end portion of the intermediate cylinder 15 and the inner cylinder 11 is 2% or more and 30% or less. This is because deterioration of the heat recovery performance and deterioration of the heat shielding performance can be more reliably avoided.
<Regarding Spacer>
The spacer 16 according to the present embodiment is configured to ensure a space between the intermediate cylinder 15 and the inner cylinder 11 and is provided between the intermediate cylinder 15 and the inner cylinder 11. The spacer 16 of the present embodiment is composed of a member different from the intermediate cylinder 15 and the inner cylinder 11. Both ends of the spacer 16 in the radial direction of the honeycomb structure 10 are brought into contact with the intermediate cylinder 15 and the inner cylinder 11, so that a space is ensured between the intermediate cylinder 15 and the inner cylinder 11. However, the spacer 16 may be integral with one of the intermediate cylinder 15 and the inner cylinder 11, such as a convex portion provided on the intermediate cylinder 15 or the inner cylinder 11, for example. When the spacer 16 is configured to be integral with one of the intermediate cylinder 15 and the inner cylinder 11, the tips of the spacer 16 in the radial direction of the honeycomb structure 10 are brought into contact with the others of the intermediate cylinder 15 and the inner cylinder 11, so that a space is ensured between the intermediate cylinder 15 and the inner cylinder 11.
It is preferable that the spacer 16 extends over the entire circumferential direction of the honeycomb structure 10. The spacer 16 may be formed by one member which continuously extends over the entire circumferential direction of the honeycomb structure 10 or may be formed by a plurality of members arranged adjacent to each other or spaced apart from each other in the circumferential direction of the honeycomb structure 10.
The spacer 16 according to the present embodiment includes first and second spacers 161, 162 which are spaced apart from each other in the axial direction 10c of the honeycomb structure 10 and are provided between the intermediate cylinder 15 and the inner cylinder 11. In the present embodiment, the first spacer 161 is disposed on the first end face 10a side of the honeycomb structure 10, and the second spacer 162 is disposed on the second end face 10b side of the honeycomb structure 10.
The first and second spacers 161, 162 according to the present embodiment are disposed outside the first and second end faces 10a, 10b of the honeycomb structure 10 in the axial direction 10c of the honeycomb structure 10. In other words, when the first and second spacers 161, 162 are viewed along the radial direction of the honeycomb structure 10, the first and second spacers 161, 162 are arranged such that the first and second spacers 161, 162 do not overlap with the honeycomb structure 10, and further the second spacers 161, 162 do not contact the honeycomb structure 10. By disposing the first and second spacers 161, 162 at such positions, it can be difficult for the heat of the honeycomb structure 10 to be transmitted to the intermediate cylinder 15 through the first and second spacers 161, 162. When the heat of the honeycomb structure 10 is transmitted to the intermediate cylinder 15 through the first and second spacers 161, 162, the effect of suppressing the heat exchange by the second fluid 3 in the gas phase will be reduced.
It is preferable that the first and second spacers 161, 162 are disposed at positions spaced apart from the first and second end faces 10a, 10b of the honeycomb structure 10 in the axial direction 10c of the honeycomb structure 10 by a distance greater than 0 mm and 10 mm or less.
If the distance from the first and second end faces 10a, 10b to the first and second spacers 161, 162 is 0 mm, the heat shielding performance is deteriorated. This is because the heat of the honeycomb structure 10 is transmitted to the intermediate cylinder 15 through the first and second spacers 161, 162.
On the other hand, if the distance from the first and second end faces 10a, 10b to the first and second spacers 161, 162 is more than 10 mm, the dimensions of the heat exchanger 1 become unnecessarily large. This is because the effect of suppressing the heat conduction through the spacer 16 does not vary even if the distance of more than 10 mm is ensured.
Further, when the protruding portions 110 are provided on the inner peripheral surface of the inner cylinder 11 as in the heat exchanger 1 of the present embodiment, the first and second spacers 161, 162 are preferably arranged on an outer side than the protruding portions in the axial direction 10c of the honeycomb structure 10. Again, this is to prevent the heat of the honeycomb structure 10 from being transmitted to the first and second spacers 161, 162 through the protruding portions 110. It is preferable that the spaced distance between the protruding portion 110 and the first and second spacers 161, 162 in the axial direction 10c of the honeycomb structure 10 is greater than 0 mm and 10 mm or less.
The spacers 16 (the first and the second spacers 161, 162) of the present embodiment each has a three-dimensional structure which allows passage of the second fluid 3 in the liquid phase and inhibits passage of bubbles of the second fluid 3. Such a three-dimensional structure includes a mesh structure (a network structure) or a sponge-like structure (a porous structure). The phrase “the spacer 16 allows passage of the second fluid 3 in the liquid phase” means that the second fluid 3 can pass through the spacer 16, and the spacer 16 may be resistance to the passage of the second fluid 3. The phrase “the spacer 16 inhibits passage of bubbles of the second fluid 3” includes the meanings that the air bubbles of the second fluid 3 adhere to the spacer 16 and the spacer 16 will be resistance during the movement of the air bubbles of the second fluid 3. It is preferable that the spacer 16 has a mesh structure for the reason that it is easy to compatibly establish the liquid passage allowable property of the second fluid 3 and the bubble permeation inhibiting property of the second fluid 3.
The spacer 16 (the first and the second spacers 161, 162) according to the present embodiment is formed between the end portion of the intermediate cylinder 15 and the inner cylinder 11 such that the second fluid 3 which goes in and out the sub flow path 124a2 through the opening portions 150 passes through the spacer 16.
When the major part in the sub flow path 124a2 is filled with the second fluid 3 in the gas phase, the temporary flowing of a large amount of the second fluid 3 into the sub flow path 124a2 results in rapid generation of boiling vaporization of the second fluid 3. Such rapid boiling vaporization of the second fluid 3 will cause vibrations and noises. The spacer 16 acts as resistance against the passage of the second fluid 3 in the liquid phase, so that the inflow of the second fluid 3 into the sub flow path 124a2 becomes gentle, and generation of vibrations and noises can be suppressed.
The spacer 16 hinders the passage of the air bubbles of the second fluid 3, so that the second fluid 3 in the gas phase accumulates in the sub flow path 124a2 and suppression of the heat exchange by the second fluid 3 in the gas phase is more reliably exerted. To suppress the heat exchange more reliably, a porosity of the spacer 16 is preferably 20% or more, and more preferably 40% or more, and even more preferably 60% or more. Further, the porosity of the spacer 16 is preferably 98% or less, and more preferably 95% or less, and even more preferably 90% or less. In the present invention, the porosity of the spacer 16 is measured by the following procedure:
(1) A true density of a material making up the spacer is obtained by the Archimedes method.
(2) A bulk density was determined from an apparent volume of the spacer calculated from outer dimensions (thickness, longitudinal and lateral lengths) of the spacer and the weight of the spacer.
(3) The porosity is calculated using the relational expression: porosity=(1−bulk density/true density)×100%.
<Regarding Cover>
The covers 17 according to the present embodiment are tubular bodies arranged on an upstream side and a downstream side of the honeycomb structure 10 in the flow direction of the first fluid 2. Each cover 17 is inserted into an inner side of the inner cylinder 11 and covers the inner cylinder 11 so as to prevent the flow of the first fluid 2 from being directly contacted with the inner cylinder 11.
It is preferable that a spaced distance between the end of each cover 17 and each of the first and second end faces 10a, 10b of the honeycomb structure 10 is 2 mm or more and 10 mm or less. The spaced distance is a distance along the axial direction 10c of the honeycomb structure 10.
If the spaced distance is less than 2 mm, the recovery performance of heat will be decreased. That is, the inflow of the first fluid 2 into the honeycomb structure 10 is limited by the covers 17, so that it is difficult to increase the temperature of the honeycomb structure 10.
On the other hand, if the spaced distance is more than 10 mm, the heat shielding performance will be deteriorated. That is, the direct contact of the flow of the first fluid 2 results in an increased temperature of the inner cylinder 11, so that the heat conduction cannot be effectively suppressed by the second fluid 3 in the gas phase in the sub flow path 124a2.
A diameter (an inner diameter) of each cover 17 is preferably 0.6 times or more and 0.95 times or less a diameter (an outer diameter) of the honeycomb structure 10.
If the diameter of each cover 17 is less than 0.6 times the diameter of the honeycomb structure 10, the heat recovery performance will be deteriorated. The heat shielding performance will be deteriorated. That is, the inflow of the first fluid 2 into the honeycomb structure 10 is limited by the covers 17, so that it is difficult to increase the temperature of the honeycomb structure 10.
On the other hand, if the diameter of each cover 17 is more than 0.95 times the diameter of the honeycomb structure 10, the heat shielding performance will be deteriorated. That is, the temperature of the inner cylinder 11 is increased by transmission of the heat of the cover 17, so that the heat conduction cannot be effectively suppressed by the second fluid 3 in the gas phase in the sub flow path 124a2.
Each cover 17 is supported by a cone 170. The cone 170 is a tubular member disposed outside the cover 17 in the radial direction of the cover 17. The cone 170 according to the present embodiment has a peripheral wall having a cross section in a crank shape. One end 170a of the cone 170 is positioned radially outward of the cone 170 and the other end 170b of the cone 170 is positioned radially inward of the cone 170. Each cover 17 is fixed to the other end 170b by welding or the like while being brought into surface contact with the other end 170b of the cone 170.
One end 170a of the cone 170 according to the present embodiment is fixed to the outer cylinder 12. More particularly, one end 170a of the cone 170 is in contact with an end wall 123 of the outer cylinder 12, and is fixed to the end wall 123 by a method such as welding. One end 170a of the cone 170 is fixed to a radially outer side of the outer cylinder 12 so as to be away from the inner cylinder 11. It is understood that the radially outer side of the outer cylinder 12 is a position closer to the expanded diameter peripheral wall 121 than the central position of the end wall 123 in the radial direction of the cone 170. If one end 170a of the cone 170 is fixed to the end portion of the inner cylinder 11, the cone 170 suppresses the expansion of the inner cylinder 11 when reaching an elevated temperature of the inner cylinder 11, so that the inner cylinder 11 may be bent. The bending of the inner cylinder 11 may generate positional deviation in each portion and deteriorate the performance of the heat exchanger 1. To suppress such deterioration of the performance, as described above, one end 170a of the cone 170 is preferably fixed to the outer cylinder 12, more preferably, it is fixed to the radially outer side of the outer cylinder 12.
Next,
As shown in
The second side portion 153 according to the present embodiment is overlaid on the first side portion 152 and positioned radially outward of the intermediate cylinder 15. As shown in
In the heat exchanger 1 according to the present embodiment, the height of the intermediate flow path 124a is lower than the heights of the supply-side side flow path 124b and the discharge-side side flow path 124c, so that the second fluid 3 can be thoroughly distributed in the supply-side side flow path 124b and the discharge-side side flow path 124c in the circumferential direction of the honeycomb structure 10 and the second fluid 3 which is not subjected to the heat exchange in the intermediate flow path 124a can be reduced, thereby enabling the heat exchange efficiency to be improved. The configuration is particularly useful for improving the heat exchange efficiency (the heat recovery efficiency) at a lower load in which the temperature of the honeycomb structure 10 is low.
Further, in the heat exchanger 1 according to the present embodiment, the second fluid 3 flows in parallel with the first fluid 2, so that the second fluid 3 which is not subjected to the heat exchange in the intermediate flow path 124a can be decreased and the heat exchange efficiency can be improved. Furthermore, the warmed second fluid 3 can be discharged in a shorter period of time and the heat collection efficiency can be improved.
Further, in the heat exchanger 1 according to the present embodiment, the supply-side side flow path 124b is disposed on the downstream side of the discharge-side side flow path 124c in the flow direction of the first fluid 2, so that the second fluid 3 can be reversed against the first fluid 2 in the intermediate flow path 124a, and as the second fluid 3 moves in the axial direction 10c, the second fluid 3 exchanges heat to the first fluid 2 having a higher temperature (the inner cylinder 11), thereby enabling the heat exchange efficiency to be improved.
Furthermore, in the heat exchanger 1 according to the present embodiment, the height of the main flow path 124a1 is 0.15 mm or more and 30 mm or less, the height of the sub flow path 124a2 is 0.05 mm or more and 3 mm or less, and the ratio of the height of the main flow path 124a1 to the height of the sub flow path 124a2 is 1.6 or more and 10 or less, so that both of the heat shielding performance and the heat recovery performance can be more reliably achieved.
Further, in the heat exchanger 1 according to the present embodiment, at least one opening portion 150 that is in communication with the sub flow path 124a2 is provided between the end portion of the intermediate cylinder 15 and the inner cylinder 11, so that vapors (air bubbles) of the second fluid 3 generated in the sub flow path 124a2 can be easily reserved in the sub flow path 124a2. This can allow an increase in a vapor layer of the second fluid 3 in the sub flow path 124a2, thereby improving the heat shielding performance.
Furthermore, in the heat exchanger 1 according to the present embodiment, the area of the opening portion 150 to the entire area between the end of the intermediate cylinder 15 and the inner cylinder 11 in the plane orthogonal to the axial direction 10c of the honeycomb structure 10 is 1% or more and 50% or less, so that both of the heat recovery performance and the heat shielding performance can be more reliably achieved.
Moreover, in the heat exchanger 1 according to the present embodiment, the spacer 16 is disposed outside the first and second end faces 10a, 10b of the honeycomb structure 10 in the axial direction 10c of the honeycomb structure 10, so that the heat of the honeycomb structure 10 can be prevented from being transmitted to the intermediate cylinder 15 through the spacer 16, thereby enabling the heat shielding performance to be improved.
Further, in the heat exchanger 1 according to the present embodiment, the spacer 16 is disposed at a position that is spaced apart from the end face of the honeycomb structure by a distance of more than 0 mm and not more than 10 mm in the axial direction 10c of the honeycomb structure 10, so that the deterioration of the heat shielding performance can be prevented and an unnecessarily increase in the size of the heat exchanger 1 can be avoided.
Furthermore, the spacer 16 has a three-dimensional structure that allows passage of the second fluid 3 in the liquid phase and inhibits passage of air bubbles of the second fluid 3, so that the inflow of the second fluid 3 can be gentle, thereby suppressing generation of vibrations and noises. In addition, the second fluid 3 in the vapor phase can be easily reserved in the sub flow path 124a2, and the suppression of the heat exchange by the second fluid 3 in the vapor phase can be more reliably exerted.
As in the Embodiment 2, the supply-side side flow path 124b may be disposed on the upstream side of the discharge-side side flow path 124c in the flow direction of the first fluid 2.
In the step shown in
In the step shown in
If both of the first and second spacers 161, 162 are fixed to both of the intermediate cylinder 15 and the inner cylinder 11, respectively, the following phenomenon may occur. That is, when the vapors (air bubbles) of the second fluid 3 is generated in the sub flow path 124a2 and the heat exchange between the second fluid 3 in the sub flow path 124a2 and the second fluid 3 in the main flow path 124a1 is suppressed, a temperature difference is generated between the inner cylinder 11 and the intermediate cylinder 15. In this case, the inner cylinder 11 is heated by the heat of the first fluid 2, while the intermediate cylinder 15 is cooled by the second fluid 3 in the main flow path 124a1, so that the inner cylinder 11 expands more than the intermediate cylinder 15. When both of the first and second spacers 161, 162 are fixed to both of the intermediate cylinder 15 and the inner cylinder 11, respectively, the fixing portions of the first and second spacers 161, 162 are broken due to stress caused by a difference in expansion between the intermediate cylinder 15 and the inner cylinder 11 to deviate the positional relationship between the intermediate cylinder 15 and the inner cylinder 11, so that the sub flow path 124a2 is lost.
As in Embodiment 3, the second spacer 162 is fixed to both of the intermediate cylinder 15 and the inner cylinder 11, while the first spacer 161 is fixed to the inner cylinder 11 and is not fixed to the intermediate cylinder 15, thereby enabling prevention of the phenomenon that the fixing portions of the first and second spacers 161, 162 are broken due to the stress caused by the difference in expansion between the intermediate cylinder 15 and the inner cylinder 11 to deviate he positional relationship between the intermediate cylinder 15 and the inner cylinder 11 and the sub flow path 124a2 is lost.
As shown in
The outer cylinder 12 according to Embodiment 4 has a shape that is symmetrical using the center position in the axial direction of the outer cylinder 12 as a center. That is, the shapes and inner diameters of the straight peripheral wall 123a and the connecting peripheral wall 123b on one end side in the axial direction of the outer cylinder 12 are the same as the shapes and inner diameters of the straight peripheral wall 123a and the connecting peripheral wall 123b on the other end side in the axial direction of the outer cylinder 12.
One end 170a of a cone 170 according Embodiment 4 linearly extends along the extending direction of the outer peripheral surface of the straight peripheral wall 123a. An inner peripheral surface of one end 170a of the cone 170 is in contact with an outer peripheral surface of the straight peripheral wall 123a. That is, one end 170a of the cone 170 is in surface contact with the end portion (the straight peripheral wall 123a) of the outer cylinder 12. In such a state, one end 170a of the cone 170 is fixed to the straight peripheral wall 123a (the outer cylinder 12). Other configurations are the same as those in Embodiments 1-3.
In the heat exchanger 1 according to Embodiment 4, one end of the cone 170 extends along the extending direction of the outer peripheral surface of the end portion (the straight peripheral wall 123a) of the outer cylinder 12 and is fixed to the end portion of the outer cylinder 12 while being in surface contact with the end portion of the outer cylinder 12, so that the fixing region between the cone 170 and the outer cylinder 12 can be expanded as compared with Embodiment 1 where one end of the cone 170 is fixed while abutting against the outer cylinder 12. This can allow the possibility of breakage of the fixing portion between the cone 170 and the outer cylinder 12 to be decreased.
As shown in
In the heat exchanger 1 according to Embodiment 5, the inner diameter of the outer cylinder 12 on one end side in the axial direction is larger than the inner diameter of the outer cylinder 12 on the other end side in the axial direction, so that the heat exchanger element body and the outer cylinder 12 can be more easily assembled.
As shown in
Next,
First, an element 60 in which the honeycomb structure 10 is fitted into the inner cylinder 11 is prepared, as shown in
Then, as shown in
Then, as shown in
Then, as shown in
In the heat exchanger 1 according to Embodiment 6, the enlarged diameter portion 11a with a diameter enlarged so as to be in contact with one end side of the outer cylinder 12 in the axial direction is provided at one end of the inner cylinder 11, so that any cap member 18 according to Embodiment 5 cannot be required and the number of parts can be reduced. Further, the enlarged diameter portion 11a is provided at a position that is not in contact with the honeycomb structure 10, so that an expansion margin of the inner cylinder 11 can be ensured when reaching an elevated temperature of the inner cylinder 11. The expansion of the inner cylinder 11 is escaped by the expansion margin of the inner cylinder 11 when reaching the elevated temperature of the inner cylinder 11, so that it is possible to suppress a decrease in the heat recovery efficiency of the heat exchanger 1 at the elevated temperature due to the distortion of the inner cylinder 11. Further, the enlarged diameter portion 11a is provided at one end of the inner cylinder 11, so that it is difficult for errors of the positions and the insertion directions of the members to be formed to occur, and it is easy to assemble the members, and it is thus easy to be produced.
Any arrangement of the turbulent flow generating portions 7 in the circumferential direction and the axial direction of the honeycomb structure 10 is possible. In terms of increasing the effect of the turbulent flow, the turbulent flow generating portions 7 are preferably arranged on the upstream side of the second flow path 124 in the flow direction of the second fluid 3. One turbulent flow generating portion 7 may be provided continuously in the circumferential direction of the honeycomb structure 10 or a plurality of turbulent flow generating portions 7 may be spaced apart from each other in the circumferential direction of the honeycomb structure 10. Further, the turbulent flow generating portion 7 may be arranged in a spiral shape. Other configurations are the same as those in Embodiments 1-6.
In the heat exchanger 1 according to Embodiment 7, at least one of the inner cylinder 11, the outer cylinder 12 and the intermediate cylinder 15 includes at least one turbulent flow generating portion 7 for generating the turbulent flow in the second fluid 3 passing through the second flow path 124, so that the heat exchange efficiency between the first fluid 2 and the second fluid 3 can be improved.
The frame 81 is a member integrated with the outer cylinder 12 by, for example, welding or the like. The frame 81 may be added to the configurations of Embodiments 1-7 or it may be formed by modifying the cones 170 in Embodiments 1-7.
The purifier 80 is a member for purifying the first fluid 2 before being introduced into the honeycomb structure 10. The purifier 80 is not particularly limited, and any known purification means in the art may be used. Examples of the purifier 80 include a catalyst body supporting a catalyst, a filter and the like. Examples of the catalyst that can be used when exhaust gas is used as the first fluid 2 include a catalyst having a function of oxidizing or reducing an exhaust gas. The catalyst includes noble metals such as platinum, rhodium, palladium, ruthenium, indium, silver and gold; aluminum, nickel, zirconium, titanium, cerium, cobalt, manganese, zinc, copper, tin, iron, niobium, magnesium, lanthanum, samarium, bismuth, barium and the like. These elements may be metal simple substances, metal oxides, and other metal compounds. Further, the catalyst may be used alone or two or more catalysts may be used. Other configurations are the same as those in the Embodiments 1-7.
In the heat exchanger 1 according to Embodiment 8, the purifier 80 disposed on the upstream side of the honeycomb structure 10 into the flow direction of the first fluid 2 is supported by the frame 81 provided integrally with the outer cylinder 12, so that it is possible to eliminate the necessity of connecting the heat exchanging member 82 and the purifying means 80 by piping and it is possible to save the space.
In the heat exchanger 1 according to Embodiment 9, the heat exchange member 82 is disposed on the upstream side of the purifier 80 in the flow direction of the first fluid 2, thereby allowing the heat exchange between the first fluid 2 having a higher temperature before removing the heat by the purifier 80 and the second fluid 3, and enabling the heat exchange efficiency to be improved.
In the heat exchanger 1 according to Embodiment 10, the heat exchange member 82 is disposed between the first and second purified bodies 80a, 80b, so that it is possible to achieve both of improvement of the heat exchange efficiency and the purification performance of the first fluid 2.
In the heat exchanger 1 according to Embodiment 11, the plurality of heat exchange members 82 are integrated with one or more purifiers 80, so that the heat exchange efficiency can be further improved.
| Number | Date | Country | Kind |
|---|---|---|---|
| JP2018-069609 | Mar 2018 | JP | national |
| JP2018-238821 | Dec 2018 | JP | national |
| Number | Name | Date | Kind |
|---|---|---|---|
| 9624814 | Mitsuda | Apr 2017 | B2 |
| 20090136710 | Ichikawa | May 2009 | A1 |
| 20120222838 | Hisanaga | Sep 2012 | A1 |
| 20120247732 | Suzuki | Oct 2012 | A1 |
| 20140326438 | Seryi | Nov 2014 | A1 |
| 20150292812 | Tomita | Oct 2015 | A1 |
| 20160341489 | Ichiyanagi | Nov 2016 | A1 |
| Number | Date | Country |
|---|---|---|
| 2012-037165 | Feb 2012 | JP |
| Number | Date | Country | |
|---|---|---|---|
| 20190301807 A1 | Oct 2019 | US |
