JP7016692B2 - Ceramic heat exchanger - Google Patents

Description

The present invention relates to a ceramic heat exchanger.

As a heat exchanger that applies heat from a high-temperature fluid such as exhaust gas discharged from an industrial furnace to a low-temperature fluid, a structure in which a ceramic wall separates two orthogonal channels has been proposed (for example). , Patent Documents 1 and 2). The structure of Patent Document 1 is a structure in which a plurality of plates having a large number of ribs protruding in one direction from a ceramic flat plate are laminated so that the directions of the ribs intersect. In such a configuration, focusing on a flat plate, a first flow path formed between the ribs on one side of the flat plate and between the ribs on the other side. The second flow path is orthogonal to each other, and heat exchange is performed through the flat plate between the first fluid flowing through the first flow path and the second fluid flowing through the second flow path. Will be.

The structure of Patent Document 2 is a ceramic honeycomb structure having a large number of cells penetrating in one direction, and both ends of each cell are sealed at every other stage to form a sealing portion and sealed. A slit penetrating in a direction orthogonal to the cell is formed by drilling the partition wall of the cell of the stage from a right angle direction except for the sealing portion and its vicinity. In such a configuration, heat is exchanged between the first fluid flowing through the cell penetrating the cell without sealing portions at both ends and the second fluid flowing through the slit orthogonal to the cell through the partition wall. Is done.

For heat exchangers, there is always a demand for higher heat exchange rates. Further, in the heat exchanger that exchanges heat through the ceramic wall as described above, it is desirable to reduce the thickness of the wall in order to increase the heat exchange rate, but this may reduce the mechanical strength. When the heat exchanger is housed in a casing so that it is tightened through a sealant to prevent mixing of the two fluids that are heat exchanged and leakage of the fluid to the outside when the mechanical strength is reduced, the heat exchanger May be damaged.

Japanese Unexamined Patent Publication No. 55-35897 Japanese Unexamined Patent Publication No. 61-24997

Therefore, in view of the above circumstances, the present invention is a heat exchanger in which a ceramic wall separates two orthogonal channels, and the heat exchange rate can be increased and the mechanical strength can be increased. The subject is to provide a ceramic heat exchanger.

In order to solve the above problems, the ceramic heat exchanger according to the present invention (hereinafter, may be simply referred to as “heat exchanger”) is
"A first flow path that penetrates in the first direction and is closed in the second direction orthogonal to the first direction, and a second flow path that penetrates in the second direction and is closed in the first direction. Provided a ceramic heat exchanger that is adjacent via a wall in the first direction and the third direction orthogonal to the second direction.
In the heat exchanger, a heat insulating layer in which air is held in a closed space is laminated on the two end faces intersecting in the third direction. "

With this configuration, the first fluid is circulated in the first flow path, and the second fluid is circulated in the second flow path, so that heat is exchanged between the first fluid and the second fluid through the wall body. can.

Here, both end faces intersecting in the first direction are surfaces for opening the first flow path, while end faces intersecting in the second direction are surfaces for opening the second flow path. Both end faces that intersect in three directions are faces that are not used for heat exchange. In this configuration, an air-retaining heat insulating layer is laminated on such an end face. Therefore, the heat exchanged because the heat insulating layer suppresses the heat held by the high-temperature fluid on the heat-giving side and the heat given to the fluid on the low-temperature side from being released to the outside of the heat exchanger. The rate can be increased.

Further, the heat exchanger in which the first flow path penetrating in the first direction and the second flow path penetrating in the second direction are adjacent to each other is a structure that is open in two directions. The heat exchanger of this configuration is provided with a heat insulating layer, which is a closed space, where the mechanical strength tends to be low. Therefore, the presence of the heat insulating layer can increase the mechanical strength of the heat exchanger.

The ceramic heat exchanger according to the present invention has the above configuration.
"The insulation layer is formed by a plurality of cells partitioned by a single axially extending partition wall, each sealed with a sealant at both ends in the axial direction . " .. Alternatively, "the heat insulating layer has slits formed by arranging a plurality of long rod-shaped spacers having the same longitudinal direction at intervals between adjacent flat plates, and a sealing material is provided at both ends in the longitudinal direction. It is formed by being sealed with . "

With such a configuration, a heat insulating layer having a large space for holding air can be easily manufactured.

In addition to the above configuration, the ceramic heat exchanger according to the present invention has
"Of the first flow path and the second flow path, the one adjacent to the heat insulating layer is the first flow path.
In the heat exchanger, a first fluid supply pipe for supplying the first fluid is connected to one of both end faces intersecting with the first direction, and a first fluid discharge pipe for discharging the first fluid is connected to the other. A second fluid supply pipe that supplies a second fluid having a temperature higher than that of the first fluid is connected to one of both end faces that are connected and intersects with the second direction, and the second fluid is connected to the other. It can be assumed that the second fluid discharge pipe to be discharged is connected. "

In this configuration, adjacent to the heat insulating layer in the heat exchanger is the first flow path through which the first fluid, which is the side to which heat is applied from the high temperature second fluid, flows. Therefore, the heat given can effectively retain the heat of the first fluid to be used by the heat insulating layer.

As described above, according to the present invention, the heat exchanger is a heat exchanger in which two flow paths for flowing a fluid are orthogonal to each other, and the heat exchange rate is increased and the mechanical strength is increased. Ceramic heat exchangers can be provided.

It is a perspective view of the heat exchanger which is the 1st Embodiment of this invention. It is an exploded perspective view of the heat exchanger of FIG. (A) is a front view of the heat exchanger of FIG. 1, and (b) is a side view of the heat exchanger of FIG. 1. (A) AA line sectional view, (b) BB line sectional view, and (c) CC line sectional view. (A) A perspective view of a heat exchanger of a modified example of the first embodiment, and (b) a diagram showing a temperature measurement position when the effect of a heat insulating layer is examined. It is a perspective view of the heat exchanger which is the 2nd Embodiment of this invention. It is an exploded perspective view of the heat exchanger of FIG. (A) is a front view of the heat exchanger of FIG. 6, and (b) is a side view of the heat exchanger of FIG. (A) DD line sectional view, (b) EE line sectional view, (c) FF line sectional view, and (d) GG line sectional view.

Hereinafter, the ceramic heat exchanger, which is a specific embodiment of the present invention, will be described. First, the heat exchanger 1 of the first embodiment and the heat exchanger 1b of a modified example thereof will be described with reference to FIGS. 1 to 5.

The heat exchanger 1 of the first embodiment mainly includes a heat exchanger 40 and a heat insulating layer 50. The heat exchanger 40 is made of ceramic, and has a first flow path P1 that penetrates the first direction X and is closed in the second direction Y that is orthogonal to the first direction X, and a first direction X that penetrates the second direction Y and is closed. The second flow path P2 blocked in the first direction X and the third direction Z orthogonal to the second direction Y are adjacent to each other via a wall body. Further, the heat insulating layer 50 is a layer having a closed space in which air is held, and is laminated on both end faces intersecting in the third direction Z in the heat exchanger 40.

Specifically, the heat exchanger 40 includes a plurality of cell rows 10 in which a plurality of cells 15 partitioned by a single axially extending partition wall 11a, 11b are arranged in a row, with the same axial direction. An adjacent cell row 10 has a slit 25 penetrating in a direction orthogonal to the axial direction of the cell 15.

Here, the case where the shape of the cells 15 (the outer shape of the cross section orthogonal to the axial direction) is square and each cell 15 is surrounded by two pairs of partition walls 11a and 11b is shown. The one-stage cell row 10 in which a plurality of cells 15 are arranged in a row via the partition wall 11a is between the cell row 10 and the cell row 10 in a state where the respective axial directions are aligned with the adjacent cell row 10. It is joined by a spacer 21 arranged in. The spacer 21 is an elongated square columnar, and its longitudinal direction is orthogonal to the axial direction of the cell 15. Further, here, the case where both ends of each of the adjacent cell rows 10 are joined by a pair of spacers 21 is illustrated by illustration, but the number of spacers 21 for joining the adjacent cell rows 10 is three. It may be the above.

In the heat exchanger 40 having such a configuration, if the axial direction of the cells 15 is the first direction X and the direction in which the cells 15 are arranged in the cell row 10 is the second direction Y, each cell 15 is in the first direction. It is a first flow path P1 that penetrates X and is closed in the second direction Y by the partition wall 11a. On the other hand, the slit 25 formed between the adjacent spacers 21 and the partition wall 11b of each of the adjacent cell rows 10 penetrates in the second direction Y and is closed in the first direction X by the spacer 21. This is the second flow path P2. Then, the cell 15 which is the first flow path P1 and the slit 25 which is the second flow path P2 are adjacent to each other in the third direction Z via the partition wall 11b. Therefore, in the present embodiment, the partition wall 11b corresponds to a "wall body" interposed between the first flow path P1 and the second flow path P2 adjacent to the third direction Z.

The cell row 10 in one stage can be obtained by cutting a honeycomb structure in which a plurality of cell rows 10 having a single axial direction are laminated, which is formed by general extrusion molding, one stage at a time. can. Alternatively, a one-stage honeycomb structure in which a plurality of cells 15 having a single axial direction are arranged in a row may be formed by extrusion molding. Further, the slit 25 forms a sealing portion by sealing both ends of the cell at every other stage in a general honeycomb structure in which a plurality of cell rows having a single axial direction are laminated. A cell row consisting of cells whose both ends are sealed can also be formed by cutting a partition wall in a direction orthogonal to the axial direction of the cell, except for the sealed portion and its vicinity.

On the other hand, the heat insulating layer 50 is partitioned by a single axially extending partition wall, and each consists of a plurality of cells 15 in which both ends in the axial direction are sealed by a sealing material 17. A closed space is formed between the partition walls 11a and 11b of the cell 15 and the sealing materials 17 at both ends, and air is held inside the space, so that the heat insulating layer 50 has a plurality of layers S of air. I have. The axial direction of the cell 15 constituting the heat insulating layer 50 may be the first direction X or the second direction Y, but here, the first direction X is the axial direction and both ends are sealed. An example is an example in which cell rows 10 in which the cells 15 are arranged in the second direction Y are stacked in a plurality of stages to form a heat insulating layer 50.

Also in the cell row 10 constituting the heat exchanger 40, some of the cells 15 near both ends intersecting in the second direction Y are sealed by the sealing material 17 over the entire length. As a result, the mechanical strength of the cell row 10, which is a structure supported only by the extremely thin partition wall, is increased.

Further, the heat exchanger 1 includes a first fluid supply pipe, a first fluid discharge pipe, a second fluid supply pipe, and a second fluid discharge pipe (all of which are not shown). In the heat exchanger 40, the first fluid supply pipe is connected to both end faces intersecting the first direction X, that is, both end faces on which the cell 15 is open, and the first fluid discharge pipe is connected to the other end surface. .. On the other hand, the second fluid supply pipe is connected to one of the end faces intersecting with the second direction Y, that is, both end faces in which the slit 25 is open, and the second fluid discharge pipe is connected to the other. In the heat exchanger 1 of the present embodiment, in the heat exchanger 40, the cell 15 which is the first flow path P1 is adjacent to the heat insulating layer 50, and the first fluid supply pipe is on the side where heat is applied. The fluid, that is, the fluid on the low temperature side is supplied. Therefore, the fluid on the side that gives heat, that is, the fluid having a higher temperature than the first fluid is supplied to the second fluid supply pipe.

With the above configuration, the first fluid is circulated through the cell 15 which is the first flow path P1, and the second fluid is circulated through the slit 25 which is the second flow path P2, so that the second fluid is between the first fluid and the second fluid. The heat can be exchanged via the partition wall 11b.

Further, in the heat exchanger 40, both end faces intersecting the first direction X are surfaces on which the first flow path P1 (here, the cell 15) is opened in order to allow the first fluid to pass therethrough, and the second direction Y The both end faces intersecting with the third direction Z are the surfaces on which the second flow path P2 (here, the slit 25) is opened in order to allow the second fluid to pass through, whereas the both end faces intersecting with the third direction Z allow the fluid to pass through. It is a surface that does not need to be opened to allow it to pass through. In the present embodiment, the heat insulating layer 50 is laminated on both end faces that intersect in the third direction Z, that is, end faces that have not been conventionally used for heat exchange. The heat insulating layer 50 has a plurality of layers S of air, and has high heat insulating properties. Therefore, the heat insulating layer 50 suppresses the heat held by the high-temperature second fluid and the heat given by the low-temperature first fluid from the second fluid to be released to the outside of the heat exchanger 1. Therefore, the heat exchange rate can be increased.

Further, the step of the cell 15 which is the first flow path P1 has a space penetrating in the first direction X, and the step of the slit 25 which is the second flow path P2 has a space penetrating in the second direction Y. On the other hand, since the heat insulating layer 50 is a closed space closed in all directions by the sealing material 17 and the partition walls 11a and 11b of the cell 15, the mechanical strength is high. Therefore, the presence of the heat insulating layer 50 can increase the mechanical strength of the heat exchanger 1, and heat exchange has high resistance to external forces such as tightening force when the heat exchanger 1 is housed in the casing while being sealed. It becomes vessel 1.

In addition, in the present embodiment, in the heat exchanger 40, adjacent to the heat insulating layer 50 is the cell 15, that is, the first flow path P1 through which the first fluid on the side to which heat is applied flows. Therefore, the heat given can effectively retain the heat of the first fluid to be used by the heat insulating layer 50.

Further, in the present embodiment, the first flow path P1 is a fine cell 15, while the second flow path P2 is a slit 25 having a wider internal space than the cell 15. Therefore, even if a fluid that may contain impurities such as exhaust gas and wastewater is used as the high-temperature second fluid, the possibility that the second flow path P2 is clogged is reduced. On the other hand, if a fluid containing no impurities such as air and water is used as the low-temperature first fluid, heat can be efficiently recovered by taking advantage of the cell 15 having a large surface area.

The results of actually manufacturing a heat exchanger provided with a heat insulating layer and measuring the heat insulating action and the heat exchange rate are shown. For the measurement, a heat exchanger E1 having the same configuration as the heat exchanger 1 shown in FIGS. 1 to 4 was used except for the number of cells, the number of cell rows and the number of spacer stages. The heat exchanger of the heat exchanger E1 is made of silicon carbide, and 20 cell rows and 19 pairs of spacers are laminated in a total of 38 stages so as to sandwich a pair of spacers between the cell rows. Each cell column consists of 98 cells. The size of the heat exchanger was 170 mm in the direction in which the cell and the slit were extended, and 138.7 mm in the stacking direction of the cell row and the spacer. Then, a heat insulating layer was laminated on each of the pair of end faces of the heat exchanger in which neither the cell nor the slit was opened. In each heat insulating layer, eight cell rows that are the same as the cell rows constituting the heat exchanger are laminated to have a length of 20 mm in the stacking direction, and both ends in the axial direction of all the cells are each having a length. It was formed by sealing with a sealing material in 20 mm increments. As the encapsulant, an inorganic adhesive (Sumiceram, manufactured by Asahi Chemical Co., Ltd.) containing ceramics such as silica and alumina as a main component was used. This inorganic adhesive is cured at 100 ° C to 300 ° C, and after curing, exhibits heat resistance of 1000 ° C or higher.

In order to examine the effect of the heat insulating layer, a heat exchanger E2 having a smaller heat insulating layer than the heat exchanger E1 was manufactured. The configuration of the heat exchanger E2 is the same as that of the heat exchanger 1b shown in FIG. 5A except for the number of cells 15, the number of stages of the cell row 10 and the spacer 21. The heat exchanger E2 and the heat exchanger E1 have a common heat exchanger. In the heat exchanger E1, eight cell rows are stacked to make the length in the stacking direction 20 mm, and both ends in the axial direction are sealed. In contrast to the heat exchanger E2, the heat exchanger E2 is made by stacking five cell rows to make the length in the stacking direction 13 mm, sealing both ends in the axial direction to form a heat insulating layer, and then silicon carbide. A 7 mm thick flat plate (corresponding to reference numeral 60 in FIG. 5) was bonded to make the total length 20 mm, which is the same as the heat insulating layer of the heat exchanger E1.

Air at room temperature is circulated as the first fluid in each of the heat exchangers E1 and E2, and high-temperature exhaust gas is circulated as the second fluid to exchange heat, and the outer surface temperature of the casing accommodating the heat exchanger is exchanged. Was measured with a contact thermometer. As the second fluid, exhaust gas A having an inflow temperature of 400 ° C. and exhaust gas B having an inflow temperature of 800 ° C. were used. The flow rate of the fluid was 140 m ³ N / h for both the first fluid and the second fluid (exhaust gas A and exhaust gas B). The part where the temperature was measured on the outer surface of the casing is both side surfaces of the casing covering both end faces on which the heat insulating layer is formed in the heat exchanger, and each side surface is divided into three in the flow direction of the first fluid. , The temperature was divided into two in the flow direction of the second fluid, and the temperatures of a total of 12 points were measured. Table 1 shows the outer surface temperature of the casing at each measurement position. The relationship between the numbers indicating the measurement positions in Table 1 and the positions on the side surfaces of the casing is shown in FIG. 5 (b).

From Table 1, when the inflow temperature of the second fluid is 400 ° C. and 800 ° C., the heat exchanger E1 has a surface on the outer surface of the casing as compared with the heat exchanger E2 at almost all measurement positions. It can be seen that the temperature is low. From this, it can be seen that the larger the heat insulating layer (the longer the length in the stacking direction), the larger the heat insulating effect. The temperature difference between the outer surfaces of the casings of the heat exchanger E1 and the heat exchanger E2 is 53 ° C at the maximum when the inflow temperature of the second fluid is 400 ° C, and when the inflow temperature of the second fluid is 800 ° C. The maximum temperature was 101 ° C, which was a large one.

Further, in each case where the second fluid, which is the exhaust gas A having an inflow temperature of 400 ° C., exchanges heat with the first fluid, and when the second fluid, which is the exhaust gas B having an inflow temperature of 800 ° C., exchanges heat with the first fluid, the first The outflow temperatures of the first fluid and the second fluid were measured, and the temperature efficiency of heat exchange was determined based on this. The temperature efficiency was calculated by the following formula. The results are shown in Table 2.
Temperature efficiency of the first fluid ( _Tair-out - _Tair-in ) / ( _Tex-in - _Tair-in )
Temperature efficiency of the second fluid ( _Tex-in - _Tex-out ) / ( _Tex-in - _Tair-in )
In the above formula,
T _air-in : Inflow temperature of the first fluid T _air-out : Outflow temperature of the first fluid _Tex-in : Inflow temperature of the second fluid _Tex-out : Outflow temperature of the second fluid

From Table 2, both the temperature efficiency of the first fluid and the temperature efficiency of the second fluid are higher in the heat exchanger E1 than in the heat exchanger E2, and the larger the heat insulating layer (the longer the length in the stacking direction), the more heat. It is clear that the temperature efficiency of the exchange will be high. Further, in both the heat exchanger E1 and the heat exchanger E2, the temperature efficiency of the first fluid and the temperature efficiency of the second fluid are the same regardless of whether the temperature of the second fluid is 400 ° C. or 800 ° C. It was about. Therefore, when the first fluid is at room temperature, the temperature of the second fluid is in the range of 400 ° C. to 800 ° C., and the length of the heat insulating layer in the stacking direction is 13 mm to 20 mm, the size of the heat insulating layer is about the same. For example, it was considered that heat exchange was performed with the same temperature efficiency regardless of the temperature of the second fluid. It is considered that the larger the length of the heat insulating layer in the stacking direction, the higher the heat insulating effect, and it is desirable that the heat insulating layer is 20 mm or more. The volume used for replacement is reduced. Therefore, considering both the heat insulating effect and the heat exchange rate, it is desirable that the upper limit of the length of the heat insulating layer in the stacking direction is 30 mm in the above temperature range. On the other hand, the lower limit of the length of the heat insulating layer in the stacking direction can be 2 mm for one stage of the cell.

Next, the heat exchanger 2 of the second embodiment will be described with reference to FIGS. 6 to 9. The difference between the heat exchanger 2 and the heat exchanger 1 is that the heat exchanger 40b is formed by stacking a flat plate 31 and an elongated square columnar spacer 32, and the adjacent flat plate 31 and the adjacent spacer 32 are formed. It is a point that the first flow path P1 and the second flow path P2 are formed by the slits 35 and 36 formed between them, respectively. It is also different from the heat exchanger 1 in that the heat insulating layer 50b is formed by sealing both ends of the slit in the longitudinal direction with the sealing material 37.

Specifically, the adjacent flat plate 31 and the flat plate 31 are joined by a plurality of spacers 32 having the same longitudinal direction and arranged at regular intervals, and the spacer 32 whose longitudinal direction is the first direction X is joined. The steps and the steps of the spacer 32 whose longitudinal direction is the second direction Y are joined so as to alternate with each other. As a result, the slit 35 formed between the adjacent flat plates 31 and the spacer 32 whose longitudinal direction is the first direction X penetrates the first direction X and is closed in the second direction Y by the spacer 32. Road P1. On the other hand, the second flow in which the slit 36 formed between the adjacent flat plates 31 and the spacer 32 whose longitudinal direction is the second direction Y penetrates in the second direction Y and is closed in the first direction X by the spacer 32. Road P2. The slit 35, which is the first flow path P1, and the slit 36, which is the second flow path P2, are adjacent to each other in the third direction Z via the flat plate 31. Therefore, in the present embodiment, the flat plate 31 corresponds to a "wall body" interposed between the first flow path P1 and the second flow path P2 adjacent to the third direction Z.

The heat insulating layer 50b is formed by sealing the slits formed between the adjacent flat plates 31 and the adjacent spacers 32 with the sealing material 37 at both ends in the longitudinal direction. The longitudinal direction of the slit in the heat insulating layer 50b may be either the first direction X or the second direction Y, but here, the first direction X is the longitudinal direction and both ends are sealed. An example is shown in which the heat insulating layer 50b is formed by both the slits having the second direction Y as the longitudinal direction and the slits having both ends sealed (see FIGS. 9C and 9D).

Further, in the heat exchanger 40b, of the steps of the slit 35 penetrating in the first direction X and the steps of the slit 36 penetrating in the second direction Y, the step of the slit 35 is adjacent to the heat insulating layer 50b. be. Then, the first fluid supply pipe is connected to one end surface of the heat exchanger 40b that intersects the first direction X, that is, both end faces of which the slit 35 is open, and the first fluid discharge pipe is connected to the other end surface. At the same time, the second fluid supply pipe is connected to one of the end faces intersecting with the second direction Y, that is, both end faces in which the slit 36 is open, and the second fluid discharge pipe is connected to the other. The point that the fluid on the low temperature side is the first fluid and the fluid on the high temperature side is the second fluid is the same as in the first embodiment.

With the above configuration, the first fluid is circulated through the slit 35 which is the first flow path P1, and the second fluid is circulated through the slit 36 which is the second flow path P2. The heat can be exchanged via the flat plate 31.

Further, in the heat exchanger 40b, the heat insulating layer 50b is laminated on the end faces intersecting the third direction Z, that is, the end faces that have not been conventionally used for heat exchange, so that the heat exchanger 1 is the same as the heat exchanger 1. In addition, the heat insulating layer 50b suppresses the heat held by the high-temperature second fluid and the heat given by the low-temperature first fluid from the second fluid to be released to the outside of the heat exchanger 2. Therefore, the heat exchange rate can be increased. Further, the presence of the heat insulating layer 50b enhances the mechanical strength of the heat exchanger 40b2, which is the same as that of the heat exchanger 1.

In addition, similarly to the heat exchanger 1, what is in contact with the heat insulating layer 50b in the heat exchanger 40b is the stage of the slit 35 which is the first flow path P1 for circulating the first fluid on the side to which heat is applied. .. Therefore, the heat given can effectively retain the heat of the first fluid to be used by the heat insulating layer 50b.

Although the present invention has been described above with reference to suitable embodiments, the present invention is not limited to the above embodiments, and as shown below, various improvements are made without departing from the gist of the present invention. And the design can be changed.

For example, in the first embodiment, the case where the cell 15 becomes the first flow path P1 and the slit 25 becomes the second flow path P2 by stacking the cell row 10 and the spacer 21 is illustrated. Not limited to this, heat exchange in a configuration in which both the first flow path and the second flow path are cells by stacking a plurality of cell rows so that the axial directions of the cells belonging to the adjacent cell rows are orthogonal to each other. It can be a vessel. Further, as the shape of the cell, the one in which the outer shape of the cross section orthogonal to the axial direction is square is exemplified. The shape of the cell is not particularly limited as long as it includes a partition wall that closes in a direction orthogonal to the axial direction, and may be a hexagon, an octagon, a triangle, or the like.

Further, in the second embodiment, the case where the flat plate 31 and the spacer 32 are laminated so that the slits 35 and 36 whose penetrating directions are orthogonal to each other become the first flow path P1 and the second flow path P2, respectively, is illustrated. Not limited to this, by laminating a "comb-toothed" structure corresponding to a shape in which a plurality of ribs arranged in the same longitudinal direction and arranged at intervals are integrated with a flat plate, similarly, the penetration direction is also obtained. Can be a heat exchanger in which the slits orthogonal to each other serve as a first flow path and a second flow path, respectively.

1,1b, 2 heat exchanger (ceramic heat exchanger)
11a partition wall 11b partition wall (wall body)
15 Cell 17 Encapsulant 31 Flat plate (wall body)
32 Spacer 37 Encapsulant 40, 40b Heat exchanger 50, 50b Insulation layer P1 First flow path P2 Second flow path X First direction Y Second direction Z Third direction

Claims (3)

The first flow path penetrating in the first direction and being closed in the second direction orthogonal to the first direction and the second flow path penetrating in the second direction and being closed in the first direction are A ceramic heat exchanger that is adjacent via a wall in the first direction and the third direction orthogonal to the second direction.
In the heat exchanger, a heat insulating layer in which air is held in a closed space is laminated on two end faces intersecting in the third direction .
In the heat insulating layer, slits formed by arranging a plurality of long rod-shaped spacers having the same longitudinal direction at intervals between adjacent flat plates are sealed with a sealing material at both ends in the longitudinal direction. Formed by being stopped
A ceramic heat exchanger characterized by that. The first flow path penetrating in the first direction and being closed in the second direction orthogonal to the first direction and the second flow path penetrating in the second direction and being closed in the first direction are A ceramic heat exchanger that is adjacent via a wall in the first direction and the third direction orthogonal to the second direction.
In the heat exchanger, a heat insulating layer in which air is held in a closed space is laminated on two end faces intersecting in the third direction.
The heat insulating layer is characterized in that a plurality of cells partitioned by a single axially extending partition wall are formed by sealing with a sealing material at both ends in the axial direction. Ceramic heat exchanger. Of the first flow path and the second flow path, the first flow path is adjacent to the heat insulating layer.
In the heat exchanger, a first fluid supply pipe for supplying the first fluid is connected to one of both end faces intersecting with the first direction, and a first fluid discharge pipe for discharging the first fluid is connected to the other. A second fluid supply pipe that supplies a second fluid having a temperature higher than that of the first fluid is connected to one of both end faces that are connected and intersects with the second direction, and the second fluid is connected to the other. The ceramic heat exchanger according to claim 1 or 2 , wherein a second fluid discharge pipe for discharging is connected .

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