JPH06101981A - Rotary heat storage type heat exchanger - Google Patents

Abstract

PURPOSE:To enhance sealing performance by minimizing the generation of warp or strain. CONSTITUTION:A straight running part 3 of a sealing board 1 is cut in the middle part and arranged so that both end edges 3a is opposed to each other with a small span G1 separated while recessed parts 4 are formed on both end edges. An auxiliary sealing board 5 whose shape is matched with the recessed parts are laid out in the recessed parts and fixed with a support member 7. This constitution makes it possible to eliminate the generation of warp or strain induced by thermal expansion or push force from a lateral direction, thereby securing excellent sealing performance.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to improvement of sealing performance of a rotary heat storage type heat exchange device.

[0002]

2. Description of the Related Art In a rotary heat storage type heat exchange device, a high temperature gas passage and a low temperature gas passage are arranged close to each other, and a disk-shaped heat storage core is provided so as to extend over both the high temperature gas passage and the low temperature gas passage. It is arranged to rotate and drive this heat storage core, and heats the low temperature gas by contacting the low temperature gas with the heat storage core heated by the high temperature gas to heat the low temperature gas. There is. In this case, a seal plate is provided between the heat storage core and a housing that supports the heat storage core or a supporting member such as a retainer attached to the housing in order to prevent gas leakage, and its shape corresponds to the outer peripheral portion of the heat storage core. Generally, a shape having an annular portion and a linear portion corresponding to a boundary portion between the high temperature gas passage and the low temperature gas passage is provided (see, for example, Japanese Utility Model Laid-Open No. 2-74538).

FIG. 13 is a schematic view of such a seal plate. The seal plate 21 is composed of an annular portion 22 and a linear portion 23. In FIG. 13A, the annular portion 22 and the linear portion 23 are integrally formed. Shows the integrated type, and (b) shows the separate type with the two separated. The seal plate 1 is heated uniformly during operation, but in the integrated type, if the amount of thermal expansion is the same, the expansion of the linear portion 23 exceeds the expansion of the diameter of the annular portion 22, so that the linear portion 23 has an annular portion. 22 is pushed up, and the linear portion 23 receives a compressive force from the annular portion 22, causing the linear portion 23 to warp and causing a seal leak. Further, in the separate type, such warpage does not occur, but a gap is formed between the annular portion 22 and the linear portion 23, which causes a seal leakage.

Further, in the case of a gas turbine engine, relatively low-pressure exhaust gas and high-pressure air compressed by a compressor correspond to the above-mentioned high-temperature gas and low-temperature gas, respectively. It is twisted due to being pushed from, which also causes seal leakage. Particularly, in the case of the integral type, the seal plate 2 is caused by generating an excessive stress near the base of the linear portion 23 or making the surface pressure of the annular portion 22 uneven.
1 was likely to be damaged or the sealing property of the annular portion 22 was impaired.

[0005]

SUMMARY OF THE INVENTION The present invention focuses on such problems and aims to minimize warpage and twist of the seal plate and to improve the seal structure by improving the seal structure of the gap. It was made as.

[0006]

In order to achieve the above object, in the first aspect of the present invention, the straight portions of the seal plate are cut in the middle so that both end edges of the seal plate face each other with a small space between them. A concave portion is formed in the concave portion, and an auxiliary seal plate having a shape corresponding to the concave portion is arranged in the concave portion and fixed to a supporting member such as a housing. Further, in the second invention, the linear portion of the seal plate is cut in the middle, or the annular portion and the linear portion are cut so that both end edges are opposed to each other, and the both end edges are arranged. A seal spring that is pressed against each other is provided. Further, in the third invention, the seal plates having the annular portion and the linear portion are arranged on both sides of the heat storage core. Further, in the fourth invention, the linear portion of the seal plate is formed by laminating at least two types of plate materials made of materials having different thermal expansion coefficients.

[0007]

According to the first aspect of the invention, since the linear portions of the seal plate are cut and are opposed to each other with a small space therebetween, warping or twisting of the linear portions due to thermal expansion or lateral pressure is unlikely to occur. Further, since the concave portion at the edge of the linear portion is pressed against the auxiliary seal plate by the pressing force from the side and the gap generated by cutting is closed, good sealing property is obtained. In the second invention, the straight portion of the seal plate is cut, or the gap between the annular portion and the straight portion is cut, so that, like the first invention, warpage and twist are unlikely to occur, and the cut portion is also cut. Since the seal spring is pressed against, a good sealing property can be obtained. Third
In the invention, the seal plates having the annular portion and the linear portion are arranged on both sides of the heat storage core, and since the annular portion is present on the entire outer circumference of both sides of the heat storage core, the pressing force acts evenly, and sliding Adhesion on the surface becomes good and good sealing property is obtained. According to the fourth aspect of the present invention, the warpage due to temperature change is reduced by appropriately selecting the thermal expansion coefficient of the material forming the linear portion of the seal plate.

[0008]

First Embodiment Next, the illustrated embodiment will be described. Figure 1
2 shows one embodiment of the first invention, in which the seal plate 1 is composed of an annular portion 2 and a linear portion 3 and is cut at the center of the linear portion 3 so that the end edges 3a, 3a are separated by a small gap G. They are facing each other with _{1 in} between. Recesses 4 and 4 are formed in the end edges 3a and 3a to form rectangular cavities, and an auxiliary seal plate 5 having a shape corresponding to the recesses is arranged in the recesses 4 and 4 and fixed to the retainer 7 by a pin 6. I am doing it. The auxiliary seal plate 5 and the pin 6
A space is fitted between them, and the auxiliary seal plate 5 is movable in the height direction. Further, the small gap G ₁ between the end edges 3a, 3a is selected so that the linear portion 3 expands and becomes almost 0 during operation, and the recess 4 and the auxiliary seal plate 5 have side edges 4a, 5a. Is a fitting, and seals at this side edge when the temperature is low. 8 is a heat storage core,
A diaphragm seal 9 is provided between the seal plate 1 and the retainer 7, and high-pressure air is supplied into the diaphragm seal 9 to seal the seal plate 1.
Are in sliding contact with the heat storage core 8.

This embodiment is constructed as described above, and the expansion of the linear portion 3 is absorbed by the small gap G ₁ during the warm state during operation, so that the warp of the linear portion 3 due to the thermal expansion or Seal leakage due to twisting is prevented. Further, when the linear portion 3 expands, the small gap G ₁ disappears, and when the linear portion 3 is pushed from the side by the pressure difference between the left and right sides, as shown in FIG.
Since the side edge 4a on the high-pressure side of the recess 4 is pressed against the side edge 5a of the auxiliary seal plate 5 as described above, and becomes the seal portion,
Due to thermal expansion, the side edge 4a of the recess 4 and the side edge 5a of the auxiliary seal plate 5
Even if the fitting dimension of is increased, the seal leakage is sufficiently prevented through the gap created between the high pressure side and the low pressure side by cutting the linear portion 3. Further, since the auxiliary seal plate 5 is fixed and the linear portion 3 is supported thereby, twisting caused by lateral deformation of the linear portion 3 does not occur, and seal leakage due to this is prevented. It is.

[0010]

Embodiment 2 FIGS. 3 to 5 show an embodiment of the second invention, and FIG. 3 shows the first embodiment. In this embodiment, as in the case of FIG. 1, the edges 3a, 3a are cut by cutting at the center of the linear portion 3.
Are opposed to each other and the auxiliary seal plates 5 are arranged in the recesses 4 and 4 of the end edges 3a, 3a, but the auxiliary seal plates 5 are not fixed. A seal spring 11 having a zigzag bent leaf spring is provided between the end edges 3a.
The dimensions are such that the outer surface of each folded-back portion 11a contacts the edge 3a. Therefore, when the linear portion 3 is pushed from the side due to the pressure difference between the left and right sides, the pressure is also applied to the seal spring 11 so that the folded portion 11a has the linear portion 3a as shown in FIG.
It is strongly pressed against the end edge 3a of the above, and this serves as a seal portion, so that seal leakage due to a gap generated by cutting the linear portion 3 is prevented.

FIG. 4 shows another embodiment, in which a small recess 3b is formed on the end edge 3a of the linear portion 3 and a cylindrical head 11b inserted into this small recess 3b is provided at both ends. Is used as the seal spring 11. Therefore, when the linear portion 3 is pushed from the side due to the pressure difference between the left and right sides, the seal spring 11
Also, pressure is applied to the head 11b, and the head 11b is strongly pressed against the inner edge of the small recess 3b as shown in FIG.
Thus, the seal leakage through the gap due to the cutting of the linear portion 3 is prevented.

FIG. 5 shows an embodiment in which a seal spring 1 having the same shape as that of FIG. 3 is used in a separate type seal plate 1 in which an annular portion 2 and a linear portion 3 are separated as shown in FIG. 13 (b). Is. That is, a zigzag-shaped seal spring 11 is arranged between the opposing edges of the annular portion 2 and the linear portion 3, and when the seal spring 11 is pressed by the pressure from the outer circumference, the folded portion 11a.
Is strongly pressed against the opposing edges 2a and 3c of the annular portion 2 and the linear portion 3 to perform sealing. As described above, in each of the embodiments of the second invention, since the seal spring 11 is not fixed, the seal plate 1 has good followability even when it is thermally deformed, and good sealability is maintained.

In the case of the separate type seal plate 1 in which the annular portion 2 and the linear portion 3 are separate bodies, a step is generated at the connecting portion between the annular portion 2 and the linear portion 3 due to thermal deformation, and this causes a seal. Since this causes leakage, it is necessary to keep the heights of the sliding surfaces of both members the same in order to prevent this, and the setting work for that purpose is troublesome and requires a considerable number of man-hours. FIG. 6 shows an embodiment of a structure in which the heights of the sliding surfaces of both members can be maintained relatively easily, and the linear portion 3 is extended to a position where the linear portion 3 rides on the connecting portion 13 of the annular portion 2. After the adjustment shim 14 is attached to the connecting portion 13 to adjust the height, the linear portion 3 is placed on it. Reference numeral 15 is a sliding surface formed by spraying ceramics on the upper surface of each member 2, 3
Is a housing to which the retainer 7 is fixed. With such a configuration, even if the linear portion 3 warps, the linear portion 3 does not lift or sink with respect to the annular portion 2 because it is only on the connecting portion 13. Since the heights of the sliding surfaces 15 of the members 2 and 3 are always the same, the setting work is facilitated.

[0014]

[Third Embodiment] FIG. 7 shows an embodiment of the third invention.
Shows a conventional example corresponding to this. That is, when the rotary heat storage type heat exchange device is used in a gas turbine engine, the heat of the high temperature exhaust gas is given to the low temperature air by heat exchange, so the low temperature side may be sealed only against the exhaust gas, Conventionally, the seal plate 21 as shown in FIG. 13 (a) is used on the high temperature side, and the low temperature side is shown in FIG. 8 (b).
The D-type seal plate 21a as shown in FIG. Therefore, in the heat storage core 8, the low temperature side of the air flow path is not pressed by the seal plate and the high temperature side of the air flow path tends to float, and the sealing property on the high temperature side of the air flow path deteriorates, contributing to air leakage. Was there. On the other hand, in this embodiment, as shown in FIG. 7 (b), a seal plate 1 having a complete annular portion 2 similar to that of FIG. 13 (a) is used, which is shown in FIG. 7 (a). The heat storage cores 8 are arranged on both sides as shown in FIG. Therefore, the heat storage core 8 is evenly pressed from both sides so that the seal plate 1 is brought into sliding contact with the one side without any deviation, the deterioration of the sealing property is prevented, and the above problems are solved.

[0015]

[Embodiment 4] By the way, one side of the seal plate is in contact with the high temperature heat storage core and the other side is in contact with the relatively low temperature housing or retainer. Therefore, as shown in FIG. There is a considerable temperature difference T with the side (hereinafter, the heat storage core side is the upper surface and the housing side is the lower surface for convenience), and the expansion amount of the upper surface is usually large and the warp of the linear portion 3 is as shown in FIG. So that it becomes convex upward. The fourth invention focuses on this point, and in this embodiment, as shown in FIG. 10, the linear portion 3 of the seal plate 1 is formed by laminating two kinds of plate materials 18 and 19 having different thermal expansion coefficients. There is. Since the linear portion 3 has an elongated shape, the coefficient of thermal expansion can be regarded as the coefficient of linear expansion in the longitudinal direction. Here, the top plate 1
The material is selected so that the coefficient of thermal expansion of 8 <the coefficient of thermal expansion of the plate material 19 on the lower surface, which prevents warpage due to temperature change and makes it possible to select a material having an appropriate coefficient of thermal expansion. The warp can be significantly reduced.

As shown in FIG. 11, the amount of air leakage sharply increases as the amount of deformation of the linear portion 3 increases. Therefore, by reducing the amount of deformation, the amount of air leakage is greatly reduced and the efficiency of the turbine engine is reduced. Driving becomes possible. FIG. 12 exemplifies this, and (a) shows the relationship between the amount of air leakage and the engine output when the turbine inlet temperature is constant,
(b) shows the relationship between the amount of air leakage and the turbine inlet temperature when the engine output is constant. As can be seen from this figure, when the turbine inlet temperature is constant, the engine output can be increased in the embodiment as compared to the conventional example in which the amount of air leakage is large, and when the engine output is constant, the engine output is increased in the embodiment. The turbine inlet temperature can be lowered as compared with the conventional example. That is, it is possible to increase the output and operate the turbine engine efficiently, or decrease the combustion temperature to improve the life of the turbine.

[0017]

As is apparent from the above description, according to the present invention, the sealing plate of the rotary heat storage type heat exchange device is prevented from warping or twisting as much as possible, and the sealing structure is improved to improve the sealing performance. Is. In particular, in the first invention, the linear portions of the seal plate are cut to face each other with a small gap therebetween, and the auxiliary seal plates fixed to the housing are arranged in the recesses formed at both ends. Less likely to impair sealing performance due to expansion and pressing force from the side,
Good sealability is secured.

A second aspect of the present invention is to cut the linear portion of the seal plate, or cut between the annular portion and the linear portion so that both end edges are opposed to each other, and the seal plate is disposed between the opposed end edges. Sealing springs that are pressed against each other are provided at the edges, so that the sealing performance is less likely to be impaired by thermal expansion and lateral pressing force, and the sealing plate has good followability against thermal deformation and good sealing performance. Reserved. The third invention is
The seal plates having the annular portion and the linear portion are arranged on both sides of the heat storage core, and the seal plates are brought into sliding contact with both sides of the heat storage core without any deviation to improve the sealing performance. Furthermore, a fourth aspect of the present invention is that the linear portion of the seal plate is formed by laminating at least two types of plate materials made of materials having different thermal expansion coefficients, and the warpage is reduced to greatly reduce air leakage, It enables efficient operation of the turbine engine.

[Brief description of drawings]

1A and 1B are a plan view, a plan view and a cross-sectional view of a main part of a sealing plate according to an embodiment of the first invention.

FIG. 2 is an operation explanatory diagram of the embodiment.

3A and 3B are a plan view of a seal plate, a plan view of a main portion and an operation explanatory view according to an embodiment of the second invention.

4A and 4B are a plan view and an operation explanatory view of a main part of another embodiment.

FIG. 5 is a plan view of a main part of another embodiment.

6A and 6B are a plan view and a side view of a main part of still another embodiment.

FIG. 7 is a schematic side sectional view and a plan view of a seal plate according to an embodiment of the third invention.

FIG. 8 is a schematic side sectional view and a plan view of a seal plate of a conventional example corresponding to the third invention.

FIG. 9 is a diagram showing the temperature and warpage of the seal plate.

FIG. 10 is a side view of a main part of a sealing plate according to an embodiment of the fourth invention.

FIG. 11 is a diagram showing a relationship between a deformation amount of a seal plate and an air leakage amount.

FIG. 12 is a diagram showing a relationship between an air leakage amount and an engine output or a turbine inlet temperature.

FIG. 13 is a plan view of a conventional seal plate.

[Explanation of reference symbols] 1 seal plate 2 annular portion 3 linear portion 3a edge 4 recessed portion 5 auxiliary seal plate 7 retainer (support member) 8 heat storage core 11 seal spring 11a folded portion 11b head portion 18, 19 plate material G ₁ small interval

Claims (4)

[Claims] 1. A disk-shaped heat storage core is arranged so as to straddle both a high temperature gas flow path and a low temperature gas flow path provided in proximity to each other, and the low temperature gas is passed through the heat storage core by rotationally driving the heat storage core. A sealing plate having an annular portion provided corresponding to the outer peripheral portion of the heat storage core and a linear portion provided corresponding to a boundary portion between the high temperature gas flow path and the low temperature gas flow path. In a rotary heat storage type heat exchange device provided between a heat storage core and a support member for the heat storage core, a straight portion of the seal plate is cut in the middle so that both end edges are opposed to each other with a small interval and at each end edge. A rotary heat storage type heat exchange device, characterized in that a concave portion is formed, and an auxiliary seal plate having a shape corresponding to the concave portion is arranged in the concave portion and fixed to the supporting member. 2. A disc-shaped heat storage core is arranged so as to straddle both a high temperature gas flow path and a low temperature gas flow path which are provided in proximity to each other, and the low temperature gas is passed through the heat storage core by rotationally driving the heat storage core. A sealing plate having an annular portion provided corresponding to the outer peripheral portion of the heat storage core and a linear portion provided corresponding to a boundary portion between the high temperature gas flow path and the low temperature gas flow path. In the rotary heat storage type heat exchange device provided between the heat storage core and the support member for the heat storage core, the linear portion of the seal plate is cut in the middle, or the annular portion and the linear portion are cut to both ends. A rotary heat storage type heat exchange device, characterized in that a seal spring is provided which has edges opposed to each other and which is disposed between the opposed edges and is brought into pressure contact with both edges. 3. A disc-shaped heat storage core is arranged so as to straddle both a high temperature gas flow path and a low temperature gas flow path which are provided close to each other, and the low temperature gas is passed through the heat storage core by rotationally driving the heat storage core. A sealing plate having an annular portion provided corresponding to the outer peripheral portion of the heat storage core and a linear portion provided corresponding to a boundary portion between the high temperature gas flow path and the low temperature gas flow path. In a rotary heat storage type heat exchange device provided between a heat storage core and a support member for the heat storage core, a rotary heat storage system characterized in that seal plates having the annular portion and the linear portion are arranged on both sides of the heat storage core. Heat exchange equipment. 4. A disc-shaped heat storage core is arranged so as to straddle both a high-temperature gas passage and a low-temperature gas passage that are provided in proximity to each other, and the low-temperature gas is passed through the heat-storage core by rotationally driving the heat storage core. A sealing plate having an annular portion provided corresponding to the outer peripheral portion of the heat storage core and a linear portion provided corresponding to a boundary portion between the high temperature gas flow path and the low temperature gas flow path. In the rotary heat storage type heat exchange device provided between the heat storage core and the support member of the heat storage core, the linear portion of the seal plate is formed by laminating at least two types of plate materials made of materials having different thermal expansion coefficients. A heat storage type heat exchange device characterized by.