JPH07317918A - Seal device for rotary type heat exchanger - Google Patents

Abstract

PURPOSE:To prevent irregular abrasion of a seal member by using a bellows type energizing member for a seal member in contact with a rotary storage rotor in operation of a rotary type heat exchanger and pressing a noncontact part in the seal member central part by high gas pressure in operating the heat exchanger so as to make pressure contact with the heat storage rotor face. CONSTITUTION:A seal device comprises an outward open bellows 7, a flange 8 abutting on the bellows 7, and a seal member 90. The seal member 90 comprises an approximately D-shaped spring member 91, the first seal member 92 attached to the outer circumferential side of the spring member 91, and the second seal member 93 attached to the internal circumferential side of the spring part 91. The spring member 91 comprises two inclined faces 91a, 91b and a spring part 91c for connecting the both. High internal pressure acts on the bellows 7 at rated operation so as to enlarge the bellows 7. Therefore, a part which is in a noncontact state during inoperative time is pressurized so that the seal member 90 is uniformly put in pressure contact with a storage rotor 1 and a reduction gear 2.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary heat exchanger seal device, and more particularly, to use the heat of exhaust gas discharged from a gas turbine engine to heat intake air to the gas turbine engine. The present invention relates to a sealing device in a rotary heat exchanger used in.

[0002]

2. Description of the Related Art Generally, in a gas turbine engine, the heat of exhaust gas is stored by a heat storage type heat exchanger, the temperature of intake air is raised by utilizing the stored heat, and the heat of exhaust gas is effectively utilized to produce an engine. The thermal efficiency of is being increased. This is because the gas turbine engine originally has a low fuel consumption rate under partial load, and the gas turbine engine used for automobiles and the like that is frequently used under partial load improves the fuel consumption rate under partial load. Therefore, a heat storage type heat exchanger is used which heats the intake air to assist the temperature rise in the combustor. As the heat storage heat exchanger, there is used a rotary heat exchanger that efficiently rotates heat by rotating a honeycomb heat storage plate in the casing.

FIG. 6 shows an example of a general structure of a conventional two-shaft gas turbine engine equipped with a heat exchanger, which is mounted on a vehicle with an automatic transmission. In FIG.
C is a compressor, HE is a rotary heat exchanger, CC is a combustor, CT is a compressor turbine, and the compressor C and the compressor turbine CT are directly connected by a rotary shaft, and the combustor CC is fueled via an actuator A1. Is being supplied. Intake air (hereinafter referred to as intake air) is compressed by the compressor C, preheated by the heat exchanger HE, mixed with fuel by the combustor CC and burned, and the combustion gas rotates the compressor turbine CT. The compressor turbine CT, the compressor C, and the combustor CC are sometimes collectively referred to as a gas generator, and the rotation speed of the compressor turbine CT affects the compression degree of the compressor C. The combustion gas that drives the compressor turbine CT drives the power turbine (output turbine) PT through the variable nozzle VN adjusted by the actuator A2, and then passes through the heat exchanger HE to be discharged as exhaust gas to the atmosphere.

The gas generator is started by rotating a front gear F / G provided on the rotary shaft of the compressor C by a starter SM with a built-in clutch. Further, the actuator A1 is a control circuit CONT
The fuel is supplied to the combustor CC according to the command from the actuator A2, and the actuator A2 adjusts the opening degree of the variable nozzle VN according to the command from the control circuit CONT. The opening degree of the accelerator pedal and the engine operating state parameter from a sensor (not shown) are input to the control circuit CONT, and the control circuit CONT drives the actuators A1 and A2 according to the operating state of the engine.

The above is the configuration of the two-shaft gas turbine GT. The rotation of the power turbine PT is decelerated by the reduction gear R / G and transmitted to the automatic transmission A / T to be converted into the number of rotations according to the shift state. After that, it is transmitted to the wheels W via the differential gear D. In general, the intake pressure at the position in FIG. 6 is P ₃ , and the temperature at the position is T ₄ , so that the subscripts attached to the intake pressure P and the temperature T indicate the positions of the numbers circled by ○. The intake pressure P and the temperature T are shown.

The rotary heat exchanger HE in the two-shaft gas turbine GT shown in FIG.
Is rotated across a low pressure exhaust gas passage 5 and a high pressure intake passage 6 by a reduction gear 2 and a shaft 3 which is interlocked with a drive shaft of a power turbine to perform heat exchange. Therefore, in this rotary heat exchanger HE, the seal member 9 that abuts the heat storage rotor 1 in the casing 4 to seal and seal the high-pressure intake air and the low-pressure exhaust gas, and the bellows 7 that urges the seal member 9. The sealing device provided with is an important component for preventing leakage of high-pressure intake air and improving performance.

In this sealing device, a sealing member 9 is in contact with an end surface of a disk-shaped heat storage rotor 1 axially supported in a casing 4 of a heat exchanger HE, and a flange fixed to an inner wall of the casing 4 facing the sealing member 9. 8 and a bellows 7 having a substantially V-shaped cross section interposed between the seal member 9 and the flange 8. The high temperature side flange 8 and the seal member 9 have a substantially θ shape or a combination of a substantially D shape and a substantially C shape, and the low temperature side flange 8 and the seal member 9 have a substantially D shape. Therefore, as can be seen from FIG. 6, a substantially D-shaped bellows 7 is used for the passages of the high-temperature low-pressure exhaust gas and the low-temperature low-pressure exhaust gas, and a substantially C-shaped bellows 7 is used for the high-temperature high-pressure intake passage. used.

FIG. 7 (a) is a perspective view of the substantially D-shaped bellows 7 used in FIG. In the rotary heat exchanger HE shown in FIG. 6, the low pressure exhaust gas passage 5 and the high pressure intake passage 6 are
Is connected to the casing 4 through a substantially D-shaped opening,
The bellows 7 that seals this opening also has a substantially D shape including a straight portion 7a and a curved portion 7b. FIG. 7B is a sectional view showing the configuration of the main part of a sealing device 10 using this bellows 7. The sealing device 10 includes a seal member 9 that comes into contact with an end surface of a disk-shaped heat storage rotor 1 that is axially supported in a casing 4 of a heat exchanger, a flange 8 that is fixed to an inner wall of the casing that faces the seal member 9, and these seals. The bellows 7 is interposed between the member 9 and the flange 8. The bellows 7 is made of a heat-resistant metal thin film material, and the cross section of any part of the ring shape is substantially V-shaped or U-shaped. Further, each base end portion of the bellows 7 is welded to each facing surface portion of the seal member 9 and the flange 8 so as to seal between the high pressure intake passage 5 and the low pressure exhaust gas passage 7 of the gas turbine. Has become.

The structure of such a seal device 10 is also disclosed in Japanese Patent Laid-Open No. 53-15651. In the seal device described in this publication, a shape control plate having a substantially U-shaped cross section is provided on the outer periphery of the bellows. Is provided, and the seal member is pressed vertically against the heat storage rotor.

[0010]

However, in the sealing device in the rotary heat exchanger configured as described above, when a high internal pressure is applied to the opening side of the bellows 7 during operation, an arrow is drawn in FIG. 7 (b). As indicated by G and g, the seal member 9
The stress is concentrated on the side pressed by the bellows 7, and as shown in FIG. 7 (c), the seal member 9 on the side where the stress is concentrated is unevenly worn, which causes gas leakage due to uneven wear. It was Regarding this uneven wear, JP-A-53-15651
Also in the sealing device disclosed in the publication, since the shape control plate has a U-shaped cross section, the displacement amount on the U-shaped opening side is the largest, and there is a risk that the sealing member in the portion in contact therewith is unevenly worn. It was

In view of the above, according to the present invention, in the sealing device for a rotary heat exchanger, the seal member is pressed against the heat storage rotor with a uniform force during the rated operation of the rotary heat exchanger, so that the seal member is unevenly worn. It is an object of the present invention to prevent the above and improve the durability of the sealing device of the rotary heat exchanger.

[0012]

A seal device for a rotary heat exchanger according to the present invention that achieves the above object has a casing containing a rotary heat storage rotor having air permeability, which is used for low-temperature high-pressure gas and high-temperature low-pressure gas. Two sets of input / output openings are provided so as to face each other through the rotary heat storage rotor, and the low temperature high pressure gas and the high temperature low pressure gas are allowed to pass through the rotary heat storage rotor to perform heat exchange without being mixed with each other. In the sealing device, the low-temperature high-pressure gas and the high-temperature low-pressure gas are separated inside the casing by a seal member that comes into contact with the rotary heat storage rotor and an urging member that presses the seal member against the rotary heat storage rotor. In the rotary heat exchanger seal device, the biasing member pushes the seal member to the rotary heat storage rotor by the pressure of high-pressure gas when the rotary heat exchanger is activated. A bellows-like urging member that increases the contact force is used, and the seal member has a contact surface of the seal member with the rotary heat storage rotor when the rotary heat exchanger is not operating, in the longitudinal direction of the seal member. Attaching another biasing means for bringing the central portion side along with it into a non-contact state, the biasing force of the biasing member increased by the pressure of the high pressure gas during the operation of the rotary heat exchanger causes the sealing member to move. The entire surface is uniformly pressed against the rotary heat storage rotor.

[0013]

According to the seal device for a rotary heat exchanger of the present invention, the biasing member of the seal member contacting the rotary heat storage rotor is rotated by the pressure of the high pressure gas during operation of the rotary heat exchanger. A bellows-like urging member that increases the force applied to the rotor is used, and the seal member has a contact surface of the seal member with the rotary heat storage rotor when the rotary heat exchanger is not operating, along the longitudinal direction of the seal member. Since another urging means for bringing the central portion side into a non-contact state is attached, the central portion side along the longitudinal direction of the seal member is increased by the pressure of the high pressure gas when the rotary heat exchanger is operated. Is pushed by the biasing force of the biasing member, and the peripheral edge side along the longitudinal direction of the seal member is pushed by the biasing force of another biasing means, and the entire surface of the seal member is pushed during the rated operation of the rotary heat exchanger. Evenly pressed against the rotating heat storage rotor As a result, uneven wear of the seal device of the rotary heat exchanger is prevented, and durability of the seal device of the rotary heat exchanger is improved.

[0014]

Embodiments of the present invention will be described in detail below with reference to the accompanying drawings. FIG. 1 is a configuration diagram showing an overall configuration of a rotary heat exchanger HE in which a sealing device 20 for a rotary heat exchanger according to an embodiment of the present invention is incorporated. In FIG. 1, FIGS.
The same reference numerals (symbols) are given to the same components as the components of the seal device for the rotary heat exchanger in the conventional gas turbine engine described in Section 2.

Also in the rotary heat exchanger HE shown in FIG. 1, the honeycomb-shaped heat storage rotor 1 connects the low pressure exhaust gas passage 6 and the high pressure intake passage 5 by the shaft 3 which is interlocked with the reduction gear 2 and the drive shaft of the power turbine. It is designed to rotate across and exchange heat. The low-pressure exhaust gas passage 6 and the high-pressure intake passage 5 are connected to the casing 4 by a substantially D-shaped opening. Reference numeral 41 is a low-temperature high-pressure air pool in the casing 4.

The sealing device 20 of this embodiment, which seals and seals the high pressure intake air and the low pressure exhaust gas inside the casing 4, corresponds to the bellows 7 and the bellows 7 which are substantially C-shaped or D-shaped and which open outward. It is composed of a flange 8 and a sealing member 90 which are in contact with each other. The bellows 7 is configured by joining two bellows plates 70 of the same shape made of a heat-resistant metal thin film material, for example. In this embodiment, an outer opening bellows 7 is used.
The local cross section of any of the parts is substantially V-shaped. The flange 8 is fixed to the casing 4.

As shown in FIG. 2, the seal member 90, for example, the substantially D-shaped seal member 90, has a substantially D-shaped spring member 91, a first seal member 92 attached to the outer peripheral side of the spring member 91, and The second seal member 93 is attached to the inner peripheral side of the spring member 91. The first seal member 92 and the second seal member 93 are, as shown in FIG. 3, contact plates 92a, 9a made of a carbon material.
3a is adhered to the mounting plates 92b and 93b and has the same thickness, but the first sealing member 92 has the same width.
Is shorter than the second seal member 93. Then, in this embodiment, the first seal member 92 and the second seal member 93 are attached to the spring member 91 by screws 94. Further, in this embodiment, with the first seal member 92 and the second seal member 93 attached to the spring member 91, a space is provided between them.

The spring member 91 is not flat but is composed of two slopes 91a and 91b and a spring portion 91c connecting the slopes 91a and 91b. The two slopes 91a and 91b form a predetermined angle θ close to 180 °. FIG. 3B is a local sectional view showing a state in which the first seal member 92 and the second seal member 93 are attached to the spring member 91. As described above, in the seal device for the rotary heat exchanger of this embodiment, the seal member 90 includes the two first seal members 92 and the second seal members 93, and the first seal member 92 and the second seal member 92 are provided. The seal member 93 is not on one plane, and is inclined so as to be recessed toward the central portion side in the longitudinal direction of the seal member 90. Therefore, if the seal member 90 is attached to the heat storage rotor 1 while being pressed,
A rotor outer end of the first seal member 92 of the seal member 90 and a rotor inner end of the second seal member 93 are pressed against the heat storage rotor 1 by the spring member 91.
The inner end of the rotor of the first seal member 92 and the outer end of the rotor of the second seal member 93 are separated from the heat storage rotor 1. Then, the spring portion 9 of the spring member 91
When 1c is deformed in the opening direction, the contact area between the first seal member 92 and the second seal member 93 with respect to the heat storage rotor 1 increases.

FIG. 4A is a sectional view showing the operation of the sealing device of the rotary heat exchanger using the seal member 90 of FIG. 3 when the rotary heat exchanger HE is not operating. In this example,
The reduction gear (ring gear) 2 fitted on the outer peripheral portion of the heat storage rotor 1 has a thick bottom portion and is flush with the core surface 1 a of the heat storage rotor 1. The seal member 90 configured as shown in FIG. 3B is attached so that the end portion of the first seal member 92 abuts on the tooth bottom portion of the reduction gear 2.

The seal member 90 is pressed by the bellows 7 provided between the seal member 90 and the flange 8 with a predetermined force. Therefore, when the rotary heat exchanger HE is not operating, the tooth bottom portion of the reduction gear 2 and the heat storage rotor 1 are connected to the end portion of the first seal member 92 and the second end portion of the seal member 90 configured as shown in FIG. Therefore, the pressing force as shown by the dotted line is received from the end of the sealing member 93.

If the portion shown in FIG. 4 (a) is the portion A of FIG. 1, when the rotary heat exchanger HE operates from the state of FIG. (a) Bellows 7
The high pressure internal pressure of the low-temperature high-pressure air reservoir 41 in the casing 4 is applied to the outward opening side of the bellows 7, and the bellows 7 is spread by the high pressure internal pressure to press the seal member 90 with a stronger force. This state is shown in FIG. 4 (b).

As shown in FIG. 4 (b), the rotary heat exchanger H
During the rated operation of E, when the bellows 7 is expanded by the high internal pressure and the seal member 90 is pressed with a stronger force, the seal member 90 is separated from the first seal member 92 and the second seal member 92.
Bottom portion of the reduction gear 2 of the seal member 93 and the heat storage rotor 1
The first seal member 92 is deformed by using the contact portion to the fulcrum as a fulcrum.
With this, the entire surface of the second seal member 93 is pressed against the tooth bottom portion of the reduction gear 2 and the heat storage rotor 1.

At this time, the force transmitted from the bellows 7 to the tooth bottom portion of the reduction gear 2 and the heat storage rotor 1 is applied to the bellows 7 of the seal member 90 as shown by solid arrows F and F'in FIG. 4 (b). The area away from the contact area is smaller. On the other hand, the first
In the state where the entire surfaces of the seal member 92 and the second seal member 93 are pressed against the tooth bottom portion of the reduction gear 2 and the heat storage rotor 1, the first seal member 92 and the second seal member 92 are pressed by the spring member 91.
The sealing member 93 of the reduction gear 2 and the heat storage rotor 1
The force to be applied to the arrow is shown by the dotted arrows f and f'in Fig. 4 (b).
As shown in, the portion of the sealing member 90 that is far from the portion with which the bellows 7 abuts is larger.

Therefore, by adjusting the urging force of the spring member 91 of the seal member 90, the entire surface of the first seal member 92 and the second seal member 93 during the rated operation of the rotary heat exchanger HE, It is possible to press the tooth bottom portion of the reduction gear 2 and the heat storage rotor 1 with a uniform force. Then, when the entire surfaces of the first sealing member 92 and the second sealing member 93 of the sealing member 90 are pressed against the tooth bottom portion of the reduction gear 2 and the heat storage rotor 1 with a uniform force, the first and second sealing members 92 and 93 are pressed.
The uneven wear of the seal members 92, 93 is prevented, and the durability of the seal device of the rotary heat exchanger is improved while suppressing gas leakage.

In the gas turbine engine, at the time of starting and idling, a part of the first seal member 92 and the second seal member 93 of the seal member 90 of the bellows 7 is part of the reduction gear 2.
However, in the gas turbine engine, the rated operation time is much longer than the start-up and idle operation times, so uneven wear occurs in the sheave member 90. Possibility is small.

FIG. 5 (a) shows another embodiment of the seal member 90 in the seal device for a rotary heat exchanger of the present invention, and is a local sectional view of the same portion as FIG. 3 (b). Also in this embodiment, the same components as those in the above-mentioned embodiments are designated by the same reference numerals. The sealing member 90 of this embodiment differs from the above-described embodiments only in the shape of the spring member 91 '. In the above-described embodiment, the spring member 90 has two slopes 91a and 91a.
b and a spring portion 91c connecting the slopes 91a and 91b.
And the two slopes 91a and 91b form a predetermined angle θ close to 180 °. On the other hand, in this embodiment, the spring member 90 'has two slopes 91a', 9 '.
1b 'and forms a predetermined angle .theta.' Close to 180.degree. As in the above-mentioned embodiment, these slopes 91a ',
There is no spring portion 91c connecting 91b 'and two slopes 91
The a'and 91b 'are extended and connected as they are at the connecting portion 91d.

The seal member 90 'of this embodiment is different from the seal member 90 of the above-described embodiment only in the spring member 91', and the operation and effect of this embodiment are the same as those of the above-mentioned embodiment. FIG. 5 (b) shows still another embodiment of the seal member 90 in the seal device for a rotary heat exchanger of the present invention, and is a local cross-sectional view of the same portion as FIG.
Also in this embodiment, the same components as those in the above-mentioned embodiments are designated by the same reference numerals.

The seal member 90 of this embodiment differs from the above-mentioned embodiment only in the shape of the spring portion 91e of the spring member 91 ". In the above-mentioned embodiment, the spring member 90 has two inclined surfaces 91a and 91b. And a spring portion 91c connecting these slopes 91a and 91b.
1a and 91b form a predetermined angle θ close to 180 °, and the spring portion 91c has a substantially U-shape. On the other hand, this embodiment is different only in that the spring portion 91e has an arc shape.

The seal member 90 "of this embodiment is different from the seal member 90 of the above-mentioned embodiment only in the spring member 91", and the operation and effect of this embodiment are the same as those of the above-mentioned embodiment. As described above, various shapes can be considered as the shape of the spring member, and the shape is not limited to the embodiment described above.

As described above, in the seal device for the rotary heat exchanger of the present invention, this is applied to the heat exchanger H of the gas turbine engine.
When adopted in E, the seal member normally contacts the bottom of the reduction gear or the heat storage core with a uniform force during rated operation where the pressure on the most downstream side of the compressor becomes large, so uneven wear of the seal member is prevented. Therefore, the durability of the seal member is improved.

[0031]

As described above, according to the seal device for a rotary heat exchanger of the present invention, the seal member is pressed against the heat storage rotor with a uniform force during the rated operation of the rotary heat exchanger. There is an effect that uneven wear of the seal member is prevented and durability of the seal device of the rotary heat exchanger is improved.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing an overall configuration of a rotary heat exchanger using a sealing device of the present invention.

FIG. 2 is an assembled perspective view showing a configuration of an embodiment of a seal member in the seal device for the rotary heat exchanger of FIG.

3 (a) is an assembled sectional view for forming a seal member in the sealing device for the rotary heat exchanger of FIG. 2, and FIG.
It is a local sectional view after the assembly of the seal member of (a).

4 (a) is an enlarged explanatory view of a main part showing the operation of the sealing device of the rotary heat exchanger using the seal member of FIG. 3 when the rotary heat exchanger is not in operation, and FIG. 4 (b) is a rotary type When the heat exchanger is operating
FIG. 7 is an enlarged explanatory view of a main part showing the operation of the seal device for the rotary heat exchanger of (a).

FIG. 5 (a) is a partial cross-sectional view of another embodiment of the seal member in the rotary heat exchanger seal device of the present invention, and FIG. 5 (b) is a seal member in the rotary heat exchanger seal device of the present invention. FIG. 8 is a local sectional view of still another embodiment of the present invention.

FIG. 6 is a configuration diagram showing an example of a general configuration of a conventional two-shaft gas turbine engine equipped with a heat exchanger, which is mounted on an automobile with an automatic transmission.

7 (a) is a perspective view of the bellows used in FIG. 6,
9B is a cross-sectional view of a main part of the sealing device of FIG. 9, and FIG. 9C is an explanatory diagram for explaining uneven wear of the sealing member in the conventional sealing device.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Heat storage rotor 2 ... Reduction gear 4 ... Casing 5 ... Low pressure exhaust gas passage 6 ... High pressure intake passage 7 ... Bellows 8 ... Flange 20 ... Sealing device 90 of the present invention 90 ... Sealing members 91, 91 ', 91 "... Spring member 91a , 91a ', 91a "... Slopes 91b, 91b', 91b" ... Slopes 91c, 91e ... Spring portion 92 ... First seal members 92a, 93a ... Contact plates 92b, 93b ... Mounting plate 93 ... Second seal member HE … Rotary heat exchanger

Claims (1)

[Claims] 1. A casing containing a breathable rotary heat storage rotor is provided with two sets of input / output openings for a low-temperature high-pressure gas and a high-temperature low-pressure gas so as to face each other through the rotary heat storage rotor. A seal device for a rotary heat exchanger that performs heat exchange by passing through this rotary heat storage rotor without mixing a high-pressure gas and a high-temperature low-pressure gas, the seal member contacting the rotary heat storage rotor, and this seal member By the biasing member pressed against the rotary heat storage rotor,
In the seal device of the rotary heat exchanger, wherein the low-temperature high-pressure gas and the high-temperature low-pressure gas are separated inside the casing, the biasing member includes the seal member at the pressure of the high-pressure gas during the operation of the rotary heat exchanger. While using a bellows-like biasing member that increases the force pressing against the rotary heat storage rotor, the seal member, of the contact surface of the seal member to the rotary heat storage rotor when the rotary heat exchanger is not operating, Attaching another urging means for bringing the central portion side along the longitudinal direction of the seal member into a non-contact state, the urging force of the urging member increased by the pressure of the high-pressure gas during the operation of the rotary heat exchanger. The sealing device for a rotary heat exchanger is characterized in that the entire surface of the sealing member is uniformly pressed against the rotary heat storage rotor.