Fluid sealing structure of a heat engine with steam turbine

Abstract

Fluid sealing structure (1) of a heat engine with a steam turbine, comprising: an inner housing (10) which rotatably accommodates a turbine rotor (2) inside the inner housing (10); an outer casing (20) which accommodates the inner casing (10) and forms a space (4) through which a fluid can flow between the outer casing (20) and an outer surface (10a) of the inner casing (10); a projecting section (30) projecting into the space (4) from one of the outer surfaces (10a) of the inner housing (10) or an inner surface (20a) of the outer housing (20), wherein the projecting section (30) is formed in an annular shape in a circumferential direction of one of the surfaces (10a, 20a); and a subdivision plate (40) which extends from the other outer surface (10a) or inner surface (20a) into the space (4) and is formed in a circular ring shape in a circumferential direction of the other surface (10a, 20a), wherein the dividing plate (40) the space (4) is divided into a first space subsection (4a) in which the preceding section (30) is not arranged and which is arranged on a first side with respect to an axial direction of the turbine rotor (2), and a second space subsection (4b) in which the preceding section (30) is arranged and which is arranged on a second side with respect to the axial direction of the turbine rotor (2), and in the axial direction of the turbine rotor (2) is deformable in a bending-stiff manner by an internal fluid pressure difference between the first space section (4a) and the second space section (4b), wherein the dividing plate (40) is designed to contact the preceding section (30) airtight only if it is deformed rigidly towards the second room section (4b) in response to the difference in internal fluid pressure which exceeds a predetermined value.

Description

Technical field

[0001] The present disclosure relates to a fluid sealing structure which seals a gap between steam chambers inside a heat engine with a steam turbine. State of the art

[0002] A steam turbine, an example of a heat engine, typically comprises an inner casing that houses a turbine rotor and an outer casing that houses the inner casing. In a steam turbine, high-pressure steam is introduced into the inner casing through a steam inlet located on the outer casing. The introduced high-pressure steam is fed into the inner casing at a high velocity, and this steam power imparts a rotational force to a multitude of turbine stages of a turbine rotor, causing the rotor to turn. The high-pressure steam, having imparted a rotational force to the turbine stages, moves from an upstream side to a downstream side through the turbine stages, decreasing in temperature and pressure, and exits through an outlet.

[0003] Meanwhile, patent document 1 discloses a steam turbine with high-pressure and intermediate-pressure stages. As disclosed in patent document 1, this steam turbine comprises a high-pressure-intermediate-pressure integration blind ring between a high-pressure stage and an intermediate-pressure stage, and an annular dividing plate arranged between the high-pressure-intermediate-pressure integration blind ring and an outer casing (outer turbine casing). The annular dividing plate separates and protects an inner casing (inner turbine casing) from intermediate-pressure steam at a high temperature, thereby reducing thermal stress on the inner casing and stress on the bolts that secure the inner casing.

[0004] The inner housing has a structure that can be divided into an upper and a lower part with abutting surfaces extending horizontally along edge sections. The upper and lower parts are fastened together with a multitude of bolts to ensure a fixed, integrated connection, while the corresponding abutting surfaces of the upper and lower parts are in contact with each other. The outer housing has a design similar to that of the inner housing.

[0005] US 8 142 146 B2 and EP 2 863 019 A1 each describe sealing structures in which a sealing element is in permanent contact with a projection regardless of a fluid pressure difference. List of literature Patent literature

[0006] Patent document 1: JPS62-284905 A (see Fig. 1) Summary Problems to be solved

[0007] As described above, in a steam turbine designed to discharge high-pressure steam through a plurality of turbine stages and an outlet, some of the high-pressure steam flowing through the plurality of turbine stages can enter a turbulent flow and enter a space between an outer casing and an inner casing, instead of flowing towards the outlet. If low-temperature steam flowing through the plurality of turbine stages passes through this space, the outer casing is cooled along the axial direction of a turbine rotor. Conversely, if high-pressure steam flows into the space from the opposite side to the outlet, the temperature of the outer casing increases along the axial direction of the turbine rotor.Consequently, the temperature of the outer casing varies along the axial direction of the turbine rotor, and the difference is particularly greater between a portion of the outer casing in contact with high-temperature steam and a portion in contact with lower-temperature steam. This can weaken the fastening force of bolts securing the upper and lower parts of the outer casing, especially when located in an area subject to rapid temperature decrease.

[0008] In this respect, the partition plate disclosed in patent document 1 can be provided inside the chamber to divide the chamber. If the partition plate can completely block the flow of low-temperature steam, it is possible to prevent rapid temperature changes in the outer casing. However, even with a partition plate arranged to provide an airtight seal between chamber sections on each side of the partition plate during steam turbine assembly, gaps can still form between the partition plate and the outer casing, or between the partition plate and the inner casing, due to an increased temperature inside the steam turbine or due to a temperature difference generated depending on the position during steam turbine operation.Thus, low-temperature steam can flow into an upstream section of the space and reduce the fastening force of bolts used to secure the upper and lower parts of the outer casing.

[0009] Consequently, it is desirable to develop a sealing structure for a steam turbine with a partition plate arranged in a space, which is capable of providing an airtight seal between a pair of space sections separated by the partition plate, without creating a gap during operation of the steam turbine.

[0010] In view of this, it is an object of at least some embodiments of the present invention to provide a fluid sealing structure of a heat engine with a steam turbine which is capable of providing an airtight seal between a pair of space sections divided by a partition plate during operation of the heat engine. Problem solving

[0011] A fluid sealing structure of a heat engine with a steam turbine according to at least some embodiments of the present invention comprises: an inner casing which rotatably receives a turbine rotor inside the inner casing; an outer casing which receives the inner casing and forms a space through which a fluid can flow between the outer casing and an outer surface of the inner casing; a projecting section which projects into the space from an outer surface of the inner casing or an inner surface of the outer casing, wherein the projecting section is formed in an annular shape in a circumferential direction of one surface; and a dividing plate which extends into the space from the other outer surface or the inner surface and is formed in an annular shape in a circumferential direction of the other surface.The partition plate divides the space into a first section, in which the aforementioned section is not located and which is positioned on one side with respect to the axial direction of the turbine rotor, and a second section, in which the aforementioned section is located and which is positioned on the other side with respect to the axial direction of the turbine rotor. The partition plate is rigidly deformable in the axial direction of the turbine rotor due to an internal fluid pressure difference between the first and second sections. The partition plate is designed to create an airtight seal with the aforementioned section only if it is rigidly deformed towards the second section in response to an internal fluid pressure difference exceeding a predetermined value.

[0012] With the fluid sealing structure described above for a heat engine comprising a steam turbine, an internal fluid pressure differential is generated during operation of the heat engine between the first and second chamber sections. If this pressure differential is such that the pressure in the first chamber section (which does not contain the protruding section) is greater than the pressure in the second chamber section (which does contain the protruding section), the dividing plate deforms rigidly in the axial direction of the turbine rotor towards the second chamber section to contact the protruding section. Thus, there is no longer a gap between the dividing plate and the protruding section.Even if a fluid in the second chamber section, located on the second side relative to the axial direction of the turbine rotor, attempts to flow into the first chamber section, located on the first side relative to the axial direction of the turbine rotor, it is therefore possible to reliably block the flow of the fluid to the first chamber section with the partition plate. Thus, it is possible to provide a fluid sealing structure for a heat engine with a steam turbine that is capable of maintaining an airtight seal between a pair of first and second chamber sections separated by a partition plate during operation of the heat engine.

[0013] In some embodiments, the dividing plate is designed to have a thickness in the axial direction of the turbine rotor that decreases outwards in a radial direction of the turbine rotor, at least at a distal end section of the dividing plate.

[0014] In this case, at least the distal end section of the partition plate is tapered, thus reducing its bending stiffness towards the distal end. If a force is applied to the partition plate in the axial direction of the turbine rotor, directed towards the protruding section, the distal end section of the partition plate deforms rigidly towards the protruding section, while being supported at an inner end of the partition plate with respect to the radial direction of the turbine rotor. This makes it possible to ensure that at least the distal end section of the partition plate comes into secure contact with the protruding section. Furthermore, it is possible to provide an airtight seal between a pair of the first and second volume sections separated by the partition plate during operation of the heat engine.

[0015] In some embodiments, the outer casing includes a fluid supply path configured to supply the fluid to the inner casing. Furthermore, the inner casing includes a drive flow path configured to direct the fluid supplied through the fluid supply path to the turbine rotor in order to drive the turbine rotor. The drive flow path and the first spatial section are also connected to each other via a connecting flow path.

[0016] In this case, it is possible to supply fluid flowing through the drive flow path to the first chamber section via the connecting flow path. The fluid flowing through the drive flow path exerts a rotational force on the turbine rotor, and thus the drive flow path is designed to pressurize the fluid. Therefore, it is possible to increase the internal fluid pressure of the first chamber section by introducing the fluid flowing through the drive flow path into the first chamber section. This further increases the internal fluid pressure difference between the first and second chamber sections, causing the partition plate to make contact with the preceding section even more easily and readily.Consequently, it is possible to provide a fluid sealing structure for a heat engine with a steam turbine that is capable of providing an airtight seal between a pair of the first space section and the second space section, which are divided by the partition plate, during operation of the heat engine.

[0017] In one embodiment, an annular sealing element is arranged on a side surface of the protruding section of the dividing plate, wherein the annular sealing element comprises a material which has a greater coefficient of linear expansion than the protruding section.

[0018] In this case, if the partition plate deforms rigidly towards the designated section in order to contact the annular sealing element, the annular sealing element deforms. If the partition plate deforms further, it also contacts the protruding section while the annular sealing element deforms. Thus, in addition to the annular sealing element, the partition plate contacts the protruding section, and this makes it possible to further improve the airtight seal between the pair of room sections. Beneficial effects

[0019] According to at least some embodiments of the present invention, it is possible to provide a fluid sealing structure of a heat engine with a steam turbine which is capable of providing an airtight seal between a pair of space sections divided by a partition plate during operation of the heat engine. Brief description of the drawings Fig. Figure 1 is a partial cross-sectional view of a steam turbine, showing an example design of a fluid sealing structure. Fig. Figure 2 is an internal structure view of a steam turbine according to one embodiment. Fig. Figure 3 is a schematic perspective view of an inner housing with a sealing ring according to one embodiment. Fig. Figure 4 is a partial cross-sectional view of a steam turbine to describe a function of a sealing ring according to an embodiment. Fig. Figure 5 is a partial cross-sectional view of another sealing ring according to one embodiment. Fig. Figure 6A is a partial cross-sectional view of another sealing ring according to one embodiment, and Fig. 6B is a perspective view of the sealing ring. Detailed description

[0020] An embodiment of a fluid sealing structure of a heat engine comprising a steam turbine, according to the present invention, will now be described with reference to the accompanying drawings. In the present embodiment, a steam turbine will be described as an example of a heat engine. However, unless specifically stated otherwise, it is intended that dimensions, materials, shapes, relative positions, and the like of components described in the embodiments are to be interpreted merely as illustrative and are not intended to limit the scope of the present invention.

[0021] As in Fig. 1 (partial cross-sectional view) and Fig. Figure 2 (internal structure view) shows a fluid sealing structure 1 of a steam turbine comprising an inner casing 10 which rotatably receives a turbine rotor 2 inside, an outer casing 20 which receives the inner casing 10 and forms a space 4 through which steam can flow between the outer casing 20 and an outer surface 10a of the inner casing 10, a projecting section 30 which projects from an inner surface 20a of the outer casing 20 into the space 4 and is formed in an annular shape in a circumferential direction of the inner surface 20a, and a dividing plate 40 which extends from the outer surface 10a of the inner casing 10 into the space 4 and is formed in an annular shape in the circumferential direction of the outer surface 10a.The partition plate 40 divides the chamber 4 into the first chamber section 4a and the second chamber section 4b, which are arranged on both sides of the partition plate 40 with respect to the axial direction of the turbine rotor 2. The partition plate 40 is rigidly deformable in the axial direction of the turbine rotor 2 in response to an internal pressure difference of steam between the first chamber section 4a and the second chamber section 4b.

[0022] In some embodiments, the inner housing 10 is made of metal (e.g., cast Cr steel) and comprises a stationary blade array 11 (see Fig. 1), which is equipped with a rotating blade row 3 (see Fig. 1) of the turbine rotor 2, which extends in the axial direction of the turbine rotor 2, is to be brought into engagement. Hereinafter, the rotating blade row 3 and the stationary blade row 11 are collectively referred to as a “high-pressure stage 6”. A drive flow path 50 (see Fig. 1) is formed between the rotating blade row 3 and the stationary blade row 11, through which high-temperature and high-pressure steam can flow. When high-temperature and high-pressure steam flows through the drive flow path 50, the rotating blade row 3 receives a flow of high-temperature and high-pressure steam to rotate the turbine rotor 2.

[0023] The inner housing 10 is designed to be divisible into an upper part and a lower part, with abutting surfaces (not shown) extending horizontally at edge sections, and wherein the turbine rotor 2 is arranged in the lower part of the inner housing 10. The upper part of the inner housing 10 is placed on the lower part, and the upper and lower parts of the inner housing 10 are fastened with a plurality of bolts while the abutting surfaces of the parts are in contact, thereby integrating and fixing them. As shown in Fig. 1 and Fig. As shown in Figure 3 (schematic perspective views), the partition plate 40 is formed in an annular shape on the outer surface 10a of the inner housing 10 in the circumferential direction of the outer surface 10a, projecting outwards in the radial direction of the turbine rotor 2. The partition plate 40 and the inner housing 10 are integrated as a single piece. The structure of the partition plate 40 will be described in detail below.

[0024] In some embodiments, the outer housing 20 is made of metal (e.g., Cr-Mo cast steel) and is designed to be separable into an upper part and a lower part, with abutting surfaces (not shown) extending horizontally at edge sections, similar to the inner housing 10. The upper part of the outer housing 20 is placed on the lower part, and the upper and lower parts of the outer housing 20 are fastened with a plurality of bolts while the abutting surfaces of the parts are in contact, and thus integrated and fixed.

[0025] As in Fig. 1 and Fig. As shown in Figure 2, the outer casing 20 has a space 4 through which steam can flow, formed between the inner surface 20a of the outer casing 20 and the outer surface 10a of the inner casing 10, in a state where the outer casing 20 accommodates the inner casing 10. A high-pressure steam inlet 21 for introducing high-temperature and high-pressure steam is arranged on an upper section of the outer casing 20, and the high-pressure steam inlet 21 is connected to the drive flow path 50 of the inner casing 10 via a fluid supply path 22. Thus, high-temperature and high-pressure steam is supplied to the drive flow path 50 through the high-pressure steam inlet 21 and the fluid supply path 22. To the right of the high-pressure steam inlet 21, with respect to the axial direction of the turbine rotor 2, a medium-pressure stage 7 is arranged, which extracts a rotational force from medium-pressure steam.High-temperature and high-pressure steam S3 is fed to the medium-pressure stage 7 via room 4.

[0026] Furthermore, to the left of the high-pressure stage 6, with respect to the axial direction of the turbine rotor 2, there is an outlet opening 8 (see Fig. 2) arranged for the discharge of low-pressure steam, which is discharged from the drive flow path 50. Low-pressure steam discharged from the drive flow path 50 flows through the chamber 4 to be discharged through the outlet opening 8 and is then heated by a reheater (not shown).

[0027] In some embodiments, the protruding section 30 is formed on the inner surface 20a of the outer housing 20 facing the outer surface 10a of the inner housing 10, with the stationary blade row 11 of high-pressure stage 6 formed thereon. The protruding section 30 is formed in an annular shape in the circumferential direction on the inner surface 20a of the outer housing 20, integrated with the outer housing 20. The protruding section 30 has a rectangular shape in a cross-sectional view. It should be noted that the cross-sectional shape of the protruding section 30 is not limited to a rectangle and can also be trapezoidal.

[0028] As in Fig. 1 and Fig. As shown in Figure 4 (partial cross-sectional views), the projecting section 30 is arranged slightly offset to the left of the partition plate 40 with respect to the axial direction of the turbine rotor 2. In particular, the projecting section 30 extends into the second spatial section 4b. If the partition plate 40 is not deformed rigidly, a gap 31 is thus formed between a distal end section of the partition plate 40 and the projecting section 30. Consequently, the partition plate 40 and the projecting section 30 do not need to be in contact during assembly of the outer casing 20, thus facilitating the assembly process.

[0029] The partition plate 40, which is capable of contacting the aforementioned section 30, is made of metal (e.g., cast chromium steel) and exhibits elasticity, and is integrated with the inner housing 10. The partition plate 40 has a thickness (thickness in the axial direction of the turbine rotor 2) that decreases outwards in the radial direction of the turbine rotor 2 from an outer surface of the inner housing 10. This reduces the bending stiffness of the partition plate 40 against a pressure P applied by high-temperature and high-pressure steam in the axial direction of the turbine rotor 2. Thus, the partition plate 40 can deform with less difficulty in the axial direction of the turbine rotor 2 in response to the pressure P applied to a side surface of the partition plate 40 in the axial direction of the turbine rotor 2.

[0030] It should be noted that the shape of the partition plate 40 is not limited to a shape that begins to taper from the outer surface 10a of the inner housing 10, and the partition plate 40 may be more tapered on a distal end side than on a base side, as shown in Fig. 5 shown.

[0031] As described above, as in Fig. 1 and Fig. Figure 2 shows that in the fluid sealing structure 1, high-temperature and high-pressure steam S1 (e.g. 500 °C to 600 °C, 170 to 240 kg / cm³) is supplied by a steam turbine according to some embodiments. 2The high-pressure steam S1 is fed to the high-pressure steam inlet 21 and flows inside the inner casing 10 to be introduced at high velocity into the drive flow path 50 of the high-pressure stage 6. As the high-temperature, high-pressure steam S1 flows through the drive flow path 50 at high velocity, it exerts a rotational force on the rotating blade array 3 of the high-pressure stage 6 and gradually decreases in temperature and pressure. A significant portion of this steam S2, with a reduced temperature (e.g., 300 to 400 °C, 35 to 60 kg / cm²), 2 ) flows through room 4 to be drained through outlet opening 8 and reheated.

[0032] However, some of the steam S2 with a reduced temperature can enter turbulent flow in chamber 4 and flow into the space between the outer casing 20 and the inner casing 10 without flowing towards the outlet opening 8. If the steam S2 with a reduced temperature flows through chamber 4, the outer casing 20 is cooled along the axial direction of the turbine rotor 2.

[0033] Meanwhile, to the right of the high-pressure steam inlet 21, with respect to the axial direction of the turbine rotor 2, the intermediate-pressure stage 7 is arranged as described above, and high-temperature, high-pressure steam S3 is supplied to the intermediate-pressure stage 7 via chamber 4. Thus, the high-temperature, high-pressure steam S3 increases the temperature of the outer casing 20 on the right side of the high-pressure steam inlet 21 with respect to the axial direction of the turbine rotor 2. Consequently, the temperature of the outer casing 20 varies between different positions in the axial direction of the turbine rotor 2, and the difference is particularly greater between a portion of the outer casing 20 in contact with the high-temperature steam and a portion of the outer casing 20 in contact with the lower-temperature steam S2.As the temperature of the outer casing 20 changes rapidly in some parts, a part of the outer casing 20 with an increased temperature expands and a part of the outer casing 20 with a decreased temperature contracts, which consequently can reduce a fastening force of bolts that fasten and fix the upper and lower parts of the outer casing 20.

[0034] In this respect, according to the present embodiment, if a pressure difference between high-temperature and high-pressure steam S3 inside the first chamber section 4a and low-temperature and low-pressure steam S2 inside the second chamber section 4b exceeds a predetermined value, the partition plate 40 deforms rigidly towards the forward section 30, and the distal end section of the partition plate 40 contacts the forward section 30 airtight. Herein, the first chamber section 4a is a section of the chamber 4 on the right side of the partition plate 40 with respect to the axial direction of the turbine rotor 2, and the second chamber section 4b is a section of the chamber 4 on the left side of the partition plate 40 with respect to the axial direction of the turbine rotor 2.

[0035] Consequently, the first chamber section 4a and the second chamber section 4b are sealed off from each other, thus preventing the low-temperature, low-pressure steam S2 from flowing into the first chamber section 4a. Only high-temperature, high-pressure steam S3 flows into the first chamber section 4a, thereby reducing the temperature difference in the axial direction of the turbine rotor 2 for the outer casing 20, which is in contact with the high-temperature, high-pressure steam S3. Furthermore, only low-temperature, low-pressure steam S2 flows into the second chamber section 4b, thus reducing the temperature difference in the axial direction of the turbine rotor 2 for the outer casing 20, which is in contact with the low-temperature, low-pressure steam S2.This means it is possible to prevent rapid temperature changes in the axial direction of the turbine rotor 2 for the outer casing 20, which is in contact with steam in each of the first and second sections 4b. This prevents the bolts securing and fixing the upper and lower parts of the outer casing 20 from loosening.

[0036] The length of the first space section 4a is longer than that of the second space section 4b, with respect to the axial direction of the turbine rotor 2. Thus, the outer casing 20 has a relatively small temperature difference between an end of the first space section 4a adjacent to the second space section 4b and a part that is in contact with low-temperature, low-pressure steam S2. Therefore, there is no risk of loosening of bolts located on the outer casing 20 at an adjacent position between the first space section 4a and the second space section 4b.

[0037] Next, an illustrative embodiment will be described in detail with reference to Fig. 1, Fig. 6A and Fig. 6B will be described. In the Fig. In the illustrative embodiment shown in Figure 1, the inner housing 10 comprises a connecting flow path 12 through which the drive flow path 50 is connected to the first chamber section 4a. The connecting flow path 12 can supply high-pressure steam flowing through the drive flow path 50 to the first chamber section 4a in order to adjust the pressure inside the first chamber section 4a. The number of connecting flow paths 12 is selected according to the pressure required in the first chamber section 4a. Thus, the connecting flow path 12 makes it possible to optionally set a pressure inside the first chamber section 4a, and this allows the outer housing 20 and the inner housing 10, which are exposed to steam inside the first chamber section 4a, to be designed with optimal material and thickness.

[0038] At the in Fig. 6A and Fig. In the illustrative embodiment shown in Figure 6B, an annular sealing element 60 is arranged on a side surface 30a of the protruding section 30 of the dividing plate 40, as shown in Fig. Figure 6A shows the annular sealing element 60 being formed from a material having a larger coefficient of linear expansion than the preceding section 30, such as austenitic stainless steel and Inconel. The annular sealing element 60 is mounted inside an annular groove 30b located on the side surface 30a of the preceding section 30. The annular sealing element 60 has a side surface 60a with a frustoconical shape and is formed in an annular shape to have an outer diameter that increases axially from one end to the opposite end.

[0039] The annular sealing element 60 comprises a sealing body 61, which is formed in a band shape, and a base 62, which connects opposite ends of the sealing body 61 to form the sealing body 61 into an annular shape. When the annular sealing element 60 is not in contact with the dividing plate 40, an end section from one side of the annular sealing element 60 projects axially from the annular groove 30b. When the annular sealing element 60 is in contact with the dividing plate 40, it deforms rigidly to the other side axially.If the partition plate 40 touches the preceding section 30, the partition plate 40 thus touches the preceding section 30 and also the annular sealing element 60, and thereby it is possible to achieve an airtight sealing property between the first room section 4a (see . Fig. 4) and the second sub-section 4b (see Fig. 4) to improve even further.

[0040] The embodiments of the present invention have been described above. However, the present invention is not limited thereto, and various modifications can be applied as long as they do not deviate from the subject matter of the present invention. For example, the present invention can be applied not only to a steam turbine but also to a gas turbine, and the embodiments described above can be implemented in combination. Description of reference symbols 1 Fluid sealing structure of steam turbine 2 turbine rotor 3 Rotating blade row 4 rooms 4a First room section 4b Second room section 6 high-pressure stage 7 Medium pressure stage 8 Outlet opening 10 inner housings 10a Outer surface 11 Stationary shovel row 12 Connecting flow path 20 outdoor enclosures 20a Internal surface 21 High-pressure steam inlet 30 Foreground section 30a, 60a Side surface 30b Circular groove 31 gap 40 Dividing plate 50 Drive flow path 60 Circular sealing element 61 sealing bodies 62 sockets

Claims

[1] Fluid sealing structure (1) of a heat engine with a steam turbine, comprising: an inner housing (10) which rotatably accommodates a turbine rotor (2) inside the inner housing (10); an outer casing (20) which accommodates the inner casing (10) and forms a space (4) through which a fluid can flow between the outer casing (20) and an outer surface (10a) of the inner casing (10); a projecting section (30) projecting into the space (4) from one of the outer surfaces (10a) of the inner housing (10) or an inner surface (20a) of the outer housing (20), wherein the projecting section (30) is formed in an annular shape in a circumferential direction of one of the surfaces (10a, 20a); and a subdivision plate (40) which extends from the other outer surface (10a) or inner surface (20a) into the space (4) and is formed in a circular ring shape in a circumferential direction of the other surface (10a, 20a), wherein the dividing plate (40) the space (4) is divided into a first space subsection (4a) in which the preceding section (30) is not arranged and which is arranged on a first side with respect to an axial direction of the turbine rotor (2), and a second space subsection (4b) in which the preceding section (30) is arranged and which is arranged on a second side with respect to the axial direction of the turbine rotor (2), and in the axial direction of the turbine rotor (2) is deformable in a bending-stiff manner by an internal fluid pressure difference between the first space section (4a) and the second space section (4b), wherein the dividing plate (40) is designed to contact the preceding section (30) airtight only if it is deformed rigidly towards the second room section (4b) in response to the difference in internal fluid pressure which exceeds a predetermined value. [2] Fluid sealing structure (1) of a heat engine with a steam turbine according to claim 1, wherein the dividing plate (40) is designed to have a thickness in the axial direction of the turbine rotor (2) which decreases outwards in a radial direction of the turbine rotor (2), at least at a distal end section of the dividing plate (40). [3] Fluid sealing structure (1) of a heat engine with a steam turbine according to claim 1 or 2, wherein the outer housing (20) comprises a fluid supply path (22) which is designed to supply the fluid to the inner housing (10), wherein the inner housing (10) comprises a drive flow path (50) which is configured to direct the fluid supplied through the fluid supply path (22) to the turbine rotor (2) in order to drive the turbine rotor (2), and wherein the propulsion flow path (50) and the first space section (4a) are connected to each other via a connecting flow path (12). [4] Fluid sealing structure (1) of a heat engine with a steam turbine according to one of claims 1 to 3, further comprising an annular sealing element (60) which is arranged on a side surface of the protruding section (30) facing the dividing plate (40), wherein the annular sealing element (60) comprises a material which has a greater coefficient of linear expansion than the protruding section (30).

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