A double-rotation-flow circuitous steam turbine gland body and a gland

Abstract

The utility model discloses a kind of double-swirl circuitous steam turbine gland body and gland;Belong to steam turbine gland technical field;Its technical key points include gland part;The gland part includes first flow guide tooth, first energy dissipation cavity is equipped in the gland body inner end face between first flow guide tooth and corresponding external rotor boss, second energy dissipation cavity is equipped in the front side of first energy dissipation cavity along steam flow advancing direction;First vortex portion is equipped in first energy dissipation cavity, and second vortex portion is equipped in second energy dissipation cavity;The same mouth of first energy dissipation cavity is entered and exported, and inlet and outlet are located between first flow guide tooth and boss front end face;The same mouth of second energy dissipation cavity is entered and exported, and inlet and outlet are located above corresponding external rotor boss;The utility model aims at providing a kind of double-swirl circuitous steam turbine gland with variable channel, circuitous energy dissipation;For steam turbine gland.

Description

Technical Field

[0001] This utility model relates to a steam turbine seal, and more specifically, to a double-swirling detour type steam turbine seal body and seal. Background Technology

[0002] During the operation of steam power equipment, the sealing effect of the steam seal has a crucial impact on the energy utilization efficiency and operational stability of the equipment. Traditional steam seal structures, such as comb-tooth steam seals, rely primarily on the tiny gaps between the teeth to increase the resistance to steam flow. However, steam can still easily leak through these gaps, leading to reduced thermal efficiency and significant energy waste. While labyrinth steam seals increase the path length of steam leakage to some extent, their complex structure and high manufacturing cost, coupled with the wear and tear on the sealing components caused by impurities carried by the steam during long-term operation, ultimately reduce sealing performance. Utility Model Content

[0003] The purpose of this utility model is to address the shortcomings of the prior art by providing a double-swirling, detour-type steam turbine seal body and seal with variable channels and detour energy dissipation.

[0004] The technical solution of this utility model is as follows: a double swirl detour steam turbine steam seal body, with a steam seal part provided on the inner end face.

[0005] The steam seal includes a first guide tooth opposite to the high-pressure gas, a first energy dissipation cavity is provided on the inner end face between the first guide tooth and the corresponding external rotor boss, a second energy dissipation cavity is provided on the front side of the first energy dissipation cavity along the steam flow direction, a first vortex part is provided in the first energy dissipation cavity, and a second vortex part is provided in the second energy dissipation cavity.

[0006] The first energy dissipation chamber has the same inlet and outlet, and the inlet and outlet are located between the first guide tooth and the front end face of the external rotor boss; the second energy dissipation chamber has the same inlet and outlet, and the inlet and outlet are located above the corresponding external rotor boss.

[0007] The high-pressure gas moving axially enters the steam seal section through the first guide tooth, and is guided to turn radially outward at the front end face of the corresponding external rotor boss. Part of it enters the first energy dissipation chamber, and part of it passes over the external rotor boss and enters the second energy dissipation chamber.

[0008] A double-swirling detour type steam turbine seal includes the aforementioned seal body.

[0009] The aforementioned double-swirling detour steam turbine seal also includes a rotor that passes through the seal body, with several protrusions distributed circumferentially on the rotor.

[0010] In the above-mentioned double-swirling detour steam turbine seal, a vortex groove is provided on the seal body between the inlet and outlet of the first energy dissipation chamber and the inlet and outlet of the second energy dissipation chamber. The opening of the vortex groove is located above the end face of the boss. After the gas collides with the boss, it enters the vortex groove and then flows to both sides into the first energy dissipation chamber and the second energy dissipation chamber respectively.

[0011] In the aforementioned double-swirling detour steam turbine seal, the first vortex section includes a flow-blocking section disposed on the inner wall of one side of the inlet and outlet of the first energy dissipation chamber. A first arc-shaped flow guide section is integrally formed on the flow-blocking section, the arc length of the first arc-shaped flow guide section being greater than half a circle. The first arc-shaped flow guide section and the inner wall of the first energy dissipation chamber cooperate to form a first flow passage. When the steam flow enters the inlet and outlet of the first energy dissipation chamber, it collides with the flow-blocking section and changes direction to enter the first flow passage. A first vortex cavity is formed in the first arc-shaped flow guide section, the diameter of the first vortex cavity being greater than the width of the first flow passage.

[0012] In the aforementioned double-swirling detour steam turbine seal, the second vortex section includes a second arc guide section disposed on the inner wall of one side of the inlet and outlet of the second energy dissipation chamber. The arc length of the second arc guide section is greater than half a circle. The second arc guide section and the inner wall of the second energy dissipation chamber cooperate to form a second flow channel. When the steam flow enters the inlet and outlet of the second energy dissipation chamber, it is guided by the second arc guide section into the second flow channel.

[0013] A second vortex cavity is formed within the second arc-shaped flow guide section. A circular flow guide block is provided within the second vortex cavity. The circular flow guide block cooperates with the inner wall of the second arc-shaped flow guide section to form a vortex channel. The width of the vortex channel is smaller than the width of the second flow channel.

[0014] In the above-mentioned double-swirling detour steam turbine seal, a second guide tooth and a third guide tooth are respectively provided on both sides of the inlet and outlet of the second energy dissipation chamber, and the gap between the second guide tooth and the third guide tooth and the boss is the same size; the second guide tooth and the third guide tooth cooperate to form the inlet and outlet of the second energy dissipation chamber with a width smaller than the width of the second flow channel.

[0015] In the above-mentioned double-swirling detour steam turbine seal, the seal body near the low-pressure end of the third guide tooth is provided with a first turbulence tooth. The gap between the first turbulence tooth and the boss is the same as the gap between the third guide tooth and the boss. The first turbulence tooth and the third guide tooth cooperate to form a turbulence cavity.

[0016] In the above-mentioned double-swirling detour steam turbine seal, a second turbulence tooth is provided at the root of the side wall on the high-pressure end side of the first guide tooth.

[0017] After adopting the above structure, the main steam flow after entering the steam seal section through the first guide tooth is guided by the front end face of the boss and splits into two streams. Most of the steam forms a radial main flow and enters the first energy dissipation chamber, while the other part forms an axial main flow that flows along the gap between the boss and the first diverting tooth to the low-pressure end and enters the second energy dissipation chamber.

[0018] After entering the steam flow channel in the first or second energy dissipation chamber and reaching the innermost end, the steam flow returns along the original path, colliding and dissipating energy with the subsequent steam flow. The subsequent steam flow can also carry some of the returning steam flow back into the energy dissipation chamber, repeating the energy dissipation cycle multiple times. Finally, it exits from the outlet and merges with the mainstream steam flow, forming an obstruction and effectively increasing the resistance and turbulence of the steam flow.

[0019] Simultaneously, the steam flow advances in a vortex pattern along the first and second vortex sections, effectively increasing frictional energy dissipation with the inner wall of the steam seal body. This significantly reduces steam leakage, substantially improves the energy utilization efficiency of steam power equipment, and reduces energy waste. Attached Figure Description

[0020] The present invention will be further described in detail below with reference to the embodiments shown in the accompanying drawings, but this does not constitute any limitation on the present invention.

[0021] Figure 1 This is a schematic diagram of the structure of this utility model;

[0022] Figure 2 This is a cross-sectional structural diagram of the present invention;

[0023] Figure 3 This is a partial structural diagram of point A of this utility model.

[0024] In the figure: 1. Steam seal body; 2. Rotor; 3. Boss; 4. Steam seal section; 5. First guide tooth; 6. First energy dissipation cavity; 7. Second energy dissipation cavity; 8. First vortex section; 8a. Baffle section; 8b. First arc guide section; 8c. First flow passage; 8d. First vortex cavity; 9. Second vortex section; 9a. Second arc guide section; 9b. Second flow passage; 9c. Second vortex cavity; 9d. Circular guide block; 9e. Vortex channel; 10. Vortex groove; 11. Second guide tooth; 12. Third guide tooth; 13. First turbulence tooth; 14. Turbulence cavity; 15. Second turbulence tooth. Detailed Implementation

[0025] See Figure 1-3 As shown, the present invention discloses a double-swirl detour type steam turbine steam seal body, wherein a steam seal part 4 is provided on the inner end face; the steam seal body includes an outer ring for cooperating and connecting with the steam turbine cylinder block, and an inner ring for cooperating with the rotor shaft, wherein the steam seal part is provided on the inner ring.

[0026] The steam seal section 4 includes a first guide tooth 5 opposite to the high-pressure gas. A first energy dissipation cavity 6 is provided on the inner end face of the steam seal body 1 between the first guide tooth 5 and the corresponding external rotor boss. A second energy dissipation cavity 7 is provided on the front side of the first energy dissipation cavity 6 along the steam flow direction. A first vortex section 8 is provided in the first energy dissipation cavity 6, and a second vortex section 9 is provided in the second energy dissipation cavity 7.

[0027] The first energy dissipation cavity 6 has the same inlet and outlet, and the inlet and outlet are located between the first guide tooth 5 and the front end face of the external rotor boss; the second energy dissipation cavity 7 has the same inlet and outlet, and the inlet and outlet are located above the corresponding external rotor boss.

[0028] The high-pressure gas advancing axially enters the steam seal section 4 through the first guide tooth 5, and is guided to turn radially outward at the front end face of the corresponding external rotor boss. Part of it enters the first energy dissipation chamber 6, and part of it passes over the external rotor boss and enters the second energy dissipation chamber 7. After entering the steam seal section through the first guide tooth, the main steam flow is guided by the front end face of the boss and splits into two streams. Most of it forms a radial main flow that enters the first energy dissipation chamber, while the other part forms an axial main flow that flows along the gap between the boss and the first split tooth to the low-pressure end and enters the second energy dissipation chamber.

[0029] After entering the steam flow channel in the first or second energy dissipation chamber and reaching the innermost end, the steam flow returns along the original path, colliding and dissipating energy with the subsequent steam flow. The subsequent steam flow can also carry some of the returning steam flow back into the energy dissipation chamber, repeating the energy dissipation cycle multiple times. Finally, it exits from the outlet and merges with the mainstream steam flow, forming an obstruction and effectively increasing the resistance and turbulence of the steam flow.

[0030] Simultaneously, the steam flow advances in a vortex pattern along the first and second vortex sections, effectively increasing frictional energy dissipation with the inner wall of the steam seal body. This significantly reduces steam leakage, substantially improves the energy utilization efficiency of steam power equipment, and reduces energy waste.

[0031] A double-swirling detour type steam turbine seal includes a steam seal body 1.

[0032] In this embodiment, a rotor 2 is also included, which is inserted into the steam seal body 1, and a plurality of protrusions 3 are distributed circumferentially on the rotor 2.

[0033] The rotor is the core component of the steam turbine. Its outer surface has several protrusions spaced axially. The steam seal seals the high-pressure gas by engaging with the rotor and these protrusions. The rotor and its surface protrusions are not the technical points to be protected by this utility model and will not be described further here.

[0034] In this embodiment, preferably, a vortex groove 10 is provided on the steam seal body 1 between the inlet and outlet of the first energy dissipation chamber 6 and the inlet and outlet of the second energy dissipation chamber 7. The opening of the vortex groove 10 is located above the end face of the boss 3. After colliding with the boss 3, the steam enters the vortex groove 10 and then flows to both sides, entering the first energy dissipation chamber 6 and the second energy dissipation chamber 7 respectively. When the main steam flow is guided by the front end face of the boss to turn radially outward and enter the vortex groove to form a vortex, the steam flow is guided by the vortex groove to form a radial steam flow towards the rotor direction, which merges with the main steam flow below, further consuming energy, changing the flow characteristics, and increasing leakage resistance.

[0035] In this embodiment, preferably, the first vortex section 8 includes a flow-blocking section 8a disposed on the inner wall of one side of the inlet and outlet of the first energy dissipation chamber 6. A first arc-shaped flow guide section 8b is integrally formed on the flow-blocking section 8a, and the arc length of the first arc-shaped flow guide section 8b is greater than half a circle. The first arc-shaped flow guide section 8b and the inner wall of the first energy dissipation chamber 6 cooperate to form a first flow passage 8c. When the steam flow enters the inlet and outlet of the first energy dissipation chamber 6, it collides with the flow-blocking section 8a and changes direction to enter the first flow passage 8c. Since the first arc-shaped flow guide section is an arc and the inner wall of the first energy dissipation chamber is rectangular, the first flow passage formed by the two has a multi-segment channel structure of different sizes, so that the steam flow passes through the channel from large to small or from small to large multiple times in the energy dissipation channel, which can effectively consume energy.

[0036] A first vortex cavity 8d is formed within the first arc-shaped guide portion 8b, and the diameter of the first vortex cavity 8d is larger than the width of the first flow channel 8c. When the steam flows into the first vortex cavity from the first flow channel, the steam velocity slows down due to the instantaneous increase in diameter, and because the inlet and outlet are the same and the diameter is small, the steam will form a reciprocating vortex within the first vortex cavity.

[0037] In this embodiment, preferably, the second vortex section 9 includes a second arc-shaped guide section 9a disposed on the inner wall of one side of the inlet and outlet of the second energy dissipation chamber 7, the arc length of the second arc-shaped guide section 9a being greater than half a circle; the second arc-shaped guide section 9a and the inner wall of the second energy dissipation chamber 7 cooperate to form a second flow channel 9b; when the steam enters the inlet and outlet of the second energy dissipation chamber 7, it is guided by the second arc-shaped guide section 9a into the second flow channel 9b. Since the second arc-shaped guide section is an arc and the inner wall of the second energy dissipation chamber is rectangular, the second flow channel formed by the two has a multi-segment channel structure of different sizes, so that the steam flows through the second flow channel multiple times through channels of decreasing size or increasing size, which can effectively consume energy.

[0038] A second vortex cavity 9c is formed within the second arc-shaped guide section 9a. A circular guide block 9d is provided within the second vortex cavity 9c. The circular guide block 9d cooperates with the inner wall of the second arc-shaped guide section 9a to form a vortex channel 9e. The width of the vortex channel 9e is smaller than the width of the second flow channel 9b. The narrower vortex channel enhances frictional energy dissipation of the steam flow, increasing leakage resistance. When the steam flow reaches the bottom of the vortex channel and returns along its original path, it enters the second flow channel through the vortex channel. The diameter instantly increases, the steam flow velocity slows down, and it is propelled by the incoming steam flow to re-enter the vortex channel for multiple cycles of energy dissipation.

[0039] More preferably, a second guide tooth 11 and a third guide tooth 12 are respectively provided on both sides of the inlet and outlet of the second energy dissipation chamber 7, and the gaps between the second guide tooth 11 and the third guide tooth 12 and the boss 3 are the same size; the second guide tooth 11 and the third guide tooth 12 cooperate to form the inlet and outlet of the second energy dissipation chamber 7 with a width smaller than the width of the second flow channel 9b. When the steam flows into the second flow channel through the inlet and outlet of the second energy dissipation chamber, the steam velocity slows down due to the instantaneous increase in diameter. On the other hand, the steam flowing out of the second flow channel to the inlet and outlet of the second energy dissipation chamber accelerates due to the instantaneous decrease in diameter. The two counteract each other, effectively increasing the resistance and turbulence of the steam flow.

[0040] In this embodiment, preferably, the steam seal body 1 near the low-pressure end of the third guide tooth 12 is provided with a first turbulence tooth 13, the gap between the first turbulence tooth 13 and the boss 3 is the same as the gap between the third guide tooth 12 and the boss 3; the first turbulence tooth 13 and the third guide tooth 12 cooperate to form a turbulence cavity 14. The steam flow that has passed through the first energy dissipation cavity and the second energy dissipation cavity in sequence enters the turbulence cavity, the diameter increases instantaneously, the steam flow velocity slows down, and several vortices of different sizes are formed in the turbulence cavity.

[0041] In this embodiment, preferably, a second turbulence tooth 15 is provided at the root of the side wall on the high-pressure end side of the first guide tooth 5. Before the high-pressure steam flow enters the steam seal section through the gap between the first guide tooth and the rotor, the high-pressure steam flow first collides with the surface of the first guide tooth, and forms a turbulence groove with the steam seal body through the second turbulence tooth, which initially turbulents the high-pressure gas and further improves the energy dissipation effect.

[0042] During operation, the high-pressure steam collides with the surface of the first guide tooth to create initial turbulence, and then enters the steam seal section through the first guide tooth. After being guided by the front end face of the boss, the main steam flow splits into two streams. Most of it becomes a radially outward main flow, while the other part forms an axial main flow that flows along the gap between the boss and the second guide tooth to the low-pressure end.

[0043] The radial mainstream first enters the vortex groove to form a vortex and flows to one side of the rotor. Then it flows towards the first guide tooth and enters the first energy dissipation chamber. After entering the first energy dissipation chamber, the steam flows along the first flow passage into the first vortex chamber and then flows back out along the first flow passage, where it merges with the mainstream steam.

[0044] After passing through the second guide tooth, the axial mainstream enters the second energy dissipation chamber under the guidance of the third guide tooth. After entering the first energy dissipation chamber, the steam flows into the second vortex chamber along the second flow passage, then flows back out along the second flow passage, merges with the axial mainstream, and enters the turbulence chamber. Finally, it continues to advance towards the low-pressure end through the first turbulence tooth.

[0045] The above-described embodiments are preferred embodiments of the present utility model and are only used to facilitate the illustration of the present utility model. They are not intended to limit the present utility model in any way. Any person skilled in the art who makes partial modifications or alterations to the technical content disclosed in the present utility model without departing from the scope of the technical features of the present utility model shall still fall within the scope of the technical features of the present utility model.

Claims

1. A double-swirl detour type steam turbine steam seal body, characterized in that, An air seal (4) is provided on the inner end face; The steam seal (4) includes a first guide tooth (5) opposite to the high-pressure gas. A first energy dissipation cavity (6) is provided on the inner end face between the first guide tooth (5) and the corresponding external rotor boss. A second energy dissipation cavity (7) is provided on the front side of the first energy dissipation cavity (6) along the direction of steam flow. A first vortex part (8) is provided in the first energy dissipation cavity (6), and a second vortex part (9) is provided in the second energy dissipation cavity (7). The first energy dissipation chamber (6) has the same inlet and outlet, and the inlet and outlet are located between the first guide tooth (5) and the front end face of the external rotor boss; the second energy dissipation chamber (7) has the same inlet and outlet, and the inlet and outlet are located above the corresponding external rotor boss; The high-pressure gas moving along the axial direction enters the steam seal section (4) through the first guide tooth (5), and is guided to turn radially outward at the front end face of the corresponding external rotor boss. Part of it enters the first energy dissipation chamber (6), and part of it passes over the external rotor boss and enters the second energy dissipation chamber (7).

2. A double-swirl detour type steam turbine seal, characterized in that, It includes the steam seal body (1) as described in claim 1.

3. The double-swirl detour steam turbine seal according to claim 2, characterized in that, It also includes a rotor (2) that passes through the steam seal body (1), and several bosses (3) are distributed circumferentially on the rotor (2).

4. The double-swirl detour steam turbine seal according to claim 3, characterized in that, A vortex groove (10) is provided on the gas seal body (1) between the inlet and outlet of the first energy dissipation chamber (6) and the inlet and outlet of the second energy dissipation chamber (7). The opening of the vortex groove (10) is located above the end face of the boss (3). After the gas collides with the boss (3), it enters the vortex groove (10) and then flows to both sides into the first energy dissipation chamber (6) and the second energy dissipation chamber (7) respectively.

5. A double-swirl detour steam turbine seal according to claim 2, characterized in that, The first vortex section (8) includes a flow-blocking section (8a) disposed on the inner wall of the inner end of the inlet and outlet of the first energy dissipation chamber (6). A first arc guide section (8b) is integrally formed on the flow-blocking section (8a), and the arc length of the first arc guide section (8b) is greater than half a circle. The first arc guide section (8b) and the inner wall of the first energy dissipation chamber (6) cooperate to form a first flow passage (8c). When the steam enters the inlet and outlet of the first energy dissipation chamber (6), it collides with the flow-blocking section (8a) and changes direction to enter the first flow passage (8c). A first vortex cavity (8d) is formed inside the first arc guide portion (8b), and the diameter of the first vortex cavity (8d) is larger than the width of the first flow channel (8c).

6. A double-swirl detour steam turbine seal according to claim 2, characterized in that, The second vortex section (9) includes a second arc guide section (9a) disposed on the inner wall of the inner end of the inlet and outlet of the second energy dissipation chamber (7), the arc length of the second arc guide section (9a) being greater than half a circle; the second arc guide section (9a) and the inner wall of the second energy dissipation chamber (7) cooperate to form a second flow passage (9b); when the steam flow enters the inlet and outlet of the second energy dissipation chamber (7), it is guided by the second arc guide section (9a) into the second flow passage (9b); A second vortex cavity (9c) is formed inside the second arc guide section (9a), and a circular guide block (9d) is provided inside the second vortex cavity (9c). The circular guide block (9d) cooperates with the inner wall of the second arc guide section (9a) to form a vortex channel (9e). The width of the vortex channel (9e) is smaller than the width of the second flow channel (9b).

7. A double-swirl detour steam turbine seal according to claim 6, characterized in that, The second energy dissipation cavity (7) is provided with a second guide tooth (11) and a third guide tooth (12) on both sides of the inlet and outlet. The gap between the second guide tooth (11) and the third guide tooth (12) and the boss (3) is the same. The second guide tooth (11) and the third guide tooth (12) cooperate to form the inlet and outlet of the second energy dissipation cavity (7) with a width smaller than the width of the second flow channel (9b).

8. A double-swirl detour steam turbine seal according to claim 7, characterized in that, The third guide tooth (12) is provided with a first turbulence tooth (13) on the steam seal body (1) near the low pressure end. The gap between the first turbulence tooth (13) and the boss (3) is the same as the gap between the third guide tooth (12) and the boss (3). The first turbulence tooth (13) and the third guide tooth (12) cooperate to form a turbulence cavity (14).

9. A double-swirl detour steam turbine seal according to claim 2, characterized in that, The first guide tooth (5) has a second turbulence tooth (15) at the root of the side wall on the high-pressure side.

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