CN117027968A - Steam turbine and gland seal structure - Google Patents
Steam turbine and gland seal structure Download PDFInfo
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- CN117027968A CN117027968A CN202311121327.XA CN202311121327A CN117027968A CN 117027968 A CN117027968 A CN 117027968A CN 202311121327 A CN202311121327 A CN 202311121327A CN 117027968 A CN117027968 A CN 117027968A
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- 210000004907 gland Anatomy 0.000 title description 15
- 230000007423 decrease Effects 0.000 claims description 3
- 230000000694 effects Effects 0.000 abstract description 23
- 244000126211 Hericium coralloides Species 0.000 description 7
- 238000009434 installation Methods 0.000 description 6
- 238000005192 partition Methods 0.000 description 5
- 238000007789 sealing Methods 0.000 description 5
- 230000004323 axial length Effects 0.000 description 4
- 230000009286 beneficial effect Effects 0.000 description 3
- 238000013461 design Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000010992 reflux Methods 0.000 description 3
- 230000006978 adaptation Effects 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000001788 irregular Effects 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/08—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between rotor blade tips and stator
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
The application provides a steam turbine and a steam seal structure, wherein the steam turbine comprises a rotor and a stator, at least one of the rotor and the stator is provided with a plurality of first grooves distributed along the axial direction, and the notch of each first groove faces the other; the groove surface of the first groove comprises a bottom surface and two opposite side surfaces, the side surface positioned at the outer side is a pressure surface, the side surface positioned at the inner side is a suction surface, the bottom surface is a first rotation surface, the suction surface, the first rotation surface and the pressure surface are concave curved surfaces, the curvature radius of the pressure surface is smaller than that of the suction surface, and the suction surface and the pressure surface are both inclined inwards by respective edges. On the premise of ensuring the steam seal effect, the safe operation of the rotor is not influenced, and the axial space can be saved.
Description
Technical Field
The application relates to the technical field of steam seals, in particular to a steam turbine and a steam seal structure.
Background
The steam turbine includes a rotor and a stator, which have a radial gap therebetween in order to ensure smooth rotation of the rotor with respect to the stator, from which steam may leak to the outside of the steam turbine. For this reason, a comb-tooth type vapor seal structure is mainly adopted at present.
The steam seal structure comprises a plurality of annular thin metal steam seal pieces which are sequentially arranged along the axial direction, namely steam seal teeth, wherein the steam seal teeth and the surface of the rotor maintain a set radial clearance value, the clearances between the steam seal teeth and the surface of the rotor form annular orifices, and an annular steam chamber is formed between every two annular orifices. When steam leaks through the steam seal structure, the steam must pass through each annular steam chamber in turn, and each time the steam passes through one annular orifice, the pressure of the steam is reduced, and the sum of the pressure differences at two sides of all the annular orifices is the total pressure difference maintained by the whole steam seal structure. Therefore, in order to improve the sealing capability, the steam seal gap needs to be reduced or the number of steam seal teeth needs to be increased.
However, reducing the gland clearance has an adverse effect on the safe operation of the rotor; increasing the number of gland seal teeth requires more axial space.
Disclosure of Invention
The application aims to provide a steam turbine and a steam seal structure, which can not influence the safe operation of a rotor and save axial space on the premise of ensuring the steam seal effect.
The steam turbine comprises a rotor and a stator, wherein at least one of the rotor and the stator is provided with a plurality of first grooves distributed along the axial direction, and the notch of each first groove faces the other; the groove surface of the first groove comprises a bottom surface and two opposite side surfaces, the side surface positioned at the outer side is a pressure surface, the side surface positioned at the inner side is a suction surface, the bottom surface is a first rotation surface, the suction surface, the first rotation surface and the pressure surface are concave curved surfaces, the curvature radius of the pressure surface is smaller than that of the suction surface, and the suction surface and the pressure surface are both inclined inwards by respective edges.
In a specific embodiment, the steam seal structure is arranged on one side of the stator facing the rotor or one side of the rotor facing the stator; the first groove is formed in the steam seal structure.
In a specific embodiment, the suction surface, the first rotation surface and the pressure surface are cambered surfaces, and the suction surface, the first rotation surface and the pressure surface are connected in a two-to-two cutting manner.
In a specific embodiment, the walls between adjacent first grooves form steam seal teeth, the steam seal teeth gradually decrease in thickness towards the direction approaching the rotor or the stator, and the steam seal teeth have end faces facing the rotor or the stator.
In one embodiment, one of the rotor and the stator is provided with the first groove, and the other is provided with a second groove; the groove surface of the second groove is a concave curved surface, and at least part of the notch of the second groove is opposite to the notch of the first groove.
In a specific embodiment, the groove surface of the second groove comprises a second rotation surface and a diversion surface which are connected in sequence, the diversion surface is positioned on the inner side of the second rotation surface, the second rotation surface and the diversion surface are cambered surfaces, the second rotation surface is connected with the diversion surface in a tangent mode, and the curvature radius of the second rotation surface is smaller than that of the diversion surface.
In one embodiment, the groove surface of the second groove further comprises a flat surface extending in a radial direction, the flat surface engaging the second rotation surface and the surface of the rotor or the stator.
In a specific embodiment, the interval between the adjacent first grooves is a first interval, the interval between the adjacent second grooves is a second interval, and the first interval is smaller than the second interval.
In one embodiment, the depth of the second groove is less than the depth of the first groove.
The application also provides a steam seal structure, which is provided with a plurality of annular first grooves distributed along the axial direction, wherein the groove surface of the first grooves comprises a bottom surface and two opposite side surfaces, the side surface positioned at the outer side is a pressure surface, the side surface positioned at the inner side is a suction surface, the bottom surface is a first rotation surface, the suction surface, the first rotation surface and the pressure surface are concave curved surfaces, the curvature radius of the pressure surface is smaller than that of the suction surface, and the suction surface and the pressure surface are both inclined inwards by respective edges.
In a specific embodiment, the suction surface, the first rotation surface and the pressure surface are cambered surfaces, and the suction surface, the first rotation surface and the pressure surface are connected in a two-to-two cutting manner.
The steam seal not only realizes the steam seal by utilizing the throttling effect of the steam seal teeth, but also has the advantage that the steam seal can be guided to enter the first groove to boost pressure and flow back to the inner coil to generate self-limiting effect, namely self-limiting steam entering, so that a better steam seal effect is achieved. Compared with the comb-tooth type steam seal structure in the background art, when the same sealing effect is achieved, only the steam seal structure with shorter axial length is needed, so that the steam seal structure is beneficial to more compact design of a steam turbine, the axial occupied space can be reduced, or when the length of the steam seal structure is the same as the axial length of the comb-tooth type steam seal structure in the background art from another angle, the steam seal effect is better.
Drawings
FIG. 1 is a schematic illustration of a gland seal position of a steam turbine in accordance with an embodiment of the present application;
FIG. 2 is an enlarged view of the portion A of FIG. 1;
fig. 3 is an enlarged view of the first groove and the second groove positions of fig. 2.
The reference numerals in fig. 1-3 are illustrated as follows:
1-a steam seal structure; 11-an installation part; 12-a sleeve-shaped body; 121-a first groove; 1211-suction side; 1212-a first surface of revolution; 1213-pressure side; 122-steam seal teeth;
2-rotor; 21-a second groove; 211-a second surface of revolution; 212-a flow guiding surface; 213-plane; 22-dividing wall.
Detailed Description
In order to better understand the aspects of the present application, the present application will be described in further detail with reference to the accompanying drawings and detailed description.
Referring to fig. 1, fig. 1 is a schematic diagram illustrating a steam seal position of a steam turbine according to an embodiment of the application.
The turbine comprises a rotor 2 and a stator, not shown in the figures, schematically a gland 1 mounted to the stator. For the inner rotor structure, the stator is sleeved outside the rotor 2, for the outer rotor structure, the rotor 2 is sleeved outside the stator, the stator and the rotor 2 are coaxially arranged, the rotor 2 of the steam turbine can rotate relative to the stator under the pushing of steam, and a certain radial gap is reserved between the rotor 2 and the stator in order to ensure flexible rotation.
The steam turbine in this embodiment includes gland structure 1, gland structure 1 sets up in the stator towards one side of rotor 2, specifically in fig. 1, gland structure 1 includes annular cover form main part 12, the outside of cover form main part 12 has annular installation department 11, the cross section of installation department 11 is the T type, the stator has seted up corresponding mounting groove towards one side of rotor 2, installation department 11 can insert in the mounting groove of stator, can dispose the spring between the bottom of installation department 11 and mounting groove to make installation department 11 and mounting groove block location, gland structure 1 and stator adopt detachable connected mode, do benefit to loading and unloading.
It should be noted that, in the vapor seal structure 1 of the present embodiment, an annular first groove 121 is formed on a surface of a side facing the rotor 2, and the vapor seal structure 1 specifically includes a plurality of first grooves 121 distributed along an axial direction, wherein a notch of each first groove 121 faces the rotor 2, and a wall between two adjacent first grooves 121 forms vapor seal teeth 122. The axial direction described in this embodiment is the axial direction of the stator and rotor 2. The gland sealing structure 1 may be provided at both ends of the turbine in the axial direction to prevent the internal steam or the like from leaking from both ends of the turbine to the outside of the turbine through a radial gap between the stator and the rotor 2.
As can be appreciated in conjunction with fig. 2 and 3, fig. 2 is an enlarged view of the portion a of fig. 1; fig. 3 is an enlarged view of the positions of the first groove 121 and the second groove 21 in fig. 2.
As can be seen from fig. 2, the groove surface of the first groove 121 of the steam seal structure 1 includes a bottom surface and two opposite side surfaces, the side surface located at the outer side is a pressure surface 1213, the side surface located at the inner side is a suction surface 1211, the bottom surface is a first rotation surface 1212, the inner side and the outer side described herein, i.e. the direction close to the axial middle position of the rotor 2 or the stator, are inward, and vice versa, steam leaks from the inner side to the outer side of the steam turbine, i.e. the suction surface 1211 is also closer to the steam inlet side, the flow direction of the steam is indicated by the hollow arrow in fig. 1, the steam seal structure 1 is obviously arranged at the left end of the steam turbine, and the steam seal structure at the right end and the steam seal structure 1 in fig. 1 are mirror symmetry. It can be seen that the first groove 121 is an annular groove, and the suction surface 1211, the first rotation surface 1212 and the pressure surface 1213 are respectively annular surfaces, which enclose the first groove 121 with a notch on one side. In this embodiment, the suction surface 1211, the first rotation surface 1212 and the pressure surface 1213 of the first groove 121 are all concave curved surfaces, i.e. the concave curved surfaces have no protrusions, and are concave as a whole relative to the solid portion of the vapor seal structure 1. In addition, in order to reduce the flow resistance of steam, suction surface 1211, first rotation surface 1212 and pressure surface 1213 are gently joined without an angular abrupt region.
It should be emphasized that the radius of curvature of the pressure surface 1213 of the first groove 121 is smaller than the radius of curvature of the suction surface 1211, the suction surface 1211 and the pressure surface 1213 are inclined inwards from the position corresponding to the notch of the first groove 121, that is, the positions corresponding to the notch, that is, the edges of the suction surface 1211 and the pressure surface 1213, the root of the suction surface 1211 is defined as the portion connected to the first rotation surface 1212, and the root of the pressure surface 1213 is also defined as the portion connected to the first rotation surface 1212, so that the suction surface 1211 and the pressure surface 1213 are inclined inwards gradually from the edge to the root, and in fig. 2, the suction surface 1211 and the pressure surface 1213 are inclined gradually to the left from the root above the edge of the lower end, and the inclined direction and the steam inlet direction (that is, the axial direction) form an included angle. In fig. 2, the center of the circle of the first rotation surface 1212 is O, the intersection point of the extension lines of the line of the suction surface 1211 and the line of the pressure surface 1213 is P, the center O is connected with the intersection point P, the included angle between the line and the axial direction is α, the included angle α can be approximately used as a reference for reflecting the inclination amplitude of the suction surface 1211 and the pressure surface 1213, in fact, the suction surface 1211 and the pressure surface 1213 are curved surfaces, the included angles between different positions relative to the axial direction are different, and a smaller deviation exists between the included angle α.
In addition, the surface of the steam seal structure 1 facing the rotor 2 is an axially extending surface, so that the end surfaces of the steam seal teeth 122 facing the rotor 2 are in the same axial plane, and accordingly, the edges of the suction surface 1211 and the pressure surface 1213 are also axially flush, and at this time, since the suction surface 1211 and the pressure surface 1213 are obliquely arranged, the length from the edge to the root of the suction surface 1211 is greater than the length from the edge to the root of the pressure surface 1213, i.e. the contour of the first groove 121 is seen from the axial cross-sectional view of fig. 2, and the line length of the suction surface 1211 is longer than the line length of the pressure surface 1213.
It can be seen that the first groove 121 in this embodiment is a special groove, and based on the above definition, the first groove 121 is a groove substantially in the shape of a leading edge section of a bird wing. As shown in fig. 2, the contours of suction surface 1211 and pressure surface 1213 are elongated and intersect to form a contour that is generally in the shape of a bird wing, where only a portion of the structure of the leading edge segment of the bird wing is taken.
As will be appreciated in connection with fig. 2, the flow path of the steam is illustrated in fig. 2 by dashed arrows. After the steam enters the steam seal gap between the steam seal teeth 122 and the rotor 2 to throttle, the steam forms an adhesion flow on the suction surface 1211 of the first groove 121 and flows forwards, in fig. 2, the steam flows forwards in an inclined way, after reaching the first rotation surface 1212, the steam flows onto the pressure surface 1213 along the first rotation surface 1212, the radian of the first rotation surface 1212 is larger, a larger steering effect is achieved, the flow direction of the steam on the pressure surface 1213 is changed into a backward inclined flow, and the fact that the curvature radius of the pressure surface 1213 is smaller than that of the suction surface 1211 can be understood that the curvature degree of the pressure surface 1213 is larger, and the pressure of the steam is gradually increased in the process of flowing along the pressure surface 1213. The higher vapor pressure of the pressure surface 1213 than the suction surface 1211 forces most or all of the vapor throttled by the seal teeth 122 of the seal structure 1 to flow along this path at all times. The pressure surface 1213 is located outside and behind the suction surface 1211 with respect to the direction of steam intake, and the pressure surface 1213 is inclined outwardly such that steam exiting the pressure surface 1213 will be directed forward, i.e., opposite the entering steam, such that steam exiting the pressure surface 1213 will have an impeding and restricting effect on the steam flowing into the first recess 121, thereby reducing the amount of steam that leaks from the seal gap.
Therefore, in the vapor seal structure 1 of the present embodiment, not only the throttling effect of the vapor seal teeth 122 is utilized to realize vapor seal, but also the first groove 121 with a bird wing shape is provided on the vapor seal structure 1, so that the vapor can be guided to enter the first groove 121 to be boosted and then flow back to the inner coil to generate a self-limiting effect, i.e. the vapor is self-limited, thereby achieving a better vapor seal effect. Compared with the comb-tooth type steam seal structure in the background art, when the same sealing effect is achieved, only the steam seal structure 1 with shorter axial length is needed, so that the steam turbine is more compact in design, occupied space can be reduced, or from another angle, when the axial length of the steam seal structure 1 is the same as that of the comb-tooth type steam seal structure in the background art, the steam seal effect in the embodiment is better.
In this embodiment, the concave curved surfaces of the suction surface 1211, the first rotation surface 1212 and the pressure surface 1213 of the first groove 121 may be cambered surfaces, and the concave curved surfaces are completely matched with the bird wing surface, so that the bird wing surface can better drain, boost and reflux, but compared with the complex bird wing surface, the cambered surfaces are more convenient to manufacture and process, and can achieve similar drainage boosting reflux effects. In addition, the suction surface 1211 is tangent to the cambered surface of the first rotary surface 1212, and the cambered surface of the first rotary surface 1212 and the cambered surface of the pressure surface 1213 are tangent to each other, that is, the positions where the suction surface and the cambered surface are connected to each other are tangent to each other, so that smooth connection can be realized, and the steam can smoothly flow according to a predetermined path. As can be seen in fig. 2, the radius of curvature of first surface of revolution 1212 is minimized to ensure that steam can flow along a predetermined path to pressure surface 1213, and first groove 121 is a relatively deep groove structure overall to provide sufficient space for the steam to swirl under pressure as it flows internally.
In the present embodiment, the thickness of the seal teeth 122 gradually decreases toward the rotor 2, as shown in fig. 3, based on the oblique arrangement of the whole first groove 121 and the airfoil design of the concave curved surface, the seal teeth 122 are not in a regular shape, and the thickness T of the seal teeth 122 is gradually designed on the axial section, of the two side surfaces distributed along the axial direction, one side surface near the inner side is a pressure surface 1213 of one first groove 121, the other side surface near the outer side is a suction surface 1211 of the other first groove 121, and the difference between the curvature radii of the suction surface 1211 and the pressure surface 1213 can be seen from the shape change of the two side surfaces of the seal teeth 122. From fig. 3, the gland teeth 122 have an end face 1221 facing the rotor 2, i.e. the gland teeth 122 have a certain thickness T, not sharp teeth. As can be seen from the foregoing description, the sealing effect of the steam seal structure 1 in this embodiment does not depend on the throttling effect of the steam seal teeth 122 completely, so the setting value of the steam seal gap in this embodiment can be designed to be larger than that of the comb-tooth type steam seal structure in the background art, and the thickness T of the steam seal teeth 122 can also be set to be larger than that of the steam seal teeth of the comb-tooth type steam seal structure in the background art, so that the increase of the steam seal gap is beneficial to ensuring safe and stable operation of the rotor 2 on the premise of meeting the steam seal requirement, and the increase of the thickness of the steam seal teeth 122 is beneficial to ensuring the long-term performance of the steam seal.
As shown in fig. 2, the first groove 121 in the present embodiment is disposed in the steam seal structure 1, and the rotor 2 is provided with a plurality of annular second grooves 21 distributed along the axial direction, where the notches of the second grooves 21 face the stator, and in this embodiment, face the steam seal structure 1 directly. The groove surface of the second groove 21 is also a concave curved surface, and at least part of the notch of the second groove 21 is opposite to the notch of the first groove 121. So configured, when the steam flowing out from the pressure surface 1213 collides with the steam flowing in from the seal teeth 122, the steam is guided by the second grooves 21 on the surface of the rotor 2 and swirls to the seal gap on the steam inlet side, thereby further preventing the steam from leaking in from the seal gap. That is, part of the steam flowing out of the pressure surface 1213 after the steam collides and a small amount of steam which has not yet entered the first groove 121 may enter the second groove 21, and after flowing along the concave curved surface of the second groove 21, the steam will also flow back to the steam seal gap position where the steam enters, so that the steam seal effect can be further improved by using the first groove 121 and the second groove 21 in combination.
Further, as shown in fig. 2, the groove surface of the second groove 21 includes a second rotation surface 211 and a diversion surface 212 which are sequentially connected, the diversion surface 212 is located at the inner side of the second rotation surface 211, and for convenience of processing, the second rotation surface 211 and the diversion surface 212 are both cambered surfaces, and the curvature radius of the second rotation surface 211 is smaller than that of the diversion surface 212. The flow guiding surface 212 is more gentle and has a longer length, so that after the steam is introduced into the second groove 21 in time and flows towards the second rotation surface 211, the second rotation surface 211 is similar to the first rotation surface 1212 in effect, the second rotation surface 211 and the first rotation surface 1212 can be in an arc between approximately one third and one half, the flow direction of the steam can be changed into reverse or approximately reverse, the flow guiding surface 212 guides the steam forwards and towards the bottom of the second groove 21, and then the steam flows back towards the direction close to the steam seal structure 1 through the guide of the second rotation surface 211, so that the steam enters the steam seal gap position again to block the steam. The second rotation surface 211 and the diversion surface 212 of the second groove 21 are also tangentially connected to each other so as to form a gentle transition.
As shown in fig. 2, the groove surface of the second groove 21 further comprises a flat surface 213, the flat surface 213 extending in a radial direction, the flat surface 213 engaging the second rotation surface 211 and the surface of the rotor 2 facing the stator. The flat surface 213 may better prevent steam from continuing forward flow, but instead form convolutions as the second surface of revolution 211 flows rearward, of course, the flat surface 213 is smaller in radial dimension to ensure that the second surface of revolution 211 has sufficient dimensional drainage.
In addition, in the present embodiment, the interval between the adjacent first grooves 121 is defined as a first interval, the interval between the adjacent second grooves 21 is defined as a second interval, and the first interval is smaller than the second interval. The gap between the steam seal teeth 122 and the surface of the rotor 2 is a steam seal gap, the wall between two adjacent second grooves 21 is defined as a partition wall 22, as shown in fig. 3, the width or thickness of the partition wall 22 at the end face position is D2, that is, the size of the second space, and the thickness or width of the steam seal teeth 122 at the end face 1221 is D1, that is, the size of the first space, and D2 is significantly larger than D1. In addition, the width of the notch of the first groove 121 in the axial direction is W1, and the widths of the notches of the second groove 21 in the axial direction are W2, W2 and W1, which are approximately equal to each other, so as to receive the corresponding steam reflux. At this time, if the first pitch and the second pitch are equal, the seal teeth 122 and the partition wall 22 are substantially aligned in the radial direction, but when the rotor 2 and the seal structure 1 are relatively aligned in the axial direction, the seal teeth 122 and the partition wall 22 are staggered, the staggered dimensions of each seal tooth 122 and the partition wall 22 are identical, and the length of the seal gap is changed identically, resulting in deterioration of the seal effect.
Referring again to fig. 3, the first pitch is set smaller than the second pitch, and the width W1 of the first groove 121 in the axial direction and the width W2 of the second groove 21 in the axial direction are substantially equal, so that in the case that no axial movement occurs, all the first groove 121 and the second groove 21 are not completely corresponding to the notch, and the notch portions of the first groove 121 and the corresponding second groove 21 are partially staggered, as in fig. 3, the notch portions of the first groove 121 on the left side and the second groove 21 on the lower side are substantially aligned, while the notch portions of the first groove 121 on the middle side and the second groove 21 on the lower side are staggered, the notch width W21 of the second groove 21 is partially opposite to the right side portion of the first groove 121 on the middle side, and the notch width 222 of the second groove 21 is partially opposite to the left side portion of the first groove 121 on the rightmost side, so that, when the rotor 2 and the steam seal structure 1 are axially displaced, for example, the first groove 121 on the left side and the second groove 21 on the lower side are staggered, and the notch widths of the first groove 121 on the lower side are partially staggered, and the width W21 on the lower side is completely aligned. Fig. 3 only illustrates the relative situation of the notches of a small part of the first groove 121 and the second groove 21, and it can be understood in conjunction with fig. 1 that, even if the steam seal structure 1 and the rotor 2 axially move, the notch parts of the first groove 121 and the second groove 21 are still opposite, and part of the first groove 121 and the second groove 21 are approximately aligned, so that consistency of the steam seal effect is ensured. The gland 1 in this embodiment is therefore particularly suitable for use in a steam turbine having a relatively large relative axial displacement from the rotor 2.
In this embodiment, the depth of the second groove 21 may be smaller than the depth of the first groove 121, and the depth is the length dimension from the notch middle to the groove bottom middle. The first grooves 121 have a certain depth to form enough space so that most or all of the entering steam can be pressurized and returned, while the main function of the second grooves 21 is to make a small part of the steam be returned, so that the depth of the second grooves 21 can be smaller than that of the first grooves 121, and the shallower second grooves 21 are also easier to be implemented on the rotor 2.
It should be noted that, in the above embodiments, the first groove 121 is disposed on the vapor seal structure 1 as an example, it is known that the first groove 121 may be directly disposed on the stator, that is, no separate vapor seal structure 1 is disposed, and a part of the body of the stator is directly used as the vapor seal structure, but the first groove 121 is an airfoil groove, and has an irregular shape and a relatively deep depth, and the first groove 121 is disposed on the separate vapor seal structure 1, so that the actual processing is easier, and the replacement and maintenance operations are convenient. It can be known that the first groove 121 may be directly formed on the rotor 2, or the vapor seal structure 1 formed with the first groove 121 may be mounted on the rotor 2; in addition, the first grooves 121 may be provided on both the stator and the rotor 2; alternatively, it is also possible that the second groove 21 is provided in the stator and the first groove 121 is provided to the rotor 2 or to the gland 1 mounted on the rotor 2. Since the stator is a structural member which is kept relatively stationary, and the rotor 2 is a rotary member, the steam seal structure 1 is arranged on the stator in the present embodiment, and the structure is more stable.
The present embodiment also provides a steam turbine, including the steam seal structure 1 of the steam turbine according to any one of the above embodiments, which has the same technical effects as those of the above embodiments, and will not be described again.
The principles and embodiments of the present application have been described herein with reference to specific examples, the description of which is intended only to facilitate an understanding of the method of the present application and its core ideas. It should be noted that it will be apparent to those skilled in the art that various modifications and adaptations of the application can be made without departing from the principles of the application and these modifications and adaptations are intended to be within the scope of the application as defined in the following claims.
Claims (11)
1. Steam turbine comprising a rotor and a stator, characterized in that at least one of the rotor and the stator is provided with a plurality of first grooves distributed in an axial direction, the notches of the first grooves facing the other; the groove surface of the first groove comprises a bottom surface and two opposite side surfaces, the side surface positioned at the outer side is a pressure surface, the side surface positioned at the inner side is a suction surface, the bottom surface is a first rotation surface, the suction surface, the first rotation surface and the pressure surface are concave curved surfaces, the curvature radius of the pressure surface is smaller than that of the suction surface, and the suction surface and the pressure surface are both inclined inwards by respective edges.
2. The steam seal structure of a steam turbine according to claim 1, further comprising a steam seal structure provided on a side of the stator facing the rotor or on a side of the rotor facing the stator; the first groove is formed in the steam seal structure.
3. The steam seal structure of a steam turbine of claim 1, wherein the suction surface, the first rotation surface and the pressure surface are cambered surfaces, and the suction surface, the first rotation surface and the pressure surface are connected in a tangential manner.
4. The steam seal structure of a steam turbine according to claim 1, wherein walls between adjacent ones of the first grooves form steam seal teeth, the steam seal teeth gradually decrease in thickness in a direction approaching the rotor or the stator, and the steam seal teeth have end faces facing the rotor or the stator.
5. The steam seal structure of a steam turbine according to any one of claims 1 to 4, wherein one of the rotor and the stator is provided with the first groove, and the other is provided with an annular second groove; the groove surface of the second groove is a concave curved surface, and at least part of the notch of the second groove is opposite to the notch of the first groove.
6. The steam seal structure of a steam turbine according to claim 5, wherein the groove surface of the second groove comprises a second rotation surface and a diversion surface which are connected in sequence, the diversion surface is located on the outer side of the second rotation surface, the second rotation surface and the diversion surface are cambered surfaces, the second rotation surface is connected with the diversion surface in a tangent mode, and the curvature radius of the second rotation surface is smaller than that of the diversion surface.
7. The steam seal structure of a steam turbine of claim 6, wherein the groove surface of the second groove further includes a flat surface extending in a radial direction, the flat surface engaging the second rotation surface and a surface of the rotor or the stator.
8. The steam seal structure of a steam turbine of claim 5, wherein a pitch between adjacent ones of the first grooves is a first pitch, a pitch between adjacent ones of the second grooves is a second pitch, and the first pitch is smaller than the second pitch.
9. The steam seal structure of a steam turbine of claim 5, wherein a depth of the second groove is smaller than a depth of the first groove.
10. The steam seal structure is characterized in that a plurality of first grooves which are distributed along the axial direction are formed, the groove surfaces of the first grooves comprise a bottom surface and two opposite side surfaces, the side surfaces which are positioned on the outer side are pressure surfaces, the side surfaces which are positioned on the inner side are suction surfaces, the bottom surface is a first rotation surface, the suction surfaces, the first rotation surfaces and the pressure surfaces are concave curved surfaces, the curvature radius of the pressure surfaces is smaller than that of the suction surfaces, and the suction surfaces and the pressure surfaces are all inclined inwards by respective edges.
11. The steam seal structure of a steam turbine of claim 10, wherein the suction surface, the first rotation surface and the pressure surface are cambered surfaces, and the suction surface, the first rotation surface and the pressure surface are connected in a tangential manner.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311121327.XA CN117027968B (en) | 2023-08-31 | 2023-08-31 | Steam turbine and gland seal structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN1217762A (en) * | 1996-05-06 | 1999-05-26 | 创新技术有限责任公司 | Method and apparatus for minimizing leakage in turbine seals |
| US7445213B1 (en) * | 2006-06-14 | 2008-11-04 | Florida Turbine Technologies, Inc. | Stepped labyrinth seal |
| US20110250073A1 (en) * | 2010-04-08 | 2011-10-13 | Sudhakar Neeli | Rotor and assembly for reducing leakage flow |
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| CN117027968B (en) | 2024-10-08 |
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