CN115680790A - Steam seal device and steam turbine - Google Patents
Steam seal device and steam turbine Download PDFInfo
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- CN115680790A CN115680790A CN202211405720.7A CN202211405720A CN115680790A CN 115680790 A CN115680790 A CN 115680790A CN 202211405720 A CN202211405720 A CN 202211405720A CN 115680790 A CN115680790 A CN 115680790A
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Abstract
The invention discloses a steam sealing device and a steam turbine, wherein the steam sealing device comprises a cylinder, wherein an air cavity for filling steam is formed inside the cylinder; the main shaft is rotatably arranged in the air cavity, and an impeller is arranged on the outer peripheral surface of the main shaft so as to drive the main shaft to rotate by the flow of the steam; the steam seal body is sleeved on the main shaft and arranged at the opening, and a gap is formed between one side of the steam seal body, which is far away from the main shaft, and the inner wall of the opening; the gland casing is connected with an inclined sheet, the inclined sheet is obliquely arranged relative to the axis direction of the main shaft and extends towards the direction deviating from the main shaft. This technical scheme has solved the big technical problem of current steam turbine steam seal structure leakage.
Description
Technical Field
The invention relates to the technical field of dynamic sealing, in particular to a steam sealing device and a steam turbine.
Background
Steam turbines are widely used as power equipment in the fields of power generation, ship power and the like. In the existing steam turbine equipment, particularly a back pressure steam turbine, a comb-tooth type, carbon ring or honeycomb type steam seal structure is generally arranged at the tail end of a main shaft and used for sealing steam in a steam turbine cylinder, so that the efficiency of the steam turbine is improved.
In the existing steam sealing structure, a throttling effect is generally formed on steam inside a steam turbine through the arrangement of a tiny gap in the sealing structure, the steam pressure is gradually reduced through a multilayer throttling mode until the steam pressure is reduced to be almost different from the atmospheric pressure, the approximate balance between the steam pressure and the external atmospheric pressure is realized, and the sealing effect is realized.
However, in the sealing structure, steam can leak from the gap of the sealing structure more or less, and in addition, in order to ensure the sealing effect, the tiny gap in the sealing structure needs to be designed to be small, and the gap is gradually increased along with the wear and the aging of the sealing structure in the operation process of equipment, so that the sealing effect is reduced, and the efficiency of the steam turbine is influenced.
Disclosure of Invention
The invention mainly aims to provide a steam sealing device, and aims to solve the technical problem of large leakage of the existing steam sealing structure of a steam turbine.
In order to achieve the above object, the present invention provides a steam sealing device, comprising:
the steam generator comprises a cylinder, a steam generator and a steam generator, wherein an air cavity for filling steam is formed inside the cylinder, and the cylinder is provided with an opening communicated with the air cavity;
the main shaft is rotatably arranged in the air cavity, and an impeller is arranged on the outer peripheral surface of the main shaft so as to drive the main shaft to rotate through the flow of the steam;
the steam seal body is sleeved on the main shaft and arranged at the opening, and a gap is formed between one side of the steam seal body, which is far away from the main shaft, and the inner wall of the opening;
the inclined sheets are arranged in the gap and connected with the steam seal body, and a plurality of inclined sheets are arranged along the circumferential direction of the steam seal body; the inclined sheet is obliquely arranged relative to the axis direction of the main shaft and extends towards the direction departing from the main shaft;
when the steam sealing device works, high-pressure water is filled in the gap, the extending direction of the inclined sheet inclines towards one side of the high-pressure water, so that the extending direction of the inclined sheet forms a certain angle relative to the normal plane of the main shaft, the inclined sheet generates an acting force which moves towards the direction far away from the air cavity for the high-pressure water filled in the gap, the high-pressure water is limited to enter the air cavity, and the opening is sealed through the matching of the high-pressure water, the steam sealing body and the inclined sheet.
Optionally, the gland sealing device includes the gland sealing ring, the gland sealing ring is followed the open-ended circumference setting of cylinder, and with the gland casing is relative in the footpath, the gland sealing ring with form between the gland casing the clearance, the gland sealing ring orientation the terminal surface of gland casing is equipped with the arch, the arch is followed the circumferencial direction of gland sealing ring extends a week, just the arch is followed the axis direction of main shaft sets up a plurality ofly.
Optionally, the steam seal body is provided with a plurality of steam seal bodies along the axial direction of the main shaft, and the steam seal ring cover is arranged outside the steam seal bodies.
Optionally, the distance between two adjacent protrusions along the axial direction of the main shaft is smaller than the length of the oblique sheet along the axial direction of the main shaft, so that the two adjacent protrusions and the two adjacent oblique sheets cooperate to form a cavity.
Optionally, an included angle between the extending direction of the oblique sheet and a normal plane of the main shaft is 40-50 °.
Optionally, the angle of inclination of the oblique piece relative to the axial direction of the main shaft is 40-50 °.
Optionally, the height of the oblique sheet along the axial direction of the main shaft is 2.4 mm-2.6 mm; and/or
The interval between two adjacent oblique sheets of the gland sealing body along the circumferential direction of the main shaft is 2.9 mm-3.1 mm.
Optionally, the outer circumferential surface of the gland casing is provided with a first groove, the first groove extends for a circle along the circumferential direction of the gland casing, and the inclined piece is connected with the first groove.
Optionally, a second groove is formed in the bottom of the first groove, the width of the second groove in the axial direction of the spindle is greater than the width of the first groove in the axial direction of the spindle, and the oblique piece is connected to the first groove and the second groove.
The invention also provides a steam turbine, which comprises the steam sealing device in any one of the embodiments.
Compared with the prior art, in the technical scheme, the steam sealing device is mainly used for steam sealing of a steam turbine, wherein the steam sealing device comprises a cylinder, an air cavity for filling steam is formed in the cylinder, and an opening communicated with the air cavity is formed in the cylinder; in addition, the air cavity is also rotatably connected with a main shaft, wherein an impeller is arranged on the peripheral surface of the main shaft, the rotation of the main shaft can be realized by pushing the impeller through steam, and the output of power is realized through the main shaft. Because of the existence of diffusion effect, steam can escape from the opening part communicated with the air cavity, therefore, in order to realize the sealing of the steam, the main shaft is sleeved with a steam seal body, the steam seal body is arranged on the main shaft and positioned at the position of the opening of the cylinder, a gap is formed between the outer peripheral wall of the steam seal body and the inner wall of the opening, and the steam seal body rotates along with the main shaft when the main shaft rotates; in addition, the peripheral surface of the gland casing is also provided with a plurality of inclined sheets which are arranged in a gap between the peripheral wall of the gland casing and the inner wall of the opening, and the inclined sheets form a certain included angle with the axis of the main shaft; in order to realize the sealing of the gap between the inclined sheet and the opening of the cylinder, when the inclined sheet extends along the direction deviating from the main shaft, the extending direction forms a certain angle with the normal plane of the main shaft and inclines towards one side of high-pressure water, at the moment, the inclined sheet pushes the high-pressure water in the gap to rotate in the rotating process of the gland sealing body, the high-pressure water is acted by centrifugal force, the acting force can decompose the acting force towards one side of the high-pressure water along the axial direction because the extending direction of the inclined sheet forms a certain angle with the normal plane of the main shaft, the acting force is embodied as the pressure intensity pointing to the outside in the axial direction in the gap between the inclined sheet and the opening of the cylinder, and the offset with the internal steam pressure intensity and the external high-pressure water pressure intensity can be realized by adjusting the pressure intensity, so that the sealing of the gap between the inclined sheet and the opening is realized. In the technical scheme, the steam seal body with the inclined sheet is arranged on the main shaft, and under the condition of high-pressure water injection, the inclined sheet and the high-pressure water interact with each other to seal steam in the cylinder, so that the working efficiency of the steam turbine is improved.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the structures shown in the drawings without creative efforts.
FIG. 1 is a schematic structural view of an embodiment of a vapor seal apparatus of the present invention;
FIG. 2 is an enlarged view of a portion of FIG. 1 at A;
FIG. 3 is a radial partial schematic view of a gland seal according to embodiments of the present invention;
fig. 4 is a schematic diagram of the high pressure water force analysis at B in fig. 2.
The reference numbers illustrate:
| reference numerals | Name (R) | Reference numerals | Name (R) |
| 100 | |
200 | |
| 300 | |
400 | |
| 500 | Gland sealing ring |
The implementation, functional features and advantages of the objects of the present invention will be further explained with reference to the accompanying drawings.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be obtained by a person skilled in the art without inventive step based on the embodiments of the present invention, are within the scope of protection of the present invention.
It should be noted that all directional indicators (such as up, down, left, right, front, back \8230;) in the embodiments of the present invention are only used to explain the relative positional relationship between the components, the motion situation, etc. in a specific posture (as shown in the attached drawings), and if the specific posture is changed, the directional indicator is changed accordingly.
In the present invention, unless otherwise expressly stated or limited, the terms "connected," "secured," and the like are to be construed broadly, and for example, "secured" may be a fixed connection, a removable connection, or an integral part; can be mechanically or electrically connected; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In addition, if there is a description relating to "first", "second", etc. in the embodiments of the present invention, the description of "first", "second", etc. is for descriptive purposes only and is not to be construed as indicating or implying relative importance or to implicitly indicate the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In addition, the meaning of "and/or" appearing throughout includes three juxtapositions, exemplified by "A and/or B" including either A or B or both A and B. In addition, technical solutions between the embodiments may be combined with each other, but must be based on the realization of the technical solutions by a person skilled in the art, and when the technical solutions are contradictory to each other or cannot be realized, such a combination should not be considered to exist, and is not within the protection scope of the present invention.
The steam sealing systems for steam turbine plants, in particular for back-pressure steam turbines, are currently largely divided into three systems: comb-tooth type steam seal, carbon ring seal, and honeycomb type steam seal. The three basic sealing principles are all in a throttling and pressure reducing sealing mode, and exhaust (with high pressure) of the back pressure turbine forms a throttling effect through a tiny gap between the gland sealing pieces.
However, in these steam seal structures, because there is a gap between the steam seal and the main shaft, a large amount of steam leaks from the gap, and according to a large amount of engineering experience and measurement, when the exhaust pressure of the steam turbine is 0.5MPa, the steam seal leakage is about 0.5t/h or more, and when the exhaust pressure is 1MPa, the steam seal leakage is about 1t/h or more, which causes serious energy waste, and the leaked steam enters the bearing seat to emulsify the lubricating oil, which causes an accident in the operation of the steam turbine.
In order to solve the above problems, the present invention provides a steam seal device, including:
a cylinder 100 in which an air chamber for filling steam is formed, the cylinder 100 having an opening communicating with the air chamber;
the main shaft 200 is rotatably arranged in the air cavity, and an impeller is arranged on the outer peripheral surface of the main shaft 200 so as to drive the main shaft 200 to rotate through the flow of steam;
the steam seal body 300 is sleeved on the main shaft 200 and arranged at the opening, and a gap is formed between one side of the steam seal body 300, which is far away from the main shaft 200, and the inner wall of the opening;
a plurality of inclined plates 400 arranged in the gap and connected to the gland casing 300, the plurality of inclined plates 400 being arranged along the circumferential direction of the gland casing 300; the inclined plate 400 is obliquely arranged relative to the axial direction of the spindle 200 and extends towards the direction departing from the spindle 200;
when the steam sealing device works, high-pressure water is filled in the gap, the extending direction of the inclined sheet 400 inclines towards one side of the high-pressure water, so that the extending direction of the inclined sheet 400 forms a certain angle relative to the normal plane of the main shaft 200, the inclined sheet 400 generates acting force which moves towards the direction far away from the air cavity for the high-pressure water filled in the gap, so that the high-pressure water is limited to enter the air cavity, and the opening is sealed through the matching of the high-pressure water, the steam sealing body 300 and the inclined sheet 400.
Compared with the prior art, in the technical scheme of the invention, the steam sealing device is mainly used for steam sealing of a steam turbine, wherein the steam sealing device comprises a cylinder 100, an air cavity for filling steam is arranged in the cylinder 100, and an opening communicated with the air cavity is also formed in the cylinder 100; in addition, a main shaft 200 is rotatably connected in the air cavity, wherein an impeller is arranged on the outer peripheral surface of the main shaft 200, the rotation of the main shaft 200 can be realized by pushing the impeller through steam, and the output of power is realized through the main shaft 200. Because of the existence of the diffusion effect, the steam can escape from the opening of the communicating air cavity, therefore, in order to realize the sealing to the steam, the main shaft 200 is sleeved with the gland sealing body 300, the gland sealing body 300 is arranged on the main shaft 200 and is positioned at the position of the opening of the cylinder 100, the peripheral wall of the gland sealing body 300 has a clearance with the inner wall of the opening, and the gland sealing body 300 rotates along with the main shaft 200 when the main shaft 200 rotates; in addition, the periphery of the gland sealing body 300 is further provided with a plurality of inclined plates 400, the inclined plates 400 are arranged in a gap between the periphery wall and the inner wall of the opening of the gland sealing body 300, the inclined plates 400 are arranged along the circumferential direction of the gland sealing body 300, a certain included angle is formed between the inclined plates 400 and the axis of the main shaft 200, in the operation process of the device, high-pressure water is injected into and filled in the gap from the outside, the gland sealing body 300 drives the inclined plates 400 to rotate, at the moment, the high-pressure water between two adjacent inclined plates 400 is pushed by the inclined plates 400 to rotate, as the inclined plates 400 and the axis of the main shaft 200 form a certain included angle, the high-pressure water between two adjacent inclined plates 400 is subjected to an outward acting force along the axis direction, the acting force is reflected as pressure intensity of the high-pressure water pointing to the outside in the axis direction, and can be superposed with the internal steam pressure intensity and the external high-pressure intensity and then offset by adjusting the size of the pressure intensity, so that the gap between the inclined plates 400 is sealed; in order to seal the gap between the inclined plate 400 and the opening of the cylinder 100, when the inclined plate 400 extends in the direction away from the main shaft 200, the extending direction forms a certain angle with the normal plane of the main shaft 200 and inclines to one side of high-pressure water, at this time, in the rotating process of the gland casing 300, the inclined plate 400 pushes the high-pressure water in the gap to rotate, at this time, the high-pressure water is acted by centrifugal force, because the extending direction of the inclined plate 400 forms a certain angle with the normal plane of the main shaft 200, the acting force can be decomposed into acting force facing one side of the high-pressure water in the axial direction, the acting force is embodied as pressure intensity pointing to the outside in the axial direction in the gap between the inclined plate 400 and the opening of the cylinder 100, and by adjusting the pressure intensity, the counteracting of the pressure intensity of the internal steam and the external high-pressure intensity can be realized, thereby realizing the sealing of the gap between the inclined plate 400 and the opening. In the technical scheme, the gland casing 300 with the inclined sheet 400 is arranged on the main shaft 200, and under the condition of high-pressure water injection, the steam in the cylinder 100 is sealed through the interaction of the inclined sheet 400 and the high-pressure water, so that the working efficiency of the steam turbine is improved.
The steam sealing device can be applied to sealing steam in a steam turbine, and as shown in fig. 1 to 3, the steam sealing device comprises a cylinder 100, an air cavity for accommodating the steam is arranged in the cylinder 100, and an opening communicated with the air cavity is further arranged on the cylinder 100; in addition, the steam sealing device is also provided with a main shaft 200, the main shaft 200 is rotatably arranged in the air cavity, an impeller is arranged on the peripheral surface of the main shaft 200, and when steam enters the air cavity, the steam can drive the impeller to further drive the main shaft 200 to rotate; the specific structure and principle of the cylinder 100 and the main shaft 200 can refer to the structure of the existing steam turbine, and are not described herein again. In addition, the main shaft 200 is further provided with a gland sealing body 300, the gland sealing body 300 is sleeved on the main shaft 200 and is located at the opening of the cylinder 100 to seal the opening, the gland sealing body 300 can be in a shape of a cylinder or the like corresponding to the opening, so that when the main shaft 200 rotates, the main shaft 200 drives the gland sealing body 300 to rotate at the opening; to prevent the gland body 300 from interfering with the opening, the end surface of the gland body 300 facing away from the main shaft 200 may form a certain gap with the inner wall of the opening. The outer circumferential surface of the gland casing 300 is further provided with a plurality of inclined pieces 400, the inclined pieces 400 are positioned in the gap, and the plurality of inclined pieces 400 can be uniformly arranged along the circumferential direction of the outer circumferential surface of the gland casing 300; in order to achieve the sealing effect, the length direction of the inclined plate 400 on the outer circumferential surface of the gland casing 300 forms a certain included angle with the axial direction of the main shaft 200, and in addition, the inclined plate 400 extends towards the direction departing from the main shaft 200, and the extending direction inclines towards the direction away from the air cavity of the cylinder 100, that is, the extending direction of the inclined plate 400 forms a certain included angle with the normal plane of the main shaft 200. The sealing principle of the vapor-sealing device will be explained in detail below.
In practical use, the inside of the cylinder 100 is filled with steam, the steam pushes the spindle 200 to rotate, the spindle 200 drives the gland casing 300 to rotate, the inclined plate 400 on the gland casing 300 rotates along with the gland casing 300, the spindle 200 rotates in a direction such that the inclined plate 400 can push the steam inside the cylinder 100 to move outwards of the opening during rotation, at this time, high-pressure water is applied to the outside of the opening, the high-pressure water pressure is greater than the steam pressure inside the cylinder 100, at this time, the high-pressure water can be injected into the gap between the inclined plates 400 and the inner wall of the opening, at this time, the high-pressure water can be driven to rotate by the rotation of the spindle 200, so as to generate dynamic pressure heads, which are opposite to the injection direction of the high-pressure water, and the size of the dynamic pressure heads changes with the rotation speed of the inclined plate 400, at this time, the size of the dynamic pressure heads and the steam pressure inside the cylinder 100 can resist the high-pressure water pressure head, the size of the dynamic pressure heads and the size inside the cylinder 100 can be adjusted until the dynamic pressure heads and the steam inside the cylinder 100 is equal to the steam pressure of the cylinder 400, at this time, the high-pressure water can be limited by the steam pressure of the cylinder 100, so that the steam outside can be sealed by the steam pressure of the steam pressure inside the cylinder 100, and the steam can be sealed.
Specifically, in the present vapor-encapsulating device, the vapor may leak from two locations, the first portion being the gap between two adjacent ramp sheets 400; second portion-the gap between the swash plate 400 and the inner wall of the cylinder 100 opening.
The sealing principle for the first part is as follows: as shown in fig. 3, during the rotation of the oblique sheets 400, a work unit is formed between every two oblique sheets 400; in the critical region between the high-pressure water and the inclined plate 400, the high-pressure water has a relative velocity u in the circumferential direction of the spindle 200 with respect to the inclined plate 400 due to the rotation of the inclined plate 400, the relative velocity u being equal to the diameter d of the sliced piece 0 Rotational speed n 0 A peripheral speed of wherein the diameter d 0 The distance between the inclined plate 400 and the axis of the spindle 200 in the radial direction of the spindle 200, the rotation speed n 0 The rotational speed of the spindle 200, from which the magnitude of the relative speed u can be derived is:
u＝*d 0 *n 0 (1)
the direction of the relative velocity u is opposite to the rotation direction of the inclined plate 400, the inclined plate 400 is inclined relative to the axis of the spindle 200, the included angle between the inclined plate 400 and the normal plane of the spindle 200 is set as a, and a velocity triangle as shown in the figure can be obtained through the relative relationship between the high-pressure water and the inclined plate 400, wherein w 1 The component velocity of the high-pressure water in the inclined direction of the inclined plate 400 can be obtained by calculation:
w 1 ＝u*cosα (2)
and w 1 The component velocity w in the axial direction of the main shaft 200 can be resolved 2 And calculating to obtain:
w 2 ＝w 1 *sinα (3)
and the high pressure water passes through the beveling sheet after entering the gap of the beveling sheet 400Due to the existence of alpha, the inclined sheets 400 give the high-pressure water in the gap between the two inclined sheets 400 a force pointing to the inlet direction of the opening along the axial direction of the main shaft 200, and the pressure generated by the force is set to be delta P 1 At this time, the relative velocity of the high-pressure water in the gap between the two inclined plates 400 with respect to the inclined plates 400 is 0, and the partial velocity thereof with respect to the inclined plates 400 in the axial direction of the main shaft 200 is 0 due to the pressure P of the steam in the cylinder 100 1 The pressure P of the high-pressure water at the inlet of the opening is known 2 It is also known, therefore, that by Bernoulli's equation we can conclude that the following relationship exists for two positions:
P 1 +1/2*ρ*w 2 ^ … ＝P 2 +0 (4)
ΔP 1 ＝P 2 -P 1 ＝1/2*ρ*w 2 ^ 2 ＝1/2*ρ*(π*d 0 *n 0 *sin(2*α)/60)^ 2 (5)
in the above formula, ρ is the density of the high-pressure water, and it can be seen from the above formula that Δ P is 1 And d 0 And n 0 Is correlated, therefore, by adjusting d 0 、n 0 And alpha, namely P can be realized 1 And P 2 The equalization is performed so that a sealing of the first part of the steam is achieved.
The sealing principle for the second part is as follows: as shown in fig. 2 and 4, when the inclined pieces 400 rotate, the high-pressure water between two adjacent inclined pieces 400 in the circumferential direction of the gland casing 300 is pushed by the inclined pieces 400, and the high-pressure water rotates at a high speed between the two inclined pieces 400 along with the inclined pieces 400 to generate a centrifugal force, which is set to be F 0 F of the reaction mixture 0 The size of (A) is as follows:
F 0 ＝m*(d 0 /2)*ω^ 2 (6)
wherein m is the mass of the high-pressure water between the two inclined plates 400, the value is related to the distance between the two inclined plates 400 and the height of the inclined plates 400 in the radial direction and the length thereof in the axial direction, ω is the angular velocity of the main shaft 200, and ω and n are 0 Can be calculated by the following formula:
ω＝2*π*n 0 /60 (7)
due to the fact thatThe inclined plate 400 extends in a direction away from the main shaft 200, the extending direction inclines in a direction away from the air chamber of the cylinder 100, the inclination angle is set to be beta, and the centrifugal force F is analyzed through stress 0 Decomposition is performed, which can be decomposed into a component force F parallel to the inclination direction of the ramp 400 1 And a component force F perpendicular to the direction of the ramp 400 2 Wherein the inclined plate 400 has a supporting force perpendicular to the inclined plate 400 for the high-pressure water in the gap, the supporting force is F 2 Equal in size and opposite in direction, can offset F 2 For the action of the high-pressure water in F 1 Will move along the extension direction of the oblique sheet 400 and pass through the pair F 1 Resolved to obtain a component F parallel to the axis of the spindle 200 11 The component force will act on the high pressure water in the gap between the oblique sheet 400 and the inner wall of the opening, and generate a pressure to the high pressure water which points to the side departing from the cylinder 100 along the axial direction of the main shaft 200, and the force analysis can obtain that:
F 1 ＝F 0 *cosβ＝ρ*m*(d 0 /2)*(2*π*n 0 /60)^ 2 *cosβ (8)
F 2 ＝F 1 *sinβ＝ρ*m*(d 0 /2)*(2*π*n 0 /60)^ 2 *cosβ*sinβ (9)
and the pressure of the force in the direction along the axis of the spindle 200 is:
ΔP 2 ＝F 2 /A (10)
wherein, a is the action area of the action force acting between the two adjacent tilted pieces 400 and the opening, and the size of the action area is equal to the product of the arc length of the end portions of the two adjacent tilted pieces 400 along the circumferential direction of the gland body 300 and the gap between the end portion of the tilted piece 400 and the inner wall of the opening:
A＝C*δ (11)
wherein C is the arc length of the end of the two adjacent oblique sheets 400 along the circumferential direction of the gland casing 300, and δ is the size of the gap between the end of the oblique sheet 400 and the inner wall of the opening. This gives:
ΔP 2 ＝ρ*m*(d 0 /2)*(2*π*n 0 /60)^ 2 *cosβ*sinβ/(c*δ) (12)
thus, the Δ P is shown 2 And d 0 、n 0 And alpha, and adjusting the three parameters to adjust the delta P 2 And P 1 And P 2 A balance is formed to effect a seal against the second portion.
Further, the gland sealing device includes a gland sealing ring 500, the gland sealing ring 500 is arranged along the circumference of the opening of the cylinder 100 and is arranged opposite to the gland sealing body 300 in the radial direction, a gap is formed between the gland sealing ring 500 and the gland sealing body 300, a protrusion is arranged on the end surface of the gland sealing ring 500 facing the gland sealing body 300, the protrusion extends for a circle along the circumferential direction of the gland sealing ring 500, and the protrusion is arranged in a plurality along the axial direction of the main shaft 200.
Specifically, in order to improve the sealing effect, the gland sealing device is further provided with a gland sealing ring 500, as shown in fig. 2, the gland sealing ring 500 is a circular ring structure, the gland sealing ring 500 is arranged on the inner wall of the opening of the cylinder 100 and is coaxially arranged with the gland sealing body 300, the gland sealing ring 500 and the gland sealing body 300 are arranged opposite to each other in the radial direction of the main shaft 200, and a gap is formed between the inner wall of the gland sealing ring 500 and the gland sealing body 300; in addition, the end surface of the gland seal ring 500 facing the gland seal body 300 is further provided with a plurality of protrusions, the protrusions extend for a circle along the circumferential direction of the gland seal ring 500, and the protrusions are arranged along the axial direction of the spindle 200, so that through the matching of the gland seal body 300 and the gland seal ring 500, a plurality of mutually communicated chambers are formed between two adjacent protrusions and two adjacent oblique sheets 400, and the chambers can form the function of a centrifugal pump in the process that the oblique sheets 400 rotate at high speed; in addition, during the process of steam escaping from the outlet, the clearance between the bulge and the inclined plate 400 can generate throttling effect on the steam, so that the pressure of the steam is reduced layer by layer, and the steam sealing effect on the d is reduced 0 、n 0 And the pressure requirement of high-pressure water, the design allowance of the steam sealing device is improved.
Further, a plurality of gland casings 300 are provided along the axial direction of the main shaft 200, and a gland ring 500 covers the plurality of gland casings 300. Specifically, in order to increase the applicable range of the gland sealing device, a plurality of gland sealing bodies 300 may be arranged along the axial direction of the main shaft 200, and correspondingly, the gland sealing ring500 can be placed over the exterior of the plurality of gland blocks 300 to ensure the sealing effect of each layer of gland blocks 300, such that each layer of gland blocks 300 will generate a sealing force Δ P opposite to the high pressure water pressure in the circumferential direction during the sealing process 1 In the actual design process, a corresponding number of gland casings 300 can be set according to the maximum value of the steam pressure to realize the adaptation to different application scenes, thereby improving the applicability of the gland sealing device.
Further, the interval between two adjacent protrusions along the axial direction of the main shaft 200 is smaller than the length of the inclined plate 400 along the axial direction of the main shaft 200, so that the two adjacent protrusions and the two adjacent inclined plates 400 cooperate to form a cavity.
Specifically, the interval between two adjacent protrusions along the axis of the spindle 200 is smaller than the length of the inclined plate 400 along the axis of the spindle 200, so that the two adjacent protrusions divide the two adjacent inclined plates 400 into independent chambers on the axis of the spindle 200,
the two adjacent inclined sheets 400 on each gland casing 300 are divided into a plurality of layers by two adjacent bulges in the axial direction of the main shaft 200, and the chamber of each layer generates a sealing force delta P opposite to the sealing water pressure in the axial direction of the main shaft 200 2 The sealing forces generated by each layer may be superimposed on the axis of the spindle 200; and by substituting the corresponding parameters, Δ P can be obtained 2 In this embodiment, assuming that the interval between the two adjacent protrusions is k, the height of the inclined plate 400 along the radial direction of the main shaft 200 is h, and the distance between the two adjacent inclined plates 400 along the circumferential direction is L, m in equation (6) is the product of the three and the water density ρ, and the product is obtained by substituting the product into equation (12):
ΔP 2 ＝ρ*(k*h/δ)*(d0/2)*(2*π*n0/60)^ 2 *cosβ*sinβ*(L/c) (13)
in the above formula, L/c is the ratio of the distance between two adjacent tilted pieces 400 on the gland casing 300 in the circumferential direction to the arc length, and is related to the number of the tilted pieces 400 on the gland casing 300, and the larger the number of the tilted pieces 400 is, the larger the value is, that is, the Δ P can be measured by adjusting the number of the tilted pieces 400 on the gland casing 300 2 So as to meet the requirements of different application scenes. Due to the pressure of the high pressure water and the cylinder 10The pressure in 0 determines the required sealing force, so the interval k between two adjacent bulges can be adjusted according to the maximum value of the steam pressure, thereby ensuring that the steam sealing device can achieve enough sealing effect, and simultaneously, along with the change of the steam pressure, the length of the gap between the steam seal body 300 and the steam seal ring 500, which is formed by the high-pressure water entering the steam seal body 200 along the axial direction of the main shaft 200, can be adaptively adjusted, thereby realizing the adaptive adjustment of the steam pressure and improving the adaptability of the steam sealing device.
Further, the extending direction of the inclined plate 400 forms an angle of 40 ° to 50 ° with the normal plane of the main shaft 200, and the inclined plate 400 is inclined at an angle of 40 ° to 50 ° with respect to the axial direction of the main shaft 200. Specifically, the angle between the extending direction of the swash plate 400 and the normal plane of the main shaft 200 is β, the angle at which the swash plate 400 is inclined with respect to the axial direction of the main shaft 200 is α, and as can be seen from equation (12), when β is 45 °, Δ P is obtained 2 The maximum value can be reached, and it can be seen from formula (5) that when α is 45 °, Δ P is 1 The maximum value can be reached, in the practical design and use process, the influence of the rotating speed, the diameter and the sealing pressure of equipment is considered, the numerical values of the alpha and the beta can be set according to the practical requirement, the influence of the processing difficulty is considered, the value range of the alpha is 40-50 degrees, and the value range of the beta is 40-50 degrees.
Further, according to engineering experience, machining cost and difficulty considerations, the height of the inclined plate 400 in the axial direction of the main shaft 200 is 2.4mm to 2.6mm; the interval between two adjacent oblique sheets 400 of the gland sealing body 300 along the circumferential direction of the main shaft 200 is 2.9 mm-3.1 mm.
Further, the outer circumferential surface of the gland casing 300 is provided with a first groove, the first groove extends for a circle along the circumferential direction of the gland casing 300, and the inclined piece 400 is connected with the first groove. Specifically, in order to improve the connection strength between the tilted vane 400 and the gland casing 300, a first groove may be formed on the outer circumferential surface of the gland casing 300, the first groove has a bottom surface and two opposite side surfaces adjacent to the bottom surface, the first groove may be formed on the outer circumferential surface of the gland casing 300 in a circle along the circumferential direction of the gland casing 300, the root of the tilted vane 400 may be partially embedded into the first groove, abut against the bottom surface and the side surfaces of the first groove, and may be connected to the first groove by welding or the like, so that, when the gland casing 300 rotates, the side surface of the tilted vane 400 along the axial direction of the main shaft 200 is subjected to the action of high pressure water and steam, the position where the tilted vane 400 is connected to the gland casing 300 will generate a large stress action, the tilted vane 400 is connected to the first groove, and the side surface of the first groove will generate a supporting action on the tilted vane 400, thereby reducing the stress concentration at the connection portion between the tilted vane 400 and the gland casing 300, improving the connection strength between the tilted vane 400 and the gland casing 300, and prolonging the service life of the gland casing 300.
Further, a second groove is formed in the bottom of the first groove, the width of the second groove in the axial direction of the spindle 200 is greater than the width of the first groove in the axial direction of the spindle 200, and the oblique piece 400 is connected to the first groove and the second groove. Specifically, in order to further improve the connection strength between the inclined plate 400 and the gland casing 300, a second groove may be formed at the bottom of the first groove, and the width of the second groove in the axial direction of the spindle 200 is greater than the width of the first groove in the axial direction of the spindle 200. In this technical scheme, can realize spacing to the lamella 400 radial position through setting up of second recess to guaranteed that lamella 400 is rotatory in-process its stability in radial position, guaranteed the sealed effect of vapor seal device.
The invention further provides a steam turbine, which comprises a steam seal device, a steam chamber and other components, wherein the steam seal device is arranged on the steam turbine, the steam chamber is connected with the steam seal device, and the other components are the steam chamber.
The above are only alternative embodiments of the present invention, and not intended to limit the scope of the invention, and all equivalent structural changes made by the present specification and drawings, or any other related technical fields directly or indirectly applied thereto under the inventive concept are included in the scope of the present invention
The invention further provides a steam turbine, which comprises a steam seal device, a steam chamber and other components, wherein the steam seal device is arranged on the steam turbine, the steam chamber is connected with the steam seal device, and the other components are the steam chamber.
The above description is only an alternative embodiment of the present invention, and is not intended to limit the scope of the present invention, and all equivalent structural changes made by using the contents of the present specification and the drawings or directly/indirectly applied to other related technical fields under the inventive concept of the present invention are included in the scope of the present invention.
Claims (10)
1. A gland seal, comprising:
the steam cylinder is internally provided with an air cavity for filling steam, and the air cylinder is provided with an opening communicated with the air cavity;
the main shaft is rotatably arranged in the air cavity, and an impeller is arranged on the outer peripheral surface of the main shaft so as to drive the main shaft to rotate through the flow of the steam;
the steam seal body is sleeved on the main shaft and arranged at the opening, and a gap is formed between one side of the steam seal body, which is far away from the main shaft, and the inner wall of the opening;
the inclined sheets are arranged in the gap and connected with the steam seal body, and a plurality of inclined sheets are arranged along the circumferential direction of the steam seal body; the inclined sheet is obliquely arranged relative to the axis direction of the main shaft and extends towards the direction departing from the main shaft;
when the steam sealing device works, high-pressure water is filled in the gap, the extending direction of the inclined sheet inclines towards one side of the high-pressure water, so that the extending direction of the inclined sheet forms a certain angle relative to the normal plane of the main shaft, the inclined sheet generates an acting force which moves towards the direction far away from the air cavity for the high-pressure water filled in the gap, the high-pressure water is limited to enter the air cavity, and the opening is sealed through the matching of the high-pressure water, the steam sealing body and the inclined sheet.
2. The gland sealing device according to claim 1, wherein the gland sealing device comprises a gland sealing ring, the gland sealing ring is arranged along the circumferential direction of the opening of the cylinder and is arranged opposite to the gland sealing body in the radial direction, the gap is formed between the gland sealing ring and the gland sealing body, a protrusion is arranged on the end face of the gland sealing ring facing the gland sealing body, the protrusion extends for one circle along the circumferential direction of the gland sealing ring, and a plurality of protrusions are arranged along the axial direction of the main shaft.
3. The gland sealing device according to claim 2, wherein a plurality of gland sealing bodies are arranged along the axial direction of the main shaft, and the gland sealing ring cover is arranged outside the plurality of gland sealing bodies.
4. The gland sealing device according to claim 3, wherein the distance between two adjacent protrusions along the axial direction of the spindle is less than the length of the ramp along the axial direction of the spindle, so that the two adjacent protrusions and the two adjacent ramps cooperate to form a chamber.
5. The gland sealing device according to claim 1, wherein the extending direction of said oblique fins forms an angle of 40 ° to 50 ° with the normal plane of said main shaft.
6. A gland seal according to claim 1 wherein said fins are inclined at an angle of from 40 ° to 50 ° to the axial direction of said main shaft.
7. The gland seal of claim 1, wherein said fins have a height along the axis of said spindle of 2.4mm to 2.6mm; and/or
The interval between two adjacent oblique sheets of the gland sealing body along the circumferential direction of the main shaft is 2.9 mm-3.1 mm.
8. The gland seal according to claim 1, wherein said gland body defines a first groove in an outer peripheral surface thereof, said first groove extending circumferentially around said gland body, said ramp being connected to said first groove.
9. The vapor seal device according to claim 8, wherein a second groove is formed at a bottom of the first groove, a width of the second groove along the axial direction of the spindle is larger than a width of the first groove along the axial direction of the spindle, and the tilted plate is connected to the first groove and the second groove.
10. A steam turbine, characterized by comprising a gland sealing device according to any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211405720.7A CN115680790A (en) | 2022-11-10 | 2022-11-10 | Steam seal device and steam turbine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211405720.7A CN115680790A (en) | 2022-11-10 | 2022-11-10 | Steam seal device and steam turbine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN115680790A true CN115680790A (en) | 2023-02-03 |
Family
ID=85051770
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202211405720.7A Pending CN115680790A (en) | 2022-11-10 | 2022-11-10 | Steam seal device and steam turbine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN115680790A (en) |
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2022
- 2022-11-10 CN CN202211405720.7A patent/CN115680790A/en active Pending
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