CN211715184U - Combined fluid dynamic pressure type dry airtight seal postposition isolation sealing device - Google Patents
Combined fluid dynamic pressure type dry airtight seal postposition isolation sealing device Download PDFInfo
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- CN211715184U CN211715184U CN202020266746.8U CN202020266746U CN211715184U CN 211715184 U CN211715184 U CN 211715184U CN 202020266746 U CN202020266746 U CN 202020266746U CN 211715184 U CN211715184 U CN 211715184U
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Abstract
The utility model relates to a modular airtight seal rearmounted isolation sealing device is done to fluid dynamic pressure type, this rearmounted isolation sealing device sets up between dry gas seal subassembly and bearing box, including labyrinth seal unit and fluid dynamic pressure type seal unit, wherein, labyrinth seal unit sets up between dry gas seal subassembly and fluid dynamic pressure type seal unit, fluid dynamic pressure type seal unit includes rotating assembly and static subassembly, the rotating assembly cover is established in the main shaft outside, and along with the high-speed rotation of main shaft, static subassembly encircles the main shaft and arranges, and fixed with the casing, a terminal surface of rotating assembly and the terminal surface laminating of static subassembly form sealed face, sealed face is perpendicular with the main shaft axial, be equipped with fluid dynamic pressure groove on rotating assembly's terminal surface. Compared with the prior art, the sealing device of the application is applied to the turbine machinery, can realize zero leakage of bearing side lubricating oil to dry gas sealing, and has small loss of isolation gas.
Description
Technical Field
The utility model relates to a mechanical seal technical field, concretely relates to modular fluid dynamic pressure type is airtight seals rearmounted isolation sealing device futilely.
Background
The turbo machinery comprises a turbo compressor (such as a centrifugal compressor and an axial flow compressor) and a turbo expander, which are high-speed rotating equipment and are key core equipment of devices such as petroleum and chemical engineering. At present, dry gas seal, namely dry running, gas lubrication and non-contact mechanical seal, is generally adopted by turbomachinery as shaft end seal. No matter the single-end face dry gas seal, the double-end face dry gas seal, the serial dry gas seal and the serial dry gas seal with the middle labyrinth are adopted, the rear isolation seal is needed to isolate the dry gas seal from the bearing box, and the condition that lubricating oil gas generated by the high-speed rotation of the main shaft in the bearing box pollutes the outer side seal of the dry gas seal through axial diffusion to cause failure of the dry gas seal is avoided.
The common sealing forms of the front and rear isolating seals are non-contact labyrinth seal (or comb seal) and split carbon ring seal. The labyrinth seal is realized by throttling and depressurizing, and has the advantages of non-contact, large working clearance and high reliability; but the defects are that the consumption of isolating gas is large, and the effect of plugging bearing lubricating oil gas is poor. The split carbon ring seal is also a throttling pressure reduction type seal, and is provided with a contact split carbon ring seal and a non-contact split carbon ring seal.
However, the contact carbon ring seal has a certain running-in period at the initial stage of use, the carbon ring has certain abrasion in the running-in period, the abrasion amount is related to the dew point of the isolation gas nitrogen, and the lower the dew point, the drier the nitrogen is, the larger the abrasion amount is. Carbon graphite powder from time to time running under wear may cause failure of the outer seal of the dry gas seal. The non-contact carbon ring seal has a large static leakage and the consumption of the barrier gas is very sensitive to the temperature at the carbon ring seal. For some special conditions, such as the bearing is too close to the dry gas seal axial distance; the position of the bearing oil drain port is unreasonable in design; the oil inlet pressure of the bearing is too high; the bearing box oil return port is too small, oil return flow is not smooth, and the labyrinth seal and the carbon ring seal are likely to have an isolation gas short circuit phenomenon, so that bearing lubricating oil or lubricating oil gas enters the outer side seal of the dry gas seal to pollute the dry gas seal, and the dry gas seal fails.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing a combined fluid dynamic pressure type dry air-tight seal rear isolation sealing device with good sealing effect in order to overcome the defects of the prior art.
In order to achieve the purpose of the present invention, the present application provides the following technical solutions.
In a first aspect, the present application provides a combined type hydrodynamic pressure type dry gas seal rear isolation sealing device, the rear isolation sealing device is disposed between a dry gas seal assembly and a bearing housing in a turbomachine, the turbomachine is provided with a main shaft rotating at a high speed, the rear isolation sealing device includes a labyrinth seal unit and a hydrodynamic pressure type seal unit, wherein the labyrinth seal unit is disposed between the dry gas seal assembly and the hydrodynamic pressure type seal unit, the hydrodynamic pressure type seal unit includes a rotating assembly and a stationary assembly, a lock nut is disposed on the main shaft, wherein both ends of the rotating assembly are respectively clamped by the lock nut and a rotating portion of the dry gas seal assembly, and the rotating assembly is sleeved outside the main shaft and rotates at a high speed along with the main shaft, the stationary assembly is disposed around the main shaft and fixed with a housing of the turbomachine, one end face of the rotating component is attached to one end face of the static component to form a sealing face, the sealing face is perpendicular to the axial direction of the spindle, and a hydrodynamic groove is formed in the end face of the rotating component.
In this application, when the turbine is rotating at high speed, the barrier gas is divided into two streams, one stream enters the labyrinth seal unit to separate the leakage gas from the outside seal in the dry gas seal, and the other stream enters the hydrodynamic seal unit. At this time, the rotating assembly rotates at a high speed along with the main shaft under the clamping of the rotating parts of the locking nut and the dry gas sealing assembly, and because the hydrodynamic pressure groove is arranged on the end surface of the rotating assembly contacting with the static assembly, a micron-order air film is formed between the rotating assembly and the static assembly (namely a sealing surface) when the rotating assembly rotates at a high speed, so that the lubricating and isolating effects on the sealing surface are realized, and the non-contact operation of sealing is realized. Because the rotating speed of the turbo machinery is very high, the rigidity of the extremely thin air film of the sealing surface is very high, the lubricating oil gas on the bearing side can be effectively isolated, and even if the air supply pressure of the isolation air is lower than the oil gas pressure of the bearing side, the zero leakage of the lubricating oil gas on the bearing side to the dry air seal can be ensured, so that the long-period stable operation of the dry air seal is ensured. The rotating part of the dry gas seal assembly described in the application can be a compressing sleeve and other parts of the dry gas seal assembly, can be selected according to different actual equipment, and is the prior art.
In a preferred scheme of the first aspect, the rotating assembly comprises a rotating ring, a shaft sleeve and a pressing sleeve, the shaft sleeve and the pressing sleeve are both annular and are sleeved outside the main shaft, wherein the shaft sleeve and the pressing sleeve are fixed through a hexagon socket head cap screw, the tail end of the shaft sleeve is abutted against a lock nut, the front end of the pressing sleeve is abutted against the rotating part of the dry gas sealing assembly, and the rotating ring is fixed with the shaft sleeve through a transmission pin and synchronously rotates.
In a preferred scheme of the first aspect, the shaft sleeve comprises a first ring and a second ring which are coaxial and integrally arranged, the tail end of the second ring is abutted to the lock nut, the front end of the second ring is integrally connected with the tail end of the first ring, the tail end of the movable ring is attached to the front end of the second ring, the movable ring is driven by the driving pin and sealed by the sealing ring, and the inner edge of the movable ring is abutted to the outer edge of the first ring.
In a preferred scheme of the first aspect, a groove is formed in a contact position of the tail end of the compression sleeve and the main shaft, the front end of the first ring is inserted into the groove and abutted against a groove wall, the bottom of the groove is fixed to the front end of the first ring through a hexagon socket head cap screw, and the tail end of the compression sleeve is abutted against the front end of the movable ring.
In a preferred version of the first aspect, a centering corrugated strip is provided between the inner edge of the rotating ring and the outer edge of the first ring. Since the rotating ring rotates at a high speed during operation, the very small eccentricity causes additional vibrations, which affect the dynamic performance of the entire device. This application adds the centering ripple area between rotating ring and first ring, can eliminate the gap between the two to guarantee that rotating ring and main shaft are with the axle center, ensure its operating stability. Preferably, the centering corrugated strip is a commercially available tolerance strip of a high alloy material.
In a preferred version of the first aspect, an O-ring is provided between the sleeve and the main shaft.
In a preferred scheme of the first aspect, a wear-resistant layer is attached to the end face of the front end of the moving ring in a spraying or surfacing mode, an annular hydrodynamic pressure groove is formed in the inner side of the wear-resistant layer, the hydrodynamic pressure groove is a one-way rotation groove type or a two-way rotation groove type, the one-way rotation groove type comprises an arc groove, a spiral groove and the like, and the two-way rotation groove type comprises a U-shaped groove, a T-shaped groove and the like. The rotating member base material preferably recommends high-strength precipitation hardening stainless steel, and martensite stainless steel or dual-phase steel can be selected for the working condition that the rotating speed is not very high; the wear-resistant layer can be made of the hard alloy sprayed by supersonic flame and can also be made of the hard alloy subjected to surface overlaying.
In a preferred version of the first aspect, the outer side of the wear resistant layer is a slotless dam region.
In a preferable mode of the first aspect, the hydrodynamic grooves have a groove depth of 3 to 20 μm.
In a preferable mode of the first aspect, a radial width of the dam region located at the outer side is 0.2 to 0.7 of a width of the sealing surface. When the width of the dam area is too small, an air film formed by the fluid dynamic pressure groove is too thick, and isolation air easily leaks outwards over the dam area, so that the sealing performance is reduced; when the width of the dam area is too large, the radial width of the hydrodynamic groove is small, an air film is not easy to form, and the service life and the performance of sealing are also influenced.
In a preferred version of the first aspect, the stationary assembly includes a spring seat, a spring push ring and a stationary ring, and the spring seat is fixed to the housing by a socket head cap screw; the end face of the tail end of the static ring is attached to the end face of the front end of the movable ring to form a sealing surface, the front end of the push ring is attached to the rear end of the spring, and the front end of the spring is attached to the end face of the bottom of the spring hole in the spring seat. And sealing rings are arranged at the matching positions of the push ring, the static ring and the spring seat. The joint of the end face of the static ring and the end face of the moving ring is realized by the axial pressing force of the spring and the gas pressure of the isolation gas. More preferably, the material of the static ring is high-quality resin-impregnated carbon graphite or antimony-impregnated carbon graphite.
In a preferred aspect of the first aspect, an isolation gas passage is provided in the spring seat, and the isolation gas enters the inner diameter of the stationary ring through the isolation passage. The isolating gas from the isolating gas channel of the spring seat is divided into two parts, wherein one part enters a cavity between the inner diameter of the static ring and the outer diameter of the compression sleeve. Then the sealing fluid enters a hydrodynamic groove, and the isolated gas at the inner diameter is pumped outwards by utilizing the hydrodynamic effect generated by the hydrodynamic groove, so that a layer of micron-order gas film is formed between the sealing surfaces, the lubricating and isolating effects are realized on the sealing surfaces, and the non-contact operation of the sealing is realized.
In a preferred aspect of the first aspect, a pin is provided between the spring seat and the push ring, and the pin prevents rotation between the spring seat and the push ring. More preferably, the push ring is provided with a limiting structure in the axial direction, so that the static assembly is convenient to mount, and the push ring and the O-shaped ring are prevented from being pushed out of the spring seat by the spring during assembly.
In a preferred arrangement of the first aspect, a pin is provided between the push ring and the stationary ring, and rotation between the push ring and the stationary ring is prevented by the pin. The arrangement ensures that the static ring and the push ring are kept static in the working state.
In a preferable mode of the first aspect, the matching surfaces of the push ring and the stationary ring with the spring seat are provided with O-rings.
In a preferred aspect of the first aspect, the mating surface of the spring seat and the housing is provided with an O-ring.
In a preferred version of the first aspect, the rear end of the spring seat is flared, which arrangement facilitates the removal of lubricant.
In a preferred embodiment of the first aspect, the housing is provided with an oil slinger, and the lock nut is provided with an oil slinger, which can prevent or reduce the diffusion or splashing of the bearing-side lubricating oil to the rear isolation seal.
In a preferred scheme of the first aspect, labyrinth seal unit includes labyrinth seal piece and sets up the dentate arch on the compression sleeve outer wall, labyrinth seal unit includes the labyrinth seal body, compresses tightly cover and spring holder, and a plurality of labyrinth teeth and labyrinth tooth chamber of labyrinth seal body internal diameter department along the continuous evenly distributed of axial carry out the throttle to the isolation gas with compressing tightly the little clearance of the annular that the cover excircle formed and stepping down and realize sealedly, the labyrinth seal body passes through the hexagon socket head cap screw with the spring holder and fixes, and is equipped with O type circle between labyrinth seal body and spring holder. The isolating gas coming out of the spring seat isolating gas channel is divided into two paths, wherein one path leaks to the inner side through small annular gaps formed by a plurality of labyrinth teeth on the labyrinth sealing body and the excircle of the pressing sleeve, and the leakage gas of the outer side seal in the dry gas seal is isolated. In the present application, the labyrinth seal is made of a soft metal, such as aluminum, and the mating clamping sleeve is made of high-strength precipitation-hardened stainless steel, martensitic stainless steel, dual-phase steel, or the like.
Compared with the prior art, the beneficial effects of the utility model reside in that:
(1) according to the dry gas dynamic pressure type sealing device, a combination form of labyrinth sealing and hydrodynamic pressure type sealing is arranged between the dry gas sealing assembly and the bearing box, so that the structures of a static ring and a dynamic ring in the pure hydrodynamic pressure type sealing are simplified, and the dry gas dynamic pressure type sealing device is particularly suitable for occasions with smaller radial space;
(2) because the clearance between the static ring and the dynamic ring is extremely small, and the sealing pressure difference is low, the consumption of the isolating gas is extremely small, namely, the zero leakage of the lubricating oil gas at the bearing side to other turbine mechanical dry gas seals can be ensured only by the extremely low consumption of the isolating gas through the fluid dynamic pressure type rear isolating sealing device;
(3) even if the pressure of the isolation gas fluctuates and even the pressure of the isolation gas is lower than that of lubricating oil gas on the bearing side, the rear isolation sealing device can work normally, and the dry gas seal is ensured not to be polluted by the oil gas and fail.
Drawings
FIG. 1 is a schematic view of the construction of a seal of the present application;
FIG. 2 is a schematic view showing the shape of a hydrodynamic groove of a unidirectional rotating groove type provided at the front end of a rotating ring according to the present application;
FIG. 3 is a schematic view showing the shape of another hydrodynamic groove of a unidirectional rotating groove type provided at the front end of the rotating ring in the present application;
FIG. 4 is an enlarged partial view of the labyrinth seal of the subject application;
fig. 5 is a schematic view showing the shape of a bidirectional rotating groove type hydrodynamic groove provided at the front end of the rotating ring in the present application.
In the drawing, 1 is a shaft sleeve, 2 is a transmission pin, 3 is a movable ring, 4 is a stationary ring, 5 is a spring seat, 6 is a spring, 7 is a pressing sleeve, 8 is an O-ring, 9 is an O-ring, 10 is a centering corrugated strip, 11 is a lock nut, 12 is a push ring, 13 is an O-ring, 14 is an O-ring, 15 is a pin, 16 is a pin, 17 is an inner hexagonal screw, 18 is a labyrinth seal body, 19 is an inner hexagonal screw, 20 is an oil baffle ring, 21 is an inner hexagonal screw, 22 is a gasket, 23 is a main shaft, 24 is a housing, 26 is a labyrinth tooth cavity, 27 is a labyrinth tooth, 28 is a first ring, 29 is a second ring, 30 is a hydrodynamic groove, 31 is an outer side dam region, 32 is an oil slinger, and 33 is an O-ring.
Detailed Description
Unless otherwise defined, technical or scientific terms used herein shall have the ordinary meaning as is understood by those of ordinary skill in the art to which the invention belongs. All numerical values recited herein as between the lowest value and the highest value are intended to mean all values between the lowest value and the highest value in increments of one unit when there is more than two units difference between the lowest value and the highest value.
In the following description of the embodiments of the present invention, it is noted that in the detailed description of the embodiments, all the features of the actual embodiments may not be described in detail in order to make the description concise and concise. Modifications and substitutions may be made to the embodiments of the present invention by those skilled in the art without departing from the spirit and scope of the invention, and the resulting embodiments are within the scope of the invention.
In the present description, all leading ends are the media side of fig. 1, i.e., the side where the dry gas seal assembly is located, and all trailing ends are the bearing side of fig. 1, i.e., the side where the bearing housing is located.
Examples
The embodiments of the present invention will be described in detail below, and the embodiments are implemented on the premise of the technical solution of the present invention, and detailed embodiments and specific operation procedures are given, but the scope of the present invention is not limited to the following embodiments.
Example 1
A combined fluid dynamic pressure type dry gas-tight seal rear isolation sealing device is structurally shown in figure 1, is arranged between a dry gas seal assembly and a bearing box and comprises a labyrinth seal unit and a fluid dynamic pressure type seal unit, wherein the fluid dynamic pressure type seal unit consists of a rotating assembly and a static assembly.
The rotating assembly comprises a movable ring 3, a shaft sleeve 1, a pressing sleeve 7, a centering corrugated belt 10, a plurality of O-shaped rings, a transmission pin 2, a plurality of inner hexagonal screws and the like, wherein the pressing sleeve 7 is connected with the shaft sleeve 1 into a whole through the inner hexagonal screws 17, specifically, the shaft sleeve 1 comprises a first ring 28 and a second ring 29 which are coaxially and integrally arranged, a groove is arranged at the tail end of the pressing sleeve 7 and is in contact with a main shaft 23, the front end of the first ring 28 is inserted into the groove and is abutted against the groove wall, the groove bottom of the groove is fixed with the front end of the first ring 28 through the inner hexagonal screws 17, the front end of the second ring 29 is integrally connected with the tail end of the first ring 28, the tail end of the movable ring 3 is attached to the front end of the second ring 29 and is transmitted through the transmission pin 2, the inner edge of the movable ring 3 is abutted against the outer edge of the first ring 28, the centering corrugated belt 10 is arranged between the inner edge, the front end of the pressing sleeve 7 abuts against the rotating part of the dry gas seal assembly and is fixed by a pin 16. Through the axial compression of the dry gas sealing assembly and the lock nut 11, torque is transmitted to the shaft sleeve 1 and the compression sleeve 7, so that the shaft sleeve 1, the compression sleeve 7 and the main shaft 23 rotate together at a high speed. The sleeve 1 in turn transmits torque to the moving ring 3 via the drive pin 2, causing the moving ring 3 to rotate at high speed with the sleeve 1. The moving ring 3 is made of metal pieces, a high-hardness wear-resistant coating is sprayed or surfacing welded on the sealing end face, and micrometer-level fluid dynamic pressure grooves 30 which are uniformly distributed along the circumferential direction are machined on the inner side of the coating or surfacing layer in a special machining mode; in the present embodiment, the hydrodynamic grooves 30 are unidirectional spiral grooves, and as shown in fig. 2 or fig. 3, the outer sides of the hydrodynamic grooves 30 are outer dams 31 without grooves. An O-ring 8 is provided between the sleeve 1 and the main shaft 23, and an O-ring 9 is provided between the rotating ring 3 and the second ring 29.
In other embodiments, the hydrodynamic grooves may also be of a bi-directional rotating groove type, as shown in fig. 5, a T-shaped groove.
The static assembly is composed of a static ring 4 made of carbon graphite, a push ring 12, a spring 6, a plurality of O-shaped rings, a spring seat 5, a plurality of pins and a plurality of hexagon socket head cap screws, and the end face of the static ring 4 is attached to the end face of the moving ring 3 by means of axial pressing force of the spring 6 and gas pressure of isolation gas. Specifically, the spring seat 5 is fixed to the housing 24 by the socket head cap screw 21, and the O-ring 33 is provided therebetween. A push ring 12, a spring 6 and a static ring 4 are arranged in the spring seat 5, wherein the front end of the push ring 12 is attached to the rear end of the spring 6, and the front end of the spring 6 is attached to the bottom of a spring hole in the spring seat 5; the tail end of the push ring 12 is attached to the front end of the static ring 4, and meanwhile, an O-shaped ring 13 is arranged on the matching surfaces of the push ring 12, the static ring 4 and the spring seat 5. In the present application, the spring seat 5, the push ring 12 and the stationary ring 4 are prevented from rotating relative to each other by a pin 15. One end of the stationary ring 4 near the axial center of the main shaft 23 (i.e., at the inner diameter of the stationary ring) is located at the inlet position of the hydrodynamic groove 30. The tail end of the static ring 4 is jointed with the front end of the dynamic ring 3 to form a sealing surface.
In this embodiment, the labyrinth seal unit includes a labyrinth seal body 18, a pressing sleeve 7 and a spring seat 5, a plurality of labyrinth teeth 27 and labyrinth tooth cavities 26 are continuously and uniformly distributed at the inner diameter of the labyrinth seal body along the axial direction, and the isolation gas is throttled and depressurized by using a small annular gap formed by the labyrinth teeth 27 and the outer circle of the pressing sleeve 7 on the labyrinth seal body to realize sealing, as shown in fig. 4, the labyrinth seal body 18 and the spring seat 5 are fixed by an inner hexagon screw 19, and an O-ring 14 is arranged between the labyrinth seal body 18 and the spring seat.
The spring seat 5 is fixed to the housing 24 by a socket head cap screw and a washer 22, an oil slinger 20 is provided on the housing 24, an oil slinger 32 is provided on the lock nut 11, and the tail end of the spring seat 5 is formed in a bell mouth shape, so that the bearing-side lubricating oil is prevented or reduced from spreading or splashing to the hydrodynamic seal unit and can be discharged in time.
When the turbomachinery works, the rotating ring rotates at a high speed, the isolating gas passes through an isolating gas channel arranged in the spring seat, then is divided into two parts, respectively enters the inner labyrinth seal unit and the outer hydrodynamic seal unit, the isolating gas passing through the one part entering the labyrinth seal unit leaks to the inner side through small annular gaps formed by a plurality of labyrinth teeth on the labyrinth seal body and the excircle of the pressing sleeve, and the leaking gas of the outer side seal in the dry gas seal is isolated. The isolating gas entering the hydrodynamic pressure type sealing unit enters the hydrodynamic pressure groove through an annular cavity between the static ring and the pressing sleeve, and the isolating gas at the inner diameter is pumped outwards by utilizing the hydrodynamic pressure effect generated by the hydrodynamic pressure groove, so that a layer of micron-order gas film is formed between the sealing end surfaces, the lubricating and isolating effects are realized on the sealing end surfaces, and the sealed non-contact operation is realized. In the view of fig. 1, the isolating gas enters the spring seat from a point A, is divided into two parts at a point B, one part of the isolating gas enters the labyrinth seal through the point C, is leaked to the inner side through the labyrinth seal, is mixed with the leakage gas of the outer side seal of the dry gas seal, and is discharged from a point E through a channel in the spring seat to carry out high-point emptying; the other strand passes through the point D to reach the hydrodynamic groove to generate an air film, so that the lubrication and the oil gas are isolated. Because the rotating speed of the turbo machinery is very high, the rigidity of the extremely thin air film on the sealing end face is very high, lubricating oil gas on the bearing side can be effectively isolated, and zero leakage of the lubricating oil gas on the bearing side to dry air sealing can be ensured even if the air supply pressure of the isolation air is lower than the oil gas pressure on the bearing side, so that the long-period stable operation of the dry air sealing is ensured. Because the end face clearance of the hydrodynamic seal is extremely small and the seal pressure difference is low, the leakage amount of the isolating gas entering the bearing box through the outer hydrodynamic seal is extremely small, namely, the zero leakage of the lubricating oil gas on the bearing side to the dry gas seal of the turbine machinery can be ensured only by extremely low isolating gas consumption through the outer hydrodynamic seal. Even if the pressure of the isolation gas fluctuates and even the pressure of the isolation gas is lower than that of lubricating oil gas on the bearing side, the rear isolation sealing device can work normally, and the dry gas seal is ensured not to be polluted by the oil gas and fail.
The embodiments described above are intended to facilitate the understanding and appreciation of the application by those skilled in the art. It will be readily apparent to those skilled in the art that various modifications to these embodiments may be made, and the generic principles described herein may be applied to other embodiments without the use of the inventive faculty. Therefore, the present application is not limited to the embodiments herein, and those skilled in the art who have the benefit of this disclosure will appreciate that many modifications and variations are possible within the scope of the present application without departing from the scope and spirit of the present application.
Claims (10)
1. A combined type fluid dynamic pressure type dry gas seal postposition isolation sealing device is arranged between a dry gas seal component and a bearing box in a turbine machine, the turbine machine is provided with a main shaft rotating at high speed, and the device is characterized in that the postposition isolation sealing device comprises a labyrinth sealing unit and a fluid dynamic pressure type sealing unit, wherein the labyrinth sealing unit is arranged between the dry gas seal component and the fluid dynamic pressure type sealing unit, the fluid dynamic pressure type sealing unit comprises a rotating component and a static component, a lock nut is arranged on the main shaft, two ends of the rotating component are respectively clamped by the lock nut and a rotating part of the dry gas seal component, the rotating component is sleeved outside the main shaft and rotates along with the main shaft at high speed, the static component is arranged around the main shaft and is fixed with a shell of the turbine machine, one end face of the rotating component is attached to one end face of the static component to form a sealing face, the sealing face is perpendicular to the axial direction of the spindle, and a hydrodynamic groove is formed in the end face of the rotating component.
2. The combined hydrodynamic pressure type dry gas seal post-isolation sealing device according to claim 1, wherein the rotating assembly comprises a rotating ring, a shaft sleeve and a pressing sleeve, the shaft sleeve and the pressing sleeve are both annular and are sleeved outside the main shaft, wherein the shaft sleeve and the pressing sleeve are fixed by a hexagon socket head cap screw, the tail end of the shaft sleeve is abutted against the nut, the front end of the pressing sleeve is abutted against the rotating part of the dry gas seal assembly, and the rotating ring is fixed with the shaft sleeve by a driving pin and synchronously rotates.
3. The combined hydrodynamic pressure type dry gas-tight seal postposition isolation sealing device as claimed in claim 2, wherein said bushing comprises a first ring and a second ring coaxially and integrally disposed, the tail end of said second ring is abutted with a locking nut, the front end of said second ring is integrally connected with the tail end of said first ring, the tail end of said rotating ring and the front end of said second ring are fixed by said driving pin, the inner edge of said rotating ring is abutted with the outer edge of said first ring;
the tail end of the compression sleeve is provided with a groove, the front end of the first ring is inserted into the groove and is abutted against the groove wall, the groove bottom of the groove is fixed with the front end of the first ring through a hexagon socket head cap screw, and the tail end of the compression sleeve is abutted against the front end of the movable ring;
a centering corrugated belt is arranged between the inner edge of the movable ring and the outer edge of the first ring;
an O-shaped ring is arranged between the shaft sleeve and the main shaft.
4. The combined hydrodynamic pressure type dry-gas-tight-seal postposition isolation sealing device as claimed in claim 3, wherein a wear-resistant layer is attached to the end face of the front end of the rotating ring by means of spraying or surfacing, and an annular hydrodynamic pressure groove is arranged inside the wear-resistant layer, the hydrodynamic pressure groove being a unidirectional rotation groove type or a bidirectional rotation groove type;
and the outer side of the wear-resistant layer is a slotless dam area.
5. The combined hydrodynamic type dry hermetic seal post-isolation seal device according to claim 4, wherein the hydrodynamic groove has a groove depth of 3 to 20 μm;
the radial width of the dam area positioned on the outer side is 0.2-0.7 of the width of the sealing surface.
6. The combined hydrodynamic dry gas-tight seal post isolation seal of claim 4, wherein said stationary component comprises a spring seat, a spring, a push ring and a stationary ring, said spring seat being secured to the housing by a socket head cap screw; the end face of the tail end of the static ring is attached to the end face of the front end of the movable ring to form a sealing surface, the front end of the static ring is attached to the tail end of the push ring, the front end of the push ring is attached to the rear end of the spring, and the front end of the spring is attached to the end face of the bottom of the spring hole in the spring seat.
7. The combined hydrodynamic dry gas seal post isolation seal of claim 6 wherein said spring seat has an isolation gas passage therein through which isolation gas enters the inner diameter of said stationary ring.
8. The combined hydrodynamic dry gas-tight rear isolation seal of claim 6, wherein a pin is provided between the spring seat and the push ring and prevents rotation between the spring seat and the push ring by the pin;
a pin is arranged between the push ring and the static ring, and the push ring and the static ring are prevented from rotating through the pin;
o-shaped rings are arranged on the matching surfaces of the push ring, the static ring and the spring seat;
and an O-shaped ring is arranged on the matching surface of the spring seat and the shell.
9. The combined hydrodynamic dry gas-tight seal back isolation seal of claim 6, wherein the tail end of said spring seat is flared;
the oil slinger is arranged on the shell, and the oil slinger is arranged on the lock nut.
10. The combined hydrodynamic pressure type dry gas seal postposition isolation sealing device as claimed in claim 6, wherein the labyrinth seal unit labyrinth seal body, the pressing sleeve and the spring seat are axially and uniformly distributed at the inner diameter of the labyrinth seal body, a plurality of labyrinth teeth and labyrinth tooth cavities are formed by utilizing a plurality of labyrinth teeth on the labyrinth seal body and the outer circle of the pressing sleeve to throttle and reduce pressure of the isolation gas to realize sealing, the labyrinth seal body and the spring seat are fixed by inner hexagonal screws, and an O-shaped ring is arranged between the labyrinth seal body and the spring seat.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020266746.8U CN211715184U (en) | 2020-03-06 | 2020-03-06 | Combined fluid dynamic pressure type dry airtight seal postposition isolation sealing device |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020266746.8U CN211715184U (en) | 2020-03-06 | 2020-03-06 | Combined fluid dynamic pressure type dry airtight seal postposition isolation sealing device |
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| CN211715184U true CN211715184U (en) | 2020-10-20 |
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| CN202020266746.8U Active CN211715184U (en) | 2020-03-06 | 2020-03-06 | Combined fluid dynamic pressure type dry airtight seal postposition isolation sealing device |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114183394A (en) * | 2021-11-25 | 2022-03-15 | 沈阳鼓风机集团安装检修配件有限公司 | Centrifugal compressor |
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2020
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114183394A (en) * | 2021-11-25 | 2022-03-15 | 沈阳鼓风机集团安装检修配件有限公司 | Centrifugal compressor |
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Address after: 201111 Room 102, building 3, no.508 Zixu Road, Minhang District, Shanghai Patentee after: Shanghai Yousai Sealing Technology Co.,Ltd. Address before: 201111 Room 102, building 3, no.508 Zixu Road, Minhang District, Shanghai Patentee before: Shanghai haomi Sealing Technology Co.,Ltd. |
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