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CN106687663B - Shaft seal, method for operation - Google Patents

Shaft seal, method for operation Download PDF

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Publication number
CN106687663B
CN106687663B CN201580050742.8A CN201580050742A CN106687663B CN 106687663 B CN106687663 B CN 106687663B CN 201580050742 A CN201580050742 A CN 201580050742A CN 106687663 B CN106687663 B CN 106687663B
Authority
CN
China
Prior art keywords
seal
sealing
fluid
pressure
shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
CN201580050742.8A
Other languages
Chinese (zh)
Other versions
CN106687663A (en
Inventor
卢德格尔·阿尔费斯
马克·伦克尔
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens Corp
Original Assignee
Siemens Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens Corp filed Critical Siemens Corp
Publication of CN106687663A publication Critical patent/CN106687663A/en
Application granted granted Critical
Publication of CN106687663B publication Critical patent/CN106687663B/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • 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
    • F01D11/003—Preventing or minimising internal leakage of working-fluid, e.g. between stages by packing rings; Mechanical seals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/122—Shaft sealings using sealing-rings especially adapted for elastic fluid pumps
    • F04D29/124—Shaft sealings using sealing-rings especially adapted for elastic fluid pumps with special means for adducting cooling or sealing fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/14—Shaft sealings operative only when pump is inoperative
    • F04D29/143—Shaft sealings operative only when pump is inoperative especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/002—Sealings comprising at least two sealings in succession
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
    • F16J15/3408—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface
    • F16J15/3412—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface with cavities
    • F16J15/342—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface with cavities with means for feeding fluid directly to the face
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3464—Mounting of the seal
    • F16J15/348—Pre-assembled seals, e.g. cartridge seals
    • F16J15/3484—Tandem seals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/44—Free-space packings
    • F16J15/447—Labyrinth packings

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)

Abstract

The invention relates to a shaft seal (SHS) for sealing a gap (G) of a lead-through (PT) of a shaft (S) running through a housing (C), wherein the sealing surfaces are arranged opposite one another in a sealing plane (SEP), wherein the sealing plane (SEP) has a substantially radial extent with respect to the shaft (S), wherein a Stationary Sealing Surface (SSS) and a Rotating Sealing Surface (RSS) are fastened to a carrier (RSUP, SSUP), i.e. to the stationary carrier (SSUP) and to the rotating carrier (RSUP), and the sealing surfaces (RSS, SSS) are elastically prestressed against one another: at least the Stationary Support (SSUP) or the Rotating Support (RSUP) is prestressed by means of an Elastic Element (EEL). For simplicity, in addition to the method for operation, it is proposed: the inner secondary seal (SS2) has at least one first labyrinth seal (LTS1), and the inner secondary seal (SS2) has at least one barrier fluid suction device (SLF) on the outside of the first labyrinth seal (LTS 1).

Description

Shaft seal, the method for operation
Technical field
The present invention relates to a kind of shaft seal, it is used to seal the gap for connecting portion of the axis through shell, wherein in shell There is the process fluid under sealed pressure in the inside of body, and there is the environment under environmental pressure except shell Fluid, wherein shaft seal includes at least two seal modules, at least one fluid input unit and at least one fluid leading-out portion, Wherein seal modules include at least one first primary seal and internal secondary sealing part, wherein the first primary seal is configured to diameter To seals, the radial seals have rotation sealing surface and static sealing surface, wherein these are close Cover is opposite in sealing plane, and wherein sealing plane has the extension for being substantially opposite axis radial direction, wherein static is close Cover and the fixation of the sealing surface of rotation on the load bearing member, are i.e. fixed on the load-bearing part of static load-bearing part and rotation, and institute State sealing surface flexibly mutually tensioning in the following way: i.e. at least static load-bearing part or the load-bearing part of rotation is by means of elasticity Element pre-tightens.
Moreover, it relates to which a kind of device of the shaft seal with aforementioned type and one kind are for running fluid energy The method of amount machinery, especially turbo-compressor, the shaft seal for the type that there is the fluid energy machine beginning to limit.
Background technique
The shaft seal of aforementioned type usually especially uses on turbomachinery, and the turbomachinery has to be drawn from shell Axis out, the axis realize the connection of driving device or slave unit.It is in the characteristic of shaft seal: since axis surface is opposite In the relative motion of adjacent shell, it is unable to reach absolutely leakproofness.Especially in toxic or volatile work In skill fluid, it is necessary to carefully export leakage, the process fluid should avoid environment by means of shaft seal.Such as in steam Or prevent process fluid to be discharged in environment also by way of this shaft seal in gas turbine, and the leakage of shaft seal or Person says that aspiration has the obtained thermal efficiency and directly affects.The minimum of the leakage of shaft seal is the design of this machinery Most important purpose in range.
In turbo-compressor, seals, especially so-called tandem seals usually undertake by shell it Task of the interior pressure space relative to atmospheric sealing.Tandem seals are contactless sealing elements and belong to dry type Seals.The tandem seals obstruct gas lubrication by dry filtered barrier fluid in other words, To avoid damaging the pollution and humidity of function.The present invention is always related to dry gas seals in seals.
The conventional device of shaft seal with the above-mentioned type is known from 10 2,008 048 942 B4 of DE.
The radial double seal for the type that known beginning has proposed from 20 2,008 003 418 U1 of DE.
The arranged in series of dry gas seals is known from JP 2,006 08 38 89 A and US 3,880,434.
The simple arrangement of radial double seal is known from US 6,325,382B1.
Known radial double containment in the case where intermediate setting labyrinth from 1 914 387 A1 of EP The arranged in series of part.
Known such equipment from 2010/254811 A1 of US.2 792 687 A1, WO 2011/ of document FR 135016 A1, US 6 524 059 B1 be also related to shaft sealer.
In normal operation, from the compressor in other words of fluid energy machine on the pressure side or pressure stage extract, dry, mistake Filtration resistance trapping body and it is conveyed to dry gas seals.In this regard, needing the extract part from barrier gas up to dry gas The pressure drop of the pressure of the inlet of sealing element.It is middle inside housings first to be formed when compressor is turned off and is then expanded So-called shutdown pressure, the shutdown pressure, which then passes through discharge medium, to be reduced.During this time period, it is not present within the compressor Pressure drop (whole space/grades have uniform pressure), and can not be by barrier gas conveying in the case where no added requirement To dry gas seals.Therefore dry gas seals are endangered during the time that shutdown status and pressure decline, because The dry gas seals can be damaged by moisture and dirt.
Up to now, known from practice: during shutting down and pressure declines, from the external source with relatively high pressure Dry and filtering obstructs gas and is conveyed to dry gas seals.
Known another feasibility is using barrier gas booster from practice.This is air compressor, the air Compressor improves the pressure of gas extracted out from compressor, and then pressure drop needed for ensuring to supply barrier gas.
Summary of the invention
Therefore, the purpose of the present invention is to: improve the device with the shaft seal for starting proposed type: i.e. reduction pair The requirement of additional sealing fluid, and be not damaged in terms of the safety of operation and leakproofness and do not need additional pressure Contracting machine.
If underneath with term inwardly or outwardly, it is internal or external, the direction provides to be related to the inside away from shell The distance of the outside of shell increaseds or decreases in other words.
In order to realize purpose according to the present invention, a kind of device of type that beginning is proposed, the pair of the inside are proposed Sealing element has at least one first labyrinth, and the secondary sealing part of the inside is in first labyrinth sealing There is at least one barrier fluid suction unit on the outside of part.In addition, proposing a kind of device with this shaft seal.This The present invention relates to a kind of methods for running this shaft seal outside.It below relates to of the invention be advantageously improved form.
By the feed-in position of the barrier gas at the first primary seal and the current pressure being present in compressor it Between pressure drop according to the present invention, can be realized during shutdown and expansion adequately barrier gas supply.
Pressure drop at the first labyrinth can pass through additional second labyrinth sealing for reducing pressure Part further improves, so that needing less barrier gas.At the first labyrinth or in two labyrinths Between be preferably able to export to gas (gas and barrier gas from compressor) with low pressure via pipeline and regulating valve Processing system in.
Regulating valve is controlled preferably via regulation device, and the regulation device adjusts pressure within the compressor and is in pressure drop In pressure between pressure difference.
When replacing via controlled regulating valve, via orifice plate or other throttle mechanisms and automated open and close valve by gas When body (gas and barrier gas from compressor) is exported in the processing system with low pressure, acquisition reaches desired pressure drop Another simpler feasibility of effect.The simpler feasibility is accurately adjusted unlike the solution with regulating valve Pressure difference is saved, but cost is preferably.Structure tolerance in labyrinth gap can influence the pressure in pressure drop, make According to stagnation pressure compression process and its boundary condition be required to correspondingly determine regulator control system.
According to according to the method for the present invention, the gas of outflow passes through the pressure loss that occurs in the first labyrinth And generate pressure drop.Due to the pressure drop, pressure difference, the pressure difference are established between pressure within the compressor and the pressure in pressure drop Be it is required, with dry and filter the barrier gas in barrier gas system.Therefore, pass through in discharge compressor in compressor Ensure during gas discharge: since pressure drop carries out the sufficient barrier gas supply of dry gas seals.Compressor being capable of root It is required according to technique and the expansion of the barrier gas condition of existing outside is up to following pressure, from the pressure outside others It is feasible for obstructing gas supply, or expansion is until atmospheric pressure, the barrier gas without conveying other outside.
Of the invention one is advantageously improved form proposition: shaft seal composition according to the present invention has the first primary seal Part or the first primary seal and the second primary seal are as radial double seal, and the double seal is by being respectively provided with rotation Sealing surface and two seals of static sealing element determine: which sealing surface is to respectively in a sealing element plane Opposite, two of them sealing plane has the extension for being substantially opposite axis radial direction, and the first of two of them sealing surface pair is close Cover in than secondary sealing area on bigger radius, and the static sealing surface and rotation of two of them sealing surface pair Sealing surface be separately fixed on common load-bearing part, that is, be fixed on the load-bearing part of static load-bearing part and rotation, and close The sealing surface of cover pair in the following way flexibly mutually tensioning: i.e. at least static load-bearing part or the load-bearing part of rotation by It is pre-tightened in elastic element, wherein being equipped with the barrier fluid chamber extended along ring circumferential direction, the barrier between two sealing surfaces pair Fluid cavity can be loaded with barrier fluid by means of barrier fluid feeding portion.
It is also feasible that: the stress level in the first leading-out portion is chosen to, makes it possible to realize and leads fluid from first It is guided in Compressor Process in portion to the Huis out.
Sealing surface is to being preferably coaxially arranged, so that obtaining simple and space-saving structure.
Preferably, the static carrying of seals is pre-tightened by means of the direction of elastic element towards the load-bearing part of rotation Part.In this manner, being less complicated to constitute the structure for being subjected to centrifugal force of rotor.
The preferred operation of sealing device according to the present invention proposes: the first primary seal is loaded with as barrier fluid Process fluid.
Second primary seal can be configured to simple dry gas seals as the first primary seal.
In the case that pressure is lower than 15bar in specified operation, it is possible to: radial direction is also used for the second primary seal Double seal, the double seal is loaded with the intermediate barrier fluid as barrier fluid.Intermediate barrier fluid herein can It is identical as the barrier fluid of the first primary seal or other fluids, such as nitrogen according to the type for the medium to be sealed.Important Be to ensure that: the second primary seal has positive pressure difference in two sides in each operating point, and then in the opposite close of sealing surface pair Stable fluid film is obtained between cover.Therefore, cancel the requirement for stopping the corresponding pressure in the first leading-out portion, so that relatively In the second primary seal, there are minimum differntial pressures.
Especially when primary seal is configured to simple dry gas seals, of the invention one is advantageously improved form It proposes: being provided with the additional first additional shaft seal, preferably labyrinth type shaft seal between two primary seals.With the party Formula ensures: the leakage of the first primary seal MS1 does not reach in the second leading-out portion via the second primary seal.Have this first In the composition scheme of additional shaft seal appropriately: the first barrier fluid leading-out portion is arranged between two primary seals at this On the side inwardly of additional shaft seal.
Of the invention one is advantageously improved form proposition: between the second primary seal and the above-mentioned additional shaft seal Input unit equipped with intermediate barrier fluid.
In addition, in order to seal sensitive axle sealing system suitably: additionally being set gradually outside towards the second primary seal There are two shaft seal, preferably labyrinth type shaft seals, i.e. the 4th internal additional shaft seal and the 5th external additional shaft Sealing element.When the two add between shaft seal the feeding portion for being equipped with separation fluid, sealing is particularly efficient.Separation Fluid can be filtered surrounding medium.Outside the entire sealing device of present dynasty for example equipped with oily storage chamber when, this arrangement is especially Interesting, the mist of oil being discharged from the oily storage chamber can reach in sealing device and can cause possible harmful fluid Mixing.
The separation fluid conveyed suitably can successively be set by means of the second leading-out portion in the second primary seal and two It is exported between the 4th and the 5th additional shaft seal set.
Leading-out portion can be guided in the common fuel spray of combustion section when necessary.
Particular advantage is obtained by feature according to the present invention and the invention improved form being described in detail.Greatly reduce outside Required barrier fluid amount, because the required stress level relative to conventional arrangement barrier fluid reduces.Furthermore it is possible to The boost in pressure of barrier fluid is abandoned, because pressure drop according to the present invention barrier fluid suction in other words makes in the first primary seal In in other words stress level in multiple primary seals reduce.Due to cancelling boost in pressure, the fluid to be sealed can be reduced Inside circulation amount and improve such as compressor volumetric efficiency.
Detailed description of the invention
In the following, the present invention is described in detail with reference to the attached drawings by embodiment.In addition to the invention being described in detail in embodiment constitutes scheme Except, additional operational feasibility can also be obtained from specification for those skilled in the art.Attached drawing is shown:
Fig. 1 shows shaft seal and the schematic diagram for running the apparatus according to the invention according to the method for the present invention.
Fig. 2 shows the exemplary diagrams of radial double seal.
Specific embodiment
Fig. 1 is shown by the shaft seal SSS of axis S rotor R, the shell C and turbo-compressor TCO in other words device constituted Composition scheme according to the present invention, the shaft seal include multiple seal modules SM.In addition, Fig. 1, which is also schematically illustrated, to be had The flow chart of the signal line of Different Fluid Flow and regulation device CU.
Arrow below seal modules SM show respectively when compressor stationary state and corresponding ground pressure decline The flow direction of inner setting.
Turbo-compressor can be interrupted by means of two valves, i.e. into valve SVI and dump valve SVE, this is to say, flow into pipe Road and outflow pipeline can be closed.
The internal mirror images that seal modules are substantially opposite turbo-compressor TCO are symmetrically arranged, and due to it is another Side is identical and does not partly indicate individually all.
The inside for starting from shell C belongs to seal modules SM:
It is configured to the first labyrinth LTS1 of labyrinth type shaft seal,
It is configured to the second labyrinth LTS2 of labyrinth type shaft seal,
- the first primary seal MS1 consists of radial simple seals or is configured to radial direction according to fig. 2 Double seal,
Third additional labyrinth LS3,
- the second primary seal MS2 consists of radial simple seals or is configured to radial direction according to fig. 2 Double seal, and
The device of-two additional shaft seal LS4, LS5, the additional shaft seal set gradually close as labyrinth type axis Sealing.
The sealed pressure PPF of process fluid PF is filled in the inside of shell C.In the first labyrinth LTS1 and There are barrier fluid suction unit SLF between two labyrinth LTS2.
First primary seal MS1 is lubricated by towards the barrier fluid SF conveyed in the first primary seal MS1.
Second primary seal MS2 is by towards intermediate barrier fluid ISF, such as nitrogen conveyed in the second primary seal MS1 Lubrication.
If the first primary seal MS1 is configured to radial double seal, barrier fluid SF is in purified technique The form of fluid PF is conveyed with over-voltage, so that being not only obtained across two sealing surfaces of radial double seal inwardly but also outwardly Pair go out flow.Similarly, it can also be run the second primary seal as radial double seal.
There are the first leading-out portion EX1, first export between the first primary seal MS1 and the second primary seal MS2 Portion exports one from the first primary seal MS1 process fluid PF flowed outward and intermediate barrier fluid ISF that may be present Component.Relative to the intermediate space between the sealing element followed in the second primary seal MS2 and outwardly, in the first primary seal Intermediate space between MS1 and the second primary seal MS2 has over-voltage, and the over-voltage is further by the second primary seal MS2 It reduces, second primary seal is preferably configured as simple seals.It follows in the second primary seal MS2 and outwardly There are the second leading-out portion EX2 between sealing element, the second leading-out portion export is made of intermediate barrier fluid ISF and following fluids Mixture, the fluid is originated from the seal combination that follows outwardly.There is the ring under environmental pressure PAM except shell Border AF.Between two additional shaft seal LS4 and LS5 at the outer end of device, feeding separation fluid SPPF, the separation Fluid leaks out in both directions and should prevent possible dirt from entering in device from outside in inlet.Separate fluid SPPF For the purified medium or inert fluid of environment, for example, nitrogen.
Be configured to labyrinth third additional labyrinth LS3 be in two primary seals MS1, MS2 it Between.First leading-out portion EX1 is in the additional third additional labyrinth LS3.
Intermediate barrier fluid is imported between additional third additional labyrinth LS3 and the second primary seal MS2 ISF, such as nitrogen.Be achieved in: the barrier fluid SF of the first primary seal MS1 can not be reached at the second primary seal MS2 And it can not be discharged in leading-out portion EX2 as leakage.
The barrier in barrier fluid system SFSY is supplied in the shaft seal of turbo-compressor TCO shown in Fig. 1 Fluid SF.In adjusting operation, barrier fluid system SFSY is obtained by means of extraction conduit PFSF from the outlet of turbo-compressor TCO The process fluid under relatively high final pressure is obtained, the process fluid is filtered and is cleaned and dries when necessary, so as to Shaft seal is supplied to using the process fluid as barrier fluid SF.It, can be by means of pipe in order to ensure barrier fluid supply External barrier fluid EXT is conveyed to barrier fluid system SFSY by road.This is for being applied to even if under following operating statuses Sealing machine: under the operating status, barrier fluid can not be provided in the case where not external barrier fluid EXT SF, this is, for example, because pressure is too small in other barrier fluids SFSY or other rough sledding.
Central regulation device CU is detected in barrier fluid system SFSY by means of barrier fluid device for pressure measurement PPSF With the pressure difference of the outlet of compressor TCO.In addition, being determined by means of pressure measurement position PPSLF in the outlet and resistance of compressor TCO Pressure difference between fluid extraction arrangement SLF.According to these pressure measurements, central regulation device CU promotes barrier fluid suction to adjust Section valve CVSLF's opens or closes, and sets by the barrier fluid suction regulator valve towards the pressure outside internal secondary sealing part SS2 Power is horizontal.In the state that compressor TCO is interrupted, normally open barrier fluid suction regulator valve CVSLF, so that being flowed in barrier In the region of the feeding of body SF, towards the first primary seal MS1 in setting than pressure water lower in barrier fluid system SFSY It is flat, so that ensuring that barrier fluid SF is flowed into clearance G, lubricate with separation and when necessary the first primary seal MS1.Barrier stream Body suction unit SLF introduces pressure drop FL, and the stress level of the pressure drop is always sufficiently low, so that for conveying barrier fluid There is no conflict with barrier fluid system SFSY in terms of the insufficient pressure difference of SF.For the shaft seal in left side, in view Middle description has the pressure history in the pressure of different axial positions.First pressure change curve PLB1 indicates direct The stress level in compressor TCO being interrupted after shutdown, second pressure change curve PLB2 indicate after inflation by Stress level in the compressor of interruption.The stress level of second pressure change curve PLB2 is basically by the barrier conveyed Gas SF is obtained.
Method according to the present invention for running fluid energy machine, especially turbo-compressor TCO, wherein the fluid Energy machinery has shaft seal according to the present invention, and described method includes following steps:
A) it is run at the revolving speed n of rotor R with the sealed pressure PPF in the inside of shell C,
B) revolving speed n and sealed pressure PPF is reduced,
C) lower than the first sealed pressure PPF or when being lower than the first revolving speed n: adjusting barrier stream according to sealed pressure PPF Barrier fluid swabbing pressure PSLF in body suction unit SLF, so that passing through the first labyrinth LTS1 from flow channel The process fluid PF of middle outflow does not reach primary seal MS1, in MS2.
Fig. 2 shows the schematic diagram of radial double seal RDS, the radial double seal is sealed in axis S and turns in other words Clearance G between sub- R and shell C.In the region for connecting portion PT through the axis S of shell C, axis S is provided with a circumferential convex shoulder SC, The rotary part of the radial double seal RDS of the convex shoulder carrying.Radial double seal is substantially by radially setting gradually Seals DGS1, DGS2 are constituted, and the seals are respectively provided with the sealing surface RSS and static sealing surface of rotation SSS, the sealing surface of the rotation and static sealing surface are correspondingly made available two sealing surfaces to SSP.In the two sealing surfaces pair Between SSP, by barrier fluid be transported to it is positioned at there, along ring circumferential direction extend chamber SFC along, the barrier fluid due to The two sealing surfaces leak out the over-voltage between the sealing surface RSS and static sealing surface SSS of each one rotation of SSP. The two sealing surfaces to the sealing surface RSS and static sealing surface SSS of the rotation of SSP by means of common load-bearing part RSUP, SSUP is fixedly connected to one another.Static load-bearing part SSUP is pre- relative to the load-bearing part RSUP of rotation by means of elastic element EEL Tightly.

Claims (8)

1.一种轴密封件(SHS)，其用于密封贯穿壳体(C)的轴(S)的穿引部(PT)的间隙(G)，1. A shaft seal (SHS) for sealing a gap (G) of a lead-through (PT) of a shaft (S) penetrating a housing (C), 其中在所述壳体(C)的内部(IN)中存在处于密封压力(PPF)下的工艺流体(PF)，并且在所述壳体(C)外存在处于环境压力(PAM)下的环境流体(AF)，Where there is a process fluid (PF) at sealing pressure (PPF) in the interior (IN) of the casing (C) and an environment at ambient pressure (PAM) outside the casing (C) Fluid (AF), 其中所述轴密封件(SHS)包括至少两个密封模块(SM)、至少一个流体输入部和至少一个流体导出部，wherein the shaft seal (SHS) comprises at least two sealing modules (SM), at least one fluid inlet and at least one fluid outlet, 其中所述密封模块(SM)包括至少一个第一主密封件(MS1)和内部的副密封件(SS2)，其中所述第一主密封件(MS1)构成为径向的气体密封件(DGS)，所述径向的气体密封件具有旋转的密封面(RSS)和静止的密封面(SSS)，其中所述密封面在密封平面(SEP)中相对置，其中所述密封平面(SEP)具有基本上相对于轴(S)径向的延伸，The sealing module (SM) comprises at least a first primary seal (MS1) and an inner secondary seal (SS2), wherein the first primary seal (MS1) is designed as a radial gas seal (DGS) ), the radial gas seal has a rotating sealing surface (RSS) and a stationary sealing surface (SSS), wherein the sealing surfaces are opposite in a sealing plane (SEP), wherein the sealing plane (SEP) has a substantially radial extension with respect to the axis (S), 其中所述静止的密封面(SSS)和所述旋转的密封面(RSS)固定在承载件(RSUP，SSUP)上、即固定在静止的承载件(SSUP)和旋转的承载件(RSUP)上，并且所述密封面(RSS，SSS)通过如下方式弹性地相互张紧：即至少所述静止的承载件(SSUP)或所述旋转的承载件(RSUP)借助于弹性元件(EEL)预紧，wherein the stationary sealing surface (SSS) and the rotating sealing surface (RSS) are fastened to the carrier (RSUP, SSUP), ie to the stationary carrier (SSUP) and the rotating carrier (RSUP) , and the sealing surfaces (RSS, SSS) are elastically tensioned against each other by means of at least the stationary carrier (SSUP) or the rotating carrier (RSUP) being prestressed by means of elastic elements (EEL) , 其特征在于，It is characterized in that, 所述内部的副密封件(SS2)具有至少一个第一迷宫式密封件(LTS1)，并且所述内部的副密封件(SS2)在所述第一迷宫式密封件(LTS1)的外侧上具有至少一个阻隔流体抽吸装置(SLF)。The inner secondary seal (SS2) has at least one first labyrinth seal (LTS1), and the inner secondary seal (SS2) has on the outside of the first labyrinth seal (LTS1) At least one barrier fluid suction device (SLF). 2.根据权利要求1所述的轴密封件(SHS)，2. Shaft seal (SHS) according to claim 1, 其中所述轴密封件(SHS)除了所述第一主密封件(MS1)还包括第二主密封件(MS2)，并且在两个所述主密封件(MS1，MS2)之间设有至少一个第一流体导出部(EX1)，借助所述第一流体导出部排出第一导出流体。The shaft seal (SHS) includes a second main seal (MS2) in addition to the first main seal (MS1), and at least two main seals (MS1, MS2) are provided between the two main seals (MS1, MS2). A first fluid outlet (EX1) by means of which the first outlet fluid is discharged. 3.根据权利要求2所述的轴密封件(SHS)，3. Shaft seal (SHS) according to claim 2, 其中所述第一主密封件(MS1)和/或所述第二主密封件(MS2)构成为简单的干式气体密封件。The first main seal (MS1) and/or the second main seal (MS2) are designed as simple dry gas seals. 4.一种具有根据权利要求1至3中任一项所述的轴密封件(SHS)的装置。4. A device with a shaft seal (SHS) according to any one of claims 1 to 3. 5.一种用于运行流体能量机械的方法，5. A method for operating a fluid energy machine, 所述流体能量机械包括用于密封贯穿壳体(C)的轴(S)的穿引部(PT)的间隙(G)的轴密封件(SHS)，The fluid energy machine comprises a shaft seal (SHS) for sealing the gap (G) of the lead-through (PT) of the shaft (S) through the housing (C), 其中所述轴密封件(SHS)包括至少一个第一主密封件(MS1)和内部的副密封件(SS2)，wherein the shaft seal (SHS) comprises at least a first primary seal (MS1) and an inner secondary seal (SS2), 其中所述第一主密封件(MS1)构成为气体密封件(DGS)，wherein the first main seal (MS1) is configured as a gas seal (DGS), 其中所述内部的副密封件(SS2)具有至少一个第一迷宫式密封件(LTS1)，并且所述内部的副密封件(SS2)在所述第一迷宫式密封件(LTS1)的外侧上具有至少一个阻隔流体抽吸装置(SLF)，wherein the inner secondary seal (SS2) has at least one first labyrinth seal (LTS1), and the inner secondary seal (SS2) is on the outside of the first labyrinth seal (LTS1) has at least one barrier fluid suction device (SLF), 所述方法具有如下方法步骤：The method has the following method steps: a)在转子(R)的转速(n)下，以在所述壳体(C)的内部中的密封压力(PPF)运行，a) at the rotational speed (n) of the rotor (R), operating with sealing pressure (PPF) in the interior of the housing (C), b)降低转速(n)和密封压力(PPF)，b) reduce the rotational speed (n) and seal pressure (PPF), c)在低于第一密封压力(PPF)的极限值或在低于第一转速(n)时：根据所述密封压力(PPF)调节所述阻隔流体抽吸装置(SLF)中的阻隔流体抽吸压力(PSLF)，使得通过所述第一迷宫式密封件(LTS1)从所述密封压力(PPF)的区域中流出的工艺流体(PF)不到达所述主密封件(MS1，MS2)中。c) Below the limit value of the first sealing pressure (PPF) or below the first rotational speed (n): the barrier fluid in the barrier fluid suction device (SLF) is adjusted according to the sealing pressure (PPF) Suction pressure (PSLF) so that process fluid (PF) flowing out of the region of the sealing pressure (PPF) through the first labyrinth seal (LTS1) does not reach the primary seals (MS1, MS2) middle. 6.根据权利要求5所述的方法，其中所述流体能量机械是涡轮压缩机(TCO)。6. The method of claim 5, wherein the fluid energy machine is a turbo compressor (TCO). 7.根据权利要求5所述的方法，其中所述轴密封件(SHS)根据上述权利要求1至3中任一项构成。7. The method according to claim 5, wherein the shaft seal (SHS) is constructed according to any of the preceding claims 1 to 3. 8.根据权利要求6所述的方法，其中所述流体能量机械具有工艺流体馈入部和工艺流体导出部，并且在步骤a)和步骤b)之间借助于截止阀中断所述涡轮压缩机，使得封闭所述工艺流体馈入部和所述工艺流体导出部。8. The method according to claim 6, wherein the fluid energy machine has a process fluid infeed and a process fluid outlet, and the turbocompressor is interrupted between steps a) and b) by means of a shut-off valve, The process fluid feed-in and the process fluid outlet are made closed.
CN201580050742.8A 2014-09-19 2015-09-08 Shaft seal, method for operation Expired - Fee Related CN106687663B (en)

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