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WO2015128250A1 - Installation comprenant un joint à gaz, procédé de fonctionnement - Google Patents

Installation comprenant un joint à gaz, procédé de fonctionnement Download PDF

Info

Publication number
WO2015128250A1
WO2015128250A1 PCT/EP2015/053574 EP2015053574W WO2015128250A1 WO 2015128250 A1 WO2015128250 A1 WO 2015128250A1 EP 2015053574 W EP2015053574 W EP 2015053574W WO 2015128250 A1 WO2015128250 A1 WO 2015128250A1
Authority
WO
WIPO (PCT)
Prior art keywords
heating element
gas
gas seal
plant
sealing gas
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.)
Ceased
Application number
PCT/EP2015/053574
Other languages
German (de)
English (en)
Inventor
Ludger Alfes
Andreas Frenkel
Michael Petersmann
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 AG
Siemens Corp
Original Assignee
Siemens AG
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 AG, Siemens Corp filed Critical Siemens AG
Publication of WO2015128250A1 publication Critical patent/WO2015128250A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/584—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling or heating the machine
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/5853—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps heat insulation or conduction
    • 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
    • F16J15/164—Sealings between relatively-moving surfaces the sealing action depending on movements; pressure difference, temperature or presence of leaking fluid
    • 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
    • F16J15/40—Sealings between relatively-moving surfaces by means of fluid

Definitions

  • the invention relates to a system with a gas seal, in particular a dry gas seal comprising:
  • At least one sealing gas supply line for supplying sealing gas to the gas seal.
  • the invention also relates to a method for operating the system.
  • Gas seals are used as shaft seals and increasingly preferred over simple labyrinth seals, because the leakage is considerably lower.
  • the gas seals in particular dry gas seals, depend on a special quality of the sealing gas for safe operation.
  • the sealing gas is to be supplied to the gas seal in a relatively narrow temperature range with only a very low moisture content. Should there be only a slight deviation in the quality of the sealing gas during operation, e.g. To introduce too high a level of moisture, there is a corresponding interruption of the lubricating film of gas between the rotating sealing surface and the standing sealing surface and consequently to damage or destruction of the gas seal.
  • gas seals or dry gas seals are used in the compression of process fluids, so that the destruction of the gas seal designed as a shaft seal usually has a decommissioning or even destruction of the compressor result. In the case of a toxic or explosive process medium, the destruction of the gas seal in the compression process can have catastrophic consequences.
  • the careful temperature control leads to a significant installation effort for the treatment of the sealing gas in conventional systems of the type mentioned.
  • To the treatment usually also includes a careful heating and temperature control of the sealing gas, depending on the current operating conditions of the plant.
  • the barrier gas flow was strongly heated so that a sufficient distance to the dew point could be maintained.
  • a disadvantage of this solution is that it does not take into account the effect of condensation on cold surfaces, but provides sufficient protection against surface condensation only for operating points with sufficient heat input from losses of the turbocompressor. Additionally, for critical operating points, an alternative gas, such as nitrogen, has been used with sufficient distance from the dew point. At this solution is disadvantageous that an external barrier gas source with sufficient external sealing gas must be available.
  • the temperature control of the sealing gas must take this into account in that the sealing gas must be able to meet the required lubricating effect on the sealing surfaces of the gas seal within the prescribed temperature range ,
  • a particular disadvantage of the sealing gas treatment is on the one hand in the high installation costs, which causes considerable costs and on the other hand in the significant space requirement, which claims the usually at least component-wise redundant running seal gas treatment for themselves.
  • the invention has therefore taken on the task, on the one hand to improve the reliability of a gas seal and on the other hand to reduce the space required for the sealing gas treatment.
  • To solve the invention proposes a system of the type mentioned above with the additional features of the characterizing part of claim 1 and a method according to the dependent method claim for the operation of the claimed system.
  • the respective dependent claims contain advantageous developments of the invention.
  • the invention is also attributable to embodiments that are not explicitly defined by means of the claim references, however, the expert from a combination of the other claimed features and the features of the embodiments make sense.
  • the invention overcomes several disadvantages of the prior art. So far, the influence of higher temperature of the barrier gas on the surface temperature of the gas seal is only low, since the transfer surface and the proportion of the sealing gas, which flows over the surface, is small. Therefore, conventionally, there is a high required power of the purge gas heater because much of the introduced heat remains unused.
  • a construction according to the invention can advantageously be a failure of liquids on the gas seal and in particular the associated surface by condensation of the sealing gas, which possibly leads to a failure of the dry gas seal, are excluded.
  • a further advantage is that the mentioned holes do not have to protrude into the pressure chamber, so that no special sealing of this heating chamber is necessary. It is also advantageous that the achievable temperature is limited only by the design temperature of the carrier component, for example the temperature capacity of the housing cover. Compared to a heating by means of oil can be advantageously dispensed with an extension of the oil system for heating purposes by means of a construction according to the invention, wherein the same function is provided electrically with much less effort. The electrical version is also more flexible to control and independent of the oil system regulated.
  • the heat input can be adjusted depending on an operating point to the thermodynamic need.
  • the heating of the gas seal carrier may possibly be switched off in normal operation if the self-heating from the heat loss occurring in the seal or the heat of a turbomachine connected in operation is sufficient to heat the gas seal.
  • an electrically formed heating element is an electrically formed heating element.
  • This can be advantageously used in elongated recess of the support element.
  • the carrier element (CE) it is particularly expedient for the carrier element (CE) to have an additional heat conductor-in particular thermal compound-wherein the additional heat conductor can be adapted to the shape of the heating element, so that an enlarged surface of direct contact between the carrier element and the additional element Heat conductor and the heating element is formed, so that compared to an arrangement without the additional heat conductor of a ne improved heat conduction from the heating element to the support element is formed.
  • the support element is expediently designed with a supply channel for the sealing gas.
  • a preferred application of the invention is a design of the system as a fluid energy machine, in particular as a turbo compressor.
  • the carrier element may be part of a housing of the turbomachine, for example as a housing cover of the housing of the fluid energy machine, in which case the housing cover may also be the carrier of the gas seal attached to the housing cover and carrier of a shaft bearing attached to the housing cover.
  • the at least one heating element transfers heat energy to the carrier element, wherein the carrier element transmits heat energy absorbed by the heating element to the gas seal.
  • the carrier element may be advantageous for the carrier element to transfer part of the heat energy absorbed by the heating element to the gas seal and another part to the supply channel for the sealing gas.
  • Embodiments are to be understood as exemplary only and do not limit the invention exclusively to the illustration. On the contrary, within the scope of his specialist knowledge, it is possible for a person skilled in the art to combine individual mentioned features with others without departing from the scope of the invention. Show it:
  • FIG. 1 shows an end view of a schematic representation of a housing cover with electrical heating cartridges inserted in bores
  • Figure 2 a longitudinal section of an embodiment with parallel to a compressor shaft introduced heating cartridge.
  • Figure 3 a longitudinal section of an embodiment with introduced perpendicular to the compressor shaft heating cartridge.
  • FIG. 4 shows a longitudinal section of an exemplary embodiment with a heating cartridge introduced at an angle to the compressor shaft.
  • FIGS. 1-4 each show schematically relevant components of a system according to the invention A.
  • a gas seal GS in particular a dry gas seal DGS
  • a support member CE on which the gas seal GS is attached and supported
  • at least one heating element HT shown.
  • a gas seal insert GSC comprising a gas seal GS or dry gas seal DGS and a certain number of heaters HT is received by the support element CE formed as a housing cover CCV.
  • a shaft bearing BEA is provided on the carrier element CE or the housing cover CCV, by means of which a shaft SH extending along an axis of rotation X is mounted.
  • the shaft SH is sealed to the otherwise stationary components by means of the gas seal GS, so that no process fluid PF in the interior of a fluid power machine passes through the gap into the environment through a gap extending in the circumferential direction between the gas seal GS and the shaft SH can escape.
  • the fluid energy machine of plant A is preferably designed as a turbocompressor TC and has a substantially hermetically sealed housing CAS, which is sealed to the environment by means of the housing cover CCV, which is designed as a carrier element CE.
  • the housing cover CCV takes as a carrier of the shaft bearing BEA on the static and dynamic bearing forces of the shaft SH and the corresponding rotor.
  • the gas seal GS is supplied by means of a sealing gas supply via a sealing gas line SGL by means of sealing gas or sealing gas.
  • the sealing gas SG is contaminated by means of a derivation, not shown, from the gas seal GS contaminated by passed into the extracted sealing gas SG process gas and ambient air along an exhaust, not shown.
  • the sealing gas line GSL has a sealing gas filter SFL and holds the sealing gas SG from a higher pressure level, which is shown in FIG. 1 as a sealing gas compressor SCO.
  • the higher pressure level may also be a reservoir of sealing gas SG.
  • Particularly preferred is an embodiment of the invention in non-environmentally harmful process fluids PF such that the sealing gas SG is simultaneously the process fluid PF and the sealing gas SG is taken from the highest pressure level of the fluid energy machine for supplying the gas seal GS.
  • the heating elements HT positioned by the carrier element CE are located on a circle RAD over the circumference - in this case distributed at equal intervals concentrically with the axis of rotation X.
  • This equidistant arrangement is only exemplary and not mandatory.
  • the respective heating element HT is arranged along a longitudinal axis XHT1, XHT2, XHT3 in a cylindrical recess CH in the carrier element CE.
  • the longitudinal axis XHT1, XHT2, XHT3 is oriented in each case in a different angular position to the axis of rotation X of the system A.
  • the heating element HT extends with the longitudinal axis XHT1 - XHT3 in any angular orientation to the axis of rotation X or a housing longitudinal axis of the housing CAS.
  • the final number of heating elements HT or of the corresponding heating element recesses CH and their orientation in the carrier element CE can be determined.
  • the heating element HT transmits by means of the support member CE not only on the gas seal GS heat, but also on the sealing gas supply CGL, which extends partially through the support member CE to the gas seal GS out.
  • the heating element HT or the heating elements HT indirectly heats both the gas seal GS and the supply of sealing gas SGL and indirectly also the sealing gas SG, so that the gas seal GS is always operated in the allowable temperature range.
  • FIG. 2 shows an embodiment in which the heating element HT is inserted parallel to the compressor shaft SH in a bore introduced in the housing cover COV and thus indirectly heats the (in simplified form) gas-tight housing including the dry gas seal DGS contained therein.
  • the heating element HT is used perpendicular to the compressor shaft in a housing cover COV introduced hole and thus indirectly heated (simplified) gas seal housing including the dry gas seal contained therein.
  • the heating elements HT are powered by a power source PSU using power lines PSL with electrical
  • a temperature measuring point TS transmits the current temperature to a central control CU, which regulates the power supply from the power source PSU to the heating elements HT.
  • the central control unit CU accesses a database PDA, so that it is ensured in all operating states that, based on empirical values stored in the database, the correct amount of energy is always fed into the heating system.
  • HT is converted to heat.
  • the control CU is connected to the central database PDA and the power source PSU and the temperature measuring point CS by means of signal lines SL in connection.
  • the heating cartridge 3 is inserted obliquely to the compressor shaft in a bore 11 introduced in the housing cover CCV and thus indirectly heats the (in simplified form) gas-tight housing including the dry gas seal 2 contained therein.
  • this design takes into account the geometry of the gas-tight seal housing and is nevertheless attached as close as possible to the gas seal insert GSC including the dry gas seal 2 contained therein.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne une installation (A) comprenant un joint à gaz (GS), en particulier un joint à gaz sec (DGS). Ladite installation comporte : - un élément de support (CE), sur lequel le joint à gaz (GS) est fixé et est en appui ; - au moins une conduite d'amenée de gaz d'étanchéité (SGL) destinée à amener un gaz d'étanchéité (SG) au joint à gaz (GS) ; - au moins un élément chauffant (HT), l'élément chauffant (HT) étant réalisé et disposé de telle manière que le gaz d'étanchéité (SG) s'écoulant à travers la conduite d'amenée de gaz d'étanchéité (SGL), avant d'entrer dans le joint à gaz (GS), et/ou le joint à gaz (GS) sont ou peuvent être chauffés directement ou indirectement au moyen de l'élément chauffant (HT). L'invention vise à diminuer les coûts et d'augmenter l'efficacité. A cet effet, l'élément de support (CE) est relié de manière thermoconductrice à l'élément chauffant (HT), de sorte que le joint à gaz (GS) et/ou le gaz d'étanchéité (SG) s'écoulant dans la conduite d'amenée de gaz d'étanchéité (SGL) sont chauffés par l'énergie calorifique émise par l'élément chauffant (HT) au moyen de la conduite de chaleur de l'élément de support (CE). L'invention concerne en outre un procédé de fonctionnement de l'installation.
PCT/EP2015/053574 2014-02-26 2015-02-20 Installation comprenant un joint à gaz, procédé de fonctionnement Ceased WO2015128250A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014203464.7 2014-02-26
DE102014203464.7A DE102014203464A1 (de) 2014-02-26 2014-02-26 Anlage mit einer Gasdichtung, Verfahren zum Betrieb

Publications (1)

Publication Number Publication Date
WO2015128250A1 true WO2015128250A1 (fr) 2015-09-03

Family

ID=52630334

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2015/053574 Ceased WO2015128250A1 (fr) 2014-02-26 2015-02-20 Installation comprenant un joint à gaz, procédé de fonctionnement

Country Status (2)

Country Link
DE (1) DE102014203464A1 (fr)
WO (1) WO2015128250A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014011042A1 (de) * 2014-07-26 2016-01-28 Man Diesel & Turbo Se Strömungsmaschine
DE102017123654B4 (de) 2017-10-11 2022-01-27 Schaeffler Technologies AG & Co. KG Temperierbare Dichtungsanordnung und Temperierelement für diese
DE102021110581A1 (de) 2021-04-26 2022-10-27 TenneT TSO GmbH Gasdichte lösbare Verbindung

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0781948A1 (fr) * 1995-12-29 1997-07-02 Sulzer Turbo AG Turbomachine pour gaz non-parfait
US20130058769A1 (en) * 2009-12-07 2013-03-07 Giusepe Sassanelli Compressor end head heating arrangement
WO2013083437A1 (fr) 2011-12-05 2013-06-13 Nuovo Pignone S.P.A Joint à gaz sec pour tampon de haute pression de pompe de co2 supercritique

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0781948A1 (fr) * 1995-12-29 1997-07-02 Sulzer Turbo AG Turbomachine pour gaz non-parfait
US20130058769A1 (en) * 2009-12-07 2013-03-07 Giusepe Sassanelli Compressor end head heating arrangement
WO2013083437A1 (fr) 2011-12-05 2013-06-13 Nuovo Pignone S.P.A Joint à gaz sec pour tampon de haute pression de pompe de co2 supercritique

Also Published As

Publication number Publication date
DE102014203464A1 (de) 2015-08-27

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