Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
  • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
  • F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
  • F01D11/04—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type using sealing fluid, e.g. steam
  • F01D11/06—Control thereof
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
  • F04D17/08—Centrifugal pumps
  • F04D17/10—Centrifugal pumps for compressing or evacuating
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
  • F04D27/002—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by varying geometry within the pumps, e.g. by adjusting vanes
• • 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
  • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
  • F04D29/053—Shafts
• • 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
• • 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
  • F04D29/102—Shaft sealings especially adapted for elastic fluid pumps
  • F04D29/104—Shaft sealings especially adapted for elastic fluid pumps the sealing fluid being other than the working fluid or being the working fluid treated
• • 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
  • F04D29/26—Rotors specially for elastic fluids
  • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
  • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
• • 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
  • F04D29/40—Casings; Connections of working fluid
  • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
  • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
  • F05D2270/00—Control
  • F05D2270/30—Control parameters, e.g. input parameters
  • F05D2270/301—Pressure

Definitions

• the invention relates to a fluid energy machine, insbesonde ⁇ re turbo compressor comprising a passage extending along an axis of the rotor, comprising a housing, wherein the housing separates an interior from an exterior, comprising min ⁇ least a shaft seal for sealing a gap see between the rotor and the housing, wherein the shaft seal is formed as a tandem dry gas seal, wherein the tandem dry gas seal comprises an inner seal and an outer seal, wherein the outer seal has a first locking gas supply ⁇ axially between the outer seal and the inner seal opens into the gap, wherein the Wel ⁇ lendichtung has a primary discharge between the inner seal and the outer seal, which sucks primary dissipation fluid from the gap.
• Fluid energy machines in particular turbocompressors, are frequently sealed at the shaft ends of a rotor with dry gas seals in tandem construction (Tandem Dry Gas Seals) in order to prevent the process gas to be compressed from entering the environment via the shaft gaps.
• These dry gas seals must be supplied with dry and filtered purge gas to avoid contamination and humidities that affect the function of the seal.
• pressure in the space between the inner seal and the outer seal is required, which can also be monitored. Only if a pressure gradient in the outer gas seal is established in this way is it possible to monitor the function on the outer gas seal. In particular, this pressure drop across the outer gas seal is also required to avoid overheating and instabilities in the gas film between a slip ring and a rotating ring of this seal.
• turbocompressors are already known from the documents WO 2010/034601 Al, WO 2010/034605 Al, WO 2010/102940 Al, WO 2010/118977 Al and WO 2014/037149 AI.
• the problem of monitoring the outer dry gas seal is already known, because it comes to low pressure drop over the outer dry gas seal due to the low leakage in particular ⁇ special in operating conditions that do not ent ⁇ the full load.
• the leakage of the inner dry gas seal is sometimes so low that the pressure in the gap between the inner dry gas seal and the outer dry gas seal drops.
• Another problem is the lack of supply of the outer dry gas seal with a cooling fluid, in particular under pressure from the inside of the outer dry gas seal adjacent process fluid or a mixture with the process fluid, so that the lubrication and cooling of this seal is guaranteed.
• a cooling fluid in particular under pressure from the inside of the outer dry gas seal adjacent process fluid or a mixture with the process fluid, so that the lubrication and cooling of this seal is guaranteed.
• blocking fluid in larger quantities in the intermediate space or in the seal itself, so that cooling and lubrication are ensured.
• this has the additional disadvantage that a larger amount of barrier fluid is required, the processing or provision is very kostspie- lig and possibly even affects the efficiency of the Maschi ⁇ ne.
• the invention has the object to ensure the function, in particular the outer seal of the tandem arrangement safer and better to monitor, without increasing the need for cooling and lubricating barrier fluids.
• a fluid energy machine of the defi ned ⁇ type is proposed with the additional features of the characterizing portion of claim 1.
• a method of operation of such a fluid energy machine overall proposed the independent method claim.
• the respective dependent claims contain advantageous developments of the invention.
• the invention also includes embodiments which result from combinations of subclaims which are not produced by explicit back references, provided that these combinations are technically possible.
• the primary derivative described leads to a Dispose of ⁇ supply system. This is in most cases a torch system and has a slight overpressure to the environment.
• Geometric information such as axial, radial, tangential and similarity ⁇ Liche refer to the defined in claim 1 axis of the rotor, unless deviating definition is introduced in the respective context.
• inner (s) and outer (s) refer to the “inside” or “exterior” of the fluid energy machine or housing of the fluid energy machine introduced in claim 1. In this case, these attributes are also used for linguistic due-fulness in such a way that in relation to one another a component is referred to as an inner component, if it is located farther toward the interior than the relatively different component which is arranged comparatively farther to the outside.
• the inner seal and the outer seal of the tandem dry gas seal are each a dry gas seal for sealing the gap between the rotor and the housing.
• Dry gas seals are non-contacting, dry-running sealing ring pairs, each having a sealing end face aufwei ⁇ sen, wherein a sealing ring is rotated, and the other sealing ring is. During operation, recesses in at least one of the two end faces cause a dynamic force, which leads to a gap between the two rings.
• the use of the so-called dry gas seals, especially in centrifugal compressors, has recently become increasingly common. because the leakage and thus the contamination of the surrounding components are extremely low and no lubricating oil is required for the use of these seals.
• a decisive advantage of the invention is that the buffering of the primary discharge according to the invention by means of the second control element ensures the differential pressure across the outer seal, without requiring additional sealing gas.
• An advantageous development of the invention provides that the outer seal facing the interior is associated with a first labyrinth seal for sealing the gap and is adjoined be ⁇ .
• the first labyrinth seal ensures that the added sealing gas serves primarily for lubrication and cooling of the outer seal and does not readily flow away in Rich ⁇ tion of the inner seal.
• a further advantageous development of the invention provides that the primary discharge line is inserted axially between the first labyrinth seal and the inner seal into the gap. empties.
• the primary discharge line is inserted axially between the first labyrinth seal and the inner seal into the gap. empties.
• a further advantageous development of the invention provides that the control unit giemaschine causes a shutdown of the Fluidener- when the first pressure to a second pressure threshold value decreases and thus the DAMAGE ⁇ free operation, in particular the outer seal is no longer guaranteed.
• the control unit giemaschine causes a shutdown of the Fluidener- when the first pressure to a second pressure threshold value decreases and thus the DAMAGE ⁇ free operation, in particular the outer seal is no longer guaranteed.
• it is expedient according to another advantageous embodiment of the invention when a second labyrinth seal of the inner seal facing the interior assigned to seal the gap and is adjacent.
• the second labyrinth seal is particularly expedient if, according to an independent development of the invention, a second sealing gas supply is assigned to the inner seal, which opens axially into the gap next to the inner seal, in particular between the inner seal and the second labyrinth seal.
• a second sealing gas supply is assigned to the inner seal, which opens axially into the gap next to the inner seal, in particular between the inner seal and the second labyrinth seal.
• the first sealing gas supply is expediently connected directly to a barrier gas supply with the interposition of the first control element, so that the first pressure in the first barrier gas supply is controlled by means of the control unit.
• the second sealing gas supply is usefully connected to the line of the first sealing gas supply.
• Figure 1 is a schematic representation of the arrangement
• Figure 1 shows a schematic representation of theroisswei ⁇ se a fluid energy machine FEM invention and a A method according to the invention for operating this fluid energy machine FEM.
• FIG. 2 schematically shows the pressure curve via a shaft seal SLS of the fluid energy machine FEM.
• the figure 2 shows the pressure curve in relation to the left shaft seal ⁇ SLS FIG. 1
• the fluid energy machine FEM according to the invention of FIG. 1 is designed as a turbocompressor TC, the turbocompressor TC having a rotor R with an impeller IMP and a housing C. Between the rotor R and the housing C results in a region of a passage of the rotor R from a In ⁇ neren IN of the housing C in an exterior EX outside the housing C between the housing C and the rotor R on both sides in each case a gap GP , In order to seal this gap, the fluid energy machine FEM provides a shaft seal SLS, which is designed as a tandem dry gas seal TDGS.
• the tandem dry gas seal TDGS includes the following modules: a second labyrinth seal LB2, an inner seal SLI, a first labyrinth seal LB1, and an outer seal SLO.
• the inner seal SLI and the outer seal SLO are each formed as dry gas seals, each comprising a rotating ring RR and a stationary ring SR.
• the rotating ring RR is part of the rotor R and the stationary ring SR is indirectly to the housing C - in the re ⁇ gel these shaft seals are components of a to be inserted into a housing recess in the shaft passages through the housing cartridge - attached.
• a process fluid pressure PFEM is provided in operation, which is usually higher than the pressure PEX in the exterior EX.
• PFEM process fluid pressure
• a third labyrinth LBEX may be provided, which in particular sealingly protects the outer seal SLO from the environment.
• axial between the second labyrinth LB2 and the inner seal FLI are on both sides of a second sealing gas supply SGS2 with the pressure PSGS2, which opens into the gap GP.
• Axially between the first labyrinth LB1 and the inner seal SLI is provided a primary discharge PV, by means of which the pressure in the gap between the first labyrinth LB1 and the inner seal SLI is adjusted to a first pressure PI or a first setpoint pressure P1SET ,
• a first barrier gas supply SGS1 is provided axially, which feeds barrier gas with a pressure PSGS1 into the gap GP if necessary.
• the pressure PSGS2 of the second purge gas supply SGS2 is determined by the supply pressure PSGS of a purge gas system SGS.
• This barrier gas system SGS delivers dry and clean barrier gas of desired chemical composition with the pressure PSGS into the second barrier gas supply SGS2.
• the first Sperrgaszu ⁇ drove SGS1 is connected to the second barrier gas supply SGS2 means of a controllable control element VI, so that a pressure PSGS1 can be set in the seal gas supply by means of the control unit VI.
• the control element VI is here a controllable valve with appropriate control and drive.
• the barrier gas Before the barrier gas enters the gap GP between the first labyrinth LB1 and the outer seal SLO by means of the first barrier gas supply SGS1, it first passes a manual valve VM and a first throttle element TH1.
• the manual valve VM is used during commissioning to interrupt the purge gas flow and isolate the area.
• the first throttle element TH1 prevents überhöh ⁇ te sealing gas supply in the event of a malfunction of the first re gelorgans. This way, it is between the first
• Labyrinth LB1 and outer seal SLO a first gap pressure PGPS1.
• the pressure PSGS is in the second barrier gas supply SGS2 by means of a second throttle element TH2 just ⁇ if lowered before the barrier gas enters the gap GP between the second labyrinth LB2 and the inner seal SLI.
• the primary outlet PV which opens into the gap GP between the first labyrinth LB1 and the inner seal SLI, leads to the discharge of a primary discharge fluid PVF by means of an adjustable second control element V2 at a pressure PPV
• the second control member can in this case be ⁇ det in Wesentli ⁇ chen as the first control member as a controllable valve difficultbil.
• a third throttle element TH3 is in the line of this primary discharge PV, so that due to the dissipating flow direction upstream of the third throttle element TH3 results in the gap GP, a pressure PI.
• a control unit CU communicates with the first re ⁇ gelorgan VI, the second regulating member V2 and a pressure measuring point PIT, which measures the pressure PI in the gap GP indirectly by the primary derivative PV.
• the control unit CU sets the open positions of the first control member VI and the second valve V2 such that in the gap GP axially between the inner seal SLI and the first labyrinth LB1 results in the pressure PI to the first target pressure P1SET.
• control unit CU is formed such that the ERS ⁇ te pressure PI to the first pressure P1SET is controlled by first opening position of the second valve V2 is controlled in a first step and the first valve VI ge ⁇ closed and in a second step with the first valve closed and a first pressure PI is less than the first target pressure P1SET the second valve V2 is opened and in a third step with the second valve closed V2, the open position is controlled by the second valve V2 until the first pressure PI corresponds to the first setpoint pressure P1SET and the first step is initiated again when the first valve is closed.
• FIG. 2 shows how, based on a process fluid pressure PFEM in the interior IN, the pressure in the second labyrinth LB2 rises due to a second nip pressure PGPS2 of the second purge gas supply SGS2, in order to progressively move closer to the exterior EX.
• PGPS2 second nip pressure of the second purge gas supply SGS2
• strong decrease of the inner seal rich SLI to the first pressure PI as a result of the high differential pressure across the seal ⁇ nere in SLI and the primary derivative PV.
• About the inner seal is after an advantageous development of the invention in operation always the higher differential pressure - compared with the outer seal SLO.
• a further slight pressure drop results at a first labyrinth LB1 to a first nip pressure PGPS1, which drops to the ambient pressure PEX with further approach to the exterior EX in the outer seal SLO.
• control unit initiates a switch-off of the fluid energy machine.

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

Applications Claiming Priority (2)

Publications (1)

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Family Applications (1)

Country Status (6)

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• 2014
  • 2014-06-18 DE DE102014211690.2A patent/DE102014211690A1/de not_active Withdrawn
• 2015
  • 2015-06-16 CN CN201580032946.9A patent/CN106460541B/zh not_active Expired - Fee Related
  • 2015-06-16 RU RU2016149625A patent/RU2658721C2/ru not_active IP Right Cessation
  • 2015-06-16 US US15/314,592 patent/US10337520B2/en not_active Expired - Fee Related
  • 2015-06-16 EP EP15730464.3A patent/EP3129605A1/de not_active Withdrawn
  • 2015-06-16 WO PCT/EP2015/063399 patent/WO2015193269A1/de active Application Filing

Non-Patent Citations (2)

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