EP2250376B1 - Turbomachine avec joint de piston d'équilibrage amélioré - Google Patents

Turbomachine avec joint de piston d'équilibrage amélioré Download PDF

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Publication number
EP2250376B1
EP2250376B1 EP08873320.9A EP08873320A EP2250376B1 EP 2250376 B1 EP2250376 B1 EP 2250376B1 EP 08873320 A EP08873320 A EP 08873320A EP 2250376 B1 EP2250376 B1 EP 2250376B1
Authority
EP
European Patent Office
Prior art keywords
cover
turbomachine
pressure
seal
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.)
Not-in-force
Application number
EP08873320.9A
Other languages
German (de)
English (en)
Other versions
EP2250376A1 (fr
Inventor
Alfred Markwalder
George Kleynhans
Urs Baumann
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.)
MAN Energy Solutions SE
Original Assignee
MAN Energy Solutions SE
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Filing date
Publication date
Application filed by MAN Energy Solutions SE filed Critical MAN Energy Solutions SE
Publication of EP2250376A1 publication Critical patent/EP2250376A1/fr
Application granted granted Critical
Publication of EP2250376B1 publication Critical patent/EP2250376B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04D29/40—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
    • 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
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • F04D17/125—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors the casing being vertically split
    • 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
    • F04D29/051—Axial thrust balancing
    • F04D29/0516—Axial thrust balancing balancing pistons

Definitions

  • the present invention relates to turbomachines such as a turbomachine or a compressor according to the preamble of claim 1 with an improved balance piston seal.
  • a seal against the environment via a shaft seal which is usually designed as a so-called dry gas seal, achieved.
  • a compensating piston seal is provided, which seals the outlet pressure against the inlet pressure on the pressure side of the compressor in order to reduce the thrust of the machine and to ensure on the shaft before the dry gas seal on both sides of the inlet pressure.
  • the DE 36 14 144 A1 shows such a high pressure compressor.
  • These gaskets generally have a hollow stator that includes the rotor, with the rotor, the stator, or both elements having recesses on the surface.
  • a dynamic resistance is created between the opposed surfaces of the rotor and the stator, which counteracts movement of the fluid in the axial direction through the sealing gap.
  • this compensating piston seal is of great importance for the functionality of the turbomachine, since this seal generally seals the larger pressure difference and therefore the larger dynamic forces occur between rotor and stator. Among other things, these dynamic forces influence the stability of the running behavior. With correct design This seal can be significantly improved, for example, the rotor dynamic stability of turbocompressors.
  • so-called Holepattern (HP) seals in which the recesses provided on the inner surface of the stator have a shape of substantially circular holes.
  • so-called honeycomb (HC) seals are also known in which the recesses provided on the inner surface of the stator are in the form of honeycombs, that is, of reticulated hexagonal holes.
  • FIG. 3 shows an in-house known compressor 100.
  • a so-called autoclave cover 104 is used, on which an inner housing 106 is supported.
  • the housing is closed by a closure lid 108.
  • a shaft 110 is mounted via shaft bearings 112 and 112 'in bearing housings 114 and 114', which are in turn attached to the autoclave cover 104 and the closure lid 108, respectively.
  • a working space 116 which is defined by the autoclave cover 104, the inner housing 106, the closure lid 108 and the shaft 110, there are the compressor stages with their built-in parts (not shown in detail).
  • shaft seals 124, 124 ' are arranged, which seal an inlet pressure of the compressor against the ambient pressure.
  • the inlet pressure prevails, so that the shaft seals 124, 124 'with the pressure difference between inlet and ambient pressure are forced apart.
  • sealing chambers communicate at the compressor inner sides of the two shaft seals 124, 124 'via a compensation line (not shown) with each other.
  • a compensating piston seal 122 is provided which consists essentially of an end portion 106a of the inner housing 106 and a sealing bushing 120 inserted therein and seals the outlet pressure against the inlet pressure.
  • Fig. 4 the area of this compensating piston seal 122 is shown in detail.
  • Fig. 4 is an enlarged view of a dash-dotted circle "IV" in Fig. 3 indicated detail.
  • the working space 116 with its built-in parts on the discharge pressure side is defined by the radial and axial inner surfaces of the inner casing 106 and the outer surface of the shaft 110.
  • a radially inwardly projecting end portion 106a of the inner housing 106 annularly surrounds a sealing portion 110a of the shaft 110 and forms in the axial direction, the boundary of the working space 116.
  • a sealing member 120 is arranged, which contains the recesses described above (not ) and reduces the gap between this inner surface of the end portion 106a and the outer surface of the seal portion 110a to a predetermined extent and defines the geometry of the gap.
  • the inner housing is composed of two parts of an upper and a lower half to allow insertion of the rotor.
  • the as a sealing bush formed sealing element is also divided in the radial direction in an upper and lower half. These two half rings are screwed into the corresponding grooves of the inner housing.
  • FIGS. 5A to 5C A major difficulty in dimensioning and operation is in the FIGS. 5A to 5C shown.
  • the FIGS. 5A to 5C essentially correspond to the section in Fig. 4 , but are kept much more schematic. Only portions of the housing 102, the autoclave cover 104, the inner housing 106 with its end portion 106a, which together with the sealing element 120 forms the compensating piston seal 122, the shaft 110 and the working space 116 are shown. A sealing gap between the sealing element 120 and the shaft 110 is designated 140.
  • Fig. 5A shows the geometry as it is made and which represents the design state. Fig.
  • FIGS. 5B and 5C is the finished, unloaded geometry Fig. 5A shown in dashed lines.
  • Fig. 5A is shown in Holepattern- or Honeycombdichtitch the sealing gap 140 in the design state tapering toward the outside, that is convergent in assumed outflow or leakage direction.
  • the inner housing 106 expands, the end portion 106a expands inward and the sealing gap 140 becomes narrower (see FIG. Fig. 5B ).
  • the extension of the end portion 106a on a shoulder 104b of the autoclave lid 104 is inhibited, whereby the whole end portion 106a rotates about this shoulder 104b.
  • the sealing gap 140 therefore also becomes more divergent.
  • the sealing gap 140 Under the influence of a large pressure difference between the outlet and inlet pressure over the seal bulges the End portion 106 a outwardly, which also causes the sealing gap 140 is divergent. As a result, the gap geometry is very difficult to control. In extreme cases, this leads to a divergent gap, which causes a rotordynamic instability.
  • the geometry change of the sealing gap 140 may take on the order of magnitude of the gap height itself.
  • An object of the present invention is to improve a turbomachine with respect to its compensating piston seal.
  • a turbomachine according to the present invention comprises the features of claim 1.
  • the lid of a turbomachine which may be for example an autoclave or a closure lid, is generally much stiffer than the inner casing, which is often formed in its end portion as a comparatively thin shell. Therefore, such a cover has a higher dimensional and dimensional stability than changes in temperature and / or pressure than the inner housing.
  • the turbomachine has at least one inner and at least one outer cover.
  • the working space of the turbomachine can be defined at an axial end substantially by an inner wall of the lid. This allows a greater freedom of design both in terms of the cover and the flow guide in the work area can be achieved. Also, the lid is a much stiffer component than the inner housing and is less deformed under large pressure and temperature differences. As a result, the geometry of the working space can be better defined and the flow conditions in the working space can be better controlled.
  • a first shaft seal which seals an inlet against an ambient pressure, is arranged on the side of the turbomachine opposite the working space, in particular in the cover.
  • a sealing space between this first shaft seal and the compensating piston seal communicates according to the invention with a sealing space which is located on the compressor interior side second shaft seal is formed, which seals the working space on the opposite side of the first shaft seal against the environment.
  • the compensating piston seal may comprise a substantially hollow cylindrical fitting sleeve or piston sleeve, which is preferably positively and / or frictionally secured within at least a portion of a through-drilled from the impeller shaft through hole of the cover and surrounds the impeller shaft without contact.
  • a sleeve or sleeve By using a sleeve or sleeve, the seal can be replaced relatively easily without changes to the supporting components. It may also be easier to carry out highly accurate shaping, machining and surface treatment processes on a comparatively handy component.
  • the sleeve or sleeve may have a first annular portion, which projects radially outward at the axial end facing the working space and bears against a wall of the cover, in particular a projecting fastening portion, facing the working space.
  • the sleeve or sleeve may have a second ring portion which protrudes from a radially outer edge of the first ring portion in the axial direction and is received in a correspondingly formed recess in the wall of the lid, in particular a protruding mounting portion. In this way, a simple and accurate centering and fixing of the radial position of the seal can be achieved.
  • annular gap having a predetermined geometry is preferably formed. This makes it possible in an advantageous and simple manner to realize a non-contact shaft seal and tune to the occurring during operation pressure, temperature and flow conditions. By convergent and / or divergent formation of the gap in at least a portion of the same defined pressure gradients can be achieved in the gap and adjusted so the sealing properties or optimized.
  • the compensating piston seal may have recesses in at least one section of its surface pointing toward the impeller shaft, which in cross-section may for example be substantially circular or polygonal, in particular hexagonal. Through the recesses, a flow resistance is generated when the shaft is running, which can promote a sealing of the working space and improve the stability properties of the rotor.
  • the compensating piston seal for a seal against a high pressure in the working space which is more than 50 bar, in particular more than 100 bar, preferably more than 500 bar, designed.
  • FIGS. 1 and 2 An embodiment of the present invention is in FIGS. 1 and 2 shown.
  • Fig. 1 shows a high-pressure compressor 1 as an example of a turbomachine.
  • an outer housing 2 a so-called autoclave cover 4 is inserted, which constitutes a cover in the sense of claim 1, and to which an inner housing 6 supported.
  • the outer housing 2 is closed on the opposite side of the autoclave 4 by a closure lid 8, which may also represent a lid in the sense of claim 1 in another embodiment, not shown.
  • An impeller shaft 10 is mounted via shaft bearings 12 and 12 'in bearing housings 14 and 14', which are in turn attached to the autoclave cover 4 and the closure cover 8.
  • the inner housing 6 In a working space 16, which is defined by the autoclave cover 4, the inner housing 6, the closure cover 8 and the shaft 10, there are the compressor stages with their built-in parts 26, 28, 30.
  • the inner housing 6 carries the built-in parts 26 of the compressor stages, the Shaft 10, the impellers 28 of the compressor stages.
  • Shaft seals 24, 24 'in autoclave or closure lid 4, 8 seal the compressor interior against the environment.
  • ambient pressure pu prevails, in the working space 16 on the outlet or pressure side (left in FIG Fig. 1 ) the outlet pressure p2, on the inlet or suction side (corresponding to the right in Fig. 1 ) the inlet pressure p1, so that in Fig. 1 right shaft seal 24 'in the closure lid 8 is acted upon by the pressure difference between inlet and ambient pressure.
  • a compensating piston seal 20 is arranged, which seals the outlet pressure p2 on the outlet side of the working space 16 against a formed between shaft seal 24 and compensating piston seal 20 seal chamber in which also the inlet pressure p1 prevails.
  • this sealing space communicates with a corresponding sealing space on the inlet or suction side of the compressor between the working space 16 and the shaft seal 24 'in the closure lid 8.
  • the working space 16 with its built-in parts on the pressure side is defined by the inner surfaces of the inner housing 6 and the autoclave cover 4 and the outer surface of the shaft 10.
  • the autoclave cover 4 has a projecting in the direction of the working space 16 projection 4 a, which thus limits the working space 16 in the axial direction on the side of higher pressure and the ring 10 surrounds a sealing portion 10 a of the shaft.
  • On the inner surface of the protrusion 4a there is disposed a bush 20 which reduces the gap between this inner surface of the protrusion 4a and the outer surface of the defined geometry seal portion 10a to a predetermined amount.
  • the projection 4 a, on which the bearing bush 20 is arranged or fastened, is thus a fastening section in the sense of the present invention.
  • the sleeve 20 has a first annular portion 20a, which protrudes from its lying on the side of the working space 16 axial end of radially outwardly and abuts the pointing to the working space 16 side of the projection 4a.
  • the section 20a is fastened by means of screws 32 on the side facing the working space 16 side of the projection 4a.
  • the portion 20a further includes a second annular portion 20b extending axially from the first portion 20a toward the autoclave lid 4 and engaging a corresponding counterpart groove in the surface of the projection 4a.
  • the sleeve 20 also has on its inner surface circular recesses 20c. These depressions ensure in a known manner for that during operation of the machine adjusts a fluid-dynamic locking effect and seals the outlet against the inlet pressure.
  • the recesses 20c are formed as circular recesses which penetrate into the inner surface of the sleeve 20 by a predetermined depth substantially perpendicular (i.e., in the radial direction).
  • the recesses 20c may also be inclined in the circumferential direction in or against the direction of rotation of the shaft 10 in order to produce turbulences in the desired form.
  • the cross section of the recesses 20c may decrease in the depth direction.
  • the circular depressions 20c are known per se to the person skilled in the art as a so-called holepattern seal.
  • the sleeve 20 is not fixed to the inner case 6 but to the comparatively rigid autoclave lid 4. As a result, a much stiffer design is achieved, and it is avoided that the otherwise large deformations of the inner housing 6 on the bearing bush 20 have an effect.
  • the rigidity in this section can be further increased.
  • the deformations of the seal assembly are orders of magnitude smaller and the gap geometry is largely maintained even under the influence of temperature and pressure differences. Therefore, a dimensioning of the seal assembly is simplified and easier to control.
  • the present invention is equally applicable to other types of annular gap seals in which exact knowledge of the geometry of the annular gap is important, such as honeycomb seals, groove seals, labyrinth seals or the like.
  • honeycomb seal recesses of substantially hexagonal cross-section are formed in the inner surface of the bushing, which are separated by a net-like structure.

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

Claims (12)

  1. Turbomachine (1), notamment compresseur, notamment compresseur à haute pression comportant un carter extérieur (2), dans lequel à l'extérieur du carter extérieur (2) prédomine une pression ambiante (pu), comportant un carter intérieur (6) disposé dans le carter extérieur (2), notamment un support d'aube directrice ;
    comportant un arbre de roue (10) placé dans le carter intérieur (6) ;
    comportant un couvercle d'autoclave (4), qui est placé dans le carter extérieur (2), sur lequel s'appuie le carter intérieur (6) et qui est fixé sur le capteur extérieur (2) ;
    un couvercle d'obturation (8), qui obture le carter extérieur (2) sur un côté opposé au couvercle d'autoclave (4) et qui est également fixé sur le carter extérieur (2),
    un espace de travail (16), qui est défini par le couvercle d'autoclave (4), le carter intérieur (6), le couvercle d'obturation (8) et l'arbre de roue (10), dans lequel dans l'espace de travail (16) sur un côté de sortie ou un côté de pression prédomine une pression de sortie (p2) et sur un côté d'entrée ou un côté d'aspiration prédomine une pression d'entrée (p1),
    un joint d'étanchéité de piston d'équilibrage (22) pour l'isolation sans contact de la pression de sortie (p2) dans l'espace de travail (16), notamment l'espace de compression (16), contre la pression d'entrée (p1), dans laquelle le piston d'équilibrage(22) est fixé sur le couvercle d'autoclave (4) ou sur le couvercle d'obturation (8),
    dans laquelle le couvercle d'autoclave (4) ou le couvercle d'obturation (8) sépare la pression d'entrée (p1) de la pression ambiante (pu) ;
    comportant des joints d'étanchéité d'arbres (24, 24') dans le couvercle d'autoclave (4) et dans le couvercle d'obturation (8),
    dans laquelle les joints d'étanchéité d'arbres (24,24') sont sollicités exclusivement avec une différence de pression entre la pression d'entrée (p1) et la pression ambiante (pu), alors que le joint d'étanchéité de piston d'équilibrage (22) isole la pression de sortie (p2) par rapport à la pression d'entrée (p1),
    comportant un espace d'étanchéité réalisé entre le joint d'étanchéité d'arbre (24) dans le couvercle d'autoclave (4) ou le joint d'étanchéité d'arbre (24') dans le couvercle d'obturation (8) et le joint d'étanchéité de piston d'équilibrage (22), dans lequel prédomine la pression d'entrée (p1),
    caractérisée en ce que cet espace de joint d'étanchéité communique avec un espace d'étanchéité supplémentaire entre l'espace de travail (16) et le joint d'étanchéité d'arbre (24') dans le couvercle d'obturation (8) ou le joint d'étanchéité d'arbre (24)dans le couvercle d'autoclave (4).
  2. Turbomachine (1) selon la revendication 1, caractérisée en ce que l'espace de travail est défini à l'extrémité axiale sur le côté de pression plus haute partiellement par une paroi intérieure du couvercle respectif (4 ;8).
  3. Turbomachine (1) selon la revendication 1 ou 2, caractérisée en ce que le couvercle respectif (4 ;8) présente une portion de fixation (4a) en saillie axialement dans la direction de l'espace de travail (16) pour fixer le joint d'étanchéité de piston d'équilibrage (22).
  4. Turbomachine selon une des revendications précédentes, caractérisée en ce que le joint d'étanchéité de piston d'équilibrage (22) présente une chemise de piston (20) ou un manchon essentiellement cylindrique creux, qui est fixé à l'intérieur d'au moins une portion d'un alésage traversant du couvercle respectif (4 ;8) traversé par l'arbre de roue (10) et enveloppe sans contact l'arbre de roue.
  5. Turbomachine (1) selon la revendication 4, caractérisée en ce que le manchon respectivement la chemise (20) présente une première portion annulaire (20a), qui dépasse radicalement vers l'extérieur sur l'extrémité axiale du joint d'étanchéité de piston d'équilibrage tourné vers l'espace de travail (16) et vient reposer sur une paroi tournée vers l'espace de travail (16) du couvercle respectif (4 ;8).
  6. Turbomachine (1) selon la revendication 4 ou 5, caractérisée en ce que le manchon respectivement la chemise (20) est fixé au moyen d'au moins un élément de liaison (32), notamment d'une goupille ou d'une vis, sur le couvercle respectif.
  7. Turbomachine (1) selon la revendication 5 ou 6, caractérisée en ce que le manchon respectivement la chemise (20) présente une deuxième portion annulaire (20b), qui s'étend à partir d'un bord extérieur radial de la première portion annulaire (20a) axialement dans la direction du couvercle respectif (4) et est renfermée dans une cavité réalisée de manière correspondante dans la paroi du couvercle respectif (4 ;8).
  8. Turbomachine (1) selon une des revendications précédentes, caractérisée en ce que entre l'arbre de roue (10) et le joint d'étanchéité de piston d'équilibrage (22) un interstice annulaire est réalisé, qui présente une géométrie prédéterminée.
  9. Turbomachine (1) selon la revendication 8, caractérisée en ce que l'interstice réalisé entre l'arbre de roue (10) et le joint d'étanchéité de piston d'équilibrage (22) est convergent dans au moins une portion.
  10. Turbomachine (1) selon une des revendications 8 ou 9, caractérisée en ce que l'interstice réalisé entre l'arbre de roue (10) et le joint d'étanchéité de piston d'équilibrage (22) est divergent dans au moins une portion.
  11. Turbomachine (1) selon une des revendications précédentes, caractérisée en ce que dans au moins une surface du joint d'étanchéité de piston d'équilibrage (22) se détournant de la surface circonférentielle extérieure d'arbre de roue et se tournant vers l'arbre de roue (22) des cavités (20c) sont réalisés au moins par portions, qui en coupe transversale sont essentiellement circulaires ou essentiellement polygonales, notamment hexagonales.
  12. Turbomachine (1) selon une des revendications précédentes, caractérisée en ce que le joint d'étanchéité de piston d'équilibrage (22) est conçu afin d'isoler contre une haute pression dans l'espace de travail, qui s'élève à plus de 50 bar, notamment plus de 100 bar, de préférence plus de 500 bar.
EP08873320.9A 2008-03-10 2008-11-03 Turbomachine avec joint de piston d'équilibrage amélioré Not-in-force EP2250376B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008013433A DE102008013433A1 (de) 2008-03-10 2008-03-10 Strömungsmaschine mit verbesserter Ausgleichskolbendichtung
PCT/EP2008/009253 WO2009112064A1 (fr) 2008-03-10 2008-11-03 Turbomachine avec joint de piston d’équilibrage amélioré

Publications (2)

Publication Number Publication Date
EP2250376A1 EP2250376A1 (fr) 2010-11-17
EP2250376B1 true EP2250376B1 (fr) 2019-04-03

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Country Status (7)

Country Link
US (1) US9494165B2 (fr)
EP (1) EP2250376B1 (fr)
JP (1) JP5425108B2 (fr)
CN (1) CN101970882B (fr)
DE (1) DE102008013433A1 (fr)
RU (1) RU2443909C1 (fr)
WO (1) WO2009112064A1 (fr)

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DE102008013433A1 (de) 2009-09-17
EP2250376A1 (fr) 2010-11-17
RU2443909C1 (ru) 2012-02-27
CN101970882A (zh) 2011-02-09
WO2009112064A1 (fr) 2009-09-17
JP2011513644A (ja) 2011-04-28
CN101970882B (zh) 2014-06-25
US20100322765A1 (en) 2010-12-23
US9494165B2 (en) 2016-11-15
JP5425108B2 (ja) 2014-02-26

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