EP1642075B1 - Conduite de vapeur d'echappement pour dispositifs a vapeur - Google Patents

Conduite de vapeur d'echappement pour dispositifs a vapeur Download PDF

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Publication number
EP1642075B1
EP1642075B1 EP20040762342 EP04762342A EP1642075B1 EP 1642075 B1 EP1642075 B1 EP 1642075B1 EP 20040762342 EP20040762342 EP 20040762342 EP 04762342 A EP04762342 A EP 04762342A EP 1642075 B1 EP1642075 B1 EP 1642075B1
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EP
European Patent Office
Prior art keywords
exhaust steam
line
steam line
branch
main
Prior art date
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Active
Application number
EP20040762342
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German (de)
English (en)
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EP1642075A1 (fr
Inventor
Markus Schmidt
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GEA Energietchnik GmbH
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GEA Energietchnik GmbH
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Publication of EP1642075A1 publication Critical patent/EP1642075A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/02—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using water or other liquid as the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B9/00—Auxiliary systems, arrangements, or devices
    • F28B9/02—Auxiliary systems, arrangements, or devices for feeding steam or vapour to condensers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S261/00—Gas and liquid contact apparatus
    • Y10S261/76—Steam
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8376—Combined
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/85938—Non-valved flow dividers

Definitions

  • the invention relates to an exhaust steam line for steam power plants with the features of the preamble of claim 1.
  • the exhaust steam line of a steam power plant serves to guide the exhaust steam from the exit of the steam turbine, that is, from the turbine exhaust steam outlet via a main steam line to branch lines, via which the exhaust steam is fed to individual condensation elements. This is largely done in vacuum operation.
  • the routing of an exhaust steam line for an air-cooled condenser is usually carried out with diameters between 1 m and 10 m.
  • the invention is based on the object of providing an exhaust steam line for steam power plants with reduced assembly and material costs, in which at the same time the pressure loss is as low as possible.
  • the invention solves this problem by an exhaust steam line with the features of claim 1.
  • the core of the invention is the arrangement of Kleinabdampf founded at an angle to the horizontal, and so that the main exhaust steam line increases in the flow direction of the exhaust steam, wherein the Abknickwinkel measured between a longitudinal section of the main exhaust pipe and the branch lines is less than 90 ° and the length of the individual branch lines decreases in the flow direction of the exhaust steam.
  • the basic idea of the new cable routing is based on the principle of the most direct possible connection between the connection of the main exhaust steam line at a low height level to a plurality of connections of the branch pipes to distributor pipes at a higher height level.
  • the rising arrangement of the main steam discharge line has the advantage that the individual branch pipes, although they have a different length from each other, but can be designed to be shorter overall than in an exclusively horizontally extending Hauptabdampf ein. As a result, the length of the flow path is reduced overall.
  • the lower material usage leads to weight savings in the exhaust steam line and not least also to savings in costs and also in terms of assembly.
  • the cost savings in the assembly result from the fact that the branch lines composed of individual ring segments are made shorter and therefore less welding work must be carried out in order to connect the ring segments to one another.
  • the total assembly weight is lower, allowing for easier handling.
  • the foundation loads are lower, so that smaller foundations can be used.
  • a significant advantage over orthogonally configured arrangements between the main exhaust steam line and the branch lines is that the flow losses leading to pressure losses are reduced.
  • the pressure loss is proportional to the resistance coefficient of the piping system.
  • the drag coefficient is largely determined by the number and design of the manifolds and pipe branches. In the area of the connection points of the branch lines, the resistance coefficient is reduced by the oblique position of the main exhaust steam line according to the invention. Basically, the drag coefficient is the smaller the smaller the kink angle. Of the Abknickwinkel is measured between the cross-sectional plane of the main steam and the cross-sectional plane of a branch line. For parallel cross-sectional planes this angle is 0 °.
  • the usual bending angle of 90 ° is reduced by the angle of inclination of the main exhaust steam line, so that smaller resistance coefficients result at each connection point of a branch line than with a 90 ° deflection. In total, this results in a much lower loss height or a lower pressure drop within the exhaust steam line than in the known orthogonally configured arrangements.
  • a further advantage is that the main exhaust steam line rises relatively gently from the lower height level of the steam turbine.
  • the bending angle measured in relation to the horizontal lies in the range of 5 ° to 60 ° according to the features of claim 2.
  • the angle is in a range of 10 ° to 20 °.
  • Larger angles would have the disadvantage that the resistance coefficient in the transition region from the horizontal length section of the main exhaust steam line to the inclined length section of the main exhaust steam line would have a greater resistance coefficient, so that larger pressure losses occur in good time.
  • the pressure losses at very low Abknickwinkeln, especially at Abknickwinkeln of less than 10 ° are compared to the commonly used 90 ° -Krümmern much lower.
  • additional redirecting means such as e.g. Schaufelkrümmer be omitted, whereby the exhaust steam line according to the invention can be designed structurally simpler. Furthermore, there is a better condensate return against the steam flow direction in the main steam line.
  • the choice of the Abknickwinkels depends on the length of the main steam and the respective plant conditions. It is essential that no 90 ° -Krümmer should be provided within the wiring harness to change the height level of the main steam line, but only bends that are much smaller than 90 °.
  • a first main steam line and a second main steam line with opposite slope are connected to a common central line.
  • At least one of the branch lines is arranged inclined at an angle to the main exhaust steam line in the flow direction of the exhaust steam. That the upper ends of the branch lines and their junctions are not in the same vertical plane. With this arrangement, the flow losses at the individual connection points are further reduced.
  • the branch line provided at the outer end of the main exhaust steam line is arranged in the same orientation as the main steam line.
  • "Same orientation" in the context of the invention is to be understood as a parallelism or congruence of the longitudinal axes of the main steam line and branch line.
  • the angle of the main exhaust pipe to the horizontal is determined decisively by the horizontal and vertical distance of the last condensation element from the turbine. Since the Hauptabdampftechnisch goes without curvature in the end-side branch line, the Hauptabdampftechnisch is correspondingly shorter. In this arrangement, the total weight is further reduced in spite of the slightly longer executed last branch line in the sum.
  • At least one branch line is divided into at least two sub-lines.
  • the exhaust steam flowing through the branch line is thereby divided into two partial streams which flow to one condensation element each.
  • it is more appropriate to divide the branch line into two sub-lines instead to provide a further branch line, which would have to be connected directly to the main steam line.
  • the additional branching of the branch line in two or more sub-lines it is possible to further reduce the cost of materials and to reduce the total assembly weight.
  • the sub-lines are arranged inclined in an angle to the branch line sloping. In this way, the flow losses are kept as low as possible.
  • the bending angles are significantly smaller than 90 °.
  • the subject of claim 11 is that in the region of at least one connection point of a branch line or a partial line a baffle for the division of the exhaust steam is arranged in Abdampfteilströme.
  • the baffle has the purpose to divide the exhaust steam with the lowest possible pressure losses.
  • the pressure losses in each of the exhaust partial streams are identical.
  • the ratio of Abdampfteilströme corresponds to the ratio of the following on a connection point distribution pipes. If, for example, a total of five branch lines are branched off from a main exhaust steam line, with equal amounts of the exhaust steam being supplied to the individual distributor pipes, then it is necessary to branch off at the first connection point 1/5 of the exhaust steam flow in the direction of flow.
  • the inclined wiring of the main exhaust pipe allows a freer cooling air supply below the capacitor elements, which can lead to a lower platform height and thus to reduce the steel construction costs depending on the arrangement.
  • the accessibility of the system is improved because you can go under the main steam line.
  • Figure 1 shows the state of the art an exhaust steam line 1 with a horizontal Hauptabdampf Gustav 2 with this perpendicularly upwardly branching branch lines 3.
  • distribution pipes 30 are connected by condensation elements not shown.
  • This configuration of an exhaust steam line 1 has the disadvantage that the individual branch lines 3 are very long and must be supported according to their length. Since compensators are provided in the branch lines 3 for compensation of thermal changes in length, the individual sections of the branch lines 3 must be position-oriented on the steel frame (not shown). The effort for this is not insignificant.
  • the line length is relatively large in the sum, so that considerable tonnages have to be transported. The mounting effort is therefore also high.
  • a horizontal length portion of the main exhaust pipe 2 is provided in a raised position, so that the individual branch lines 3 can be made shorter.
  • This has the advantage that the correspondingly lighter branch lines 3, despite the inclusion of compensators with less effort are iageorientierbar.
  • an at least two-fold 90 ° bend of the main exhaust duct is required to redirect the exhaust steam emerging in the horizontal direction into the vertical length section and from the vertical length section in turn into the horizontal length section.
  • spring supports 4 are used to compensate for the thermally induced change in length to ensure adequate support of the horizontally extending length portion of the main steam line.
  • additional shock brakes must be provided in the form of hydraulic dampers.
  • the spring supports 4 in combination with the impact brakes are relatively complex components, since they must be provided several times depending on the length of the main steam pipe 2 to ensure a uniform lifting or lowering of the horizontal length portion of the main steam line 2.
  • the other spring supports 4 are indicated schematically by double broken lines.
  • FIG. 3.1 shows the exhaust steam line 5 according to the invention, which differs from the embodiments of FIGS. 1 and 2, that is to say from the prior art in that the main steam exhaust line 10 is arranged at an angle W to the horizontal H in the direction of flow of the exhaust steam.
  • the angle W is 10 °.
  • a total of five branch lines 6 extending vertically upwards are connected to the main exhaust steam line 10, wherein the line cross-section decreases after each connection point 7 of a branch line 6.
  • the right branch line 6 in the image plane is much shorter than the first outgoing branch line 6 in the left half of the picture.
  • the bending angle W1 measured between the rising length section 9 of the main exhaust steam line 10 and the respective branch lines 6 is less than 90 °. In this embodiment, it is 80 °.
  • the resistance coefficients of the pipe branches are therefore smaller than with a 90 ° branch.
  • the rising length section 9 of the main exhaust pipe 10 is mounted on pendulum supports 11.
  • the pendulum supports 11 compensate for acting in the longitudinal direction of the rising length portion 9 thermal length changes. Elaborate spring struts and shock brakes are not required in this arrangement.
  • the rising length section 9 does not exert any inadmissible forces on the steam turbine in the case of vertically acting earthquake loads, so that the constructional outlay for an exhaust steam line 5 configured according to the invention is lower overall. Due to the rising course of the main exhaust steam line 10, a freer air inlet below the platform of the air-cooled condensation elements is possible. In addition, the accessibility to the entire system is improved. In the embodiment of FIG. 1, very long paths often had to be covered, since the direct route was blocked by the main exhaust steam line 2 arranged near the bottom.
  • the embodiment of Figure 3.2 differs from that of Figure 3.1 in that the individual branch lines 6 ', 6 ", 6'" are not aligned perpendicular to the horizontal, but also extend obliquely rising.
  • the pitch of the rising length portion 9 of the main exhaust pipe or the angle W is set so that the branch pipe 6 "located at the outer end of the rising length portion 9 has the same orientation as the rising length portion 9 of the main exhaust pipe
  • the angle W is greater than the horizontal H in FIG. 3.2, it is larger than in the embodiment FIG.
  • Each located between two connection points 7 portion of the rising length portion 9 is supported by a support 11 '.
  • the bending angles W3 ', W3 "to the outer end of the rising length section 9 can become smaller and even approach zero, as FIG. 3.2 shows.
  • a central line 16 is likewise provided, from which in each case a main waste steam line 17 to the right and a main waste steam line 18 to the left with opposite directions Slope gone.
  • the individual Hauptabdampftechnischen 17, 18 are in turn supported by supports 11, in particular pendulum supports.
  • supports 11, in particular pendulum supports for the advantages of this embodiment, reference is made to the description of Figure 3.1, which also applies to this variant of the exhaust steam line 19 according to the invention.
  • the pendulum supports 11 can also be replaced by fixed supports with a Teflon stainless steel Gleitfuß.
  • the embodiment of Figure 6.2 differs from that of Figure 6.1, inter alia, in that the angle W between the horizontal H and the Hauptabdampf Kochen 17, 18 is increased.
  • the angle W is chosen so that the respective last or end-side branch line 6 "'runs in alignment with the main exhaust steam line 17, 18. That is to say that the outer branch line 6"' has become part of the main exhaust steam line 17, 18.
  • the central branch lines 6 "of the individual main exhaust steam lines 17, 18 do not run perpendicular to the horizontal H, as is the case in Figure 6.1, but are also inclined, the angle between the main steam exhaust line 17, 18 and these branch lines 6 In comparison with the embodiments of FIGS.
  • FIG. 7 shows an embodiment of an exhaust steam line 20 in which the angle W between the horizontal H and the main exhaust steam line 21 is increased compared to the previous embodiments.
  • the Kleinabdampf Arthur 21 is connected directly to a central line 22 without a horizontally extending center piece.
  • the angle W is in turn chosen so that the last or end-side branch line 6 "'in alignment with the main exhaust steam line 21 runs. Since the Hauptabdampftechnisch 21 increases relatively steeply in this embodiment, the Abknickwinkel W2 between the vertically upwardly from the main steam outlet 21 outgoing branch lines 6, 6a and the Hauptabdampftechnisch 21 is very small, so that the flow losses in the connection points 7 of Hauptabdampf effet 21 are low.
  • the special feature of this embodiment is that the branch line 6a is divided into two sub-lines 23, 24, each sub-line 23, 24 leading to a respective condensation element, not shown.
  • the branch line 6a extends from the main steam line 21, starting initially vertically up to a junction 7a. From this connection point 7a branches off in a Abknickwinkel W4 the sub-line 24, while the other sub-line 23 is continued in a straight extension of the branch line 6a vertically upwards. Through the additional part of line 24, a further branch line is saved, which would have to be performed on the Hauptabdampf Koch 21. In particular, in the case of steeper exhaust steam lines 21, it is therefore expedient to provide additional ramifications or partial lines to the individual branch lines.
  • FIGS. 7 and 8 show an enlarged section of the embodiment of Figure 7.
  • baffles 25, 26, 27 are integrated into the connection points 7, 7a.
  • the baffles 25, 26, 27 serve to divide the Abdampfstroms in Abdampfteilströme corresponding to the ratio of the following on a connection point 7, 7a distribution pipes.
  • a total of four distributor tubes of the condensation elements are fed with exhaust steam. Accordingly, there is a division of the exhaust steam in a ratio of 1: 1 at each connection point.
  • the uniform distribution is achieved in that the baffles 25, 26, 27 are already mounted in front of the respective connection points 7, 7a within the main steam line 21 and the branch line 6a.
  • a circular cross-section of the main exhaust steam line 21 and the branch line 6a is thereby divided into two semicircles. Differs the cross section of Hauptabdampf effet 21 and the branch line 6a from a circular cross-section from, there is an area equal division.
  • the respective baffle 25, 26, 27 is preferably designed such that an areal same division is realized both in front of the respective connection point 7, 7a and in the region of the respective connection point 7, 7a. It is essential that the pressure losses of Abdampfteilströme in the region of the connection points 7, 7a are almost equal and the Abdampfmenge is divided into equal parts.
  • the respective baffles 25, 26, 27 configured angled.
  • the respective front length region 28 of the individual baffles 25, 26, 27 has a length L which corresponds to the diameter D 1 , D 2 , D 3 of the main steam line 21 and the exhaust steam line 6 a in front of the respective connection point 7, 7 a.
  • the beginning of a connection point 7, 7a is defined as the intersection of the central longitudinal axes of the respective branch line 6, 6a with the main exhaust steam line 21 or as the intersection of the part line 24 with the branch line 6a. It can be seen that the straight course of the respectively front longitudinal sections 28 of the baffles 25, 26, 27 extends beyond this point of intersection, before the respective rear longitudinal section 29 is attached at an angle.
  • the starting point of the rear longitudinal section 29 is selected so that the flow cross sections in the region of the connection points 7, 7a are as equal as possible.

Claims (12)

  1. Conduite de vapeur d'échappement dans laquelle les groupes-vapeur présentent plusieurs éléments de condensation en particulier refroidis par air avec une conduite principale de vapeur d'échappement (10, 17, 18, 21), à laquelle sont raccordées au moins deux conduites de dérivation (6, 6', 6", 6"', 6a) conduisant respectivement vers un élément de condensation, la section transversale de la conduite principale de vapeur d'échappement (10, 17, 18, 21) étant rétrécie après un point de raccordement (7) d'une conduite de dérivation (6, 6', 6", 6"', 6a),
    caractérisée en ce que
    la conduite principale de vapeur d'échappement (10, 17, 18, 21) est disposée de manière ascendante en formant un angle (W) par rapport à l'horizontale (H) dans le sens d'écoulement de la vapeur d'échappement, le coude (W1, W2, W3, W3', W3"), mesuré entre un tronçon longitudinal (9) de la conduite principale de vapeur d'échappement (10, 17, 18, 21) et les conduites de dérivation (6, 6', 6", 6"', 6a), étant inférieur à 90° et la longueur des différentes conduites de dérivation (6, 6', 6", 6"', 6a) diminuant dans le sens d'écoulement de la vapeur d'échappement.
  2. Conduite de vapeur d'échappement selon la revendication 1,
    caractérisée en ce que
    l'angle (W) est de l'ordre de 5° à 60°.
  3. Conduite de vapeur d'échappement selon la revendication 1 ou 2,
    caractérisée en ce que
    l'angle (W) est de l'ordre de 10° et 20°.
  4. Conduite de vapeur d'échappement selon l'une quelconque des revendications 1 à 3,
    caractérisée en ce qu'
    une première conduite principale de vapeur d'échappement (17) et une deuxième conduite principale de vapeur d'échappement (18) sont raccordées, avec une pente ascendante, à une conduite centrale (16) commune.
  5. Conduite de vapeur d'échappement selon l'une quelconque des revendications 1 à 4,
    caractérisée en ce que
    la conduite principale de vapeur d'échappement (10, 17, 18) s'appuie sur des étais (11) qui présentent des moyens de compensation pour la compensation de modifications thermiques de la longueur de la conduite principale de vapeur d'échappement (10, 17, 18).
  6. Conduite de vapeur d'échappement selon la revendication 5,
    caractérisée en ce que
    les étais (11) présentent un tronçon pendulaire ou un tronçon glissant grâce auquel les modifications de la longueur de la conduite principale de vapeur d'échappement (10, 18, 19) peuvent être compensées.
  7. Conduite de vapeur d'échappement selon l'une quelconque des revendications 1 à 6,
    caractérisée en ce qu'
    au moins une des conduites de dérivation (6, 6", 6"') est disposée, en pente ascendante oblique, en formant un coude (W3, W3', W3") par rapport à la conduite principale de vapeur d'échappement (10, 17, 18) dans le sens d'écoulement de la vapeur.
  8. Conduite de vapeur d'échappement selon l'une quelconque des revendications 1 à 7,
    caractérisée en ce qu'
    une conduite de dérivation (6"') terminale de la conduite principale de vapeur d'évacuation (17, 18, 21) a la même orientation que la conduite principale de vapeur d'échappement (17, 18, 21).
  9. Conduite de vapeur d'échappement selon l'une quelconque des revendications 1 à 8,
    caractérisée en ce qu'
    au moins une conduite de dérivation (6a) est divisée au moins en deux conduites partielles (23, 24).
  10. Conduite de vapeur d'échappement selon la revendication 9,
    caractérisée en ce qu'
    au moins une conduite partielle (24) est disposée en pente ascendante oblique en formant un coude (W4) par rapport à la conduite de dérivation (6a).
  11. Conduite de vapeur d'échappement selon l'une quelconque des revendications 1 à 10,
    caractérisée en ce qu'
    au niveau d'au moins un point de raccordement (7, 7a) d'une conduite de dérivation (6, 6', 6", 6"', 6a) ou d'une conduite partielle (23, 24), est disposé un déflecteur (25, 26, 27) pour la répartition du courant de vapeur d'échappement en courants partiels de vapeur d'échappement.
  12. Conduite de vapeur d'échappement selon la revendication 11,
    caractérisée en ce que
    le rapport entre les courants partiels de vapeur d'échappement correspond au rapport entre les tubes répartiteurs (30) suivant un point de raccordement (7, 7a).
EP20040762342 2003-07-08 2004-07-02 Conduite de vapeur d'echappement pour dispositifs a vapeur Active EP1642075B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10330659A DE10330659B3 (de) 2003-07-08 2003-07-08 Abdampfleitung für Dampfkraftanlagen
PCT/DE2004/001417 WO2005005902A1 (fr) 2003-07-08 2004-07-02 Conduite de vapeur d'echappement pour dispositifs a vapeur

Publications (2)

Publication Number Publication Date
EP1642075A1 EP1642075A1 (fr) 2006-04-05
EP1642075B1 true EP1642075B1 (fr) 2006-12-13

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EP20040762342 Active EP1642075B1 (fr) 2003-07-08 2004-07-02 Conduite de vapeur d'echappement pour dispositifs a vapeur

Country Status (14)

Country Link
US (1) US7168448B2 (fr)
EP (1) EP1642075B1 (fr)
KR (1) KR100739933B1 (fr)
CN (2) CN100340743C (fr)
AT (1) ATE348308T1 (fr)
AU (1) AU2004255669B2 (fr)
DE (2) DE10330659B3 (fr)
EG (1) EG24188A (fr)
ES (1) ES2277278T3 (fr)
IL (1) IL171512A (fr)
MX (1) MXPA05008679A (fr)
RU (1) RU2298750C2 (fr)
WO (1) WO2005005902A1 (fr)
ZA (1) ZA200506469B (fr)

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CN100340743C (zh) 2007-10-03
CN1576520A (zh) 2005-02-09
RU2298750C2 (ru) 2007-05-10
IL171512A (en) 2011-06-30
EG24188A (en) 2008-10-08
EP1642075A1 (fr) 2006-04-05
MXPA05008679A (es) 2005-10-05
AU2004255669B2 (en) 2007-05-24
WO2005005902A1 (fr) 2005-01-20
KR100739933B1 (ko) 2007-07-16
US7168448B2 (en) 2007-01-30
ATE348308T1 (de) 2007-01-15
ES2277278T3 (es) 2007-07-01
DE10330659B3 (de) 2004-12-23
AU2004255669A1 (en) 2005-01-20
DE502004002322D1 (de) 2007-01-25
KR20060029279A (ko) 2006-04-05
ZA200506469B (en) 2006-08-30
RU2005129703A (ru) 2006-02-10
US20050161094A1 (en) 2005-07-28
CN2695642Y (zh) 2005-04-27
WO2005005902A8 (fr) 2005-09-09

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