EP0020813B1 - Steam-desuperheating valve - Google Patents

Steam-desuperheating valve Download PDF

Info

Publication number
EP0020813B1
EP0020813B1 EP79103335A EP79103335A EP0020813B1 EP 0020813 B1 EP0020813 B1 EP 0020813B1 EP 79103335 A EP79103335 A EP 79103335A EP 79103335 A EP79103335 A EP 79103335A EP 0020813 B1 EP0020813 B1 EP 0020813B1
Authority
EP
European Patent Office
Prior art keywords
valve
steam
cooling water
cage
peripheral surface
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP79103335A
Other languages
German (de)
French (fr)
Other versions
EP0020813A1 (en
Inventor
Karlheinz Grotloh
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.)
Sulzer AG
Original Assignee
Gebrueder Sulzer AG
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 Gebrueder Sulzer AG filed Critical Gebrueder Sulzer AG
Publication of EP0020813A1 publication Critical patent/EP0020813A1/en
Application granted granted Critical
Publication of EP0020813B1 publication Critical patent/EP0020813B1/en
Expired legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G5/00—Controlling superheat temperature
    • F22G5/12—Controlling superheat temperature by attemperating the superheated steam, e.g. by injected water sprays
    • F22G5/123—Water injection apparatus
    • F22G5/126—Water injection apparatus in combination with steam-pressure reducing valves
    • 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
    • Y10T137/6416—With heating or cooling of the system
    • 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
    • Y10T137/87571—Multiple inlet with single outlet
    • Y10T137/87652—With means to promote mixing or combining of plural fluids

Definitions

  • the invention relates to a steam throttle valve according to the preamble of claim 1.
  • a valve of this type is known from DE-B-1 526 977. With this valve, the injection water is supplied near the valve seat. This results in strong temperature changes on the valve seat and on the closure part, which leads to rapid wear of the material of these two parts due to thermal stresses. This tendency is reinforced by the fact that the water emerges from a ring plate which, due to uneven warping, shows uneven widths over the circumference after a short time.
  • a steam throttle valve in which no valve cage is provided, but the cooling water outlet area is formed by a plurality of channels which are delimited by grooves machined into the valve rod and a guide surface surrounding the valve rod. Because of the relative movements between the guide surface and the valve rod in cooperation with the flowing cooling water, there is a risk that the surfaces sliding on one another will wear out heavily, which leads not only to an incorrect amount of injection water, but also to poor guidance of the valve spindle.
  • the solution according to claim 2 has the constructive advantages that any division errors in the manufacture of the cooling water channels are negligible, because the two parts of the valve abutting in the contact area are manufactured independently of one another, and that one of the two parts is relieved of thermal stresses more.
  • the features of claim 4 additionally reduce the effects of thermal shock stresses in the cooling water outlet area and generally reduce the thermal stresses.
  • the feature according to claim 5 shows a way to reduce the thermal stresses resulting from high heat transfer even in the massive parts of the valve.
  • a steam throttle valve 1 according to FIG. 1 has a valve housing 2 with a steam inlet nozzle 3 and a steam outlet nozzle 4, as well as a removable cover 6 with a water supply bore 7.
  • the cover 6 is tightly connected to the housing 2 by a series of screws 10, which at the same time hold the base flange 11 of a stand 12 for a servo motor, not shown.
  • the cover 6 has an axial bore 14 in a central guide 13, in which a valve spindle 15 is movably arranged.
  • the valve spindle 15 carries a closure body 16 which cooperates with a valve seat 18 protected by hard metal application 17.
  • a stuffing box 20 is arranged, which seals the gap between the spindle 5 and the bore 14.
  • an approximately circular cylindrical valve cage 30 is fastened by screws 32.
  • the other end 34 of the valve cage 30 is guided laterally in a recess 36 in the housing 2.
  • a network of through bores 38 is provided for the steam flowing through the valve.
  • the latter has an inwardly directed flange 40 which has grooves 42, which are distributed uniformly over the circumference.
  • the flange 40 is, with very little radial play, an outwardly directed flanch 44 opposite * .
  • annular space 50 is formed, which is connected to the water supply bore 7 via a vertical bore 52.
  • a head 56 of a water supply line 58 is pressed laterally by a crosshead 60 by means of screws (not shown) on the cover 6.
  • the injection water is supplied to the annular space 50 via a valve (not shown), the line 58, the water supply bore 7 and the vertical bore 52. Particularly during transient conditions, it has a considerably lower temperature in the annular space 50 than the steam below the flanges 40 and 44. There are therefore considerable temperature differences at the parts 30 and 6, in particular in the region of the flange 44. Particularly in the area of the grooves 42, this leads to high temperature gradients because of the high flow velocity of the water there, but these do not have a destructive effect in the present case, because there is a separation between the flange 40, the outside, and the flange 44, the want to shrink inwards.
  • the increase in the radial play between the two flanges that results in this state is not significant, since the total additional cross section for the water does not increase significantly due to the small additional play.
  • an inner sleeve 64 with a U-shaped cross section is pushed onto the guide 13 of the cover 6 instead of a flange 44 and fastened with a weld seam 66.
  • an outer sleeve 68 with an S-shaped cross section is arranged analogously, which has a flange 70 at the top, which is clamped between the shoulder 25 of the cover 6 and the upper flange 27 of the valve cage 30.
  • the sleeves 64 and 68 touch in a cylindrical surface, from which grooves 42 forming water injection channels are machined into the outer sleeve 68.
  • This embodiment has the advantage that in addition to the lips 72 of the sleeves 64 and 68, annular spaces 74 are formed, in which the water essentially stagnates, so that there is a zone of relatively little heat transfer on the water side, which results in lower temperature gradients in the sleeves.
  • Another advantage of this embodiment is that the outer sleeve 68, on which erosion corrosion may occur, can be replaced easily and inexpensively.
  • the lips 72 are not directed upwards but rather downwards, so that the annular spaces, filled with stagnant steam, are again next to the two lips 72.
  • the temperature of the sleeves is thus closer to the lower water temperature. Therefore, lower temperature gradients are to be expected than in the case according to FIG. 3, because in the area of the grooves 42 the water temperature has a dominant effect on the temperature of the sleeves.
  • the cover 6, the sleeve 68 and the valve cage 30 are then connected to one another by a circular weld seam 76.
  • This weld seam can be easily grinded away or turned away when the valve cage 30 is replaced. This also releases the sleeve 68, which - depending on the condition - can also be replaced or reinstalled.
  • the inner sleeve 64 is supported at both ends on the guide 13 of the cover 6. A practically closed annular space 80 is thereby formed, which reduces the temperature gradient at the extension 13 in the axial direction.
  • the sleeve 64 is paired here with the inwardly directed flange 40 of the valve body 30.
  • valve cage 30 is connected to the cover 6 by a circular weld 82.
  • the different sleeves and flanges can also be combined with each other in other ways, each with particular advantages, e.g. with regard to production and assembly, expandability and costs can occur.
  • the grooves 42 run along a conical surface, this is also easily possible by shaping the contact surfaces accordingly.
  • this conical surface is to expand downward, it is expedient to provide an inner sleeve and an outer sleeve, the inner sleeve 64 being welded onto the water-side edge in accordance with the exemplary embodiment according to FIG. 5, based on the water.
  • the two sleeves, cone to cone are pushed onto the guide 13 until the flange of the outer sleeve touches the shoulder 25 of the cover 6.
  • the grooves 42 can also be expedient to arrange the grooves 42 obliquely to the axis instead of parallel to the valve axis, for example at an angle of 25 °.
  • the grooves 42 can also be designed as helical lines of the same pitch.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lift Valve (AREA)
  • Sliding Valves (AREA)
  • Control Of Turbines (AREA)
  • Details Of Valves (AREA)
  • Valve Housings (AREA)

Description

Die Erfindung betrifft ein Dampf-Drosselventil nach dem Oberbegriff des Anspruchs 1.The invention relates to a steam throttle valve according to the preamble of claim 1.

Ein Ventil dieser Art ist aus der DE-B-1 526 977 bekannt. Bei diesem Ventil wird das Einspritzwasser nahe dem Ventilsitz zugeführt. Dies hat starke Temperaturänderungen am Ventilsitz und am Verschlussteil zur Folge, was zu einer raschen Zermürbung des Werkstoffs dieser beiden Teile durch Wärmespannungen führt. Verstärkt wird diese Tendenz noch dadurch, dass das Wasser aus einem Ringsplat austritt, der im Laufe des Betriebes, durch ungleiches Verziehen bedingt, nach kurzer Zeit über dem Umfang ungleiche Weiten aufweist.A valve of this type is known from DE-B-1 526 977. With this valve, the injection water is supplied near the valve seat. This results in strong temperature changes on the valve seat and on the closure part, which leads to rapid wear of the material of these two parts due to thermal stresses. This tendency is reinforced by the fact that the water emerges from a ring plate which, due to uneven warping, shows uneven widths over the circumference after a short time.

Es ist Aufgabe der Erfindung, das Ventil der eingangs genannten Art so zu verbessern, dass Wärmespannungen am Ventilsitz und am Verschlussteil auf konstruktiv einfache Art vermieden werden.It is an object of the invention to improve the valve of the type mentioned at the outset in such a way that thermal stresses on the valve seat and on the closure part are avoided in a structurally simple manner.

Diese Aufgabe wird durch die Merkmale nach dem Kennzeichen des Anspruchs 1 gelöst.This object is achieved by the features according to the characterizing part of claim 1.

Die Vorteile der Erfindung liegen in der erheblich einfacheren Konstruktion des Ventils sowie darin, dass am Ventilsitz keine Erhöhung des Temperaturgradienten auftritt. Ueberdies lassen sich Schäden durch Erosion oder Thermoschock im Bereich der Kühlwasserkanäle leicht reparieren, ohne dass dabei kostspielige Teile, wie Ventilgehäuse oder Ventildeckel, ersetzt werden müssten.The advantages of the invention lie in the considerably simpler construction of the valve and in the fact that there is no increase in the temperature gradient at the valve seat. In addition, damage caused by erosion or thermal shock in the area of the cooling water ducts can be easily repaired without having to replace expensive parts such as the valve housing or valve cover.

Aus der DE-B-1 626 313 ist ein Dampf- drosselventil bekannt, bei dem kein Ventilkorb vorgesehen ist, jedoch der Kühlwassermündungsbereich durch eine Vielzahl von Kanälen gebildet ist, die durch in die Ventilstange eingearbeitete Nuten und eine die Ventilstange umgebende Führungsfläche begrenzt sind. Wegen den Relativbewegungen zwischen der Führungsfläche und der Ventilstange im Zusammenwirken mit dem strömenden Kühlwasser besteht die Gefahr, dass sich die aufeinandergleitenden Flächen stark abnutzen, was nicht nur zu einer falschen Einspritzwassermenge, sondern auch zu einer schlechten Führung der Ventilspindel führt.From DE-B-1 626 313 a steam throttle valve is known, in which no valve cage is provided, but the cooling water outlet area is formed by a plurality of channels which are delimited by grooves machined into the valve rod and a guide surface surrounding the valve rod. Because of the relative movements between the guide surface and the valve rod in cooperation with the flowing cooling water, there is a risk that the surfaces sliding on one another will wear out heavily, which leads not only to an incorrect amount of injection water, but also to poor guidance of the valve spindle.

Die Lösung nach Anspruch 2 hat die konstruktiven Vorteile, dass etwaige Teilungsfehler beim Herstellen der Kühlwasserkanäle nicht ins Gewicht fallen, weil die beiden in der Berührungsfläche aneinanderstossenden Teile des Ventils unabhängig voneinander gefertigt werden, und dass der eine der beiden Teile mehr von Wärmespannungen entlastet wird.The solution according to claim 2 has the constructive advantages that any division errors in the manufacture of the cooling water channels are negligible, because the two parts of the valve abutting in the contact area are manufactured independently of one another, and that one of the two parts is relieved of thermal stresses more.

. Das Merkmal nach Anspruch 3 führt zu einer konstruktiv besonders einfachen Lösung, da der Ventilkorb dann einen leicht demontierbaren Verschleissteil bildet.. The feature of claim 3 leads to a structurally particularly simple solution, since the valve cage then forms an easily removable wear part.

Durch das Merkmal nach Anspruch 4 werden Wirkungen von Thermoschockbeanspruchungen im Kühlwassermündungsbereich zusätzlich herabgesetzt und allgemein die Wärmespannungen vermindert.The features of claim 4 additionally reduce the effects of thermal shock stresses in the cooling water outlet area and generally reduce the thermal stresses.

Das Merkmal gemäss Anspruch 5 zeigt einen Weg, um auch in den massiven Teilen des Ventils die durch hohen Wärmeübergang entstehenden Wärmespannungen zu reduzieren.The feature according to claim 5 shows a way to reduce the thermal stresses resulting from high heat transfer even in the massive parts of the valve.

Die Erfindung wird in der Zeichnung an vier Ausführungsbeispielen näher erläutert. Es zeigen :

  • Fig. 1 einen Axialschnitt durch ein Dampf- Drosselventil nach der Erfindung,
  • Fig. 2 einen Teilschnitt nach 11-11 in Fig. 1,
  • Fig. 3 einen axialen Teilschnitt durch ein zweites Ausführungsbeispiel,
  • Fig. 4 ein drittes Beispiel, der Fig. 3 entsprechend dargestellt,
  • Fig. 5 ein viertes Beispiel, ebenfalls der Fig. 3 entsprechend dargestellt.
The invention is explained in more detail in the drawing using four exemplary embodiments. Show it :
  • 1 is an axial section through a steam throttle valve according to the invention,
  • 2 shows a partial section according to 11-11 in Fig. 1,
  • 3 is a partial axial section through a second embodiment,
  • 4 shows a third example, which is shown corresponding to FIG. 3,
  • Fig. 5 shows a fourth example, also shown in Fig. 3 accordingly.

Ein Dampf-Drosselventil 1 nach Fig. 1 weist ein Ventilgehäuse 2 mit einem Dampfeintrittstutzen 3 und einem Dampfaustrittstutzen 4, sowie einen abnehmbaren Deckel 6 mit Wasserzufuhrbohrung 7 auf. Der Deckel 6 ist durch eine Reihe von Schrauben 10, die gleichzeitig den Fussflansch 11 eines Ständers 12 für einen nicht gezeichneten Servomotor halten, dicht mit dem Gehäuse 2 verbunden. Der Deckel 6 weist in einer zentralen Führung 13 eine axiale Bohrung 14 auf, in der eine Ventilspindel 15 beweglich angeordnet ist. Die Ventilspindel 15 trägt einen Verschlusskörper 16, der mit einem durch Hartmetallauftrag 17 geschützten Ventilsitz 18 zusammenwirkt. In der oberen Partie des Deckels 6 ist eine Stopfbüchse 20 angeordnet, welche den Spalt zwischen der Spindell5 und der Bohrung 14 abdichtet.A steam throttle valve 1 according to FIG. 1 has a valve housing 2 with a steam inlet nozzle 3 and a steam outlet nozzle 4, as well as a removable cover 6 with a water supply bore 7. The cover 6 is tightly connected to the housing 2 by a series of screws 10, which at the same time hold the base flange 11 of a stand 12 for a servo motor, not shown. The cover 6 has an axial bore 14 in a central guide 13, in which a valve spindle 15 is movably arranged. The valve spindle 15 carries a closure body 16 which cooperates with a valve seat 18 protected by hard metal application 17. In the upper part of the cover 6, a stuffing box 20 is arranged, which seals the gap between the spindle 5 and the bore 14.

An einer Schulter 25 des Deckels 6, die durch eine Eindrehung 26 zu einem Flansch gestaltet ist, ist ein etwa kreiszylindrischer Ventilkorb 30 durch Schrauben 32 befestigt. Das andere Ende 34 des Ventilkorbs 30 ist in einer Eindrehung 36 des Gehäuses 2 seitlich geführt. Im mittleren Bereich des Ventilkorbs 30 ist ein Netz von Durchtrittsbohrungen 38 für den das Ventil durchströmenden Dampf vorgesehen. Im oberen Teil des Ventilkorbs weist dieser einen nach innen gerichteten Flansch 40 auf, der - über den Umfang gleichmässig verteilt - Nuten 42 aufweist. Dem Flansch 40 steht, mit sehr geringem Radialspiel, ein nach aussen gerichteter Flanch 44 gegenüber *, Oberhalb der beiden Flansche 40 und 44 und unterhalb der Schulter 25 ist ein Ringraum 50 gebildet, der über eine Vertikalbohrung 52 mit der Wasserzufuhrbohrung 7 verbunden ist. An der Mündung der Wasserzufuhrbohrung 7 sitzt ein Kopf 56 einer Wasserzufuhrleitung 58, der durch ein Querhaupt 60 mittels nicht gezeichneter Schrauben am Deckel 6 seitlich angepresst wird.On a shoulder 25 of the cover 6, which is formed into a flange by a recess 26, an approximately circular cylindrical valve cage 30 is fastened by screws 32. The other end 34 of the valve cage 30 is guided laterally in a recess 36 in the housing 2. In the central area of the valve cage 30, a network of through bores 38 is provided for the steam flowing through the valve. In the upper part of the valve cage, the latter has an inwardly directed flange 40 which has grooves 42, which are distributed uniformly over the circumference. The flange 40 is, with very little radial play, an outwardly directed flanch 44 opposite * . Above the two flanges 40 and 44 and below the shoulder 25, an annular space 50 is formed, which is connected to the water supply bore 7 via a vertical bore 52. At the mouth of the water supply bore 7 is a head 56 of a water supply line 58, which is pressed laterally by a crosshead 60 by means of screws (not shown) on the cover 6.

* der eine zylindrische Umfangsfläche 43 aufweist (Fig. 2). * which has a cylindrical peripheral surface 43 (Fig. 2).

Im Betrieb strömt Dampf unter dem angehobenen Verschlusskörper 16 hindurch in den Raum innerhalb des Ventilkorbs 30, wo eine starke Turbulenz herrscht. Ueber die von den Nuten 42 gebildeten Wassereinspritzkanäle wird aus dem Ringraum 50 Wasser in den Dampf eingedüst, das dort zum grössten Teil verdampft und zum kleineren Teil vom Dampf in Form kleiner Tröpfchen durch die Bohrungen 38 mitgerissen und gegebenenfalls über den Austrittstutzen 4 mitgeschleppt wird.In operation, steam flows under the raised one NEN closure body 16 into the space within the valve cage 30, where there is strong turbulence. Via the water injection channels formed by the grooves 42, water is injected from the annular space 50 into the steam, which for the most part evaporates there and the smaller part is entrained by the steam in the form of small droplets through the bores 38 and, if necessary, is carried along via the outlet connection 4.

Das Einspritzwasser wird über ein nicht gezeichnetes Ventil, die Leitung 58, die Wasserzufuhrbohrung 7 und die Vertikalbohrung 52 dem Ringraum 50 zugeführt. Besonders während transienter Zustände weist es im Ringraum 50 eine erheblich tiefere Temperatur auf als der Dampf unterhalb der Flansche 40 und 44. An den Teilen 30 und 6, dort insbesondere im Bereich des Flansches 44, ergeben sich daher erhebliche Temperaturdifferenzen. Besonders im Bereich der Nuten 42 führt dies wegen der dort herrschenden, hohen Strömungsgeschwindigkeit des Wassers zu hohen Temperaturgradienten, die sich aber im vorliegenden Fall nicht zerstörend auswirken, weil ja eine Trennung zwischen dem Flansch 40, der nach aussen, und dem Flansch 44, der nach innen wegschrumpfen möchte, besteht. Die bei diesem Zustand sich ergebende Vergrösserung des Radialspiels zwischen den beiden Flanschen ist nicht erheblich, da durch das geringe zusätzliche Spiel der Gesamtdurchtrittsquerschnitt für das Wasser nicht erheblich zunimmt.The injection water is supplied to the annular space 50 via a valve (not shown), the line 58, the water supply bore 7 and the vertical bore 52. Particularly during transient conditions, it has a considerably lower temperature in the annular space 50 than the steam below the flanges 40 and 44. There are therefore considerable temperature differences at the parts 30 and 6, in particular in the region of the flange 44. Particularly in the area of the grooves 42, this leads to high temperature gradients because of the high flow velocity of the water there, but these do not have a destructive effect in the present case, because there is a separation between the flange 40, the outside, and the flange 44, the want to shrink inwards. The increase in the radial play between the two flanges that results in this state is not significant, since the total additional cross section for the water does not increase significantly due to the small additional play.

Im Ausführungsbeispiel nach Fig. 3 ist auf der Führung 13 des Deckels 6 anstelle eines Flansches 44 eine innere Hülse 64 mit U-Förmigem Querschnitt aufgeschoben und mit einer Schweissnaht 66 befestigt. Statt des am Ventilkorb 30 nach innen gerichteten Flansches 40 ist analog eine äussere Hülse 68 mit S-förmigem Querschnitt angeordnet, die oben einen Flansch 70 aufweist, der zwischen der Schulter 25 des Deckels 6 und dem oberen Flansch 27 des Ventilkorbes 30 eingespannt ist. Die Hülsen 64 und 68 berühren sich in einer zylindrischen Fläche, von der aus Wassereinspritzkanäle bildende Nuten 42 in die äussere Hülse 68 eingearbeitet sind. Diese Ausführungsform hat den Vorteil, dass neben den Lippen 72 der Hülsen 64 und 68 Ringräume 74 gebildet sind, in denen das Wasser im wesentlichen stagniert, sodass dort wasserseitig eine Zone relativ geringen Wärmeübergangs besteht, was geringere Temperaturgradienten in den Hülsen zur Folge hat. Ein weiterer Vorteil dieser Ausführungsform besteht darin, dass die äussere Hülse 68, an der eventuell Erosionskorrosionen auftreten können, leicht und kostengünstig ausgewechselt werden kann.In the exemplary embodiment according to FIG. 3, an inner sleeve 64 with a U-shaped cross section is pushed onto the guide 13 of the cover 6 instead of a flange 44 and fastened with a weld seam 66. Instead of the flange 40 directed inwards on the valve cage 30, an outer sleeve 68 with an S-shaped cross section is arranged analogously, which has a flange 70 at the top, which is clamped between the shoulder 25 of the cover 6 and the upper flange 27 of the valve cage 30. The sleeves 64 and 68 touch in a cylindrical surface, from which grooves 42 forming water injection channels are machined into the outer sleeve 68. This embodiment has the advantage that in addition to the lips 72 of the sleeves 64 and 68, annular spaces 74 are formed, in which the water essentially stagnates, so that there is a zone of relatively little heat transfer on the water side, which results in lower temperature gradients in the sleeves. Another advantage of this embodiment is that the outer sleeve 68, on which erosion corrosion may occur, can be replaced easily and inexpensively.

Im Beispiel nach Fig. 4 sind, im Unterschied zu Fig. 3, die Lippen 72 nicht nach oben, sondern nach unten gerichtet, sodass die Ringräume, mit stagnierendem Dampf gefüllt, wieder neben den beiden Lippen 72 liegen. Damit ist die Temperatur der Hülsen näher an der tieferen Wassertemperatur. Es sind daher geringere Temperaturgradienten zu erwarten als im Falle nach Fig. 3, weil im Bereich der Nuten 42 ohnehin die Wassertemperatur dominierend auf die Temperatur der Hülsen einwirkt.In the example according to FIG. 4, in contrast to FIG. 3, the lips 72 are not directed upwards but rather downwards, so that the annular spaces, filled with stagnant steam, are again next to the two lips 72. The temperature of the sleeves is thus closer to the lower water temperature. Therefore, lower temperature gradients are to be expected than in the case according to FIG. 3, because in the area of the grooves 42 the water temperature has a dominant effect on the temperature of the sleeves.

Im Gegensatz zu Fig. 3 sind sodann im Beispiel nach Fig. 4 der Deckel 6, die Hülse 68 und der Ventilkorb 30 durch eine zirkulare Schweissnaht 76 miteinander verbunden. Diese Schweissnaht lässt sich beim Ersatz des Ventilkorbes 30 leicht wegschleifen oder wegdrehen. Dabei wird auch die Hülse 68 frei, die - je nach Zustand - ebenfalls ersetzt oder wieder eingebaut werden kann.In contrast to FIG. 3, in the example according to FIG. 4 the cover 6, the sleeve 68 and the valve cage 30 are then connected to one another by a circular weld seam 76. This weld seam can be easily grinded away or turned away when the valve cage 30 is replaced. This also releases the sleeve 68, which - depending on the condition - can also be replaced or reinstalled.

Bei der Ausführungsform nach Fig. 5 stützt sich die Innenhülse 64 an ihren beiden Enden auf der Führung 13 des Deckels 6 ab. Dadurch wird ein praktisch geschlossener Ringraum 80 gebildet, der den Temperaturgradienten an der Verlängerung 13 in axialer Richtung herabsetzt. Die Hülse 64 ist hier gepaart mit dem nach innen gerichteten Flansch 40 des Ventilkorbes 30.In the embodiment according to FIG. 5, the inner sleeve 64 is supported at both ends on the guide 13 of the cover 6. A practically closed annular space 80 is thereby formed, which reduces the temperature gradient at the extension 13 in the axial direction. The sleeve 64 is paired here with the inwardly directed flange 40 of the valve body 30.

Analog wie bei Fig. 4 ist der Ventilkorb 30 durch eine zirkulare Schweissnaht 82 mit dem Deckel 6 verbunden.Analogously to FIG. 4, the valve cage 30 is connected to the cover 6 by a circular weld 82.

Selbstverständlich lassen sich die verschiedenen Hülsen und Flansche auch auf andere Weise miteinander kombinieren, wobei jeweils besondere Vorteile, z.B. hinsichtlich Fertigung und Montage, Ausbaubarkeit und Kosten auftreten können. Ist es erwünscht, dass die Nuten 42 nach einer Konusfläche verlaufen, so ist auch das ohne weiteres möglich, indem die Berührungsflächen entsprechend geformt werden. Soll diese Konusfläche nach unten sich erweitern, so ist es zweckmässig, eine innere Hülse und eine äussere Hülse vorzusehen, wobei die innere Hülse 64 entsprechend dem Ausführungsbeispiel nach Fig. 5, auf das Wasser bezogen, am stromunterseitigen Rand angeschweisst wird. Zu dieser Operation werden die beiden Hülsen, Konus auf Konus gesteckt, auf die Führung 13 aufgeschoben bis der Flansch der äusseren Hülse die Schulter 25 des Deckels 6 berührt.Of course, the different sleeves and flanges can also be combined with each other in other ways, each with particular advantages, e.g. with regard to production and assembly, expandability and costs can occur. If it is desired that the grooves 42 run along a conical surface, this is also easily possible by shaping the contact surfaces accordingly. If this conical surface is to expand downward, it is expedient to provide an inner sleeve and an outer sleeve, the inner sleeve 64 being welded onto the water-side edge in accordance with the exemplary embodiment according to FIG. 5, based on the water. For this operation, the two sleeves, cone to cone, are pushed onto the guide 13 until the flange of the outer sleeve touches the shoulder 25 of the cover 6.

Um die Einspritzwasserstrahlen von der Führung 13 weg gegen den Ventilkorb 30 zu richten, kann es auch zweckmässig sein, die Nuten 42, statt parallel zur Ventilachse, beispielsweise unter einem Winkel von 25°, windschief zur Achse anzuordnen. Zum gleichen Zwecke können die Nuten 42 auch als Schraubenlinien gleicher Steigung ausgebildet sein.In order to direct the injection water jets away from the guide 13 against the valve cage 30, it can also be expedient to arrange the grooves 42 obliquely to the axis instead of parallel to the valve axis, for example at an angle of 25 °. For the same purpose, the grooves 42 can also be designed as helical lines of the same pitch.

Anstelle der zirkularen Schweissnähte 66, 76 und 82 können auch Heftschweissungen genügen.Instead of the circular weld seams 66, 76 and 82, tack welds can also suffice.

Claims (6)

1. A steam throttle valve, with a valve cage (30) disposed downstream of the throttle cross-section and having a cooling water discharge area leading into the flow chamber between the throttle cross-section and the valve cage apertures (38), and fed from an annular chamber (50) disposed concentrically with respect to the valve spindle (15), characterised in that the cooling water discharge area is formed by a plurality of ducts (42) extending along a peripheral surface (43) provided between the valve cage (30) and the guide (13) of the valve spindle (15), said guide being disposed concentrically in the valve cage.
2. A steam throttle valve according to claim 1, characterised in that the contact surface (43) forms a cylindrical or conical peripheral surface and the cooling water ducts are defined by grooves (42) in a flange (40) of the valve cage (30) and by the peripheral surface (43).
3. A steam throttle valve according to claim 1 or 2, characterised in that the valve cage (30) is replaceable.
4. A steam throttle valve according to any one of claims 1 to 3, characterised in that the guide (13) for the valve spindle is in the form of a thin-walled sleeve extending to the peripheral surface (43).
5. A steam throttle valve according to any one of claims 1 to 4, characterised in that at least one annular chamber (74) for stagnant water of stagnant steam is formed in the region of the cooling water ducts (42).
6. A steam throttle valve according to any one of claims 1 to 5, characterised in that the cooling water ducts are arranged skew fashion (helically or possibly spirally) relative to the valve axis preferably each at the same angle.
EP79103335A 1979-06-20 1979-09-07 Steam-desuperheating valve Expired EP0020813B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH574679A CH643043A5 (en) 1979-06-20 1979-06-20 STEAM THROTTLE VALVE.
CH5746/79 1979-06-20

Publications (2)

Publication Number Publication Date
EP0020813A1 EP0020813A1 (en) 1981-01-07
EP0020813B1 true EP0020813B1 (en) 1982-02-03

Family

ID=4298646

Family Applications (1)

Application Number Title Priority Date Filing Date
EP79103335A Expired EP0020813B1 (en) 1979-06-20 1979-09-07 Steam-desuperheating valve

Country Status (9)

Country Link
US (1) US4366833A (en)
EP (1) EP0020813B1 (en)
JP (1) JPS566960A (en)
AU (1) AU531274B2 (en)
CA (1) CA1132120A (en)
CH (1) CH643043A5 (en)
DE (1) DE2962057D1 (en)
ES (1) ES8103324A1 (en)
PL (1) PL128177B1 (en)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61197201U (en) * 1985-05-29 1986-12-09
GB2198214A (en) * 1986-11-27 1988-06-08 John Joseph Jones Flow restriction device for a tap
DE20018563U1 (en) * 2000-10-30 2002-03-21 CAMERON GmbH, 29227 Celle Actuating device, in particular for a throttle device
US6991883B2 (en) 2002-05-16 2006-01-31 Troy Group, Inc. Toner for producing secure images and methods of forming and using the same
US8899551B2 (en) * 2012-02-24 2014-12-02 Fisher Controls International Llc Oblique mating surfaces in a valve assembly
US10119416B2 (en) 2014-10-28 2018-11-06 Mitsubishi Hitachi Power Systems, Ltd. Main steam valve and steam turbine
CN104500762A (en) * 2014-12-08 2015-04-08 章华 Protection structure of pilot sealing surface of electromagnetic decompression valve
CN105698006B (en) * 2016-03-25 2018-06-22 吴忠仪表有限责任公司 Integral type reducing-and-cooling plant
US11585456B2 (en) 2019-01-07 2023-02-21 Fisher Controls International Llc Valve assemblies with integrated temperature control

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE874775C (en) * 1943-02-17 1953-04-27 Siemens Ag Device for cooling steam
US3243157A (en) * 1961-06-14 1966-03-29 Zimmer Verfahrenstechnik Reducing valves
DE1626213B1 (en) * 1963-04-24 1970-12-17 Arap Armaturen U App Gmbh Pressure reducing control valve for steam
US3228603A (en) * 1963-05-07 1966-01-11 Powers Regulator Co Thermostatic mixing valve with volume control
US3298389A (en) * 1964-07-07 1967-01-17 Rockwell Mfg Co Pressure balanced valve
DE1243691B (en) * 1965-02-15 1967-07-06 Schaeffer & Budenberg Gmbh Valve for converting the pressure and temperature of superheated steam
DE1526977B2 (en) * 1967-03-13 1975-05-07 Kraftwerk Union Ag, 4330 Muelheim Steam conversion valve for hot steam cooling
GB1159463A (en) * 1967-06-19 1969-07-23 Copes Regulators Ltd Improvements in or relating to Pressure Reducing and Desuperheating Valves
SE326456B (en) * 1968-11-29 1970-07-27 Kaelle Regulatorer Ab
AT325064B (en) * 1973-07-24 1975-10-10 Schaeffer & Budenberg Gmbh VALVE FOR CONVERTING THE PRESSURE AND TEMPERATURE OF HOT STEAM
US3964516A (en) * 1975-09-09 1976-06-22 Dresser Industries, Inc. Flow control valve for decoking
DE2552077A1 (en) * 1975-11-20 1977-06-02 Otto & Co Gmbh Dr C SLAG BATH GENERATOR

Also Published As

Publication number Publication date
US4366833A (en) 1983-01-04
JPS566960A (en) 1981-01-24
JPS6135361B2 (en) 1986-08-13
CA1132120A (en) 1982-09-21
DE2962057D1 (en) 1982-03-11
PL128177B1 (en) 1984-01-31
ES490922A0 (en) 1981-02-16
PL225016A1 (en) 1981-02-27
CH643043A5 (en) 1984-05-15
AU5943080A (en) 1981-01-08
EP0020813A1 (en) 1981-01-07
ES8103324A1 (en) 1981-02-16
AU531274B2 (en) 1983-08-18

Similar Documents

Publication Publication Date Title
DE102016102756B4 (en) Control cylinder for a control valve and control valve with such a control cylinder
DE3235552C2 (en) Backwash filter
DE2622041C2 (en) Changeover valve
DE3304523C2 (en) Steam conversion valve
DE2505657C3 (en) Steam recirculation valve
DE1476801A1 (en) Cooling device
EP0020813B1 (en) Steam-desuperheating valve
EP1668236B1 (en) Combustion chamber comprising a cooling unit and method for producing said combustion chamber
DE2839552B2 (en) Nozzle head for the production of plastic granulate
DE2539711B2 (en) Volute casing for flow machines
DE10064035A1 (en) Mold for the production of resin pellets
DE1922470C3 (en) High pressure throttle device
DE2158578A1 (en) Stator blade construction
DE3536236C2 (en)
EP2723908B1 (en) Lance head for an oxygen lance
DE1425644B2 (en) PALTTENVENTIL
EP0164503A2 (en) Fluid-conveying conduit with at least one choke
DE2736708C2 (en)
DE3917487A1 (en) CASTING CONTAINER FOR WARM CHAMBER DIE CASTING MACHINES
DE2512051A1 (en) External ring on large diameter tube - has keyways machined in ring with wedged internal keys
CH627820A5 (en) Valve cage with cooled valve seat for the exhaust valve of a diesel engine
DE1583277B1 (en) Delivery of steel degassing vessels and procedures for repairing such vessels
DE1962953C3 (en) Gate valve housing with welded-in angle pieces designed as sealing seats and delimiting the cooling chambers
DE10246701B4 (en) Injection molding device and nozzle with a gap seal between nozzle components
DE2829010C2 (en) Mold consisting of a solid mold body with coolant channels for the electrical remelting of metals

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19790907

AK Designated contracting states

Designated state(s): DE FR GB IT NL

ITF It: translation for a ep patent filed

Owner name: ING. ZINI MARANESI & C. S.R.L.

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Designated state(s): DE FR GB IT NL

REF Corresponds to:

Ref document number: 2962057

Country of ref document: DE

Date of ref document: 19820311

ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19980814

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19980821

Year of fee payment: 20

Ref country code: DE

Payment date: 19980821

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 19980827

Year of fee payment: 20

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990906

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 19990907

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Effective date: 19990906

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT