EP0020813B1 - Dampf-Drosselventil - Google Patents

Dampf-Drosselventil Download PDF

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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)
English (en)
French (fr)
Other versions
EP0020813A1 (de
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/de
Application granted granted Critical
Publication of EP0020813B1 publication Critical patent/EP0020813B1/de
Expired legal-status Critical Current

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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)
  • Valve Housings (AREA)
  • Details Of Valves (AREA)
EP79103335A 1979-06-20 1979-09-07 Dampf-Drosselventil Expired EP0020813B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH574679A CH643043A5 (de) 1979-06-20 1979-06-20 Dampf-drosselventil.
CH5746/79 1979-06-20

Publications (2)

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

Family

ID=4298646

Family Applications (1)

Application Number Title Priority Date Filing Date
EP79103335A Expired EP0020813B1 (de) 1979-06-20 1979-09-07 Dampf-Drosselventil

Country Status (9)

Country Link
US (1) US4366833A (enrdf_load_stackoverflow)
EP (1) EP0020813B1 (enrdf_load_stackoverflow)
JP (1) JPS566960A (enrdf_load_stackoverflow)
AU (1) AU531274B2 (enrdf_load_stackoverflow)
CA (1) CA1132120A (enrdf_load_stackoverflow)
CH (1) CH643043A5 (enrdf_load_stackoverflow)
DE (1) DE2962057D1 (enrdf_load_stackoverflow)
ES (1) ES490922A0 (enrdf_load_stackoverflow)
PL (1) PL128177B1 (enrdf_load_stackoverflow)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61197201U (enrdf_load_stackoverflow) * 1985-05-29 1986-12-09
GB2198214A (en) * 1986-11-27 1988-06-08 John Joseph Jones Flow restriction device for a tap
DE20018563U1 (de) * 2000-10-30 2002-03-21 CAMERON GmbH, 29227 Celle Betätigungsvorrichtung, insbesondere für eine Drosseleinrichtung
US6991883B2 (en) 2002-05-16 2006-01-31 Troy Group, Inc. Toner for producing secure images and methods of forming and using the same
CN203348668U (zh) * 2012-02-24 2013-12-18 费希尔控制国际公司 阀组件及阀笼
JP6269855B2 (ja) 2014-10-28 2018-01-31 三菱日立パワーシステムズ株式会社 主蒸気弁、及び蒸気タービン
CN104500762A (zh) * 2014-12-08 2015-04-08 章华 电磁泄压阀先导密封面的防护结构
CN105698006B (zh) * 2016-03-25 2018-06-22 吴忠仪表有限责任公司 一体式减温减压装置
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 (de) * 1943-02-17 1953-04-27 Siemens Ag Vorrichtung zum Kuehlen von Dampf
US3243157A (en) * 1961-06-14 1966-03-29 Zimmer Verfahrenstechnik Reducing valves
DE1626213B1 (de) * 1963-04-24 1970-12-17 Arap Armaturen U App Gmbh Druckminder-Regelventil für Dampf
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 (de) * 1965-02-15 1967-07-06 Schaeffer & Budenberg Gmbh Ventil zum Umformen des Druckes und der Temperatur von Heissdampf
DE1526977B2 (de) * 1967-03-13 1975-05-07 Kraftwerk Union Ag, 4330 Muelheim Dampfumformventil zur HeiBdampfkühlung
GB1159463A (en) * 1967-06-19 1969-07-23 Copes Regulators Ltd Improvements in or relating to Pressure Reducing and Desuperheating Valves
SE326456B (enrdf_load_stackoverflow) * 1968-11-29 1970-07-27 Kaelle Regulatorer Ab
AT325064B (de) * 1973-07-24 1975-10-10 Schaeffer & Budenberg Gmbh Ventil zum umformen des druckes und der temperatur von heissdampf
US3964516A (en) * 1975-09-09 1976-06-22 Dresser Industries, Inc. Flow control valve for decoking
DE2552077A1 (de) * 1975-11-20 1977-06-02 Otto & Co Gmbh Dr C Schlackenbadgenerator

Also Published As

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

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