WO2020193702A1 - Ensemble soupape - Google Patents

Ensemble soupape Download PDF

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Publication number
WO2020193702A1
WO2020193702A1 PCT/EP2020/058555 EP2020058555W WO2020193702A1 WO 2020193702 A1 WO2020193702 A1 WO 2020193702A1 EP 2020058555 W EP2020058555 W EP 2020058555W WO 2020193702 A1 WO2020193702 A1 WO 2020193702A1
Authority
WO
WIPO (PCT)
Prior art keywords
flow
valve device
feed section
fluid
fluid flow
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.)
Ceased
Application number
PCT/EP2020/058555
Other languages
German (de)
English (en)
Inventor
Andreas Hellmann
Carsten PÜTTBACH
Viktor Schäfer
Olaf Tebbenhoff
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.)
Welland and Tuxhorn AG
Original Assignee
Welland and Tuxhorn 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 Welland and Tuxhorn AG filed Critical Welland and Tuxhorn AG
Publication of WO2020193702A1 publication Critical patent/WO2020193702A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • 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

Definitions

  • the present application relates to a valve device according to the preamble of claim 1.
  • the valve device comprises a housing in which the other components of the valve device are arranged.
  • the housing extends along a central axis and - apart from connecting lines and the like - is typically at least essentially rotationally symmetrical with respect to the central axis.
  • the valve device comprises a movable piston which is suitable for sealingly cooperating with an associated sealing seat.
  • the piston can be transferable between a closed position and an open position, a flow through the valve device being prevented when the piston is in its closed position and a flow limited by the sealing seat when the piston is in its open position
  • the piston can preferably be locked in any number of intermediate positions relative to the sealing seat, whereby an amount of the fluid flow can be regulated.
  • An injection device by means of which a cooling fluid can be injected into the fluid flow, is arranged inside the housing. Furthermore, the valve device comprises a flow element which comprises a plurality of flow channels.
  • the flow element is preferably designed to be rotationally symmetrical and, as a rule, its axis of symmetry is aligned congruently with the central axis of the housing.
  • the flow channels are preferably arranged in a circumferentially distributed manner on the flow element.
  • the fluid flow is locally constricted at the flow channels, accelerated in the process and passed on through the flow channels.
  • at least part of the fluid flow is accelerated and in this way transferred into a number of atomization flows corresponding to the number of flow channels, the
  • the flow element is arranged relative to the injection device in such a way that the injection of the cooling fluid into the
  • Atomization flows takes place. This is an atomization of the cooling fluid
  • Valve devices of the type described at the outset are already known in the prior art. They are used in particular in power plants as so-called bypass valves in order to circulate a fluid flow, which is typically from a pressurized
  • Steam flow is formed to lead past a turbine of the power plant.
  • the injection of the cooling fluid serves to reduce the thermal energy of the fluid flow, that is to say in particular to lower its temperature.
  • the temperature of the fluid stream is typically in a range between 400 ° C. and 650 ° C. at a pressure of over 50 bar, typically of over 100 bar.
  • Pipelines of the power plant may be the case.
  • individual particles become detached from the pipelines and are then introduced into the fluid flow with and finally into the valve device.
  • Such particles have a highly abrasive effect in the valve device, so that the valve devices are destroyed comparatively quickly.
  • Valve device generally a construction must be produced which is more robust than the previous valve devices. The requirement for greater robustness led to the consideration of reducing the use of parts that could move relative to one another. In valve devices of the prior art, it is common to have a
  • Flow channels that are responsible for generating corresponding atomization flows a proportion of atomizing current can be specifically assigned so that the problem did not occur in the same way.
  • the valve device according to the invention is characterized in that the flow element has a protruding into a flow area of the fluid flow,
  • an inner wall of the housing has a circumferential annular projection assigned to the feed section and extending radially in the direction of the central axis, by means of which at least part of the fluid flow can be directed away from the inner wall of the housing in the direction of the feed section of the flow element.
  • the invention provides that the fluid flow is directed specifically to a feed section of the flow element, which over a plurality of
  • the geometry of the feed section is matched to the formation of the annular projection of the inner wall of the housing, the possibility is now created of the fluid flow to a reliably high proportion of the flow channels
  • Feed section so that the processed by means of the feed section
  • Atomization flow portion of the fluid flow is accelerated appreciably.
  • the atomization flow component is advantageously greater with a relatively low amount of fluid flow than with a larger amount of fluid flow.
  • an absolute mass flow of the atomizing flow component is at least essentially constant regardless of the amount of the total fluid flow. This ensures that the fluid flow is accelerated sufficiently strongly in any case by means of the flow channels of the supply section and consequently provides the desired atomizing effect for the injected cooling fluid.
  • Valve device the annular projection - viewed in the direction of flow of the fluid flow - is designed to be curved or “swung”.
  • This configuration has the advantage that the fluid flow, which flows along the inner wall of the housing at least substantially parallel to the central axis of the housing, when it hits the
  • the ring projection does not suddenly strike a discontinuously protruding wall, but is received as a result of the continuously curved design of the ring projection and is directed to the feed section while maintaining an at least substantially directed flow characteristic.
  • the feed section of the flow element is formed equally curved, the curvature of the feed section preferably the curvature of the
  • the feed section can be locally designed, so to speak, in the shape of a shell, so that it captures the atomization flow portion of the fluid flow directed towards it.
  • the curvature in the area of the feed section - viewed radially in relation to the central axis of the housing - gradually increases from the outside to the inside. The only option for the captured
  • the atomization flow component to leave the feed section in the flow direction is then provided by the flow channels through which the fluid flow is pressed.
  • the described acceleration takes place as desired, so that the atomization flow component leaves the flow channels of the flow element as a plurality of atomization flows.
  • the acceleration effect of the flow channels can in particular lead to that a flow velocity of the fluid flow is accelerated locally by several 100 m / s.
  • Flow element must flow through the valve device in the course of its flow.
  • the flow element adjoins the housing so that there is no possibility for the fluid flow to leave the valve device without flowing through the flow element. In this way it is avoided that the fluid flow “evades” the flow resistances represented by the flow channels.
  • valve device according to the invention is advantageous, in which the annular projection of the housing and the supply section of the
  • End edges thereof are spaced apart from one another. In this way, the end edge of the annular projection and the end edge of the feed section together delimit a flow gap through which a part of the fluid flow passes
  • Execution creates the possibility of temporarily dividing the fluid flow by means of the flow element into two parts, namely a first part which is directed to the feed section (atomization flow part) and a second part which is directed to the
  • Feed section flows past (secondary flow portion).
  • the flow-catching configuration of the feed section is the latter primarily
  • the diameters of the flow channels of the feed section are advantageously larger, in particular at least twice as large, as the diameters of the flow channels that are not assigned to the feed section.
  • the latter can in particular such be designed that they act as a throttle stage for the fluid flow and in this way contribute to a desired pressure and temperature reduction of the fluid flow.
  • the flow channels of the flow element which are assigned to the feed section are advantageously designed such that - viewed in the flow direction of the fluid flow - they extend obliquely in the direction of the central axis of the housing.
  • the flow channels act in such a way that they each impress on the atomization flows generated by their action at least one - in relation to the central axis of the housing - radial directional component.
  • the flow channels are aligned at an angle of approximately 45 ° with respect to the central axis.
  • the inclined configuration of the flow channels of the feed section helps to direct the generated atomization flows in a targeted manner “under” the injection device so that the cooling fluid injected by means of the injection device is injected directly into the atomization flows.
  • the flow element is relative to the
  • Injection device arranged that the flow channels of the feed section the
  • valve device according to the invention further comprises that
  • the cantilever section can in particular adjoin a radially outer end of the feed section and extend from there.
  • the cantilever section together with the inner wall of the housing, delimits an annular space into which the secondary flow portion of the fluid flow can flow.
  • the cantilever section has a multiplicity of flow channels through which the secondary flow component can then pass, starting from the annular space, in the direction of a central space of the flow element.
  • a feed of a portion of the fluid flow to the annular space can in particular take place through a flow gap described above, which is between mutually associated end edges of the annular projection of the
  • the cantilever section is advantageously designed in such a way that it cooperates tightly with the housing at its end remote from the feed section, that is to say, in particular, is connected to the inner wall of the housing in a sealing manner. In this way it is ensured that the secondary flow portion of the fluid flow located in the annular space can leave the annular space exclusively through the flow channels of the cantilever section. A flow around the flow element is therefore prevented.
  • the annular space delimited between the housing and the cantilever section tapers when viewed in the direction of flow of the fluid flow. This tapering can be achieved in particular in that the cantilever section is designed in the form of a truncated cone section which widens conically starting from the feed section.
  • the flow element is arranged downstream of the injection device.
  • the flow element preferably adjoins a lower end of the injection device. It is particularly advantageous if the feed section of the flow element surrounds a lower end of the injection device all the way around, viewed in the direction of flow of the fluid flow. This has the advantage that the flow channels assigned to the feed section are as close as possible to the
  • Atomization flows as close as possible to the injection device. In this way it is achieved that the flow velocity of the atomizing streams in one
  • Injection area in which the cooling fluid mixes with the fluid flow is as large as possible. Accordingly, the atomizing effect of the atomizing streams is as great as possible in the desired manner.
  • such a valve device can also be particularly advantageous in which the inlet connector is assigned a particularly rotationally symmetrical perforated cylinder which surrounds the piston circumferentially and has a large number of flow channels.
  • the perforated cylinder serves to equalize the inflow of the fluid flow through the inlet nozzle, so that the inflow of the piston or the sealing seat is as uniform as possible.
  • this is advantageous, since an asymmetrical flow onto certain areas of the valve device is avoided and consequently a load on the material of the valve device is evened out.
  • Valve device are formed countersunk regardless of their affiliation to individual components of the same.
  • a diameter of a respective flow channel is expanded in a funnel-shaped manner in a front end region, viewed in the direction of flow of the fluid flow.
  • This configuration helps to at least partially provide inner lateral surfaces of the flow channels with a coating that has a resistance of the respective affected component increased against abrasive wear.
  • FIGS. 1 and 2 A schematic detail of a flow element of the valve device according to FIG. 1.
  • An exemplary embodiment which is shown in FIGS. 1 and 2, comprises a valve device 1 according to the invention. This comprises a housing 3 which is at least essentially rotationally symmetrical with respect to a central axis 2 is formed. An inlet nozzle 4 is connected to the housing 3, by means of which the valve device 1 can be supplied with a fluid flow 5.
  • the fluid stream 5 first flows into an inlet space 34, within which an axially movable piston 6 is arranged.
  • Said piston 6 serves to cooperate in a sealing manner with a sealing seat 7 assigned to it.
  • the piston 6 can be moved between different positions relative to the sealing seat 7, and depending on the position of the piston 6, an amount of the fluid flow 5 which flows through the valve device 1 can be regulated.
  • Perforated cylinder 22 is arranged, which has a plurality of flow channels 23.
  • the perforated cylinder 22 surrounds both the piston 6 and the sealing seat 7, so that it is only possible to pass through the sealing seat 7 after the flow channels 23 of the perforated cylinder 22 have flowed through.
  • the perforated cylinder 22 acts to a certain extent as a throttle stage, which achieves an equalization of the flow to both the piston 6 and the sealing seat 7. After passing through the sealing seat 7, the fluid flow 5 reaches a central space 35 of the valve device 1, the central space 35 in the example shown being a
  • Throttle stage 28 is assigned. This comprises a plurality of flow channels 29 through which the fluid flow 5 must flow in the course of flowing through the valve device 1.
  • the flow channels 29 cause a pressure reduction and a
  • valve device 1 can be equipped with a plurality of throttle stages 28 in order to achieve a desired one
  • the valve device 1 further comprises an injection device 9, which is provided with a supply channel 24 for supplying a Cooling fluid 31 cooperates.
  • the feed channel 24 adjoins a nozzle housing 25 of the injection device 9, within which an injection nozzle 36 is arranged. This is pressed against a nozzle seat 27 by means of a spring 26, so that the injection nozzle 36, together with the nozzle seat 27, cooperates in a sealing manner when it is in an otherwise force-free state.
  • the injection device 9 is charged with the cooling fluid 31. Under the pressure of the latter, a spring force of the spring 26 is overcome, so that the injection nozzle 36 is pressed out of its nozzle seat 27.
  • Atomization flow portion 33 of the fluid flow 5 is formed.
  • the valve device 1 comprises a flow element 8 which, in the example shown, is pot-shaped.
  • the flow element 8 comprises an upper one
  • Feed section 13 and a lower cantilever section 19 In the example shown, the feed section 13 adjoins a lower end 37 of the injection nozzle 36 of the injection device 9, viewed in the flow direction of the cooling fluid 31, and extends in the radial direction relative to the central axis 2 of the housing 3 outward. In this way, the feed section 13 protrudes to a certain extent into a flow of the fluid flow 5.
  • the cantilever section 19 adjoins a radially outer end of the feed section 13 on the latter and, starting from the feed section 13, extends in a conically widening manner in the flow direction of the fluid flow 5.
  • the feed section 13 of the flow element 8 interacts with an annular projection 15 formed on an inner wall 14 of the housing 3.
  • Fluid flow 5 exerts.
  • a radially inwardly directed directional component is impressed on the fluid flow 5 by means of the annular projection 15.
  • the annular projection 15 is continuously curved, viewed in the direction of flow of the fluid flow 5, that is to say without a discontinuously projecting projection.
  • the fluid flow 5 is deflected away from the inner wall 14 over a steering path, without the fluid flow 5 striking a discontinuously protruding baffle surface and thereby becoming a turbulent one Electricity is converted.
  • the feed section 13 of the flow element 8 is designed to be curved in the same way, the feed section 13 continuing the curvature of the annular projection 15. This can be seen particularly well on the basis of the detail according to FIG. 2.
  • a curvature profile is based on FIG. 2.
  • the feed section 13 is connected directly to the injection device 9 at its radially inner end, with the flowing past
  • Atomization flow portion 33 of the fluid flow 5 at the flow element 8 between the feed section 13 and the injection device 9 is not possible.
  • the feed section 13 interacts with a plurality of flow channels 10 which allow a flow through the flow element 8.
  • the flow channels 10 intentionally narrow a flow cross-section for the atomization flow portion 33 of the fluid flow 5, so that the atomization flow portion 33 is greatly accelerated in the course of the flow through the flow channels 10.
  • a plurality of atomization streams 12 is generated, the flow rate of which is compared to a flow rate of the fluid stream 5 on this side
  • Flow element 8 is greatly increased.
  • the flow channels 10 are oriented obliquely inward relative to the central axis 2 of the housing 3, so that the
  • Atomization streams 12 receive a radial directional component which is directed towards the central axis 2. In this way, the atomization streams 12 are guided directly below the injection device 9. As a result, the cooling fluid 31 is injected directly into the atomization streams 12, in which there is a high flow velocity. What is achieved hereby is that the cooling fluid 31 is very finely atomized, as a result of which very rapid evaporation of the cooling fluid 31 is achieved.
  • the annular projection 15 and the feed section 13 of the flow element 8 are arranged at a distance from one another, with mutually associated end edges 16, 17 of the annular projection 15 or the feed section 13 jointly delimiting a flow gap 18.
  • a portion of the fluid flow 5 can be conducted past the feed section 13 through this flow gap 18. This portion is referred to here as the secondary flow portion 32.
  • the secondary flow portion 32 flows into an annular space 20, which of the
  • the cantilever section 19 is frustoconical here, with an in Has a conically widening cross-section when viewed in the direction of flow of the fluid flow 5.
  • the cantilever section 19 adjoins the inner wall 14 of the housing 3 in a sealing manner at a contact point 30 (or a circumferential contact ring).
  • the secondary flow portion 32 of the fluid flow 5 can flow exclusively through flow channels 11 of the flow element 8 which are assigned to the cantilever section 19.
  • the bypass flow portion 32 is in the radial direction based on the central axis 2 of the housing 3 in a central space 21 of the
  • the interaction of the annular projection 15 and the protruding feed section 13 has the effect that the atomization flow component 33, which is fed to the central space 21 by means of the feed section 13, is relatively independent of an amount of the total
  • Fluid flow 5 remains the same in relation to the secondary flow portion 32.
  • the atomizing flows 12 exert a sufficient atomizing effect on the cooling fluid 31 so that the latter is finely atomized and consequently evaporated quickly.
  • the valve device 1 according to the invention thus achieves the goal of achieving a fine atomization of the cooling fluid 31 without having to adjust the flow element 8.
  • valve device 1 is significantly more robust than known valve devices 1 which use such mechanisms.
  • valve device 1 in the example shown is designed to be coated.
  • all surfaces that interact directly with the fluid flow 5 are provided with a chromium carbide coating.
  • all flow channels 10, 11, 23, 29 valve device 1 are countersunk in a particularly advantageous manner, with a front inflow area of a respective flow channel widened in a funnel shape when viewed in the flow direction of the fluid flow 5.
  • This configuration of the flow channels 10, 11, 23, 29 has proven to be particularly advantageous for coating inner lateral surfaces of the flow channels 10, 11, 23, 29 with a respective coating.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Nozzles (AREA)
  • Lift Valve (AREA)

Abstract

L'invention concerne un ensemble soupape (1), en particulier sous la forme d'une soupape de réglage, comprenant un boîtier (3) s'étendant le long d'un axe central (2), une tubulure d'entrée (4) pour introduire un flux fluidique (5) dans le boîtier (3), un piston mobile (6) ainsi qu'un siège d'étanchéité (7) associé au piston (6), un élément d'écoulement (8) symétrique en rotation disposé dans le boîtier (3) pour traiter le flux fluidique (5), ainsi qu'un système d'injection (9) pour injecter un fluide de refroidissement. L'élément d'écoulement (8) comprend une pluralité de canaux d'écoulement (10) à travers lesquels une partie du flux fluidique (5) peut être dirigée et, ce faisant, peut être accélérée et donc transférée localement dans des jets de pulvérisation (12), l'élément d'écoulement (8) étant disposé par rapport au système d'injection (9) de façon à pouvoir injecter le fluide de refroidissement dans les jets de pulvérisation (12). Afin de fournir un ensemble soupape robuste permettant une pulvérisation fiable du fluide de refroidissement pour des quantités de flux fluidique très différentes, l'élément d'écoulement (8) de l'invention comprend une section d'alimentation (13) périphérique faisant saillie dans une zone d'écoulement du flux fluidique (5), au moyen de laquelle une partie du flux fluidique (5) peut être capturée et transmise à des canaux d'écoulement (10) associés à la section d'alimentation (13). Une paroi intérieure (14) du boîtier (3) comprend une partie saillante annulaire (15) périphérique associée à la section d'alimentation (13) et s'étendant radialement dans la direction de l'axe médian (2), au moyen de laquelle au moins une partie du flux fluidique (5) peut être dirigée dans la direction de la section d'alimentation (13) de l'élément d'écoulement (8).
PCT/EP2020/058555 2019-03-28 2020-03-26 Ensemble soupape Ceased WO2020193702A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019108090.8 2019-03-28
DE102019108090.8A DE102019108090B4 (de) 2019-03-28 2019-03-28 Ventileinrichtung

Publications (1)

Publication Number Publication Date
WO2020193702A1 true WO2020193702A1 (fr) 2020-10-01

Family

ID=70049889

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2020/058555 Ceased WO2020193702A1 (fr) 2019-03-28 2020-03-26 Ensemble soupape

Country Status (2)

Country Link
DE (1) DE102019108090B4 (fr)
WO (1) WO2020193702A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1049828B (fr) * 1959-02-05
FR2082083A5 (fr) * 1970-03-03 1971-12-10 App Precision Cont
DE2151910A1 (de) * 1970-10-19 1972-07-13 Skoda Np Dampfkuehler
US6131612A (en) * 1994-11-18 2000-10-17 Beurskens; Theo Valve for a superheated-steam conversion plant
EP2554902A1 (fr) * 2011-08-05 2013-02-06 Siemens Aktiengesellschaft Refroidisseur de vapeur en dérivation

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE9502555D0 (sv) * 1995-07-10 1995-07-10 Btg Kaelle Inventing Ab Anordning vid en tryckregleringsventil
JP3817132B2 (ja) * 2000-11-30 2006-08-30 ニイガタ・メーソンネーラン株式会社 蒸気変換弁
US8978706B2 (en) * 2012-02-08 2015-03-17 Fisher Controls International Llc Pressure reducer

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1049828B (fr) * 1959-02-05
FR2082083A5 (fr) * 1970-03-03 1971-12-10 App Precision Cont
DE2151910A1 (de) * 1970-10-19 1972-07-13 Skoda Np Dampfkuehler
US6131612A (en) * 1994-11-18 2000-10-17 Beurskens; Theo Valve for a superheated-steam conversion plant
EP2554902A1 (fr) * 2011-08-05 2013-02-06 Siemens Aktiengesellschaft Refroidisseur de vapeur en dérivation

Also Published As

Publication number Publication date
DE102019108090A1 (de) 2020-10-01
DE102019108090B4 (de) 2023-08-17

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