NO802428L

NO802428L - ROTOR VALVE.

Info

Publication number: NO802428L
Application number: NO802428A
Authority: NO
Inventors: Erik Helge Frisk
Original assignee: Sunds Defibrator
Priority date: 1979-08-15
Filing date: 1980-08-14
Publication date: 1981-02-16
Also published as: SE7906819L; BR8004938A; FI802208A7

Description

Foreliggende oppfinnelse angår rotorventiler for kontrollert mating av materiale til eller fra et trykkar. Slike ventiler anvendes f.eks- ved innmating i eller utmating fra trykkar såsom kokere, basningskar, forvarmere eller liknende innen celluloseindustrien. The present invention relates to rotor valves for controlled feeding of material to or from a pressure vessel. Such valves are used, for example, for feeding into or discharging from pressure vessels such as boilers, basins, preheaters or the like within the cellulose industry.

Angjeldende ventiler omfatter en rotor som er utstyrt med et antall lommer og bæres av en aksel i et hus som er forsynt med inn- og utmatingsstusser for materialet. En slik ventil er The valves in question comprise a rotor which is equipped with a number of pockets and is carried by a shaft in a housing which is provided with inlet and outlet nozzles for the material. Such a valve is

i prinsipp enkel og driftssikker og den muliggjør overføring av fast materiale til eller fra et trykkar, samtidig som rotoren i alle stillinger tetter mot damp- henholdsvis væsketrykk. Det faste materialet utsettes ikke for noen mekanisk påvirkning. in principle simple and operationally reliable and it enables the transfer of solid material to or from a pressure vessel, while the rotor in all positions seals against steam or liquid pressure. The solid material is not exposed to any mechanical influence.

For at rotorventilen skal fungere tilfredsstillende kreves likevel en effektiv tetning mellom rotoren og huset. Slike tet-ninger kan utgjøres av pakkbokser med rundtløpende paknings-ringer. Pakkboksene har imidlertid den ulempe at pakningsrin-gene hurtig slites slik at etterstilling og utskifting av pak-ningsringer må utføres altfor ofte. Dette har medført at man i praktisk drift vanligvis anvender ventiler med konisk rotor som kan innstilles til seteanlegg under drift. Slike ventiler krever imidlertid stor presisjon på konvinkelen, hvilket gjør dem dyre i fremstilling. Innstillingsanordningene blir også komplisert ved disse ventiler. In order for the rotor valve to function satisfactorily, an effective seal between the rotor and the housing is nevertheless required. Such seals can be constituted by packing boxes with circumferential sealing rings. The packing boxes, however, have the disadvantage that the sealing rings wear out quickly, so that adjustment and replacement of the sealing rings must be carried out far too often. This has meant that, in practical operation, valves with a conical rotor are usually used which can be adjusted to the seat system during operation. However, such valves require great precision on the cone angle, which makes them expensive to manufacture. The setting devices also become complicated with these valves.

Foreliggende oppfinnelse fremskaffer en rotorventil med en tetningsanordning uten ovenstående ulemper. Tetningen utgjøres av to konsentriske ringer med koniske kontaktflater som vender mot hverandre. Innstillingen av ønsket klaring henholdsvis anleggstrykk kan lett utføres ved aksiell forskyvning av den ene ring i forhold til den andre. Tetningen kan gjøres meget effektiv, slitasjen blir liten og friksjonen lav. The present invention provides a rotor valve with a sealing device without the above disadvantages. The seal consists of two concentric rings with conical contact surfaces that face each other. The setting of the desired clearance or installation pressure can easily be carried out by axial displacement of one ring in relation to the other. The seal can be made very effective, wear is small and friction is low.

Oppfinnelsens karakteristiske trekk fremgår av patentkra-vene. The characteristic features of the invention appear from the patent claims.

Oppfinnelsen skal i det følgende beskrives i tilknytning til en utføringsform som er vist på tegningene. Figur 1 viser en gjennomskåret rotorventil ifølge oppfinnelsen. In the following, the invention will be described in connection with an embodiment shown in the drawings. Figure 1 shows a sectioned rotor valve according to the invention.

Figur 2 viser et snitt langs linjen II-II på figur 1.Figure 2 shows a section along line II-II in Figure 1.

Figur 3 viser en detalj av figur 1 der tetningsarrangementet tydelig fremgår. Figure 3 shows a detail of Figure 1 where the sealing arrangement is clearly visible.

Figur 4 viser et riss ifølge IV-IV på figur 1.Figure 4 shows a drawing according to IV-IV in Figure 1.

Figur 5 viser en annen utføringsform av tetningsarrangementet i et riss som motsvarer figur 3. Figur 6 viser den andre utføringsform i et riss som motsvarer figur 4. Figure 5 shows another embodiment of the sealing arrangement in a view corresponding to Figure 3. Figure 6 shows the second embodiment in a view corresponding to Figure 4.

Rotorventilen ifølge figur 1 omfatter et hus 1 med innma-tings- henholdsvis utmatingsstusser 2 henholdsvis 3, i hvilket en rotor 4 er opplagret. Rotorens aksel 5 bæres av lågere 6 i huset og mellom akselen og huset er anordnet pakkbokser 7. Rotoren har et antall lommer 8 som er åpne radielt utad og av-grenses fra hverandre av mellomvegger 9 som strekker seg ut til huset. Den ytre kanten av mellomveggene er forsynt med en tetningsskinne 10 som sikrer tetningen mellom lommene. Lommene 8 begrenses aksielt av rotorens sidevegger 11 som tetter mot huset og trykksikkert sperrer lommene 8 fra omgivelsene. The rotor valve according to Figure 1 comprises a housing 1 with inlet and outlet nozzles 2 and 3 respectively, in which a rotor 4 is stored. The rotor's shaft 5 is supported by bearings 6 in the housing and packing boxes 7 are arranged between the shaft and the housing. The rotor has a number of pockets 8 which are open radially outwards and are demarcated from each other by intermediate walls 9 which extend to the housing. The outer edge of the intermediate walls is provided with a sealing rail 10 which ensures the seal between the pockets. The pockets 8 are limited axially by the rotor's side walls 11 which seal against the housing and pressure-proof the pockets 8 from the surroundings.

Til huset er også kanaler 12 og 13 tilkoplet. Disse kanaler er forbundet med hverandre, hvorved trykket i lommene 8 ut-lignes når lommene passerer forbi kanalene.: Derved unngår rotoren radiell skjevbelastning. Videre minskes trykklekkasjen ut gjennom ventilen. I innmatingsstussen 2 er en sjaberanord-ning 14 plassert for å hindre materiale i å trenge inn mellom rotorens mellomvegger 9 og huset 1. Channels 12 and 13 are also connected to the house. These channels are connected to each other, whereby the pressure in the pockets 8 is equalized when the pockets pass past the channels: The rotor thereby avoids radial biasing. Furthermore, the pressure leakage out through the valve is reduced. In the feed connection 2, a scraper device 14 is placed to prevent material from penetrating between the rotor's intermediate walls 9 and the housing 1.

Tetningen ved rotorens 4 omkrets og huset 1 avstedkommes ved hjelp av to konsentriske ringer henholdsvis 15 og 16. En klemring 15 med en sylindrisk innerflate som ligger an mot en sylindrisk flate i form av en avsats 17 på rotorens sidevegg 11 og en tetningsring 16 med en sylindrisk ytterflate som tettende ligger an mot en sylindrisk flate i huset 1. De to ringer 15 og 16 har koniske kontaktflater som ligger an mot hverandre. Ved at tetningringen 16 er relativt tynn kan dens ytterdiameter påvirkes ved aksiell forskyvning av ringene i forhold til hverandre. Derved kan ønsket klaring henholdsvis anleggstrykk innstilles mellom tetningsringen 16 og husets sylindriske tet-ningsflate. The seal at the circumference of the rotor 4 and the housing 1 is provided by means of two concentric rings 15 and 16, respectively. A clamping ring 15 with a cylindrical inner surface that rests against a cylindrical surface in the form of a ledge 17 on the side wall 11 of the rotor and a sealing ring 16 with a cylindrical outer surface that rests sealingly against a cylindrical surface in the housing 1. The two rings 15 and 16 have conical contact surfaces that lie against each other. As the sealing ring 16 is relatively thin, its outer diameter can be affected by axial displacement of the rings in relation to each other. Thereby, the desired clearance or contact pressure can be set between the sealing ring 16 and the housing's cylindrical sealing surface.

Klemringen 15 er festet til rotoren 4 ved hjelp av stillskruer 18 hvorved klemringen kan forskyves aksielt i forhold til rotoren. De koniske kontaktflatene mellom klemringen 15 The clamping ring 15 is attached to the rotor 4 by means of set screws 18, whereby the clamping ring can be displaced axially in relation to the rotor. The conical contact surfaces between the clamping ring 15

og tetningsringen 16 har en hellning som gjør at tetningsringen trykkes mot rotorens sidevegg 11 hvorved tetningsringen hindres fra aksiell forskyvning. Vinkelen mellom kontaktfla- and the sealing ring 16 has an inclination which means that the sealing ring is pressed against the side wall 11 of the rotor, whereby the sealing ring is prevented from axial displacement. The angle between contact surfaces

tene og rotorakselen er 2 - 30°, hensiktsmessig 5 - 20° og fortrinnsvis 10 - 20°. Ved forskyvning av klemringen 15 vil dia-meteren til den forholdsvis tynne tetningsringen 16 øke eller minske, hvorved ønsket tetning opprettes. Tetningsringen 16 skal være sammenkoplet med rotoren 4 for omdreining sammen med denne. Minst ett radielt spor 19 er derfor utformet i tetningsringen, hvilket spor passer inn på en tetningsskinne 10. Derved sikres at begge ringene roterer sammen med rotoren 4. Stillskruene 18 er tilgjengelige utenfra gjennom i huset 1 utformede hull 20 som dekkes av løsbare lokk 21. Ved hjelp av stillskruene 18 reguleres klemringens 15 aksielle stilling og derved tetningen mellom tetningsringen 16 og huset ifølge ovenstående. tene and the rotor shaft are 2 - 30°, suitably 5 - 20° and preferably 10 - 20°. When the clamping ring 15 is displaced, the diameter of the relatively thin sealing ring 16 will increase or decrease, whereby the desired seal is created. The sealing ring 16 must be connected to the rotor 4 for turning together with it. At least one radial groove 19 is therefore formed in the sealing ring, which groove fits onto a sealing rail 10. This ensures that both rings rotate together with the rotor 4. The set screws 18 are accessible from the outside through holes 20 formed in the housing 1 which are covered by removable covers 21. With the help of the adjusting screws 18, the axial position of the clamping ring 15 and thereby the seal between the sealing ring 16 and the housing is regulated according to the above.

Ifølge en annen utføringsform, som fremgår av figur 5 ogAccording to another embodiment, which appears in Figure 5 and

6, er tetningsarrangementet modifisert. Rotorventilen er for-øvrig lik utføringsformen ifølge figur 1. Ved det modifiserte tetningsarrangement er klemringen 22 plassert ytterst og tetningsringen 23 innenfor. Klemringens 22 sylindriske flate ligger således an mot den sylindriske flate i huset og tetningsringens 23 sylindriske flate tetter mot den den sylindriske flaten på avsatsen 17 på rotorens sidevegg. Istedenfor på en avsats kan den sylindriske flaten anordnes på annen måte, f.eks. på sideveggens omkrets. Funksjonen blir likevel den samme. 6, the sealing arrangement is modified. The rotor valve is otherwise similar to the embodiment according to figure 1. In the modified sealing arrangement, the clamping ring 22 is placed on the outside and the sealing ring 23 on the inside. The cylindrical surface of the clamping ring 22 thus rests against the cylindrical surface in the housing and the cylindrical surface of the sealing ring 23 seals against the cylindrical surface on the landing 17 on the side wall of the rotor. Instead of on a ledge, the cylindrical surface can be arranged in another way, e.g. on the perimeter of the side wall. The function will still be the same.

Klemringen 22 er festet i huset 1 ved hjelp av stillskruer 24, slik at den kan forskyves aksielt i forhold til huset. Hellningen til de koniske kontaktflater medfører at tetningsringen 23 trykkes mot huset og derved hindres fra aksiell forskyvning. Stillskruene 24 er dreibare i frie hull 25 i husets sidevegg og passer inn i gjengede hull i klemringen 12. Tetningsringen 23 hindres fra å rotere ved at den er koplet til huset 1 ved hjelp av minst én holdeskrue 26 som er innskrudd i husets sidevegg. Denne skrue er i enden hensiktsmessig utformet med en tapp som passer inn i spor 27 i tetningsringen 23 The clamping ring 22 is fixed in the housing 1 by means of set screws 24, so that it can be displaced axially in relation to the housing. The inclination of the conical contact surfaces means that the sealing ring 23 is pressed against the housing and thereby prevented from axial displacement. The set screws 24 are rotatable in free holes 25 in the side wall of the housing and fit into threaded holes in the clamping ring 12. The sealing ring 23 is prevented from rotating by being connected to the housing 1 by means of at least one retaining screw 26 which is screwed into the side wall of the housing. This screw is suitably designed at the end with a pin that fits into groove 27 in the sealing ring 23

på samme måte som ved den første utføringsform. Innstillingen av tetningen mellom tetningsringen 23 og avsatsen 17 på rotorens sidevegg skjer ved hjelp av stillskruene 24 for klemringen 22. in the same way as in the first embodiment. The adjustment of the seal between the sealing ring 23 and the landing 17 on the side wall of the rotor takes place with the help of the set screws 24 for the clamping ring 22.

Ringene er hensiktsmessig fremstilt av rustfritt stål.The rings are appropriately made of stainless steel.

For tetningsringen, som danner tetningsflaten, skal en herdbar stålkvalitet velges. Stor hårdhet på tetningsflaten (opp til 300 Brinell) medfører langsom slitasje og lav friksjonskoeffi-sient. Eventuelt kan tetningsflaten på tetningsringen istedenfor belegges med stellit eller liknende for å oppnå ønsket hårdhet. For the sealing ring, which forms the sealing surface, a hardenable steel quality must be selected. High hardness of the sealing surface (up to 300 Brinell) results in slow wear and a low friction coefficient. Optionally, the sealing surface of the sealing ring can instead be coated with stellite or similar to achieve the desired hardness.

Claims

1. Rotor valve for controlled feeding of material in connection with a pressure vessel, comprising a housing (1) with an inlet (2) and an outlet (3), a motor stored in the housing (4) provided with a number of radially outwardly open pockets ( 8) which are delimited from each other by intermediate walls (9) and axially limited by the rotor's side walls (11), a seal being arranged between each of the rotor's side walls (11) and the housing (1), characterized in that the seal comprises a sealing ring (16 , 23) and a clamping ring (15, 22), which rings are concentric and have conical contact surfaces that lie against each other, that organ (18, 24) is arranged for axial displacement of the clamping ring (15, 22) in relation to the sealing ring (16, 23) so that the diameter of the sealing ring is affected, that the opposite surfaces of the rings are cylindrical and that the rings are arranged between a cylindrical surface on the rotor's side wall (11) and a cylindrical surface in the housing (1) and that the rings are prevented from rotating relative to each other.

2. Rotor valve according to claim 1, characterized in that the cylindrical surface on the side wall (11) of the rotor is designed as a ledge (17) on the side wall, the clamping ring's cylindrical surface abuts against this ledge, and the sealing ring (16) seals against the cylindrical surface in the housing (1) and that both rings are designed to rotate together with the rotor (4).

3. Rotor valve according to claim 1, characterized in that the cylindrical surface of the clamping ring (22) rests against the cylindrical surface in the housing (1) and the sealing ring (23) seals against the cylindrical surface on the side wall of the rotor (11), and that both rings are prevented from rotating.

4. Rotor valve according to claim 2, characterized in that the clamping ring (15) is fixed to the side wall (11) of the rotor and axially adjustable by means of set screws (18) and that the sealing ring (16) rests against the side wall (11) of the rotor and is connected with the rotor (4) for rotation together with this.

5. Rotor valve according to claim 4, characterized in that the sealing ring (23) is connected to the rotor (4) by means of at least one radial groove (19) which fits onto a sealing rail (10) which is attached to the rotor's intermediate walls (9) .

6. Rotor valve according to claim 3, characterized in that the clamping ring (22) is fixed in the housing (1) and axially adjustable by means of set screws (24) and that the sealing ring (23) supports against the housing (1) in the axial direction and is connected to the housing so that it is prevented from rotating.

7. Rotor valve according to one of the preceding claims, characterized in that the angle between the contact surfaces of the sealing ring (16, 23) respectively the clamping ring (15, 22) and the rotor shaft is 2 - 30°, suitably 5 - 20° and preferably 10 - 20°.