HRP950029A2 - Apparatus for the pressure maintenance in guide vane bearings of pump turbines - Google Patents
Apparatus for the pressure maintenance in guide vane bearings of pump turbines Download PDFInfo
- Publication number
- HRP950029A2 HRP950029A2 HRP4403786.4A HRP950029A HRP950029A2 HR P950029 A2 HRP950029 A2 HR P950029A2 HR P950029 A HRP950029 A HR P950029A HR P950029 A2 HRP950029 A2 HR P950029A2
- Authority
- HR
- Croatia
- Prior art keywords
- piston
- spring
- bearing
- connection
- cover
- Prior art date
Links
- 238000012423 maintenance Methods 0.000 title description 2
- 239000004519 grease Substances 0.000 claims description 37
- 238000005461 lubrication Methods 0.000 claims description 17
- 230000006835 compression Effects 0.000 claims description 14
- 238000007906 compression Methods 0.000 claims description 14
- 239000006096 absorbing agent Substances 0.000 claims description 3
- 230000035939 shock Effects 0.000 claims description 3
- 238000013016 damping Methods 0.000 description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 4
- 230000036316 preload Effects 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000001050 lubricating effect Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000011664 signaling Effects 0.000 description 2
- 230000001143 conditioned effect Effects 0.000 description 1
- 239000006185 dispersion Substances 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated
- F16N7/38—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with a separate pump; Central lubrication systems
- F16N7/385—Central lubrication systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B11/00—Parts or details not provided for in, or of interest apart from, the preceding groups, e.g. wear-protection couplings, between turbine and generator
- F03B11/06—Bearing arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B13/00—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates
- F03B13/06—Stations or aggregates of water-storage type, e.g. comprising a turbine and a pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
- F03B3/16—Stators
- F03B3/18—Stator blades; Guide conduits or vanes, e.g. adjustable
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N2260/00—Fail safe
- F16N2260/20—Emergency
- F16N2260/24—Emergency using accumulator
-
- 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
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
-
- 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
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Hydraulic Turbines (AREA)
- Rotary Pumps (AREA)
Description
Ovaj izum se odnosi na uređaj za održavanje tlaka u kliznim ležajima privodnih lopatica turbopumpi, koji su podmazivani mašću s određenim pretlakom pomoću centralnog uređaja za podmazivanje, pri čemu su privodne lopatice uležištene iznad i ispod prostrujnih kanala. This invention relates to a device for maintaining pressure in the sliding bearings of the drive blades of turbopumps, which are lubricated with grease with a certain overpressure using a central lubrication device, where the drive blades are located above and below the flow channels.
Habanje u ležajima privodnih lopatica je relativno malo čak i kod velikih, dinamičnih opterećenja, tipičnih za turbopumpe, tako dugo dok se u rasporu ležaja može zadržati dovoljna količina masti. Ukoliko se to ne može postići, npr. zbog oštećenja unutarnje brtve, habanje počinje progresivno rasti i konačno dovodi do ispada ležaja. Pored podmazivanja, mast u rasporu ležaja ima i značajnu ulogu prigušivanja. Poznato je da se mogu postići odlične vrijednosti prigušivanja vibracija rukavca u rasporu ležaja, ako je raspor ležaja potpuno ispunjen mašću za podmazivanje i ako se mast može držati pod određenim pretlakom. Wear in the vane bearings is relatively low even under high, dynamic loads, typical of turbopumps, as long as a sufficient amount of grease can be retained in the bearing gap. If this cannot be achieved, for example due to damage to the internal seal, the wear starts to grow progressively and finally leads to bearing failure. In addition to lubrication, the grease in the bearing gap also plays a significant damping role. It is known that excellent vibration damping values of the sleeve can be achieved in the bearing gap, if the bearing gap is completely filled with lubricating grease and if the grease can be kept under a certain overpressure.
S druge strane pretlak ne smije prekoračiti određene granične vrijednosti, kako se ne bi ugrozile brtve. Pretlačni ventili koji se mogu kupiti u dućanima, kao što su ventili koji se koriste za tekuće i plinske medije, rade vrlo nepouzdano kada se kao medij pojavljuje mast i to zbog velikog rasipanja proradnih vrijednosti, kao i s velikom histerezom. On the other hand, the overpressure must not exceed certain limit values, so as not to endanger the seals. Over-the-counter pressure relief valves, such as those used for liquid and gas media, operate very unreliable when grease is used as the medium, due to the high dispersion of operating values, as well as high hysteresis.
Kod ležaja privodnih lopatica turbopumpi se pojavljuje slijedeći problem. U pogonu pumpe ili turbine, privodne lopatice kao i njihovi ležaji preuzimaju približno temperaturu pogonske vode. Kod vrste pogona s kompenzatorom reaktivne energije dolazi, uslijed ventilacijskih gubitaka rotora koji se okreće u zraku, do postepenog zagrijavanja turbopumpe koje na privodnim lopaticama može iznositi do ΔT=30K u odnosu na temperaturu dotoka pogonske vode. The following problem appears with the bearing of the turbopump inlet vanes. In a pump or turbine drive, the drive vanes as well as their bearings take on approximately the temperature of the drive water. In the type of drive with a reactive energy compensator, due to the ventilation losses of the rotor rotating in the air, there is a gradual heating of the turbopump, which on the drive vanes can be up to ΔT=30K in relation to the temperature of the drive water inflow.
Pošto mast za podmazivanje u odnosu na materijal rukavca ležaja i tuljca ležaja ima za oko 103 veće koeficijente rastezanja, kod zatvorenog volumena masti i gore navedenog povišenja temperature dolazi do znatnog povišenja tlaka masti. Ugrađeni pretlačni ventil se u tom slučaju otvara (s gore spomenutim netočnostima) i omogućava izlaženje masti, sve dok se ne postigne tlak zatvaranja ventila odn. dok mast izlazi preko brtve raspora ležaja. Taj proces se kod dužeg rada kompenzatora reaktivne energije može više puta ponoviti. Ako tada dođe do prijelaza sa pogona kompenzatora reaktivne energije na turbinski pogon, tada temperatura ležaja unutar nekoliko minuta pada na temperaturu pogonske vode. Uslijed pada temperature smanjuje se volumen preostale masti i raspor ležaja više nije potpuno ispunjen mašću. Ovaj efekt se pojačava time, što kod prijelaza s pogona kompenzatora reaktivne energije s niskim tlakom u turbopumpi na turbinski pogon s visokim tlakom u turbopumpi, uslijed elastičnog proširenja dijelova kućišta dolazi do aksijalnog pomaka donjeg rukavca ležaja privodne lopatice, a time i do povećanja volumena raspora za podmazivanje. Kod obratnog procesa se volumen raspora podmazivanja smanjuje. Gubitak masti nakon početka rada pretlačnog ventila odnosno uslijed izlaženja preko brtvi raspora ležaja se mora nadoknaditi odgovarajućim dopunjavanjem masti. Iz tog razloga dolazi kod višestrukih dnevnih prebacivanja pogona do veće potrošnje masti. Osim toga se mast koja izlazi i više se ne može upotrijebiti, mora ukloniti uz odgovarajući trošak. Since the lubricating grease has about 103 higher expansion coefficients compared to the material of the bearing sleeve and the bearing sleeve, with the closed volume of the grease and the above-mentioned temperature increase, there is a significant increase in the pressure of the grease. In this case, the built-in overpressure valve opens (with the above-mentioned inaccuracies) and allows the grease to escape, until the closing pressure of the valve is reached, or while grease escapes through the bearing gap seal. This process can be repeated several times during long-term operation of the reactive energy compensator. If then there is a transition from the reactive energy compensator drive to the turbine drive, then the bearing temperature drops to the operating water temperature within a few minutes. As the temperature drops, the volume of remaining grease decreases and the bearing gap is no longer completely filled with grease. This effect is enhanced by the fact that when switching from the reactive energy compensator drive with low pressure in the turbopump to the turbine drive with high pressure in the turbopump, due to the elastic expansion of the housing parts, there is an axial displacement of the lower sleeve of the drive vane bearing, and thus an increase in the gap volume. for lubrication. In the reverse process, the volume of the lubrication gap is reduced. The loss of grease after the start of the pressure valve operation, i.e. as a result of leakage through the bearing gap seals, must be compensated by adequate replenishment of grease. For this reason, multiple daily gear changes result in higher grease consumption. In addition, the grease that comes out and can no longer be used must be removed at an appropriate cost.
Zadatak ovog izuma je dobivanje uređaja za održavanje tlaka u kliznim ležajima privodnih lopatica turbopumpi koji su uz određeni pretlak podmazivani pomoću centralnog uređaja za podmazivanje, a koji su smješteni iznad i ispod prostrujnih kanala, kod kojeg uređaja pri promjenama tlaka u rasporu za podmazivanje, koje nisu regulirane već su uvjetovane vrstom pogona, ne dolazi do gubitka masti odnosno nije potrebno naknadno dopunjavanje, a istovremeno se pritisak u rasporu za podmazivanje održava u navedenim granicama. The task of this invention is to obtain a device for maintaining the pressure in the sliding bearings of the inlet vanes of turbopumps that are lubricated with a certain overpressure by means of a central lubrication device, and which are located above and below the flow channels, in which device, during pressure changes in the lubrication interval, which are not regulated are already conditioned by the type of drive, there is no loss of grease, i.e. no subsequent replenishment is necessary, and at the same time the pressure in the lubrication gap is maintained within the specified limits.
To se prema ovom izumu postiže tako, da se na svaku privodnu lopaticu u gornji i donji ležaj prema prostrujnom kanalu postave brtve koje djeluju u oba smjera, da se u provrt privodne lopatice u donjem ležaju ugradi dosjedni dio i jedan poklopac koji zatvara otvor i koji ima jedan aksijalni otvor, da se u rukavac donjeg ležaja na gornjem rubu izvede radijalni kanal od dosjednog dijela prema rasporu ležaja, a na donjem rubu radijalni kanal od raspora ležaja prema provrtu u poklopcu, da se u sredinu provrta privodne lopatice uvuče cijev koja prolazi do dosjednog dijela, a koju na čeonoj površini gornjeg ležaja drži odgovarajući priključak koji je u sredini izveden s aksijalnim otvorom i koji ima jedan aksijalni otvor koji nije u sredini, da je u rukavcu gornjeg ležaja na donjem rubu izveden radijalni kanal od provrta privodne lopatice do raspora ležaja, te da je na postojeći aksijalni provrt centralnog uređaja za podmazivanje, na postojeći aksijalni otvor u poklopcu turbine kao i na priključke spojena po jedna odbojna mazalica. According to this invention, this is achieved by placing seals that act in both directions on each drive vane in the upper and lower bearing towards the flow channel, by installing an adjacent part and a cover that closes the opening and in the bore of the drive vane in the lower bearing. it has one axial opening, to make a radial channel from the adjacent part towards the bearing gap in the sleeve of the lower bearing on the upper edge, and on the lower edge a radial channel from the bearing gap to the hole in the cover, so that a tube can be inserted into the middle of the hole of the drive vane that passes to of the adjacent part, which is held on the front surface of the upper bearing by a corresponding connection which is made with an axial opening in the middle and which has one axial opening which is not in the middle, that a radial channel is made in the sleeve of the upper bearing on the lower edge from the bore of the drive vane to the gap bearing, and that it is on the existing axial bore of the central lubrication device, on the existing axial opening in the turbine cover as well as on the Yesterday, one repulsor oiler was connected.
Odbojna mazalica se sastoji od cilindra podijeljenog na klipni i opružni dio, pri čemu u klipni dio dolazi klip, a u opružni dio dolazi opruga; stijenka cilindra je na strani klipa deblja nego na strani opruge, a klip ima manji promjer od tlačne opruge, pri čemu je između klipa i tlačne opruge ugrađena opružna (elastična) ploča; u stijenku klipnog dijela je postavljena odvodna cijev koja je povezana sa sabirnim spremnikom pričvršćenim na cilindar, a cilindar je na klipnoj strani zatvoren poklopcem a na strani opruge navojnom kapom; u poklopcu su izvedeni priključci za dovod od aksijalnog otvora odnosno za priključak kontrolnog manometra. The rebound greaser consists of a cylinder divided into a piston and a spring part, where the piston comes into the piston part, and the spring comes into the spring part; the cylinder wall is thicker on the piston side than on the spring side, and the piston has a smaller diameter than the compression spring, with a spring (elastic) plate installed between the piston and the compression spring; a drain pipe is placed in the wall of the piston part, which is connected to a collection tank attached to the cylinder, and the cylinder is closed on the piston side with a cover and on the spring side with a screw cap; in the cover, there are connections for the feed from the axial opening, that is, for the connection of the control pressure gauge.
U daljnjoj izvedbi je klip prema strani opruge opremljen rukavcem koji prima elastičnu ploču. Tlačnu oprugu na kraju opružnog dijela drži druga elastična ploča koja ulazi u kapu (poklopac). Nadalje je u klipu učvršćeno navojno vreteno koje prolazi sredinom opružnog dijela i završnog poklopca prema van i funkcionalno je povezano s graničnom sklopkom postavljenom na cilindru. In a further version, the piston towards the side of the spring is equipped with a sleeve that receives an elastic plate. The compression spring at the end of the spring part is held by another elastic plate that enters the cap (cover). Furthermore, a threaded spindle is fixed in the piston, which passes through the middle of the spring part and the end cap to the outside and is functionally connected to the limit switch placed on the cylinder.
Nadalje se izum pobliže objašnjava izvedbenim primjerima. Na slijedećim crtežima je prikazano: Furthermore, the invention is explained in more detail with practical examples. The following drawings show:
Sl.1: Privodna lopatica jedne turbopumpe s uležištenjem i sustavom podmazivanja u presjeku Fig. 1: Drive vane of one turbopump with bearing and lubrication system in section
Sl.2: Detalj gornjeg i donjeg ležaja jedne privodne lopatice u presjeku Fig. 2: Detail of the upper and lower bearing of one drive vane in section
Sl.3: Pogled s prednje strane na odbojnu mazalicu u polupresjeku Fig. 3: View from the front of the shock absorber in half section
Sl.4: Bočni pogled na odbojnu mazalicu Fig. 4: Side view of the repulsive oiler
Uređaj za održavanje tlaka se koristi na mašću podmazivanim kliznim ležajima privodne lopatice 1 turbopumpe, pri čemu su privodne lopatice 1 radijalno uležištene iznad i ispod prostrujnih kanala 4 u gornjem ležaju 2 i donjem ležaju 3. Dovod masti u klizni ležaj koji radi s određenim pretlakom se vrši preko centralnog uređaja za podmazivanje 16. Na svakoj privodnoj lopatici 1 su na gornjem ležaju 2 i donjem ležaju 3 prema prostrujnom kanalu 4 postavljene brtve 36, koje djeluju u oba smjera. Te brtve 36 su i kod viših tlakova nepropusne za mast u smjeru prostrujnog kanala 4 i vodonepropusne u smjeru ležaja. Kako bi se spriječilo izlaženje masti u atmosferu, u oba ležaja 2 i 3 su postavljene brtve 37 prikladne za više tlakove, koje djeluju u jednom smjeru. U otvor 5 privodne lopatice 1 u donjem ležaju 3 se postavlja dosjedni dio 6 i priključak 7 koji zatvara otvor 5 s aksijalnim otvorom 8. U rukavcu donjeg ležaja 3 je na gornjem rubu postavljen radijalni kanal 9 od dosjednog dijela 6 prema rasporu ležaja i na donjem rubu radijalni kanal 10 od raspora ležaja prema aksijalnom otvoru 8 u priključku 7. U rukavac gornjeg ležaja 2 je na donjem rubu izveden radijalni kanal 15 od otvora 5 privodne lopatice 1 do raspora ležaja. U sredinu otvora 5 privodne lopatice 1 je odozgo postavljena cijev 11, koja prolazi do dosjednog dijela 6, koju na čeonoj strani gornjeg ležaja 2 drži priključak 12. Promjer cijevi 11 je manji od otvora 5 u statorskoj lopatici 1. Zbog toga se na osovini privodnih lopatica stvaraju dva međusobno odvojena prostora. Priključak 12 je opremljen aksijalnim središnjim otvorom 13 i aksijalnim otvorom 14, koji nije u sredini. Na aksijalne otvore 13 i 14 se preko tlačnih vodova 38 i povratnih ventila 39 priključuje centralni uređaj za podmazivanje 16. Na aksijalni otvor 17 na poklopcu turbine kao i na priključak 7 se priključuje po jedna odbojna mazalica 18. Odbojna mazalica 18 se sastoji od cilindra 21 podijeljenog na klipnu stranu 19 i opružnu stranu 20. Klipna strana 19 prihvaća u izbrušeni i polirani otvor klip 22. Na opružnoj strani 20 je postavljena tlačna opruga 23. Stijenka cilindra klipne strane 19 je deblja od stijenke cilindra opružne strane 20. Klipni dio 19 se zatvara pomoću poklopca 27, pri čemu se između poklopca 27 i klipnog dijela 19 u prstenasti utor umeće gumena brtva 40. Klipni dio 19 je na suprotnoj strani od poklopca 27 opremljen vanjskim navojem 41. Na taj navoj 41 se navija opružni dio 20 cilindra 21 i pomoću zatika s navojem 42 osigurava od otpuštanja. U određenom razmaku od čeone površine klipnog dijela 19 izveden je u stijenci klipnog dijela 19 radijalni otvor 43, u koji se postavlja odvodna cijev 44. Odvodna cijev 44 je povezana sa sabirnim spremnikom 45 koji je s vanjske strane cilindra 21 pričvršćen preko elementa za prihvaćanje 46. Klip 22 ima manji promjer od tlačne opruge 23. Prema strani opruge 20 klip 22 ima rukavac 32, na koji se postavlja elastična ploča s prirubnicom. Tlačna opruga 23 se s jedne strane postavlja na prirubnicu elastične ploče 24 i na taj način vođen. Drugi kraj tlačne opruge 23 prihvaća druga elastična ploča 33 koja isto tako prema unutra služi kao vodilica opruge. Ta druga elastična ploča 33 dosjeda u završnu kapu 28. Okretanjem kape (poklopca) 28 postiže se prednaprezanje tlačne opruge 23. Za to služi šesterokutna prirubnica 47 koja se zavaruje na poklopac 28. Nakon podešavanja željenog prednaprezanja, poklopac 28 se osigurava od samootpuštanja pomoću vijka 48. Poklopac 27 ima osim četiri provrta za vijke 25 za pričvršćenje poklopca 27 još i dva provrta koji ulaze u radni prostor cilindra 26. U jedan provrt se postavlja priključak 29 za dovod od raspora za podmazivanje kliznog ležaja. Drugi otvor služi za montažu kontrolnog manometra 31 preko priključka 30. U klipu 22 je učvršćeno navojno vreteno 34, koje prolazi sredinom opružnog dijela 20 i završnog poklopca 28 i izlazi van, te ovisno o položaju klipa 22 aktivira graničnu sklopku 35 postavljenu na cilindru 21. Preko granične sklopke 35 se signalizira tlak koji je izvan prethodno određenog područja. Za ispravan rad odbojne mazalice 18 nije nužan neki posebni položaj za ugradnju. U prikazanom slučaju, na ležajima privodne lopatice 1 turbopumpe je ugradnja izvršena u vertikalnom položaju u blizini pojedinih ležaja privodne lopatice. U tu svrhu je na cilindar 21 postavljena pričvrsna prirubnica 49. Klip 22 se pomoću tlačne opruge 23 drži u svom krajnjem položaju. Elastična ploča 24 naliježe na stražnju stranu klipa 22 i na čeonu stranu klipnog dijela 19. Na taj je način moguće demontirati poklopac 27 kao i klip 22, a da se ne treba otpustiti tlačna opruga 23. The pressure maintenance device is used on the grease-lubricated sliding bearings of the drive blade 1 of the turbopump, where the drive blades 1 are radially positioned above and below the flow channels 4 in the upper bearing 2 and the lower bearing 3. The supply of grease to the sliding bearing, which operates with a certain overpressure, it is done through the central lubrication device 16. On each supply vane 1, on the upper bearing 2 and the lower bearing 3 towards the flow channel 4, seals 36 are placed, which act in both directions. Even at higher pressures, these seals 36 are impermeable to grease in the direction of the flow channel 4 and impermeable to water in the direction of the bearing. In order to prevent grease from escaping into the atmosphere, seals 37 suitable for higher pressures, which act in one direction, are installed in both bearings 2 and 3. In the opening 5 of the supply vane 1 in the lower bearing 3, the adjacent part 6 and the connection 7 are placed, which closes the opening 5 with the axial opening 8. In the sleeve of the lower bearing 3, a radial channel 9 is placed on the upper edge from the adjacent part 6 towards the gap of the bearing and on the lower edge radial channel 10 from the bearing gap towards the axial opening 8 in connection 7. In the sleeve of the upper bearing 2, on the lower edge, a radial channel 15 is made from the opening 5 of the supply vane 1 to the bearing gap. In the middle of the opening 5 of the drive vane 1, a tube 11 is placed from above, which passes to the adjacent part 6, which is held by the connection 12 on the front side of the upper bearing 2. The diameter of the tube 11 is smaller than the opening 5 in the stator vane 1. Therefore, on the shaft of the drive vanes the blades create two separate spaces. The connection 12 is equipped with an axial central opening 13 and an axial opening 14, which is not in the middle. The central lubrication device 16 is connected to the axial openings 13 and 14 via pressure lines 38 and check valves 39. One repulsor oiler 18 is connected to the axial opening 17 on the turbine cover as well as to port 7. The repulsor oiler 18 consists of a cylinder 21 divided into a piston side 19 and a spring side 20. The piston side 19 accepts a piston 22 in a ground and polished opening. A compression spring 23 is placed on the spring side 20. The cylinder wall of the piston side 19 is thicker than the cylinder wall of the spring side 20. The piston part 19 is is closed by means of a cover 27, whereby a rubber gasket 40 is inserted between the cover 27 and the piston part 19 in the annular groove. The piston part 19 is equipped with an external thread 41 on the opposite side of the cover 27. The spring part 20 of the cylinder 21 is wound onto this thread 41 and by means of a threaded pin 42 it is secured against loosening. At a certain distance from the front surface of the piston part 19, a radial opening 43 is made in the wall of the piston part 19, into which the drainage pipe 44 is placed. The piston 22 has a smaller diameter than the compression spring 23. Towards the side of the spring 20, the piston 22 has a sleeve 32, on which an elastic plate with a flange is placed. The compression spring 23 is placed on one side on the flange of the elastic plate 24 and thus guided. The other end of the compression spring 23 receives another elastic plate 33 which also serves as a spring guide inwards. This second elastic plate 33 fits into the end cap 28. By turning the cap (lid) 28, the preload of the compression spring 23 is achieved. For this, the hexagonal flange 47 is used, which is welded to the cover 28. After setting the desired preload, the cover 28 is secured against self-release by means of a screw 48. The cover 27 has, in addition to four holes for screws 25 for fastening the cover 27, two more holes that enter the working space of the cylinder 26. In one hole, a connection 29 is placed for the supply from the gap for lubrication of the sliding bearing. The second opening serves for the mounting of the control manometer 31 via the connection 30. The threaded spindle 34 is fixed in the piston 22, which passes through the middle of the spring part 20 and the end cap 28 and goes out, and depending on the position of the piston 22 activates the limit switch 35 placed on the cylinder 21. The limit switch 35 signals a pressure that is outside the previously determined range. No special installation position is necessary for the proper operation of the shock absorber 18. In the case shown, on the bearings of the drive blade 1 of the turbopump, installation was carried out in a vertical position near the individual bearings of the drive blade. For this purpose, a fastening flange 49 is placed on the cylinder 21. The piston 22 is held in its end position by means of a compression spring 23. The elastic plate 24 rests on the back side of the piston 22 and on the front side of the piston part 19. In this way, it is possible to dismantle the cover 27 as well as the piston 22, without having to release the pressure spring 23.
Potrebna mast se od centralnog uređaja za podmazivanje 16 dovodi preko otvora 13 i cijevi 11 do rukavca donjeg ležaja 3. Pri tome mast ulazi na gornjem rubu preko radijalnog kanala 9 u raspor ležaja, preko jednog prstenastog kanala i više utora za podmazivanje prvo puni raspor ležaja, a tada donji radijalni kanal 10 do otvora 8 u priključku 7. Raspor u gornjem ležaju 2 se puni preko ekscentrično izvedenog provrta 14 u priključku 12, preostalog prstenastog prostora u provrtu 5 privodne lopatice 1 i radijalnog kanala 15. Preko odgovarajućeg prstenastog kanala i više utora za podmazivanje puni se sve do gornjeg ruba kompletan raspor ležaja uključujući i provrt 17 u turbinskom poklopcu. The necessary grease is supplied from the central lubrication device 16 through the opening 13 and the pipe 11 to the sleeve of the lower bearing 3. At the same time, the grease enters the bearing gap at the upper edge through the radial channel 9, through one annular channel and several lubrication grooves it first fills the bearing gap , and then the lower radial channel 10 to the opening 8 in the connection 7. The gap in the upper bearing 2 is filled through the eccentric bore 14 in the connection 12, the remaining annular space in the hole 5 of the supply vane 1 and the radial channel 15. Through the corresponding annular channel and more of the lubrication groove is filled up to the upper edge of the entire bearing gap, including bore 17 in the turbine cover.
Kod povišenja tlaka masti u gornjem i/ili donjem rasporu ležaja, taj tlak djeluje preko priključka 22 na klip 12 odgovarajuće odbojne mazalice 18. Ako umnožak površine klipa s tlakom masti bude veći od sile prednaprezanja tlačne opruge 23, tada se klip 22 pokreće uz povećavanje sile opruge prema tlačnoj opruzi 23, dok se ne postigne ravnotežno stanje. Pri tome u radni prostor cilindra 26 utječe količina masti koja je proporcionalna putu klipa u radnom prostoru cilindra 26. Ako klip 22 u toku svog kretanja oslobodi radijalni provrt 43, tada mast preko odvodne cijevi 44 ulazi u sabirni spremnik 45. Na taj način se ograničava porast tlaka u rasporu ležaja. When the grease pressure increases in the upper and/or lower gap of the bearing, this pressure acts via connection 22 on the piston 12 of the corresponding lubricator 18. If the product of the area of the piston with the grease pressure is greater than the preload force of the pressure spring 23, then the piston 22 moves with increasing spring forces towards compression spring 23, until the equilibrium state is reached. At the same time, an amount of grease that is proportional to the path of the piston in the working space of the cylinder 26 enters the working space of the cylinder 26. If the piston 22 releases the radial bore 43 during its movement, then the grease enters the collection tank 45 via the drain pipe 44. In this way, it is limited pressure increase in the bearing gap.
Promjer klipa 22 kao i njegov hod do oslobađanja radijalnog otvora 43, te dimenzije tlačne opruge 23 uključujući konstante te opruge, moraju se odrediti prema volumenu masti koji se kompenzira i prema graničnim tlakovima masti u rasporu ležaja koje treba održavati. Ako se tlak u rasporu ležaja smanji, tada tlačna opruga 23 preko klipa 22 potiskuje akumuliranu mast u natrag u raspor ležaja. The diameter of the piston 22, as well as its stroke until the release of the radial opening 43, and the dimensions of the pressure spring 23, including the spring constants, must be determined according to the volume of grease to be compensated and according to the limit pressures of the grease in the bearing gap to be maintained. If the pressure in the bearing gap decreases, then the pressure spring 23 via the piston 22 pushes the accumulated grease back into the bearing gap.
Pomoću ovog izuma postižu se slijedeće prednosti: This invention achieves the following advantages:
- klizni ležaj je stalno ispunjen mašću - the sliding bearing is constantly filled with grease
- punjenje masti se održava unutar određenog područja tlaka - grease filling is maintained within a certain pressure range
- punjenje mašću pod stalnim pretlakom dovodi do velikog prigušivanja vibracija u ležajima privodnih lopatica - filling with grease under constant overpressure leads to a large damping of vibrations in the bearings of the drive vanes
- veliko prigušivanje vibracija smanjuje habanje i produžava vijek trajanja ležaja privodne lopatice - high vibration damping reduces wear and extends the service life of the drive vane bearing
- signalizacijom preko granične sklopke i odgovarajućim ožičenjem moguća je stalna kontrola s jednog centralnog mjesta - constant control from one central location is possible through signaling via a limit switch and appropriate wiring
- pomoću signalizacije se može automatski upravljati dovođenjem svježe masti - the supply of fresh grease can be automatically controlled using signaling
- stara mast koja izlazi se sakuplja - the old fat that comes out is collected
- količina masti se može svesti na najmanju mjeru bez ograničavanja funkcioniranja ležaja - the amount of grease can be reduced to a minimum without limiting the functionality of the bearing
- nema zagađivanja okoline uslijed izlaženja masti iz ležaja - there is no pollution of the environment due to the release of grease from the bearing
Claims (6)
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4403786A DE4403786C2 (en) | 1994-02-03 | 1994-02-03 | Arrangement for maintaining pressure in the guide vane bearings of pump turbines |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| HRP950029A2 true HRP950029A2 (en) | 1997-02-28 |
Family
ID=6509684
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| HRP4403786.4A HRP950029A2 (en) | 1994-02-03 | 1995-01-20 | Apparatus for the pressure maintenance in guide vane bearings of pump turbines |
Country Status (3)
| Country | Link |
|---|---|
| DE (1) | DE4403786C2 (en) |
| HR (1) | HRP950029A2 (en) |
| WO (1) | WO1995021325A1 (en) |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1341866A (en) * | 1919-03-10 | 1920-06-01 | Taylor Harvey Birchard | System of lubrication |
| CH454628A (en) * | 1966-03-24 | 1968-04-15 | Sulzer Ag | Method for starting up a pump or pump turbine of radial design in a storage power plant |
| US4094293A (en) * | 1976-04-16 | 1978-06-13 | Evans John W | Engine preoiler and lubricant reservoir |
| DE3415076C1 (en) * | 1984-04-21 | 1985-11-07 | Deutsche Tecalemit Gmbh, 4800 Bielefeld | Central lubrication device |
| US5147014A (en) * | 1991-07-09 | 1992-09-15 | Pederson Walter H | Lubricating system for an engine prior to start-up |
-
1994
- 1994-02-03 DE DE4403786A patent/DE4403786C2/en not_active Expired - Lifetime
-
1995
- 1995-01-20 HR HRP4403786.4A patent/HRP950029A2/en not_active Application Discontinuation
- 1995-01-30 WO PCT/EP1995/000304 patent/WO1995021325A1/en active Application Filing
Also Published As
| Publication number | Publication date |
|---|---|
| WO1995021325A1 (en) | 1995-08-10 |
| DE4403786C2 (en) | 1997-05-22 |
| DE4403786A1 (en) | 1995-08-10 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4390322A (en) | Lubrication and sealing of a free floating piston of hydraulically driven gas compressor | |
| US4390082A (en) | Reserve lubricant supply system | |
| EP0775264B1 (en) | Purifying apparatus in a fluid-operating system | |
| US4782919A (en) | Supply system for oil dampers | |
| US6468028B1 (en) | Vertical pump with oil lubricant; C-seal for pump; and pump with threaded shaft position adjustment | |
| KR100606994B1 (en) | A screw compressor injected with water | |
| US9404494B2 (en) | Screw pump having an integrated pressure limiting valve | |
| DE2443204A1 (en) | TURBINE BEARING | |
| JP4310062B2 (en) | Variable speed fluid coupling | |
| CZ20021454A3 (en) | Device for compensation of axial shift in turbine machines | |
| US3960245A (en) | Lubricating and sealing liquid for a high pressure compressor | |
| HRP950029A2 (en) | Apparatus for the pressure maintenance in guide vane bearings of pump turbines | |
| US2130583A (en) | Pump lubricator | |
| US4383804A (en) | Lubrication and sealing of a free floating piston of hydraulically driven gas compressor | |
| US4277221A (en) | Wicket gate bearing seal | |
| US5984315A (en) | Reclamation system for a hydraulic pump system | |
| CN221032793U (en) | Lubricating oil pressure regulating device for marine diesel engine | |
| KR20120081818A (en) | Hydraulic shock absorbing tilting disc check valve | |
| JPS62131979A (en) | Water turbine | |
| JP2022520146A (en) | Civil engineering machines, especially slurry wall cutters | |
| CN213393483U (en) | Rolling mill gear box pressure regulating device | |
| CN213145134U (en) | Bearing box with exhaust and oil spilling device | |
| CN111561580A (en) | Axial flow control valve | |
| US3187839A (en) | Pump actuators counterbalance assemblies | |
| RU186946U1 (en) | Device for controlling the flow rate of the working fluid of a heat engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A1OB | Publication of a patent application | ||
| ODBC | Application rejected |