NO129644B - - Google Patents
Download PDFInfo
- Publication number
- NO129644B NO129644B NO220171A NO220171A NO129644B NO 129644 B NO129644 B NO 129644B NO 220171 A NO220171 A NO 220171A NO 220171 A NO220171 A NO 220171A NO 129644 B NO129644 B NO 129644B
- Authority
- NO
- Norway
- Prior art keywords
- pockets
- load
- pump
- pressure
- bearing
- Prior art date
Links
- 239000012530 fluid Substances 0.000 claims description 26
- 230000002706 hydrostatic effect Effects 0.000 claims description 10
- 238000006073 displacement reaction Methods 0.000 claims description 7
- 238000011144 upstream manufacturing Methods 0.000 claims 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
- F16C32/0644—Details of devices to control the supply of liquids to the bearings
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0681—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load
- F16C32/0692—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load for axial load only
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
- Rotary Pumps (AREA)
Description
Trykkfordelingsanordning ved et hydrostatisk lager. Pressure distribution device at a hydrostatic bearing.
Den foreliggende oppfinnelse vedrører hydrostatiske lagre av det slag der et flertall lommer er anordnet i lagerflaten mellom to lagerkomponenter og forsynes med trykkfluidum fra en felles pumpe idet et til pumpens trykkledning tilsluttet apparat er innrettet til å opprettholde forutbestemte forhold mellom de til de forskjellige lommer leverte trykkfluidumstrømmer. The present invention relates to hydrostatic bearings of the kind where a plurality of pockets are arranged in the bearing surface between two bearing components and are supplied with pressure fluid from a common pump, as a device connected to the pump's pressure line is arranged to maintain predetermined conditions between the pressure fluid flows delivered to the various pockets .
Det er tidligere kjent ved lagre av ovennevnte type hvor det fordres stor nøyaktighet, å ordne det slik at hver lomme mates med trykkfluidum fra en egen pumpe. Dette er naturligvis kost-bart og krever en komplisert ledningsføring. En kan mate samtlige eller en gruppe lommer fra en og samme pumpe men ved en eventuell forskyvning i lagerflaten kan det inntreffe at den spalte som bestem-mer den naturlige utlekking av trykkfMdum endres påtagelig og^.at en uventet stor mengde trykkfluidum strømmer ut gjennom noen av lommene. Ettersom flere andre lommer er tilsluttet samme pumpe kan hele<;>lager-ets funksjon forstyrres ettersom fluidumtrykket i selve lageret kan komme til å synke altfor meget......... It is previously known for bearings of the above-mentioned type where great accuracy is required, to arrange it so that each pocket is fed with pressure fluid from a separate pump. This is of course expensive and requires complicated wiring. All or a group of pockets can be fed from one and the same pump, but in the event of a possible displacement in the bearing surface, it can happen that the gap that determines the natural leakage of pressure fluid changes significantly and that an unexpectedly large amount of pressure fluid flows out through some of the pockets. As several other pockets are connected to the same pump, the entire<;>bearing's function can be disrupted as the fluid pressure in the bearing itself can drop far too much.........
En mulighet for. å unngå denne ulempe oppnås slik som-innledningsvis nevnt, ved at det i pumpens trykkledning er innkoplet et apparat for opprettholdelse av et forutbestemt forhold mellom de til de forskjellige lommer leverte trykkfluidumstrømmer. An opportunity for. avoiding this disadvantage is achieved, as mentioned at the outset, in that a device is connected to the pump's pressure line for maintaining a predetermined ratio between the pressure fluid flows delivered to the various pockets.
U.S.-patent 2.938.756 viser en anordning ved hydrostatiske lager hvorved det oppnås opprettholdelse av nevnte forutbestemte forhold mellom de til de forskjellige lommer leverte trykkfluidum-strømmer. Dette er oppnådd ved at det i tilførselsledningen for hver lagerlomme er anordnet en strømningsstyreventil som omfatter kapilære strupninger. Ulempen ved en slik'anordning er at den sentrale pumpe må dimensjoneres med hensyn til trykkfallet i strupningene og tenkbart maksimalt trykk i.en lagerlomme. Disse strupninger medfører effekttap og trykket i en enkel lagerlomme kan til sine tider øke betraktelig ' utover middeltrykket hvorfor pumpen må overdimensjoneres i forhold til det teoretisk nødvendige med hensyntagen kun til den gjennomsnitt-lige trykkoppbygning i lagerlommene. U.S. patent 2,938,756 shows a device for hydrostatic bearings by which maintenance of said predetermined ratio is achieved between the pressure fluid flows delivered to the various pockets. This has been achieved by a flow control valve comprising capillary chokes being arranged in the supply line for each storage pocket. The disadvantage of such an arrangement is that the central pump must be dimensioned with regard to the pressure drop in the chokes and conceivable maximum pressure in a storage pocket. These bottlenecks cause a loss of power and the pressure in a simple bearing pocket can at times increase considerably above the average pressure, which is why the pump must be over-dimensioned in relation to what is theoretically necessary, taking into account only the average pressure build-up in the bearing pockets.
I det hydrostatiske lager ifølge den foreliggende oppfinnelse behøver pumpen kun dimensjoneres etter det gjennomsnittlig nød-vendige trykk i lagerlommene med hensyn til maksimal lasteopptagnings-evne og dette oppnås ifølge oppfinnelsen ved at det innledningsvis nevnte apparat som er tilsluttet pumpens trykkledning, omfatter et antall som positive deplasementspumper -hensiktsmessige tannhjulspumper- utformede doseringsenheter sammenkoplet med en felles aksel og til hvilke tilførselsledningene til lommene er tilsluttet, og at doseringsenhetene drives av det av pumpen leverte fluidum. In the hydrostatic bearing according to the present invention, the pump only needs to be dimensioned according to the average necessary pressure in the bearing pockets with regard to maximum load absorption capacity, and this is achieved according to the invention by the initially mentioned device which is connected to the pump's pressure line, comprising a number of positive displacement pumps -proper gear pumps- designed dosing units connected by a common shaft and to which the supply lines to the pockets are connected, and that the dosing units are driven by the fluid supplied by the pump.
Ved en skråstilling av den lagrede aksel kommer lagerspal-ten ved noen lagerlommer til å minske og ved andre lommer til å øke. When the bearing shaft is tilted, the bearing gap will decrease in some bearing pockets and increase in other pockets.
I de lommer der spalten øker kommer fluidumstrykket nedstrøms i forhold til de respektive deplasementspumper, til å synke men da de nevnte pumper ar mekanisk sammenkoplet slik åt de til enhver tid leverer like store fluidummengder, vil de ikke tillate at mer fluidum passerer ut gjennom den eller de lommer der spalten øker enn gjennom den eller de lommer hvor spalten minskes hvorved det oppstår et øket fluidumtrykk i' de' sistnevnte lommer hvor spalten minskes hvilket vil bevirke sentrering åv'lagerkdmpbnentene. In the pockets where the gap increases, the fluid pressure downstream in relation to the respective displacement pumps will decrease, but as the aforementioned pumps are mechanically linked so that they deliver equal amounts of fluid at all times, they will not allow more fluid to pass out through it or the pockets where the gap increases than through the pocket(s) where the gap is reduced, whereby an increased fluid pressure occurs in the latter pockets where the gap is reduced, which will cause centering of the bearing components.
'Den sentrale pumpe'behøver således kun dimensjoneres med hensyn til den tenkte maksimale last som skal opptas av hele lageret og det behøver ikke' tas hensyn til innvirkning av eventuelt skråstilling av akselen, dvs. variasjoner i spaltehøyden ved de respektive lagerlommer. The 'central pump' thus only needs to be dimensioned with regard to the intended maximum load to be taken up by the entire bearing and there is no need to take into account the effect of any tilting of the shaft, i.e. variations in the gap height at the respective bearing pockets.
Oppfinnelsen vil bli nærmere béskrevet i det etterføl-gende med henvisning til tegningen som viser tp utførelseseksempler av oppfinnelsen for bærelagre som er forsynt med fire lommer i la-gérflaten. De karakteristiské trekk vil forøvrig fremgå av de etter-følgende krav. The invention will be described in more detail in what follows with reference to the drawing which shows exemplary embodiments of the invention for bearings which are provided with four pockets in the bearing surface. The characteristic features will also be apparent from the following requirements.
På tegningen viser The drawing shows
'fig.l et aksialsnitt av et hydrostatisk lager med trykkfdrdelingsapparat tilsluttet trykkiedningen' fra den sentrale pumpe og 'fig.l an axial section of a hydrostatic bearing with a pressure distribution device connected to the pressure chain' from the central pump and
fig. 2 viser den faste lagerdel i planriss og med en modifikasjon ved trykkfluidumtilførselsledningene til lommene. fig. 2 shows the fixed bearing part in plan view and with a modification at the pressure fluid supply lines to the pockets.
Det i fig.l viste lager er innrettet til å bære en kom-ponent som støttes av en aksel 10 og lageret består av en med akselen forenet, roterende del 11 som samvirker med en fast lagerskål 12. I lagerflaten mellom disse deler er det anordnet fire stykker lommer 13,1^,15 og 16. Den siste er anordnet sentralt under del.11 mens de tre førstnevnte lommer som hver og en ér bueformet, er anordnet i en ring som konsentrisk omslutter den sentrale lomme 16. 'TrykkfMdum tilføres lageret ved hjelp av et pumpean-legg omfattende en første pumpeenhet 17 cg en motor 18 som driver denne, såmt en reservepumpe 19 og tilhørende moto.r 20. Trykkledningene fra begge disse pumper er forsynt med de nødvendige ventiler og er . tilsluttet en felles utgående trykkledning 21. Lageret er i foreliggende tilfelle beregnet til å arbeide med fluidum med trykk på 100 ato og i systemet inngår en akkumulator 22 som har tilstrekkelig kapasi-tet til å holde systemet under trykk i et kortere tidsintervall ifall den i øyeblikket virksomme pumpe skulle fållé ut. I trykkiedningen fra hver pumpe finnes en trykkovervåkning 23 som automatisk kopler inn den ikke arbeidende pumpe hvis trykket i systemet ved svikt av den arbeidende pumpe, skulle begynne å synke. The bearing shown in fig.l is designed to carry a component which is supported by an axle 10 and the bearing consists of a rotating part 11 united to the axle which cooperates with a fixed bearing cup 12. In the bearing surface between these parts there is arranged four pieces of pockets 13, 1^, 15 and 16. The last one is arranged centrally under part 11, while the three first-mentioned pockets, each of which is arc-shaped, are arranged in a ring which concentrically surrounds the central pocket 16. Pressure is supplied to the bearing by means of a pump system comprising a first pump unit 17 and a motor 18 which drives this, as well as a reserve pump 19 and associated motor 20. The pressure lines from both of these pumps are provided with the necessary valves and are . connected to a common outgoing pressure line 21. In the present case, the bearing is designed to work with fluid with a pressure of 100 ato and the system includes an accumulator 22 which has sufficient capacity to keep the system under pressure for a shorter time interval if at the moment working pump should fail. In the pressure chain from each pump there is a pressure monitor 23 which automatically switches on the non-working pump if the pressure in the system should start to drop due to failure of the working pump.
I trykkiedningen 21 er det innkoplet et fordelingsappa-rat for styring av trykkstrømmene til lommene 13,14,15. Dette apparat består av et antall som positive deplacementspumper, i dette tilfelle tannhjulspumper, utformede doseringsenheter 24,25,26 hvis aksler kan være sammenkoplet.. Enheten 24 står gjennom, en ledning 27 i forbindelse med lommen 13, enheten 26 står via en ledning 28 i forbindelse med lommen 14, og enheten 25 står via en ledning 29 i forbindelse med den i det her viste snitt ikke fremkommende, tredje lomme 15. Doseringsenhetene drives av det fluidum som leveres fra pumpen og kommer således til å avgi en bestemt mengde til hver og en av ledningene 27-29. Hvis nu ved en tilfeldig sideforskyvning av lageret, spalten ved den ene av lommene skulle økes, så minskes motstanden og fluidumet skulle få en tendens til å strømme ut gjennom denne lomme. Ved den her viste fordelingsanordning kommer imidlertid, alle måleenheter til å rotere med samme omdreiningstall og kommer således ikke til å tillate at mer fluidum passerer ut gjennom den tilfeldigvis mer åpne ledning enn gjennom de to andre. A distribution device is connected to the pressure chain 21 for controlling the pressure flows to the pockets 13,14,15. This apparatus consists of a number of positive displacement pumps, in this case gear pumps, designed dosing units 24,25,26 whose shafts can be interconnected. The unit 24 stands through, a line 27 in connection with the pocket 13, the unit 26 stands via a line 28 in connection with the pocket 14, and the unit 25 is connected via a line 29 to the third pocket 15, which does not appear in the section shown here. The dosing units are powered by the fluid delivered from the pump and will thus deliver a specific amount to each and one of the wires 27-29. If now, by a random lateral displacement of the bearing, the gap at one of the pockets should be increased, then the resistance would decrease and the fluid would tend to flow out through this pocket. With the distribution device shown here, however, all measuring units will rotate at the same number of revolutions and will thus not allow more fluid to pass out through the accidentally more open line than through the other two.
Den sentrale lomme 16 tilføres her fluidum gjennom en ledning 30 direkte fra trykkiedningen 21. I. ledningen 30 er det anordnet et strupeorgan 31 som uavhengig av fordelingsanordningens til-feldige arbeidsforhold regulerer strømningen gjennom den sentrale lomme. The central pocket 16 is here supplied with fluid through a line 30 directly from the pressure chain 21. In the line 30, there is arranged a throttle 31 which, regardless of the distribution device's random working conditions, regulates the flow through the central pocket.
Den i fig.2 viste utførdisesf orm stemmer overens i alt vesentlig med den som er vist i fig.l. Den faste lagerdel 12 vises her i planriss og av denne fremgår, at i dette tilfelle er ledningen 30 til den sentrale lomme 16 koplet sammen med ledningen 29 til den bueformede lomme 15. Den sentrale lomme tar opp en vesentlig del av den aksielle belastning og dens arbeidsforhold påvirkes ikke så meget av en eventuell sideforskyvning av akselen. Det er under alle forhold snakk om kun en meget ubetydelig stillingsforandring og i mange til-feller kan en lette ledningsføringen ved å sammenkople den sentrale lomme med den ene av de bueformede lommer. The embodiment shown in fig. 2 corresponds essentially to that shown in fig. 1. The fixed bearing part 12 is shown here in a plan view and from this it appears that in this case the line 30 to the central pocket 16 is connected together with the line 29 to the arc-shaped pocket 15. The central pocket takes up a significant part of the axial load and its working conditions are not affected so much by any lateral displacement of the axle. Under all circumstances, there is only a very insignificant change in position and in many cases the wiring can be facilitated by connecting the central pocket with one of the arc-shaped pockets.
Istedetfor tannhjulspumper kan det anvendes ringpumper eller skruepumper, og det-er naturligvis i og for seg ikke nødvendig at doseringsenhetene innbyrdes er like store men at de alt etter behov ved de forskjellige lommer, utformes til å mate frem en mengde som er tilpasset den tilhørende lommes behov. Instead of gear pumps, ring pumps or screw pumps can be used, and it is naturally not necessary in and of itself that the dosing units are mutually the same size, but that they, depending on the needs of the different pockets, are designed to feed forward an amount that is adapted to the corresponding pocket need.
Claims (5)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE815870A SE340200B (en) | 1970-06-12 | 1970-06-12 |
Publications (1)
Publication Number | Publication Date |
---|---|
NO129644B true NO129644B (en) | 1974-05-06 |
Family
ID=20273309
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
NO220171A NO129644B (en) | 1970-06-12 | 1971-06-10 |
Country Status (11)
Country | Link |
---|---|
JP (1) | JPS5421503B1 (en) |
AT (1) | AT309158B (en) |
CA (1) | CA932366A (en) |
CS (1) | CS157714B2 (en) |
DE (1) | DE2127478A1 (en) |
FI (1) | FI52395C (en) |
FR (1) | FR2096278A5 (en) |
GB (1) | GB1309518A (en) |
NL (1) | NL7108074A (en) |
NO (1) | NO129644B (en) |
SE (1) | SE340200B (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
SE416075B (en) * | 1977-09-01 | 1980-11-24 | Skf Ab | DEVICE FOR MAINTENANCE OF REQUIRED LIQUID PRINTING IN A HYDROSTATIC STOCK |
US4194796A (en) * | 1978-09-05 | 1980-03-25 | Aktiebolaget Skf | Device for maintaining a required liquid pressure in a hydrostatic bearing |
DE102008003297A1 (en) * | 2008-01-05 | 2009-07-23 | Khs Ag | Apparatus for treating containers and method for operating such a device |
TWI538852B (en) | 2011-07-19 | 2016-06-21 | 季航空股份有限公司 | Personal aircraft |
CN103742534A (en) * | 2013-12-04 | 2014-04-23 | 镇江新区汇达机电科技有限公司 | Oil-injection-type radial bearing |
CN109595264B (en) * | 2018-12-26 | 2020-07-28 | 中国航空工业集团公司北京航空精密机械研究所 | Cooling mechanism of hydrostatic bearing |
-
1970
- 1970-06-12 SE SE815870A patent/SE340200B/xx unknown
-
1971
- 1971-06-03 DE DE19712127478 patent/DE2127478A1/en active Pending
- 1971-06-04 CA CA114810A patent/CA932366A/en not_active Expired
- 1971-06-10 NO NO220171A patent/NO129644B/no unknown
- 1971-06-11 GB GB2756671A patent/GB1309518A/en not_active Expired
- 1971-06-11 FI FI165371A patent/FI52395C/en active
- 1971-06-11 JP JP4109771A patent/JPS5421503B1/ja active Pending
- 1971-06-11 FR FR7121394A patent/FR2096278A5/fr not_active Expired
- 1971-06-11 NL NL7108074A patent/NL7108074A/xx unknown
- 1971-06-11 CS CS432971A patent/CS157714B2/cs unknown
- 1971-06-14 AT AT513471A patent/AT309158B/en not_active IP Right Cessation
Also Published As
Publication number | Publication date |
---|---|
GB1309518A (en) | 1973-03-14 |
CS157714B2 (en) | 1974-09-16 |
NL7108074A (en) | 1971-12-14 |
FR2096278A5 (en) | 1972-02-11 |
FI52395C (en) | 1977-08-10 |
FI52395B (en) | 1977-05-02 |
SE340200B (en) | 1971-11-08 |
JPS5421503B1 (en) | 1979-07-31 |
CA932366A (en) | 1973-08-21 |
AT309158B (en) | 1973-08-10 |
DE2127478A1 (en) | 1971-12-16 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
NO129644B (en) | ||
US2643516A (en) | Fluid pressure system | |
NO119561B (en) | ||
CN101155722A (en) | Electro-hydraulic steering control system | |
TW428067B (en) | Control system for multi-pump operation | |
US2408851A (en) | Pump | |
US2532856A (en) | Liquid feeding system | |
US3753604A (en) | Pressure fluid distributor at an hydrostatic bearing | |
US2479759A (en) | Apparatus for the treatment of webs or fleeces | |
US5308298A (en) | Hydraulic control systems | |
US3374863A (en) | Automatic high pressure lubrication system for rotary grinding mills | |
US4194796A (en) | Device for maintaining a required liquid pressure in a hydrostatic bearing | |
US11834972B2 (en) | Turbomachinery lubrication system improvement gravity rundown tanks | |
US3039266A (en) | Flow divider system | |
NO146407B (en) | DEVICE FOR MAINTENANCE OF A NECESSARY LIQUID PRESSURE IN A HYDROSTATIC STOCK | |
JPS60237946A (en) | Control apparatus of pressure applied to roll bearing of chocolate refining machine | |
US2505887A (en) | Control for fluid-pressure actuated devices | |
US3064759A (en) | Two-fluid signaling lubricating system | |
US3073253A (en) | Lubrication system | |
US2914908A (en) | Shaft revolving apparatus, particularly for turbine generators | |
US1200408A (en) | Accumulator. | |
US3423938A (en) | Hydropneumatic drive and hydraulic pressure control device for the journals of rolls' necks in chocolate milling and refining machines | |
US3293898A (en) | Auxiliary drive system for steel rolling mills | |
US3540783A (en) | Hydrostatic bearing system | |
JP3566781B2 (en) | Vertical shaft submersible pump device for liquefied gas tank |