SE508141C2 - Hydraulic axial bearing for a radially stored shaft - Google Patents

Hydraulic axial bearing for a radially stored shaft

Info

Publication number
SE508141C2
SE508141C2 SE9500424A SE9500424A SE508141C2 SE 508141 C2 SE508141 C2 SE 508141C2 SE 9500424 A SE9500424 A SE 9500424A SE 9500424 A SE9500424 A SE 9500424A SE 508141 C2 SE508141 C2 SE 508141C2
Authority
SE
Sweden
Prior art keywords
pressure
hydraulic
shaft
thrust bearing
sealing ring
Prior art date
Application number
SE9500424A
Other languages
Swedish (sv)
Other versions
SE9500424D0 (en
SE9500424L (en
Inventor
Thomas Arvidsson
Original Assignee
Sprout Bauer Inc Andritz
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 Sprout Bauer Inc Andritz filed Critical Sprout Bauer Inc Andritz
Priority to SE9500424A priority Critical patent/SE508141C2/en
Publication of SE9500424D0 publication Critical patent/SE9500424D0/en
Priority to EP96908455A priority patent/EP0808427A4/en
Priority to PCT/US1996/001435 priority patent/WO1996024777A1/en
Priority to CA002212433A priority patent/CA2212433C/en
Priority to US08/894,029 priority patent/US6082901A/en
Publication of SE9500424L publication Critical patent/SE9500424L/en
Priority to NO973491A priority patent/NO973491D0/en
Priority to FI973250A priority patent/FI973250A0/en
Publication of SE508141C2 publication Critical patent/SE508141C2/en

Links

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
    • F16C32/0681—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
    • 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/02—Sliding-contact bearings
    • F16C23/04—Sliding-contact bearings self-adjusting
    • 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
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • 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
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/02—Sliding-contact bearings
    • F16C25/04—Sliding-contact bearings self-adjusting
    • 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
    • F16C32/0696—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load for both radial and axial load

Abstract

A hydraulic axial bearing for a radially-mounted axle (1), which has a flange (1a) incorporating an outer, substantially axial sealing gap (7) formed between the flange and a sealing ring (3), and an inner, substantially radial sealing gap (9), formed between the axle and a sealing ring (5a) confined in the bearing housing (5). A hydraulic pressure medium is supplied, through the line (D) to the cavity (11) formed between the sealing gaps, whereupon the medium is evacuated through the gaps, under a considerable drop in pressure, to absorb axial loadings applied to the axle. The outer axial gap can be controlled by an additional pressure medium that is supplied to the pressure chamber (5b) via the line (D). This permits the pressure in the cavity (11) and consequently the axial loadings absorbed, to be regulated.

Description

508 141 2 Fördelama gentemot systemen i tidigare nämnda publikationer år uppenbara för fackmannen, b1.a.: - En axiell tätspalt blir till sldllnad från två okånslig för utböjningar och värmeutvidgningar i fläns och lager. 508 141 2 The advantages over the systems in the previously mentioned publications are obvious to the person skilled in the art, i.a.

- Tilliörsel av tryckmedium till hålrummen mellan tâtspaltema behöver ej ske genom lagret.- Supply of pressure medium to the cavities between the sealing gaps does not have to take place through the bearing.

- Den yttre tâtningsringen har låg massa och därmed tröghet och följer däriör flänsens vibrationer lättare.- The outer sealing ring has low mass and thus inertia and follows the vibrations of the shaft more easily.

- En inre radiell spalt ger större utnyttjad hydraularea, vilket ger högre last- kapacitet.- An internal radial gap provides greater utilized hydraulic area, which results in higher load capacity.

- Lägre energiförbrukning, eftersom den inre spalten ligger närmare centrum- linjen.- Lower energy consumption, as the inner gap is closer to the center line.

Fig. 1 visar ett dubbelsidig-t lager enligt uppfinningen.Fig. 1 shows a double-sided bearing according to the invention.

Den radiellt lagrade axeln 1 har en fast ßrbunden fläns la. I vardera lagerhus 4, 5 är anordnat en yttre axiell tätningsring 2, 3 förskjutbar i resp. tryckkammare 4b, 5b avtâtad med tätningar 2a, 3a. I lagerhusen 4, 5 finns även en inre radiell tät- ningsring 4a, Sa som bildar en huvudsakligen fast tätspalt 8, 9 med axeln.The radially mounted shaft 1 has a fixedly connected shaft. In each bearing housing 4, 5 an outer axial sealing ring 2, 3 is arranged displaceable in resp. pressure chambers 4b, 5b sealed with seals 2a, 3a. In the bearing housings 4, 5 there is also an inner radial sealing ring 4a, Sa which forms a substantially fixed sealing gap 8, 9 with the shaft.

Till de utbildade hålrummen 10, 1 1 filltörs ett hydrauliskt tiyckmedium från pum- parna 15, 16 genom ledningarna C, D. Detta medium evakueras från hålrummen genom de fasta radiella spalterna 8, 9 och de justerbara 6, 7, varvid ett tryckfall uppstår som påverkar flänsen la. Med hjälp av en hydraulisk styrventil 12, matad med tryck från pumpen 14 driven av motorn 17, påverkas tâtningsringarna 2, 3 genom ledningarna A, B att strypa de yttre tätspaltema i relation till den pälagda axialbelasmingen. Styrventílen har hjälp av ett axeln lâgesavkânnande organ 13 för att reglera detta. Evakueringsflöden indikeras I, J resp. G, H i figur. 508 141 3 Fig. 2 visar en frilagd förstorad tätningsring 3, där hålrummets ll tryck förklaras som funktion av geometrin och det tryck som styiventilen ñrser uyckkanirnaren Sb med.To the formed cavities 10, 1, a hydraulic pressure medium is pumped from the pumps 15, 16 through the lines C, D. This medium is evacuated from the cavities through the fixed radial gaps 8, 9 and the adjustable 6, 7, whereby a pressure drop occurs which affects fl änsen la. By means of a hydraulic control valve 12, supplied with pressure from the pump 14 driven by the motor 17, the sealing rings 2, 3 are actuated by the lines A, B to throttle the outer sealing gaps in relation to the piled axial load. The control valve is aided by a shaft position sensing means 13 to regulate this. Evacuation fates are indicated I, J resp. G, H i fi gur. 508 141 3 Fig. 2 shows an exposed enlarged sealing ring 3, in which the pressure of the cavity 11 is explained as a function of the geometry and the pressure with which the control valve causes the pressure channel Sb.

På detta sätt kan styrventilen programmeras att hålla axeln i en viss position oav- sett yttre pålagd last och även att under drift justera nämnda position.In this way, the control valve can be programmed to hold the shaft in a certain position regardless of the externally applied load and also to adjust said position during operation.

Fig. 3 visar en förstoring av den inre tätningsrixigen med trryckmediets txyckfall ut- efter spalten inritad.Fig. 3 shows an enlargement of the inner sealing strip with the pressure drop of the pressure medium after the gap drawn.

En utveckling här innebär att man låter hålrummets tzyck verka längs tätnings- ringens yttre periferi med en tätning Sd, vilket innebär att tätningsringens diame- ter, dvs. tâtspaltens höjd, minskar med ökad belastning. Sålunda ökar inte läckflö- det så mycket med ökad last.A development here means that the thickness of the cavity is allowed to act along the outer periphery of the sealing ring with a seal Sd, which means that the diameters of the sealing ring, ie. the height of the toe gap decreases with increasing load. Thus, the leakage does not increase so much with increased load.

Fig. 4 visar en möjlig applikation av ett dubbelsidigt lager enligt uppfinningen.Fig. 4 shows a possible application of a double-sided bearing according to the invention.

Axeln år lagrad i står-iska axialrullager 18, 19 för glappfri radiell lagring med viss axiell lastupptagande förmåga. Lagerhusen 4, 5 bildar här kolven i en linjär hyd- raulmotor med den yttre cylindem 20, 21. Den linjära hydraulrnotorn har två tiyckkarrunare 4c, 5c, vilkas tryck och mängd av hydraulrnedium regleras genom ledningarna E, F med hjälp av en hydraulisk styrventil 12 och ett lägesavkännande organ 13.The shaft is mounted in static axial roller bearings 18, 19 for play-free radial bearing with a certain axial load-bearing capacity. The bearing housings 4, 5 here form the piston in a linear hydraulic motor with the outer cylinder 20, 21. The linear hydraulic motor has two pressure coils 4c, 5c, the pressure and amount of hydraulic fluid being regulated through the lines E, F by means of a hydraulic control valve 12. and a position sensing body 13.

Tryckkarnrarna 4c och Sc kommunicerar direkt med de hydrauliska lagrens resp. tryckkammare 4b, 5b genom ledningarna A, B lör att på så sätt som "slav"-1ager uppta den på hydraulmotorn pålagda axialbelastriingen.The pressure carriages 4c and Sc communicate directly with the hydraulic bearings resp. pressure chambers 4b, 5b through the lines A, B allow to absorb the axial load applied to the hydraulic motor in the same way as "slave" -1 bearings.

Sålunda används hydraulmotorn ßr att justera axelns axiella position och hyd- raullagren för att absorbera axiallast som kan variera till storlek och riktning. 508 141 4 Det i fig. 1 beskrivna hydrauliska tryckmediet, vilket filliörs hålrummen 10, 1 1 , år ej indikerade i denna figur men är givetvis nödvändigt för lagrens filnlcfion.Thus, the hydraulic motor is used to adjust the axial position of the shaft and the hydraulic bearings to absorb axial loads that can vary in size and direction. 508 141 4 Det i fi g. 1 described hydraulic pressure medium, which is the cavities 10, 1 1, are not indicated in this figure but are of course necessary for the bearing of the bearings.

Claims (7)

508 141 PATENTKRAV508 141 PATENT CLAIMS 1. Hydrauliskt axiallager för en radiellt lagrad axel (1) med en med axeln fast förbunden fläns (la), innefattande en yttre, huvudsakligen axiell tätspalt (7) formad mellan flänsen och en yttre tätningsring (3) samt en inre, huvudsakligen radiell tätspalt (9) formad mellan axeln och ett lagerhus (5) eller mellan axeln och en med lagerhuset (5) förbunden inre tätningsring (Sa), varvid ett hydrauliskt tryckmedium tillföres ett mellan tätspalterna (7),(9) bildat hålrum (11) för upptagande av en på axeln påförd axialbelastning, k ä n n e t e c k n a t av att den yttre tätningsringen (3) är axiellt förskjutbart anordnad i en tryckkammare (5b), och genom ett i tryckkammaren infört hydrauliskt tryckmedium är manövrerbar för reglering av den yttre tätspaltens (7) höjd.Hydraulic thrust bearing for a radially mounted shaft (1) with a shaft (1a) firmly connected to the shaft, comprising an outer, substantially axial sealing gap (7) formed between the shaft and an outer sealing ring (3) and an inner, substantially radial sealing gap (9) formed between the shaft and a bearing housing (5) or between the shaft and an inner sealing ring (Sa) connected to the bearing housing (5), a hydraulic pressure medium being supplied to a cavity (11) formed between the sealing gaps (7), (9) for receiving an axial load applied to the shaft, characterized in that the outer sealing ring (3) is arranged axially displaceably in a pressure chamber (5b), and through a hydraulic pressure medium introduced into the pressure chamber is operable to adjust the height of the outer sealing gap (7) . 2. Hydrauliskt axiallager enligt krav 1, k ä n n e t e c k n a t av att två lager är anordnade i inbördes motstående riktningar kring en eller två flänsar.2. A hydraulic thrust bearing according to claim 1, characterized in that two bearings are arranged in mutually opposite directions about one or two axes. 3. Hydrauliskt axiallager enligt krav 2, k ä n n e t e c k n a t av ett axeln (1) lägesavkännande organ (13) vilket via en styrventil (12) reglerar mängd och tryck av i tryckkammaren (5b) infört tryckmedium för axiell inställning av den yttre tätningsringen (3).Hydraulic thrust bearing according to claim 2, characterized by a shaft (1) position sensing means (13) which regulates via a control valve (12) the amount and pressure of pressure medium introduced into the pressure chamber (5b) for axial adjustment of the outer sealing ring (3). ). 4. Hydrauliskt axiallager enligt krav 2, k ä n n e t e c k n a t av att den inre tätningsringen (Sa), avgränsande den radiella tätspalten (9), kring sin yttre periferi är påverkad av ett hydrauliskt tryckmedium för reglering av den radiella tätspaltens höjd.Hydraulic thrust bearing according to claim 2, characterized in that the inner sealing ring (Sa), delimiting the radial sealing gap (9), around its outer periphery is influenced by a hydraulic pressure medium for regulating the height of the radial sealing gap. 5. Hydrauliskt axiallager enligt krav 4, k ä n n e t e c k n a t av att trycket mot den inre tätningsringens (Sa) yttre periferi härrör från det axiallast bärande trycket i hålrummet (1 1).Hydraulic thrust bearing according to claim 4, characterized in that the pressure against the outer periphery of the inner sealing ring (Sa) originates from the axially load-bearing pressure in the cavity (1 1). 6. Hydrauliskt axiallager enligt krav 4, k ä n n e t e c k n a t av att trycket mot den inre tätningsringens (Sa) yttre periferi härrör från trycket i tryckkammaren (5b).Hydraulic thrust bearing according to claim 4, characterized in that the pressure against the outer periphery of the inner sealing ring (Sa) derives from the pressure in the pressure chamber (5b). 7. Hydrauliskt axiallager enligt krav 3, innefattande två stycken, på motstående sida av åtminstone en fläns (la) anordnade axiallager-enheter, k ä n n e t e c k n a t av att 508 141 6 axiallager-enheternas resp. lagerhus (4,5) bildar kolven (4,5) av en linjär hydraulmotor (20,21) i vilken lagerhusen är axiellt förskjutbara och tillordnade en resp. tryckkammare (4c,5c), varvid det axeln lägesavkännande organet (13) via styrventilen (12) reglerar mängd och tryck av hydrauliskt tryckmedium i tryckkam- rarna (4c,5c) för upptagande av till storlek och riktning varierande axialbelastning på kolven samt för att medge axiell förskjutbarhet hos densamma, samt av att tryckkamrarna (4c,5c) står i direkt flödesförbindelse med de två axiallager- enhetemas resp. yttre tätningsringars tryckkammare (4b,5b), varigenom de båda hydrauliska axiallagerenheterna upptar hela eller delar av den hydraulmotorn (20,21) påförda axiella belastningen.Hydraulic thrust bearing according to claim 3, comprising two pieces, on the opposite side of at least one thrust bearing assembly arranged on one side (1a), characterized in that the thrust bearing units resp. bearing housings (4,5) form the piston (4,5) of a linear hydraulic motor (20,21) in which the bearing housings are axially displaceable and assigned a resp. pressure chamber (4c, 5c), the shaft position sensing means (13) via the control valve (12) regulating the amount and pressure of hydraulic pressure medium in the pressure chambers (4c, 5c) for accommodating axial load on the piston varying in size and direction and for allow axial displaceability thereof, and that the pressure chambers (4c, 5c) are in direct contact with the two axial bearing units resp. pressure chamber (4b, 5b) of outer sealing rings, whereby the two hydraulic thrust bearing units take up all or part of the axial load applied to the hydraulic motor (20, 21).
SE9500424A 1995-02-07 1995-02-07 Hydraulic axial bearing for a radially stored shaft SE508141C2 (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
SE9500424A SE508141C2 (en) 1995-02-07 1995-02-07 Hydraulic axial bearing for a radially stored shaft
EP96908455A EP0808427A4 (en) 1995-02-07 1996-02-06 Hydraulic axial bearing
PCT/US1996/001435 WO1996024777A1 (en) 1995-02-07 1996-02-06 Hydraulic axial bearing
CA002212433A CA2212433C (en) 1995-02-07 1996-02-06 Hydraulic axial bearing
US08/894,029 US6082901A (en) 1995-02-07 1996-02-06 Hydraulic axial bearing
NO973491A NO973491D0 (en) 1995-02-07 1997-07-30 Hydraulic axial bearing
FI973250A FI973250A0 (en) 1995-02-07 1997-08-07 Hydraulic axial bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
SE9500424A SE508141C2 (en) 1995-02-07 1995-02-07 Hydraulic axial bearing for a radially stored shaft

Publications (3)

Publication Number Publication Date
SE9500424D0 SE9500424D0 (en) 1995-02-07
SE9500424L SE9500424L (en) 1996-08-08
SE508141C2 true SE508141C2 (en) 1998-09-07

Family

ID=20397105

Family Applications (1)

Application Number Title Priority Date Filing Date
SE9500424A SE508141C2 (en) 1995-02-07 1995-02-07 Hydraulic axial bearing for a radially stored shaft

Country Status (5)

Country Link
EP (1) EP0808427A4 (en)
FI (1) FI973250A0 (en)
NO (1) NO973491D0 (en)
SE (1) SE508141C2 (en)
WO (1) WO1996024777A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115111266B (en) * 2022-06-24 2024-02-23 哈尔滨工业大学（威海） Multi-embedded point type porous gas hydrostatic bearing

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1268575A (en) * 1916-02-12 1918-06-04 Anatol David Iskols Hydraulic thrust-bearing.
US3146037A (en) * 1963-01-25 1964-08-25 Mechanical Tech Inc Thurst bearings
SE455431B (en) * 1986-11-12 1988-07-11 Cellwood Machinery Ab HYDROSTATIC AXIAL STORAGE
SE464370B (en) * 1989-07-27 1991-04-15 Desart Ab BEFORE A RADIALLY STORED AXEL DEVIED AXIAL STORAGE SYSTEM
SE467343B (en) * 1990-10-03 1992-07-06 Sunds Defibrator Ind Ab STORAGE SYSTEM IN A REFINING DEVICE FOR PREPARING PULP

Also Published As

Publication number Publication date
FI973250A (en) 1997-08-07
NO973491L (en) 1997-07-30
FI973250A0 (en) 1997-08-07
SE9500424D0 (en) 1995-02-07
NO973491D0 (en) 1997-07-30
WO1996024777A1 (en) 1996-08-15
EP0808427A4 (en) 1998-06-17
SE9500424L (en) 1996-08-08
EP0808427A1 (en) 1997-11-26

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