SE441296B

SE441296B - Lubricating apparatus at angled centrifugal pumps

Info

Publication number: SE441296B
Application number: SE8400943A
Authority: SE
Inventors: I Bergevald; G Meissner
Original assignee: Scanpump Ab
Priority date: 1984-02-21
Filing date: 1984-02-21
Publication date: 1985-09-23
Also published as: FI844874A0; SE8400943D0; FI73049B; FI73049C; FI844874L; SE8400943L

Abstract

In an apparatus at centrifugal pumps, which pump-wheel axle (4) is mechanically coupled to a rotating axle in an internal combustion engine and driven with this and which pump medium is for cooling the motor, the pump-wheel axle is stored in at least one bearing (6) in a bearing housing (1), that has an upward facing opening (13) for application of lubricating oil from the motor to the mentioned bearing. To ensure satisfactory lubrication of the bearing even in those cases when the pump-wheel axle (4) slants downward in the direction of the motor in respect to the horizontal plane, there exists a partial partition (15), that is especially closely adfixed to the bottom part of the bearing housing's (1) inner wall beside the bearing (6) and together with this confines a pocket (16) or the like for accumulation of lubricant from the induction opening (13). When this is not positioned essentially precisely above the pocket there is also a pipe (17), that stretches inside the bearing housing from the opening (13) to the pocket (16) or to a point essentially precisely above it for induction of lubricant to the pocket and that beside this existing bearing (6).<IMAGE>

Description

8400943-0 Fig. 2 är en perspektivvy av en i anordningen enligt uppfinningen ingående hylsa. 8400943-0 Fig. 2 is a perspective view of one in the device according to sleeve included in the invention.

Fig. 3 föreställer en med fig. l analog axialsektion och åskådliggör smörjning av pumphjulsaxeln i ett annat fall.Fig. 3 represents an axial section analogous to Fig. 1 and illustrates lubrication of the impeller shaft in another case.

Fig. 4 och 5 visa en modifikation av hylsan enligt fig. 2, likaledes i perspektiv.Figs. 4 and 5 show a modification of the sleeve according to Fig. 2, also in perspective.

I fig. l betecknar l ett lagerhus samt 2 och 3 ett pumphus resp. ett pumphuslock, vilka endast antydas och vid vilka lagerhuset l är fastbultat. I lagerhuset är en pump- hjulsaxel 4, på vilken ett ej visat pumphjul är fastsatt, roterbart lagrad i ett inre och ett yttre lager 6 resp. 7.In Fig. 1, l denotes a bearing housing and 2 and 3 a pumphus resp. a pump housing cover, which are only hinted at and at which bearing housing 1 is bolted. In the warehouse is a pump- wheel shaft 4, on which a pump wheel (not shown) is attached, rotatably mounted in an inner and an outer bearing 6 resp. 7.

Dessa visas i utföringsexemplet vara kullager men skulle alternativt kunna vara t.ex. rullager.These are shown in the exemplary embodiment as ball bearings but would alternatively be able to be e.g. roller bearing.

Lagerhuset l uppvisar en ringformig fläns eller krage 8, vilken medelst bultar eller dylikt är fäst vid en motsvarande ringformig fläns 9 på ändväggen till en i övrigt ej visad dieselmotor (eller en annan förbränningsmotor). Pumpen har i utföringsexemplet enligt fig. l till ändamål att cirkulera kyl- nædhm1gaum1mmxmn.De i fiq. l till höger om flänsen 8 belägna delarna av lagerhuset skjuta in i motorn, vilken driver pumpen via ett t.ex. på änden av motorns kamaxel fastsatt (ej visat) kugghjul, som är i ingrepp med ett kugghjul ll, som är fäst på pumphjulsaxelns 4 utanför lagerhusets l hög- ra gavel utskjutande, fria ände. Denna lagerhusgavel ut- göres av ett ringformigt lagerlock l2. I lagerhusets andra gavel är en tätning 14, som tätt omsluter axeln 4, insatt.The bearing housing 1 has an annular flange or collar 8, which is fastened to it by means of bolts or the like a corresponding annular flange 9 on the end wall of an i otherwise not shown diesel engine (or another internal combustion engine). The pump in the embodiment according to Fig. 1 for the purpose of circulating the cooling nædhm1gaum1mmxmn.De i fiq. l to the right of the flange 8 located the parts of the bearing housing slide into the engine, which drives the pump via an e.g. attached to the end of the engine camshaft (not shown) gear engaged with a gear ll, which is attached to the impeller shaft 4 outside the height of the bearing housing 1 ra gable protruding, free end. This bearing housing end is made of an annular bearing cap l2. In the warehouse second end is a seal 14, which tightly encloses the shaft 4, inserted.

Upptill, vid sin inuti motorn belägna ände uppvisar lagerhusets l mantelyta en lämpligen trattliknande öppning 13 för uppfångning av smörjmedel, som vid motorns smörjning stänker upp i motorblocket, samt inledande av sådant smörjmedel i lagerhuset l.At the top, at its end located inside the engine the bearing surface of the bearing housing has a suitably funnel-like opening 13 for catching lubricant, as in engine lubrication splashes up in the engine block, as well as the initiation of such lubricant in the bearing housing l.

I enlighet med uppfinningen är i lagerhuset l an- ordnat dels en vid den undre delen av lagerhusets inre man- telyta väsentligen tätt fäst partiell skiljevägg 15, som 8400945-0 är belägen bredvid det inre lagret 6 samt tillsammans med detta och den mellan lagret 6 och skiljeväggen 15 belägna delen av mantelytan bildar en ficka 16 eller dylikt, dels en ränna 17, vars ena ände är belägen under öppningen 13 och vars andra ände är belägen rakt ovanför fickan 16.In accordance with the invention, in the bearing housing 1 arranged on the one hand at the lower part of the inner housing of the warehouse teal surface substantially tightly attached partial partition 15, which 8400945-0 is located next to the inner layer 6 and together with this and that located between the bearing 6 and the partition wall 15 the part of the mantle surface forms a pocket 16 or the like, partly a chute 17, one end of which is located below the opening 13 and the other end of which is located just above the pocket 16.

Skiljeväggens 15 avstånd från det inre kullagret 6 (fickans 16 bredd) är så valt, att rännans 17 undre ände befinner sig rakt ovanför fickan även när pumphjulsaxeln i förhållan- de till horisontalplanet och följaktligen även oljeytan 10 lutar nedåt den förutbestämda vinkeln (d = f)i Ek; 1) irikt- ning från fickan mot motorn. Skiljeväggens 15 höjd är så vald, att vid pumphjulsaxelns nämnda lutningsvinkel olja, som befinner sig i fickan 16, kan strömma in i mellanrummet mellan det inre kullagrets 6 löpringar och smörja kulorna.The distance of the partition 15 from the inner ball bearing 6 (pocket) 16 width) is so chosen that the lower end of the chute 17 is located directly above the pocket even when the impeller shaft in those to the horizontal plane and consequently also the oil surface 10 inclined downwards the predetermined angle (d = f) in Ek; 1) irikt- from the pocket to the engine. The height of the partition 15 is as follows selected, that at the said angle of inclination of the impeller shaft oil, located in the pocket 16, can flow into the gap between the 6 ball rings of the inner ball bearing and lubricate the balls.

Vidare är det inbördes avståndet mellan kullagren 6, 7 samt förhållandet mellan dessas resp. diametrar så valda, att olja, som runnit ut ur fickan 16, över skiljeväggen 15 kan rinna ut ur lagerhuset genom mellanrummet mellan det yttre kullagrets löpringar samt öppningen i lagerlocket 12, såsom åskådliggöres i fig. 1. Rännans lutning bör givet- vis överstiga nämnda förutbestämda gradtal.Furthermore, it is the mutual distance between the ball bearings 6, 7 and the relationship between their resp. diameters so selected, that oil, which has run out of the pocket 16, over the partition 15 can flow out of the bearing housing through the space between it the outer ball bearing running rings and the opening in the bearing cover 12, as illustrated in Fig. 1. The slope of the gutter should be exceed said predetermined degrees.

Rännan 17 och skiljeväggen 15 kan vara utformad resp. anbragt i en separat insats 18. Denna åskàdliggöres i fig. 2 och har i huvudsak formen av öppen hylsa, som bildar en del av en väsentligen cirkulärcylindrisk mantel- yta och som upptager en medelpunktsvinkel av cirka 2513609 Denna hylsa kan anses utgöra en del av lagerhusets mantel- vägg. Från den undre änden av rännan, som vidgar sig i riktning nedåt vänster i fig. 2, utgår en cirkelbågformigt böjd tunga l9, som kan utgöra en fortsättning av hylsans man- telyta och som med överlappning överbryggar öppningen i hyl- sans mantelyta och vars bredd är företrädesvis större än fickans 16 bredd. Hylsan 18 uppvisar även en flik eller tunga 20, som är avsedd att ingripa i en motsvarande öppning 21 i lagerhusets l mantelvägg för att härigenom fixera hylsan i rätt läge i vridningsled med rännan 17 upp och skiljeväggen 15 ner.The gutter 17 and the partition 15 can be designed resp. placed in a separate insert 18. This is illustrated in Fig. 2 and is substantially in the form of an open sleeve, which forms part of a substantially circular-cylindrical shell surface and occupying a center angle of about 2513609 This sleeve can be considered as part of the casing of the bearing housing. wall. From the lower end of the gutter, which widens in direction downwards left in Fig. 2, a circular arc emerges bent tongue 19, which may be a continuation of the sleeve which overlaps the opening in the shelf sans mantle surface and whose width is preferably larger than the pocket 16 width. The sleeve 18 also has a flap or tongue 20, which is intended to intervene in a corresponding opening 21 in the bearing housing 1 casing wall to thereby fix the sleeve in the correct position in pivot joint with the chute 17 up and the partition wall 15 down.

POOR QUÅÜW 8400945-o; Vid monteringen anbringas lämpligen kullagren 6, 7 på axeln 4 innan hylsan l8 träs på axeln mellan dem, varefter hela enheten, inklusive lager och hylsa inskjutes i lager- huset l.POOR QUÅÜW 8400945-o; During assembly, the ball bearings 6, 7 are suitably applied shaft 4 before the sleeve 18 is threaded onto the shaft between them, after which the whole unit, including bearings and sleeve, is inserted into the bearing the house l.

Man har även uppställt kravet att pumphjulsaxeln skall kunna luta åtminstone en viss förutbestämd vinkel ß, speciellt 40, åt motsatta hållet, d v s uppåt från det inre lagret i riktning mot det yttre lagret, utan att olja rinner ut ur lagerhuset l genom öppningen i lager- locket 12. Detta fall åskådliggöres i fig. 3, som visar att oljeytan 10 vid nämnda gränsvärde når upp till och in i mellanrummet mellan det inre kullagrets 6 inre och yttre löpring.The requirement for the impeller shaft has also been set must be able to tilt at least a certain predetermined angle ß, especially 40, in the opposite direction, i.e. upwards from it the inner layer in the direction of the outer layer, without oil flows out of the bearing housing 1 through the opening in the bearing the lid 12. This case is illustrated in Fig. 3, which shows that the oil surface 10 at said limit value reaches up to and into the gap between the inner and outer bearings of the inner ball bearing 6 running ring.

I vissa extrema fall kräves att pumphjulsaxeln åtminstone kortvarigt skall kunna luta så mycket som 350 mot horisontalplanet, nedåt från det inre lagret 6 i riktning mot det yttre lagret 7, utan att smörjningen av det förstnämnda upphör. I detta fall kan rännan 17 ej vara rak, eftersom den då skulle kollidera med pumphjulsaxeln 4, utan sträcker sig väsentligen i skruvspiralform genom det cylinderringformiga mellanrummet mellan lagerhusets 1 mantelvägg och pumphjulsaxeln, såsom visas i fig. 4 och 5, i vilka samma hänvisningsbeteckningar som i fig. 2 användas för att beteckna motsvarande detaljer. I det visade utföringsexemplet är hylsan 18 cirkulärcylindrisk och sluten, vilken innebär att den måste ha ett mitt för tratten 13 beläget inlopp 23, som utmynnar i en uppfång- ningsbehållare 24 i den övre änden av rännan 17 samt måste anbringas på axeln 4 före det yttre lagret 7.In some extreme cases, the impeller shaft is required at least briefly be able to tilt as much as 350 towards the horizontal plane, downwards from the inner layer 6 i direction towards the outer bearing 7, without the lubrication of the former ceases. In this case, the chute 17 cannot be straight, as it would then collide with the impeller shaft 4, but extends substantially in helical form therethrough the cylindrical space between the bearing housing 1 jacket wall and impeller shaft, as shown in Figs. 4 and 5, in which the same reference numerals as in Fig. 2 be used to denote corresponding details. In it shown in the exemplary embodiment, the sleeve 18 is circular-cylindrical and closed, which means it must have a middle for funnel 13 located in the hopper 13, which opens into a catch container 24 at the upper end of the chute 17 and must applied to the shaft 4 before the outer bearing 7.

De ovan beskrivna och på ritningarna visade utfö- ringsformerna äro givetvis att betrakta blott såsom icke begränsande exempel och kunna till sina detaljer modifieras på flera sätt inom ramen för följande patentkrav. Sålunda kan exempelvis rännan 18 utbytas mot ett rör och åtminstone det ena kullagret 6 eller 7 mot ett rullager. Vidare kan öppningen 13 i lagerhuset anbringas väsentligen rakt ovan- 8400945-0 för fickan l6, varvid ledningen eller rännan 18 kan undvaras. Därjämte äro vinklarna oz och ß givetvis icke låsta till de angivna värdena 70 resp. 40 utan kunna exempelvis vara så stora som 100, 200 eller till och med 3s°.The embodiments described above and shown in the drawings the forms of ringing are, of course, to be regarded merely as not restrictive examples and can be modified to their details in several ways within the scope of the following claims. Thus for example, the gutter 18 can be exchanged for a pipe and at least one ball bearing 6 or 7 against a roller bearing. Furthermore, can the opening 13 in the bearing housing is arranged substantially directly above 8400945-0 for the pocket 16, whereby the conduit or channel 18 can undvaras. In addition, the angles oz and ß are of course not locked to the specified values 70 resp. 40 without being able to for example, be as large as 100, 200 or even with 3s °.

Claims

s4nu94z-a '¿PATENTK RAV

l) A device for centrifugal pumps, the impeller shaft (4) of which is mechanically coupled to a rotating shaft of an internal combustion engine and driven by it and the pumped medium of which is the cooling medium of the engine, the impeller shaft being mounted in at least one bearing (6) in a bearing housing (1), having an upwardly facing opening (13) for supplying lubricating oil from the engine to said bearing, characterized by a partial partition wall (15), which is substantially tightly attached to the lower part of the inner wall of the bearing housing (1) next to the bearing (6) and together with it limits a pocket (16) or the like, also of a channel (17) extending inside the bearing housing from the opening (13) to the pocket (16) or to a point substantially directly above and for supplying lubricating oil to the pocket and the existing bearing (6) adjacent to it, in cases where the opening (13) of the bearing housing is not located substantially directly above the pocket.

2) Device according to claim 1, characterized in that the partition wall (15) is so high that at least some point on it is located closer to the impeller shaft (4) than the casing wall of the bearing housing (1).

3) Device according to claim 1, characterized in that the jacket wall (1) of the bearing housing (1) is double at least partially, and comprises an inner, suitably detachable pipe sleeve (18L in or to which the gutter (17) is formed or fastened.

4) Device according to claim 3, characterized by means arranged for fixing the pipe sleeve relative to the wall of the bearing housing, e.g. in the form of a projecting flap (20) or tongue, and an opening (21) for receiving it in the bearing housing wall. 'i 8400943-0

Device according to one of the preceding claims, characterized in that the channel is a preferably open channel (17), which preferably has a substantially V-shaped cross section and suitably widens in the direction from the opening (13) to the bearing ( 6).

Device according to claim 3, characterized in that the gutter (17) is attached to and extends along the inside of the jacket wall (1) of the bearing housing from said opening to the pocket and forms part of a screw spiral, the inclination of which to the impeller shaft exceeds a predetermined angle, especially 350.

7. A device according to claim 1, characterized in that said bearing is a ball or roller bearing (6) mounted at the inner end of the bearing housing, facing away from the motor, in which a seal surrounding the impeller shaft is mounted (14), and that the impeller shaft (4) is mounted in a second ball or roller bearing (7), which allows drainage of lubricating oil from the bearing housing (1) and return of oil to the engine, at the other end of the bearing housing facing the engine.

8) Device according to claim 7, characterized in that the partial partition wall is so positioned relative to the bearings and so dimensioned with respect to its height that the balls or rollers in the inner bearing facing the engine (6) are at least partially located below the oil surface when the upper edge of the partition (15) is substantially in the oil surface, even when the inner bearing is so much higher than the outer bearing, which corresponds to a predetermined inclination, especially 70, of the impeller shaft towards the horizontal plane. mer nzfarxrr)