DE7140687U - Multi-stage axial bearing - Google Patents

Description

DIPL · -ING. HORST ROSE DIPL-ING. PETER KOSEL PATINTANWXLTI

awl omdwtiMim, January 26, 1973

'V ^ BnMIHHn ^ Weew · BMQPMWlt BojQQQflQQIVfMllll

Uht * r.AktM <No. 2704/3 Rellway Bearing Company, Ine "

Rellway Bearing Company, la
7600 Mergan RA.

Axiall * «« r

This applies to · 1η Bekretmfifei Axi »llaf« r iu axial load · »rea« in «r shaft cone to« in «&« h & u * «* oculter _f nit aimdtiteaa swai Sfttsam rea LaufriBgen, (wtleh» »inieeteae eiaen an Aafaacsaats 4ar Wellcneehnlter end • in "n bndsats on the ftam & mataolraltar have, weaei the" a race ring equipment javeila on · a shaft race arranged on the corrugation "with an on the & aaame · arranged Oehäueelaufriag» eatehem _v which have been matched · pederkenetanteu · and where the race ring ^ eweil · a niohtr * ohteekfermig "a Quereetait ^ amfweie" n and projecting BAW, aifcd cantilevered, se DAB they check dureabiegen at Ailalbelftötung, further iwiseilen each with the opposite faces of a · Laufringeataes arranged roller 8ätsen ₉ näaliok at least one initial and a EndrollensatSt and with support "rings" ur transfers j ng τοη axial forces, with at least one initial and one endsthtsrisg are possible and shaft stut rings each "like b adjacent well

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Races and Gtehäusestützringe each between adjacent & * hiL «» eleven rings, arranged. Under "multilevel" should be understood to mean two or more levels

Given the volume of available housing for a bearing in terms of the bearing capacity to be accommodated therein investigated, it is known that a thrust bearing with a multi-stage roller arrangement offers no advantages compared to a single-stage axial bearing with a large outer diameter. However, if it is required to keep the outer diameter of the housing as small as possible, see this sin axial bearings in a multi-stage arrangement offers considerable advantages in terms of load capacity compared to a single-stage bearings with the same outside diameter

From US Pat. No. 2,374,820, a multi-stage warehouse is disclosed by the entry point Aft isekssBt. 3 * 1 sslchss readers have »carried out investigations over a period of 25 years on a large number of τοη fellers with normal and abnormal fatigue strength that arbitrary combinations of a) roller seeders, b) design of the raceways and o) diameters of the supporting surfaces are not sufficient, In order to obtain a consistently satisfactory bearing life, although many different design combinations and arrangements have been proposed, it has been determined that, in general, multi-stage roller bearings are only designed with maximum load-bearing capacity in mind, but with the critical dimensions of the outer surfaces supporting the lamellar rings or the support rings separating the races (i.e. the members transmitting the thrust) were not or at least not sufficiently taken into account. In the earlier bearing constructions of this type, the type of fastening or the specific clamping or supporting influence of the bearing rings and support rings was not sufficiently taken into account.

714618? -S. 4th

The invention is based on the object of providing a multi-stage bearing with predictably reliable fatigue strength to sehsfiea.

This object is achieved according to the invention in that in the axial bearing the entire contact surface of a set of rollers with the surfaces of the associated races is approximately the same as the corresponding contact surface in the other roller etching, that the deflection of the race »rings under axial load is designed so that at least almost identical inclinations of the races are present on opposite roller contact surfaces, and that the ratio (S / E) of the diameter (S) of the shaft shoulder to the mean diameter (E) of the initial bearing ring between the two shaft races closest to the shaft shoulder is in the range of I. ₁ QQ up to 1.30 «This gives a special combination of the above-mentioned features a), b) and c). This leads to a predictable behavior of the bearing during operation and at the same time makes it possible to achieve the desired load-bearing capacity of the bearing.The developed design criteria are based on the classical theory of elasticity, which, where necessary, supplements and corrects the results of tests and experience from actual operation became; These design criteria must be strictly adhered to in order to guarantee the theoretical bearing life

to ensure the theoretical fatigue strength of the bearing, the interacting cantilevered races for each roller set must be complementary to one another Load-bending properties or spring constants · The size of the roller itself is determined by the required load range of the bearing, and the primary thickness of the races is chosen so that that the Rellelement-Diameter of the race is the desired Receives spring conataats. The races have a non-rectangular shape Cross section, and there those arranged on the shaft Shaft races other deflection characteristics have ale d ± e at the rt ftefeurlng », will-

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the secondary or variable bead of the individual race rings each chosen in such a way that they have a cooperative effect under load Have deflection of the surfaces at the contact surfaces with the assigned roller sets.

The load-bending characteristics of the race rings is based on the idea of the mutually interacting raceway inclinations on the roller contact surfaces. These inclinations are roughly the same between interacting races, and this applies to all pairs of races in the bearing. Since the deflection characteristics of the 4-well · or the running ring arranged on the housing When the types of fastening of these races are determined, great importance is attached to this fastening (i.e. the characteristics of the support and sinusoidal stress of the raceway ·) · Si · The construction of the support ring is also of great importance in effecting a proportional distribution of the load on all levels of the multi-level warehouse. Therefore, as in the case of cooperating races, the spring constants are preferably adjusted proportionally, and the supporting rings also have the prescribed F “rconstant” n, wi · das in the following is described in detail · Si · correct · Dimensioning of the shoulder height oJnos against the 1η η seat ring The raceway is also important to achieve the required degree of attachment.

In one embodiment of the invention, the ratio (S / 0) of the corrugated shoulder diameter (S) to the diameter (Q) of the initial roller set is in the range from 0.90 to 1.10. The ratio (T / F) from lAn «ndurehm« ee «r (T) of the housing shoulder to middle ·« DureluMsa «r (?) D ·· between the two of the o« housing «ehult« r next to the «g« nd · »oil housing rings. häus «support ring ·· range from 0.80 to 1.00. Furthermore, the Tefhaltais (T / B) from the housing shoulder inside diameter (T) to the outer diameter (H) of the end roller set i * range from 0.90 to 1.10

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According to another embodiment of the invention lies in the case of a three-stage bearing, the ratio (J / 0) of the Bittleres outer Durohmeseer (J) to those between neighboring ones Shaft rings arranged shaft support rings to the pitch circle diameter (C) the mean set of rollers in the range from 0.70 to 0.90, the ratio (K / C) τοπ mean Inner diameter (K) of the between adjacent housing rings arranged oehäusestutaringe su aellkreisdurchmeeeer (G) of the middle. Rolleas & tses la range τθ «Ij10 to 1.3B.

Haeh a further embodiment of the invention take the Rellkreiedurokmeeser the one-one roller seeders In a manner known to me from the initial roles of the Bndrellensat * down.

Haeh one embodiment of the invention are in one The two-stage warehouse is the leatherworking part of the starter ring proportional to the carrying capacity of the starting roller satees and the spring constant dos Sndstütsring proportional to the load capacity of sndrolleeaties.

laugh another embodiment of the invention in the case of a three-stage warehouse, the one closest to the wave switch Housing support ring and the one closest to the housing shoulder Wave tütering at least approximately the same Spring constant, where the ratio of the spring constant of these two support rings to the spring constant ios initial shaft support rings and the backshell support string sumindost is approximately 1: 2 »

7140887-8.4.73

Several exemplary embodiments of the invention are shown in the drawing »

Show it:

Fig. 1 shows a longitudinal section through a two-stage axial bearing and

Fig. 2 is a longitudinal section through a three-stage axial bearing *

Pig · 1 shows «in · wave 5» that in a stationary housing 6 is arranged, which forms part of a machine • that of a device or τβη this or this carried · The two-stage bearing is arranged between a shoulder 7 of the shaft 5 and a shoulder 8 of the housing 6 and has two axially spaced sets of rolling elements in the form of two sets of rollers 9 and 10, which are arranged in a ring shape around the shaft 5. The rollers 9 are supported by a cage 11 and a nit cooperating retaining ring 11A held, while the rollers 10 by a cage 12 and a Halterimg 12A are held.

Against the rollers 9 lies an upper one, on the shaft 5 arranged shaft running ring 14 and egg lower, on the housing 6 arranged precision race 15 on. Lies in the same way against the rollers 10 eim on the shaft 5 arranged shaft running ring 16 and eim arranged on the housing 6 housing runner rim 17 am. The shaft race 14 is against the shoulder 7 the shaft 6 supported, and the housing raceway 17 against the Housing shoulder 8 "The other shaft race 16 is over a shaft support rim 18 arranged on the shaft 5 and the shaft race 14 likewise against the shaft switch 7 supported, and in the same way is the housing raceway 15 via a housing support 19 arranged on the housing 6 and the housing race 17 against the housing shoulder 8 supported.

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The axial load to be borne by the shaft 5 or the in Fig. 1 downward thrust of the shaft 5 is ron the shaft shoulder 7 over the running rings 14-, 15, 16 and 17, the roller sets 9 and 10 and the support rings 18 and 19 transferred in two creams, like the ± n at the beginning U.S. Pat. No. 2,374,820 mentioned in detail, and Although one of the two tracks leads from the shaft race 14 over the rollers 9 »the housing race 13 and the Housing support ring 19 to the housing running ring 17 »and the other Sahn leads töü the Wellenlsafriag 14 over the Wedlenstütsring 18, the shaft race 16 and the rollers 10 sub housing race 17th

If the desired deflection of the races 14, 15t 16 and 17 is obtained, they are not rectangular in cross-sectional area, and they are thinner at their unsupported circumference of a set of elements of the multistage bearing have mutually adapted spring constants (i.e., load-durometer bending characteristics). This prevents an uneven distribution of occupation on the mutual contact surfaces of rollers and running rings. The races 14 and 16 arranged on the shaft 5 have a deflection characteristic which, in the case of the shaft race 14, is analogous to that of an annular disc clamped in the center or, in the case of the shaft race 16, to that of an annular disc supported in the center, each with a free outer circumference. The races 15 and 17 arranged on the housing 6 have a bending characteristic that \. # I. the housing raceway 17 to that of an annular disk clamped on its outside, or the housing raceway 15 to that of one supported on its outside. Ring washer, each with a free inner circumference, is analogous. Because of these different characteristics, each race has a very specific shape.

- 8 With the two-stage Axlal roller bearing, the usual

optimal · shape of the lager to cool down. Sa dl · load capacity usually the most important thing is the diameter of roles 9 and 10 determined. They primary sieves of my barrel rings 14 »15» 16 and 17 in the lake of the Areas in which theee each arranged Bind, let to the Roll diameter adjusted »to a compromise swisoheni an undesirable card suspension system with undesirably small elastic bearing ring deflections and an undesirable soft suspension system with large deflections BU eries, which plumb to large bearing ring bending vean » would bring talks with you. The course of the secondary the variable thief of the one his running rings is how given above, se chosen so that one idestise & e Deformable webs on the contact surfaces of one of the roller assemblies "

The effective mean bead of both the races on the shaft 5 and the races on the housing 6 must be determined; it is in each case a function of the applied load and the circumferential radii of the roller units assigned to the respective pair of races.As can be seen from Fig. 1, the rolling circle diameter of the roller units indicated by the dashed lines 20 and 21 take 9 bsw <10 τοη of the initial stage, i.e. the upper level Sa, as mentioned above, the deflection characteristics of the shaft race rings 14 and 16 arranged on the shaft 5 on the one hand and the housing race rings 15 and 17 arranged on the housing 6 on the other hand are different, are theirs have different effects, and it is essential that the ratio of the mean bead of a casing raceway to the middle bead is chosen so that the same degree of deflection is obtained.

Zua Braielea oiaer as uniform as possible load

& M «* £ <% 11 · St« f mm 4ee Lagere let 44 · AiM »U4ufie dor 8 tilt ar lag · 18 mmd 19 Tea Torraagigor Bodomtumg · (Dor» eaauaesttttaring 19 itt hler old eyeholes in the ion τοη radial perforations 19 * rereehen .) Bbeaao, like the susamaea acting running carriage mutually adapted spring core stants kabea mtteoom, mttesem auoh all Bttttiriage eiao Torgoaokrlelioae fodorkonatamto kaben. At the iweiatufigea camp naek fig In order to ensure uniform loading tortoilang on the dom contact surfaces, iat oa aaek important, a rioktigo shape and dimension of the running carriage? Bstütsen4ea fläeken su kabea * laseesemdere should be the ring surface · the Wolleafe ^ ultor 7 mad of the eekamaeaekmlter 8 old doa , and these surfaces roped glolok far oratrookoa like the radialoa surfaces of the gogoa they aaliegeadea races U mad 17.

Zuaätaliok at the cathedral Irfordormlaaom for dlo dio running ring troa influx in front of the boatiaato carrying sureamoasor In the warehouse according to spoiiollom KoAatruktiomaparamotorm determined It laaere storage amordnmag is so constructed that it dl were determined and one the desired Bejrokbiogangskurve receives, for the two-tier camp naek flg. 1 there is Animal such special parameters, which see as follows Express relationships, let:

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S / B - 1.00 ... 1.30 (1)

Here let

8 the diameter of the wave switch 7 »and 1 is the mean · diameter of the shaft support ring 18;

S / a - 0.90 ... 1.10 (2)

Here*·! is

Q is the inner diameter of the roller set 9;

JB / F - Ο, β © ... 1.00 (3)

Here is

T is the inner diameter of the housing shoulder 8, and F is the mean diameter of the large housing support ring 19; f / H - 0.90 ... 1.10 (4)!

Here iet! W the outer endurance of the role set iö.

Fig «2 shows a three-stage roller thrust bearing, which in principle has the same structure as the bearing according to Pig. 1, but has a eusätaliehe level. Go to Pig camp. 2, a shaft 24 with a shoulder 25 is arranged in a housing 26 which has a load-bearing shoulder 27 · As whale elements, three Rellensätse 28, 29 and 30 are seen,; against which the upper shafts arranged on shaft 24 »'; Races 32, 33 and 34 and the lower, on the housing 26 arranged öehauselaiafringe 36, 37 and 38 are in contact. Furthermore! There are two shaft stems arranged on the full 24 and two arranged on the housing 26 (Jehilusestütsrlnge 43, 44 Torgeeehen, the latter each having oil bores in the form of ▼ at openings 43 * or «44 *.

For the three-stage warehouse, the design parameters are the same as those given above for the two-stage saw. However, there are two additional special satellite throws.-j parameters; Expressed in terms of terminology, these are ^: Parameter as follows j

7146 * 87 -1.4.71

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S / E

S / G

T / F

T / Hi

J / G

K / C

1.00 0.90 0.80 0.90 0.70 1.10

1.30 1.10 1.00 1.10 0.90 1.35

(D (2) (5) (4) (5) (6)

Here are

5 is the diameter of the shaft shoulder

E is the mean diameter of the shaft adapter ring-4Q -

6 is the inner diameter of the roller set

T the inner diameter of the housing shoulder F is the mean diameter of the case support ring H is the outer diameter of the roller set J is the mean outer diameter of the shaft support

riage 4 © sad 41

0 is the rolling circle diameter of the roll set K the mean inner durometer of the housing β does jump 43 and 44 ·

As you can see on the dashed lines 46, and 48 sees, takes just like in the two-stage camp after lig. 1 of the Roillcreisdurohmesser of the roller sets 28, 29 and ▼ on the top or starting level of the camp aur the bottom or power amplifier down. It should also be pointed out that in the case of three-stage bearings (Tig · 2) the ratio of the Peder constants of the step rings 40 and 44 to the Fodor constants of the support ring 41 and 43 is usually about 2: 1, while the support rings 40 and 44 are usually the same "ederkonstant" and the members 41 and 43 usually have the same federation date.

From rorstehenden description concerns that duroh the invention provides a multi-stage · thrust bearing design dor receives _r in a uniform and controlled Belastungererteilung Durohbiegung under load result in a predictably reliable Dauerfeetigkeit of Lagexj.

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Claims (1)

DIPL-INQc HORST ROSE DIPL-ING. TcTER KOSEL (7 PATENT LAWYERS 3353 Bad Gandereheim, January 26, 1973 P.O. Box 129 Hohenhofen S. Telephone: (05388) 2842 Telegram address: Siedpatent Badgandershelm Our file no. 2704/3 Rollway Bearing Company, Inc. Protection claims 1 · Multi-stage axial bearing for transferring axial loads τοη ei ^ er wave switch on a housing shoulder, old At least two sets of races, which are at least an initial sat ~ on the wave bottom and an end seat of the housing shoulders, with the individual barrel sets each consist of a shaft bearing ring arranged on the shaft and a housing runner arranged on the housing, which have coordinated reducer constants and where the races each have a non-rectangular shape Have cross-section and cantilever or self-supporting eye-Q are in order, see that they bend under axial load, furthermore with sets of rollers each arranged between the opposing surfaces of a set of raceways, namely min-Ctest a beginning and a Bndrolleeatz, and with support rings for transmitting τοη axial forces, with at least Eia start and end support rings are seen and shaft support rings between adjacent shaft races as well as housing support rings between adjacent housing races « rings are arranged, daduroh characterized in that the total contact surface of a Rollensatses in the axial bearing (9,10 {28,29,30) with the faces of the associated races (H, 15, U, 17i 32,36,33,37,34,38) each approximately equal to the corresponding one Is the contact surface with the other sets of rollers, PK / Hn BanMconto: Norddwi "foh * UndMbwik, Pinal" BadaandwsMin, toilet no.22.11S.era · Potttcheokkonto: Hannover MT " that the deflection of the races under axial load is designed so that on opposite roller contact surfaces at least almost identical inclinations of the races are present, and that the ratio (S / E) of diameter (S) of the shaft shoulder (7; 25) to the middle diameter knife (E) of the one between the two of the shaft shoulder (7 - 25) closest shaft races (14,16; 32,35) arranged Initial shaft seat ring (18; 40) in the range of 1.00 to 1.30. 2 Axial bearings according to protection claim 1, characterized in that that the ratio (S / G) of shaft shoulder diameter (S) on the inner diameter (G) of the initial block set (9; 28) ranges from 0.90 to 1, $ 0 3., axial bearing according to protection claim 1 or 2, thereby characterized in that the ratio (T / P) of the inner diameter (T) of the housing shoulder (β; 27) to the mean diameter (?) of the between the two of the housing shoulder (8; 27) closest housing rings (15, 17; 37, 38) are arranged End housing support ring (19; 44) in the range of 0.80 to 1.00. 4. Axial bearings according to one of the protection claims? to 3, characterized in that the ratio (Τ / Η) τοη housing-'3 trains the inside diameter (T) to the outside diameter (H) of the End roller set (10; 30) is in the range of 0.90 to 1.10. 5 thrust bearing according to one of the slot claims 1 to 4, characterized in that in a three-stage bearing the ratio (J / C) of the mean outside diameter (J) of the welen support rings (40, 41) arranged between adjacent shaft races (32, 33; 33, 34) to form a rolling circle diameter (C) of the middle roller set (29) ranges from 0.70 to 0.90, and that the ratio (K / C) is middle Inner diameter (K) of the between adjacent housing races. (36,37; 37,38) arranged housing support rings (43,44) to the pitch circle diameter (C) of the middle roller set (29) ranges from 1.10 to 1.35 m · Λ > i 6. Axial bearings according to one of the 3ohutsan requirements 1 to 5, daduröh evkvuaävie'öÄw «,« w mis Remove one of its roll parts (9 _t 10j 2 ·, 29 »30) from the well-known white tob beginning roll part (9 {28) ims Bndrolleeati (10; 30). 7 · Axial bearings according to one of the Sohutian series 1 to 4 or 6, which are identified that with a multi-stage bearing the edge constant of the initial ring (18) is proportional to the load capacity of the initial roller position (9) xuxd the spring constant proportional to the final rolling ring (19) (10) are 8. Axiallager naoh Sohutsanepruoh 5 or 6, daduroh characterized in that in a three-stage bearing of the shaft switch (25) closest Sehäusestutsring (43) and that of the aehäueeeohulter (27) adjacent shaft support ring (41) has at least approximately the same spring conetante, and have the spring constant of the two support rings (43,41) and the spring constant of the beginning shaft support ring (40) and the end housing ring (44) is at least approximately 1: 2 Patent attorney · Dipl.-Ing. Hear Roee Oipl.-Ing. Peter Ko β el