AT107213B - Shaft bearing. - Google Patents
Shaft bearing.Info
- Publication number
- AT107213B AT107213B AT107213DA AT107213B AT 107213 B AT107213 B AT 107213B AT 107213D A AT107213D A AT 107213DA AT 107213 B AT107213 B AT 107213B
- Authority
- AT
- Austria
- Prior art keywords
- bearing
- shaft
- shaft bearing
- cylindrical
- conical
- Prior art date
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
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/02—Sliding-contact bearings
- F16C23/04—Sliding-contact bearings self-adjusting
- F16C23/041—Sliding-contact bearings self-adjusting with edge relief
-
- 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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial 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
- F16C2300/00—Application independent of particular apparatuses
- F16C2300/02—General use or purpose, i.e. no use, purpose, special adaptation or modification indicated or a wide variety of uses mentioned
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sliding-Contact Bearings (AREA)
Description
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Wellenlagerung.
EMI1.1
Liegt die Welle a gleichachsig im Lager b (Fig. 1), so ist über die ganze Länge der Spalt von gleicher Weite und die Schmiermittelschicht von gleicher Stärke, so dass der Druck der Welle, sich gleichmässig auf die ganze Länge verteilt. Liegt die Welle dagegen schief im Lager, wie Fig. 2 zeigt, so nimmt je nach dem Grade der Schiefstellung nur noch ein grösserer oder geringerer Teil der Lagerlänge den Druck auf, z. B. zwischen den Punkten 1 und 2. Dabei ist 2 derjenige Punkt, an dem der Spalt etwa dieselbe Weite hat wie in Fig. 1.
Aus Fig. 2 ist ferner ersichtlich, dass ein besonders starker Druck im Punkt 7 auftritt, an dem sich keine genügende Schmiermittelschicht mehr befindet. Ähnlich ungünstig wird die Druckverteilung, wenn die Welle sich unter der Belastung durchbiegt, wie Fig. 3 zeigt.
Bekanntlich ist die Lagerreibung, falls die Belastung pro Flächeneinheit sich in zulässigen Grenzen hält, proportional der Lageriänge. Es wäre also theoretisch vorteilhaft, die Lager so kurz zu machen, wie es die Rücksicht auf dem spezifischen Fläehendtuek gestattet. Dies gilt aber nur bei einwandfreier gleichachsiger Lagerung. Dies zeigt Fig. 4 bei einem Lager bl, das bei gleichem Innendurchmesser und gleicher Wellenstärke erheblich kürzer als in Fig. 1-3 gehalten ist.
Hier ist eine viel stärkere Neigung
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der Welle möglich, und bei dieser stärkeren Neigung elgibt sieh eine beträchtlich weitere Verkürzung
EMI2.1
zeigt, so kann man die maximale Neigung wieder auf das Mass der Fig. 2 zurückführen und die tragende Strecke 6-6 bei geneigter Welle wieder auf das Mass 1-2 bringen ; jedoch geschieht dies auf Kosten der Stärke der Schmiermittelsehicht, was seinerseits, da die Lagerreibung umgekehrt pioportional der Ölschichte ist, zu einer derartigen Erhöhung der Lagerreibung führt, dass die durch Verkürzung des Lagers angestrebte Herabsetzung der Reibung illusorisch wird.
Bei der die Erfindung verkörpernden Lagerung gemäss Fig. 6 ist das Lager b3 im mittleren Teil von 7-8 zylindrisch und in den beiden Endteilen von 7-9 und von 8-10 konisch nach aussen sich erweiternd ausgebohrt. Der durch strichpunktierte Linien abgegrenzte mittlere Teil entspricht dem
EMI2.2
an in der Umfangsriehtung erheblich vergrösseit. Das gilt in entsprechender Abstufung auch für die Zwisehenpunkte. Hieraus folgen besonders günstige Reibungsverhältnisse. Die Fig. 10 und 11 zeigen, dass diese. Lagerform auch bei einfach und doppelt gekrümmten Wellen günstige Verhältnisse ergibt.
Fig. 12 stellt eine umgekehrte Anordnung dar, indem hier das Lager durchwegs zylindrisch ausge-
EMI2.3
konisch verjüngende Teile von 14-16 und von 15-17 besitzt.
In Fig. 13 sind die Lagerflächen des Lagers b4 sowohl als der Welle a2 in der Mitte zylindrisch, dagegen an den Enden divergierend konisch gestaltet.
Bei dem Lager b5 der Fig. 14, das wieder eine durchwegs zylindrische Welle a aufnimmt, haben die an den zylindrischen mittleren Teil des Lagers sich anschliessenden Kegelflächen kmvenförmige Eizeugende 18-20 und 19-21, zu denen die Erzeugende des zylindrischen Teiles 18-19 tangential verläuft, so dass man keine Übergangskanten erhält. Diese Kanten, z. B. bei 7 und 8 der Fig. 6, sind natürlich bei der praktischen Ausführung nicht so ausgeprägt, wie in. den Zeichnungen dargestellt, die, wie eingangs bemerkt, zur besonderen Veranschaulichung stark übertreiben, und machen sieh daher praktisch kaum störend bemerkbar.
In Fig. 15 ist umgekehrt wie bei Fig. 14 wieder das Lager b zylindrisch ausgebohrt und der damit zusammenwirkende Teil der Welle a3 nach einer konvexen, in der Mitte im wesentlichen parallel zur Achse verlaufenden Kurve abgedreht.
In Fig. 16 ist das Lager b6 an einem Ende von 22-23 zylindrisch gehalten und bis zum ändern Ende von 23-24 konisch erweitert. Diese Form kommt in Betracht, wenn man nur mit einer Deformation der Welle a auf der einen Seite des Lagers zu rechnen hat, wie dargestellt ist. Natürlich wird auch das beiderseits konisch erweiterte Lager gemäss Fig. 6 diesem Falle gerecht.
PATENT-ANSPRÜCHE :
1. Wellenlagerung, dadurch gekennzeichnet, dass die Lagerflächen des Lagers und der Welle derart gestaltet sind, dass sie nur in einem Teil sowohl unter sich als zur Achse im wesentlichen parallel verlaufen und im übrigen mindestens nach einem Lagerende hin divergieren.
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Shaft bearing.
EMI1.1
If the shaft a lies coaxially in the bearing b (Fig. 1), the gap is of the same width over the entire length and the lubricant layer is of the same thickness, so that the pressure of the shaft is evenly distributed over the entire length. If, on the other hand, the shaft is inclined in the bearing, as shown in FIG. 2, then, depending on the degree of inclination, only a greater or lesser part of the bearing length takes on the pressure, e.g. B. between points 1 and 2. Here, 2 is the point at which the gap has approximately the same width as in FIG. 1.
It can also be seen from FIG. 2 that a particularly strong pressure occurs at point 7 at which there is no longer a sufficient layer of lubricant. The pressure distribution becomes similarly unfavorable if the shaft deflects under the load, as FIG. 3 shows.
It is known that the bearing friction is proportional to the bearing length if the load per unit area is within permissible limits. In theory, it would therefore be advantageous to make the camps as short as the specific surface area allows. However, this only applies to perfect coaxial storage. This is shown in FIG. 4 with a bearing B1 which, with the same inner diameter and the same shaft thickness, is kept considerably shorter than in FIGS. 1-3.
Here is a much stronger bias
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of the wave possible, and with this greater inclination there is a considerably further shortening
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shows, the maximum inclination can be brought back to the dimension of FIG. 2 and the bearing distance 6-6 can be brought back to the dimension 1-2 when the shaft is inclined; However, this happens at the expense of the strength of the lubricant layer, which in turn, since the bearing friction is inversely proportional to the oil layer, leads to such an increase in bearing friction that the reduction in friction aimed at by shortening the bearing becomes illusory.
In the case of the bearing according to FIG. 6 embodying the invention, the bearing b3 is bored outwardly in a cylindrical manner in the middle part from 7-8 and in the two end parts from 7-9 and from 8-10. The middle part delimited by dash-dotted lines corresponds to this
EMI2.2
considerably enlarged in the circumferential direction. This also applies in a corresponding gradation to the intermediate points. This results in particularly favorable friction conditions. Figs. 10 and 11 show that this. Bearing shape results in favorable conditions even with single and double curved shafts.
Fig. 12 shows the reverse arrangement, in that here the bearing is cylindrical throughout.
EMI2.3
Has conical tapering parts 14-16 and 15-17.
In FIG. 13, the bearing surfaces of the bearing b4 as well as the shaft a2 are cylindrical in the middle, but have a diverging conical shape at the ends.
In the case of the bearing b5 of FIG. 14, which again receives a completely cylindrical shaft a, the conical surfaces adjoining the cylindrical central part of the bearing have kmvoid-shaped ovoid ends 18-20 and 19-21, to which the generatrix of the cylindrical part 18-19 runs tangentially so that there are no transition edges. These edges, e.g. B. at 7 and 8 of FIG. 6, are of course not as pronounced in the practical implementation as shown in the drawings, which, as noted at the beginning, exaggerate greatly for the purpose of special illustration, and therefore make it practically hardly noticeable.
In Fig. 15, contrary to Fig. 14, the bearing b is again bored out cylindrically and the part of the shaft a3 cooperating with it is turned off according to a convex curve running essentially parallel to the axis in the center.
In Fig. 16, the bearing b6 is held cylindrically at one end of 22-23 and flared to the other end of 23-24. This form comes into consideration if one only has to reckon with a deformation of the shaft a on one side of the bearing, as shown. Of course, the bearing which is flared on both sides according to FIG.
PATENT CLAIMS:
1. Shaft bearing, characterized in that the bearing surfaces of the bearing and the shaft are designed in such a way that they run essentially parallel to each other and to the axis only in part and otherwise diverge at least towards one end of the bearing.
Claims (1)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT107213T | 1926-07-16 |
Publications (1)
Publication Number | Publication Date |
---|---|
AT107213B true AT107213B (en) | 1927-09-10 |
Family
ID=3624228
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
AT107213D AT107213B (en) | 1926-07-16 | 1926-07-16 | Shaft bearing. |
Country Status (1)
Country | Link |
---|---|
AT (1) | AT107213B (en) |
Cited By (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2674904A (en) * | 1950-04-22 | 1954-04-13 | Gen Motors Corp | Camshaft |
US2870719A (en) * | 1955-10-04 | 1959-01-27 | Thompson Prod Inc | Bushing for pressure loaded gear pump having a tapered journal surface |
US2870720A (en) * | 1956-01-10 | 1959-01-27 | Thompson Prod Inc | Movable bushing for a pressure-loaded gear pump |
US2883738A (en) * | 1955-03-09 | 1959-04-28 | Diamond Chain Company Inc | Method of making annular elements for power-transmission chains |
US3129984A (en) * | 1961-06-16 | 1964-04-21 | Do Company | Journal stop and adapter therefor |
US3454217A (en) * | 1964-08-31 | 1969-07-08 | Measuring & Scient Equipment L | Load carriers and centrifuges |
US3490819A (en) * | 1968-01-18 | 1970-01-20 | Babcock & Wilcox Co | Hydrostatic spindle |
US3766792A (en) * | 1970-11-24 | 1973-10-23 | Halbach & Braun | Planer drive system |
US4485743A (en) * | 1982-09-29 | 1984-12-04 | General Motors Corporation | High efficiency semi-articulated railway power truck |
US4940002A (en) * | 1988-12-07 | 1990-07-10 | General Motors Corporation | Railway traction motor with skewed support bearings |
US5407334A (en) * | 1991-03-04 | 1995-04-18 | Mitsubishi Denki Kabushiki Kaisha | Scroll type compressor having a convex surface on the sub frame bushing |
EP0753678A2 (en) * | 1996-07-17 | 1997-01-15 | Maag Pump Systems AG | Sliding-contact bearing for a shaft |
US6168403B1 (en) | 1999-05-10 | 2001-01-02 | Carrier Corporation | Rotating compressor bearing with dual taper |
EP1717466A2 (en) * | 2005-04-27 | 2006-11-02 | A. Friedr. Flender Ag | Slide bearing with an enlarging bearing gap in the end zone |
EP2087227A1 (en) * | 2006-10-31 | 2009-08-12 | Robert Bosch GmbH | Delivery pump, in particular for delivering diesel fuel, having improved mounting of the drive shaft |
DE102012217856A1 (en) * | 2012-09-28 | 2014-04-03 | Sennheiser Electronic Gmbh & Co. Kg | Electronic device has electronic or electrical component arranged in housing is adjustable by rotating and is comprised with rotational axis, and spherical element is provided in region of opening and is coupled with rotational axis |
DE102017131096A1 (en) * | 2017-12-22 | 2019-06-27 | Lucas Automotive Gmbh | Gear assembly for a geared motor of an electrically actuated brake, gear motor, parking brake system and service brake system |
EP3705723A1 (en) * | 2019-03-08 | 2020-09-09 | LG Electronics Inc. | Scroll compressor |
US11085240B2 (en) * | 2018-07-27 | 2021-08-10 | Halliburton Energy Services, Inc. | Radial bearing apparatus for use with side forces |
EP3865675A1 (en) * | 2020-02-13 | 2021-08-18 | Honeywell International Inc. | Variable vane system for turbomachine with linkage having tapered receiving aperture for unison ring pin |
-
1926
- 1926-07-16 AT AT107213D patent/AT107213B/en active
Cited By (26)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2674904A (en) * | 1950-04-22 | 1954-04-13 | Gen Motors Corp | Camshaft |
US2883738A (en) * | 1955-03-09 | 1959-04-28 | Diamond Chain Company Inc | Method of making annular elements for power-transmission chains |
US2870719A (en) * | 1955-10-04 | 1959-01-27 | Thompson Prod Inc | Bushing for pressure loaded gear pump having a tapered journal surface |
US2870720A (en) * | 1956-01-10 | 1959-01-27 | Thompson Prod Inc | Movable bushing for a pressure-loaded gear pump |
US3129984A (en) * | 1961-06-16 | 1964-04-21 | Do Company | Journal stop and adapter therefor |
US3454217A (en) * | 1964-08-31 | 1969-07-08 | Measuring & Scient Equipment L | Load carriers and centrifuges |
US3490819A (en) * | 1968-01-18 | 1970-01-20 | Babcock & Wilcox Co | Hydrostatic spindle |
US3766792A (en) * | 1970-11-24 | 1973-10-23 | Halbach & Braun | Planer drive system |
US4485743A (en) * | 1982-09-29 | 1984-12-04 | General Motors Corporation | High efficiency semi-articulated railway power truck |
US4940002A (en) * | 1988-12-07 | 1990-07-10 | General Motors Corporation | Railway traction motor with skewed support bearings |
US5407334A (en) * | 1991-03-04 | 1995-04-18 | Mitsubishi Denki Kabushiki Kaisha | Scroll type compressor having a convex surface on the sub frame bushing |
EP0753678A3 (en) * | 1996-07-17 | 1997-02-05 | Maag Pump Systems Ag | |
EP0753678A2 (en) * | 1996-07-17 | 1997-01-15 | Maag Pump Systems AG | Sliding-contact bearing for a shaft |
US5913608A (en) * | 1996-07-17 | 1999-06-22 | Maag Pump Systems Textron Ag | Slide bearing for a shaft |
US6168403B1 (en) | 1999-05-10 | 2001-01-02 | Carrier Corporation | Rotating compressor bearing with dual taper |
EP1717466A2 (en) * | 2005-04-27 | 2006-11-02 | A. Friedr. Flender Ag | Slide bearing with an enlarging bearing gap in the end zone |
DE102005019984A1 (en) * | 2005-04-27 | 2006-11-09 | A. Friedr. Flender Ag | plain bearing |
EP1717466A3 (en) * | 2005-04-27 | 2008-04-23 | A. Friedr. Flender Ag | Slide bearing with an enlarging bearing gap in the end zone |
EP2087227A1 (en) * | 2006-10-31 | 2009-08-12 | Robert Bosch GmbH | Delivery pump, in particular for delivering diesel fuel, having improved mounting of the drive shaft |
DE102012217856A1 (en) * | 2012-09-28 | 2014-04-03 | Sennheiser Electronic Gmbh & Co. Kg | Electronic device has electronic or electrical component arranged in housing is adjustable by rotating and is comprised with rotational axis, and spherical element is provided in region of opening and is coupled with rotational axis |
DE102017131096A1 (en) * | 2017-12-22 | 2019-06-27 | Lucas Automotive Gmbh | Gear assembly for a geared motor of an electrically actuated brake, gear motor, parking brake system and service brake system |
US11639165B2 (en) | 2017-12-22 | 2023-05-02 | Zf Active Safety Gmbh | Gear assembly for a geared motor of an electrically operable brake, geared motor, parking brake system, and service brake system |
US11085240B2 (en) * | 2018-07-27 | 2021-08-10 | Halliburton Energy Services, Inc. | Radial bearing apparatus for use with side forces |
US11639634B2 (en) | 2018-07-27 | 2023-05-02 | Halliburton Energy Services, Inc. | Radial bearing apparatus for use with side forces |
EP3705723A1 (en) * | 2019-03-08 | 2020-09-09 | LG Electronics Inc. | Scroll compressor |
EP3865675A1 (en) * | 2020-02-13 | 2021-08-18 | Honeywell International Inc. | Variable vane system for turbomachine with linkage having tapered receiving aperture for unison ring pin |
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