WO1990015264A1 - Palier a glissement - Google Patents

Palier a glissement Download PDF

Info

Publication number
WO1990015264A1
WO1990015264A1 PCT/AT1990/000059 AT9000059W WO9015264A1 WO 1990015264 A1 WO1990015264 A1 WO 1990015264A1 AT 9000059 W AT9000059 W AT 9000059W WO 9015264 A1 WO9015264 A1 WO 9015264A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
plain bearing
particular according
grooves
annular groove
Prior art date
Application number
PCT/AT1990/000059
Other languages
German (de)
English (en)
Inventor
Miroslav Beranek
Friedrich Franek
Andrzej Maciszewski
Original Assignee
Miroslav Beranek
Friedrich Franek
Andrzej Maciszewski
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 Miroslav Beranek, Friedrich Franek, Andrzej Maciszewski filed Critical Miroslav Beranek
Publication of WO1990015264A1 publication Critical patent/WO1990015264A1/fr

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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid

Definitions

  • the invention relates to a slide bearing with a grooved axial bearing part, for building up a hydrodynamic lubricating film.
  • the object of the invention is to specify plain bearings that absorb both axial and radial forces, with an overall design that is as cost-effective as possible. This object is achieved in the invention specified in claim 1.
  • the axial bearing part is formed in the one-piece plain bearing made of sintered material as the bottom of a cylindrical depression, the inner cylindrical surface of which forms the radial bearing part, the grooves deepening radially outward and opening into an outer annular groove.
  • the sintered material makes it possible to form the slide bearing in one piece without a separate lubricant feed, which would have to pass through the slide bearing, for example.
  • the sintered material has advantageous properties when starting, in the area of mixed and transitional friction. Due to the fact that the grooves are recessed towards the outside, a load-bearing lubricating film is obtained relatively quickly.
  • the bearing is also suitable for appropriately absorbing the increasing axial force with higher speeds.
  • the outer annular groove produces a certain jam of the lubricant, which is exposed to a correspondingly high centrifugal force at the high speeds.
  • a second annular groove is formed concentrically with the first annular groove.
  • This second ring groove can also advantageously be deeper than the first ring groove.
  • the bottom of the cylindrical recess is essentially perpendicular to a shaft axis.
  • the inner cylinder surface is preferably essentially flat, without grooves.
  • the shaft also preferably has a groove formation neither in the area of the radial nor the axial bearing part.
  • the grooves themselves, in the bottom of the cylindrical depression, are preferably formed with a wedge-shaped cross section.
  • the slide bearing is held by means of a diaphragm part compensating for angular deviations. Any slight angular deviations that may occur in the axial alignment of the shaft can thus advantageously be compensated for.
  • the membrane part likewise provides a certain resilient reception in the axial direction.
  • the membrane part can consist, for example, of a spring material.
  • the plain bearing is held by means of a double membrane.
  • the cross-section is tapered radially outwards. In this way, too, an advantageous jamming effect can be achieved, the tapering also being able to be provided in combination with the mentioned outer ring grooves.
  • Figure 1 is a schematic representation of a shaft of a vacuum cleaner motor with two bearings.
  • FIG. 2 shows a cross section, partly in a schematic position, of a first embodiment of a slide bearing for absorbing axial and radial forces
  • 3 shows a representation according to FIG. 2 of a second embodiment
  • FIG. 5a-e plan views of different embodiments of the slide bearing with respect to the grooves; and FIG. 6 shows a cross section through FIG. 5b along the line VI-VI.
  • the invention is described below in connection with the mounting of the shaft of a vacuum cleaner motor. However, the invention is in no way limited to this.
  • the slide bearing according to the invention is suitable for any application in which axial and radial forces arise during operation and are to be absorbed by the bearing.
  • 1 denotes the shaft of a vacuum cleaner motor which is not shown in detail.
  • a rotor 2 is arranged on the shaft 1, which is shown in FIG. 1 in an exaggeratedly asymmetrical manner on the shaft 1 for clarity. This results in a radial force F R during operation.
  • An impeller 3, which is shown only schematically in the drawing, is arranged at one shaft end and generates an axial force FA to be absorbed in the bearings during operation.
  • the shaft is supported in two plain bearings 4 and 5. While the plain bearing 4 is essentially only designed to absorb radial forces, the plain bearing 5, which in various embodiments according to the invention is described below in detail, is is written, designed to absorb axial and radial forces.
  • the slide bearing 5 consists of an axial bearing part 6 and a radial bearing part 7.
  • the slide bearing 5 is formed in one piece and further consists of a sintered material. Separate feeds for lubricants, which penetrate the slide bearing 5, for example, are not provided with respect to the radial bearing part 7.
  • the axial bearing part is designed as a bottom of a cylindrical depression that extends essentially perpendicular to a shaft axis 8. The cylindrical inner surface forms the radial bearing part 7.
  • Grooves 9 are formed in the axial bearing part 6, which deepen radially outwards and open into an annular groove 10.
  • a second annular groove 10 ′ is formed concentrically with the first annular groove 10, which also has a greater depth than the first annular groove 10.
  • the grooves 9 are formed with a substantially wedge-shaped cross section.
  • the radial bearing part 7 is formed with an essentially flat surface. Because of the sintered material from which the slide bearing 5 is made, there are also favorable conditions with regard to the radial bearing part 7 when the vacuum cleaner motor starts up.
  • the plain bearing 5 continues beyond the bottom forming the axial bearing part 6 in the form of a smaller-diameter hub 11, which forms a shoulder 13 at a distance from an outer cylindrical bottom ring surface 12, which merges into a smaller-diameter section 14.
  • the slide bearing 5 is fastened by means of a fastening ring 15 to a membrane part 16, which in turn is fastened to a bearing plate 17.
  • the diaphragm part 16, which can consist, for example, of a thin spring steel element, is designed such that it - relatively small - angular deviations of the motor shaft 1, the can compensate for the angle deviations of the axis 8 by an angle plus / minus alpha - shown exaggerated in FIGS. 2 and 3.
  • a membrane part 16 ' is provided, which goes directly into a bearing element 16 ".
  • FIG. 3 shows an axial and radial sliding bearing accommodated in two membrane parts 16.
  • the same reference symbols refer to the same elements or features as have already been described above, unless deviations are explained in the following.
  • the sliding bearing 5 is also designed in its outer dimensions as an essentially cylindrical body, with ball-joint-like transition regions 18 which interact with ball socket-like configurations 19 of the two membranes. Due to the double-provided diaphragms 16, the slide bearing 5 can compensate for angular deviations of the axis 8 and slight axial displacements in approximately the same way as in the embodiment according to FIG. 2, but is stiffer in the radial direction.
  • Fig. 4 shows a perspective view of a plain bearing 5, essentially in accordance with the configuration according to Fig. 2. However, in this embodiment only an outer annular groove 10 is provided. The wedge-shaped design of the grooves 9 can be seen.
  • the grooves 9 are delimited by two convexly curved flank regions 20 and 21 such that a cross-sectional area decreases from radially inside to radially outside.
  • the cross-sectional area also decreases from radially inside to radially outside.
  • the flank regions 20 'and 21' are curved in the same direction.
  • a center line 22 is also correspondingly curved.
  • the center line 22 of a groove 9 is curved.
  • the flank areas 20 "and 21 " run in the same direction in this embodiment.
  • the cross section in this embodiment increases from radially inside to radially outside.
  • the grooves 9 are designed as relatively large, essentially triangular, outwardly widening recesses. These recesses can, for example, have an opening angle beta of 60 °.
  • the triangular tip lies on the inner circumference 23, which delimits the opening for the throughput of the shaft.
  • a triangular base body 24 is arranged in the recesses or grooves 9 in such a way that two separate grooves 9 'and 9 "result.
  • the triangular base bodies are at their tips 24'.
  • the center line 25 lies on a radial of the slide bearing 5.
  • two divided triangular base bodies 24 are arranged such that there is a third flow path 9 in the area of the radial of the slide bearing 5 "'results.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Mechanical Engineering (AREA)
  • Sliding-Contact Bearings (AREA)
  • Support Of The Bearing (AREA)

Abstract

Palier à glissement comportant une partie palier de butée (6) dotée de rainures (9) et servant à constituer un film lubrifiant hydrodynamique. Cette partie palier de butée (6) prend dans le palier à glissement monobloc en matériau fritté (5) la forme du fond d'un évidement cylindrique dont la surface cylindrique interne constitue la partie palier proprement dite (7). Les rainures (9) se creusent radialement vers l'extérieur et débouchent dans une rainure annulaire extérieure (10).
PCT/AT1990/000059 1989-06-09 1990-06-11 Palier a glissement WO1990015264A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19893918844 DE3918844A1 (de) 1989-06-09 1989-06-09 Staubsaugermotor
DEP3918844.2 1989-06-09

Publications (1)

Publication Number Publication Date
WO1990015264A1 true WO1990015264A1 (fr) 1990-12-13

Family

ID=6382408

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/AT1990/000059 WO1990015264A1 (fr) 1989-06-09 1990-06-11 Palier a glissement

Country Status (2)

Country Link
DE (1) DE3918844A1 (fr)
WO (1) WO1990015264A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB0125402D0 (en) 2001-10-23 2001-12-12 Johnson Electric Sa Electric motor
GB0125400D0 (en) 2001-10-23 2001-12-12 Johnson Electric Sa Electric motor

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH473324A (de) * 1965-10-05 1969-05-31 Philips Nv Hydrodynamisches Gleitlager
DE1525216A1 (de) * 1965-05-06 1969-09-04 Ringsdorff Werke Gmbh Gleitlager fuer Axialdruckaufnahme
FR2152023A5 (fr) * 1971-08-31 1973-04-20 Philips Nv

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1525216A1 (de) * 1965-05-06 1969-09-04 Ringsdorff Werke Gmbh Gleitlager fuer Axialdruckaufnahme
CH473324A (de) * 1965-10-05 1969-05-31 Philips Nv Hydrodynamisches Gleitlager
FR2152023A5 (fr) * 1971-08-31 1973-04-20 Philips Nv

Also Published As

Publication number Publication date
DE3918844A1 (de) 1990-12-13

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