WO2013178558A1 - Palier lisse radial comprenant un corps de coussinet flottant - Google Patents

Palier lisse radial comprenant un corps de coussinet flottant Download PDF

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Publication number
WO2013178558A1
WO2013178558A1 PCT/EP2013/060806 EP2013060806W WO2013178558A1 WO 2013178558 A1 WO2013178558 A1 WO 2013178558A1 EP 2013060806 W EP2013060806 W EP 2013060806W WO 2013178558 A1 WO2013178558 A1 WO 2013178558A1
Authority
WO
WIPO (PCT)
Prior art keywords
radial bearing
imbalance
bearing according
shaft
floating bush
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/EP2013/060806
Other languages
German (de)
English (en)
Inventor
Ralf Böning
Ralph-Maurice KÖMPEL
Christian Schmidt
Jürgen KROTTENTHALER
Stefan Reuter
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aumovio Germany GmbH
Original Assignee
Continental Automotive Technologies GmbH
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 Continental Automotive Technologies GmbH filed Critical Continental Automotive Technologies GmbH
Publication of WO2013178558A1 publication Critical patent/WO2013178558A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/18—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with floating brasses or brushing, rotatable at a reduced speed
    • 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

Definitions

  • the invention relates to a radial bearing which has a shaft mounted in a housing and a floating body provided between the housing and the shaft, wherein between the shaft and the Bergbüchsen endeavor an inner lubrication gap and between the housing and the Bergbüchsen redesign present an outer lubrication gap.
  • FIG. 1 A simplified, dimensionally oversized cross-sectional representation of such a radial bearing is shown in FIG.
  • a rotating shaft 8 which rotates at a speed n w
  • a housing 10 a likewise rotating floating bush body 1, which rotates at a speed n B .
  • a lubricating oil-filled outer lubricating gap 9 is provided between the housing 10 and the floating bush body 1.
  • lubricating oil is provided between the floating body 1 and the shaft 8 is also filled with lubricating oil inner lubricating gap 11.
  • the outer lubricating gap 9 the lubricating oil is provided by provided in the housing 10, not shown holes.
  • not shown holes are also provided in the floating body 1, through which the inner lubrication gap 11 is supplied from the outer lubricating gap 9 with lubricating oil.
  • a radial bearing equipped with a floating body has many advantages over a standing slide bearing the disadvantage that in operation when the shaft rotates at a high rotational speed, even small imbalances of the shaft instabilities of the camp have the result to complete destruction lead the camp.
  • the object of the invention is to provide a radial bearing in which an occurrence of instabilities of the radial bearing is reduced in the entire rotational speed range of the shaft. This object is achieved by a radial bearing with the features specified in claim 1. Advantageous embodiments of the invention are specified in the dependent claims.
  • a radial bearing having a rotatably mounted in a housing shaft and a provided between the housing and the shaft, rotatable in the housing about a rotation axis floating body, said floating body in the manner of a hollow cylinder, with an inner diameter of the shaft receives and an outer diameter for receiving in the housing, is formed and formed between the shaft and the inner diameter of the Wegbüchsen emotionss an inner lubricating gap and between the housing and the outer diameter of the Weg joschsen endeavor an outer lubricating gap, wherein the Weg joschsen endeavor is further designed such that it is equipped with a defined imbalance with respect to the axis of rotation of the floating body.
  • the imbalance refers to the axis of rotation of the
  • Floating bush body which is identical to the longitudinal axis of the floating bush body, which is located in the center relative to the outer diameter, and which coincides with the axis of rotation of the shaft with a concentric arrangement of the inner diameter and uniform formation of the inner lubricating gap over the circumference.
  • the defined imbalance is determined both in terms of their location relative to the swimming pool body as well as the amount in advance. The determination of the required amount as well as the advantageous position of the unbalance can be made in advance mathematical way, by computer simulation or in appropriate test series.
  • the cause of an imbalance lies in an uneven mass distribution of the rotating body, here the Wegbüchsen- body, based on its circumference on its structurally predetermined axis of rotation.
  • the uneven mass distribution Enver ⁇ a positional deviation of the axis of inertia of the rotating body results in relation to its rotational axis.
  • This positional deviation can be used as a measure of the size, ie the amount of imbalance and is also referred to as eccentricity.
  • the eccentricity indicates the magnitude of the positional deviation of the inertial axis of a rotary body to its axis of rotation, for example in millimeters (mm).
  • the radial bearing according to the invention in an advantageous embodiment is characterized in that the defined imbalance of the floating bush body, specified as eccentricity in relation to the bearing clearance of the inner lubricating gap, in a range between 15% and 35%, in particular 20% to 30% of the inner lubrication gap formed bearing clearance is.
  • the bearing clearance calculated as the double gap width of the inner lubricating gap with concentric arrangement of the shaft in the floating body.
  • there is a circumferential inner lubrication gap of 0.011 mm thus the bearing clearance is 0.022 mm.
  • an eccentricity of 0.0033 mm to 0.0077 mm would thus be provided.
  • the radial bearing according to the invention is characterized in that the defined unbalance of the floating bush body, specified as eccentricity, is in a range of 0. 003 mm to 0.008 mm, in particular 0.005 mm.
  • the ranges mentioned in the two aforementioned examples of the dimensioning of the imbalance have proven to be particularly advantageous in tests with shafts of a diameter range between 8 mm to 25 mm, since the defined imbalance on the one hand small is enough, in turn, not to negatively affect the concentricity of the overall system, on the other hand, however, is large enough to counterbalance the imbalance of the wave in the entire rotational speed range, especially in the range of high rotational speeds up to 250,000 revolutions / minute and beyond Act .
  • the unbalance of one, two or more introduced into the floating body bumps can be formed.
  • swimming pool body introduced through holes or blind holes, an inserted into the floating sleeve body inner groove or be formed by a deformation of the outer shell of the floating sleeve body.
  • the imbalance introduced into the floating body counteracts an imbalance of the shaft during operation of the radial bearing.
  • FIG. 2 shows a perspective sketch of a conventional one
  • FIG. 3 is a sectional view of a floating bush body whose imbalance is formed by a stepped bore;
  • FIG. 4 shows a sectional view of a floating bush body whose unbalance is formed by a blind hole
  • FIG. 5 shows a sectional view of a floating bush body whose imbalance is formed by a through-hole
  • Figure 6 is a sectional view of a floating bush body, the imbalance is formed by an inner groove and Figure 7 is a perspective sketch of a Wegstrachsenkör ⁇ pers, the imbalance is formed by a deformation of the Au ⁇ .mantels the Weghoffsen stressess.
  • Figure 8 is a frontal view of a swimming pool body, whose
  • Imbalance is formed by the eccentric arrangement of the outer diameter of the ⁇ floating bucket to the inner diameter of the floating sleeve.
  • FIG. 2 is a perspective sketch of a conventional swimming forth ⁇ can body 1 is shown.
  • This buoy body 1 is substantially hollow cylinder-shaped or tubular with an outer diameter D A and an inner diameter Di and has over its circumference evenly distributed more oil supply holes 2 through which in operation lubricating oil from the outside to the inside, ie from the outer lubrication gap to the inner Lubrication gap, is transported.
  • These oil feed bores 2 generally run in the radial direction in each case, have a predetermined diameter and are designed as through bores. alinstrument.
  • the floating body 1 shown in Figure 2 is symmetrical and thus has no intentional imbalance.
  • FIG. 3 shows a sectional view of a floating bush body 1 whose imbalance is formed by a stepped bore introduced into the floating bush body 1.
  • This swimming pool body 1 is also substantially hollow cylindrical or tubular. It has a total of six oil supply bores 2, of which 5 are denoted by the reference numeral 2 and one by the reference numeral 3.
  • This oil supply borehole 3 simultaneously serves to generate the imbalance of the floating bush body. It is designed to be stepped for this purpose, wherein it has in its radially outer region has a diameter which is greater than the diameter of the same bore in its radially inner region.
  • Diameter of the bore 3 in its radially inner region coincides with the diameter of the holes 2 respectively.
  • the diameter of the bore 3 in its radially outer region is greater than the diameter of the bore 3 in its radially inner region and thus larger than the diameter of the holes 2. This causes a targeted uneven mass distribution of the floating body over the circumference and thus in amount and location defined imbalance.
  • the imbalance of the floating bush body realized in the form of a stepped bore 3 counteracts an imbalance of the shaft in the entire rotational speed range of the shaft, in particular in the range of high rotational speeds, so that instabilities of the radial bearing and the probability of destruction of the bearing are reduced.
  • This swimming pool body 1 is also substantially hollow cylindrical or tubular. He has a total of six evenly distributed over the circumference introduced oil supply holes 2.
  • the blind hole 4 is used to generate the imbalance of the swimming pool body.
  • the blind hole 4 may in principle have the same diameter as the oil supply holes 2, which allows the production in the same operation with the same tool.
  • the blind bore 4 can also have a diameter different from the oil feed holes 2 if this is necessary for sufficient material removal to define the imbalance. This also causes a deliberately uneven mass distribution of the floating bush body over the circumference and thus an unbalance defined in magnitude and position.
  • FIG. 5 shows a sectional view of a floating bush body whose imbalance is formed by a through bore introduced into the floating bush body.
  • This swimming pool body 1 is also substantially hollow cylindrical or tubular. He has a total of six
  • This oil supply hole 5a simultaneously serves to generate the imbalance of the swimming ⁇ bushing body. It is designed for this purpose as a through hole whose diameter is constant and continuously larger than the diameter of the remaining holes 2. A corresponding result can alternatively be achieved by the arrangement of an additional through hole 5b (shown in phantom) between the equally distributed oil supply holes. 2 These two alternatives also cause a deliberately uneven mass distribution of the floating ⁇ bush body over the circumference and thus defined in magnitude and location unbalance. 0
  • the imbalance of the floating bush body implemented in the form of a through-hole 5 counteracts an imbalance of the shaft during operation of the radial bearing in the entire rotational speed range of the shaft, in particular in the range of high rotational speeds, so that instabilities of the radial bearing and the probability of destruction of the bearing are reduced.
  • FIG. 6 shows a sectional view of a floating bush body whose imbalance is formed by an inner groove 6 introduced into the floating bush body.
  • This swimming pool body 1 is also substantially hollow cylindrical or tubular. He has a total of six
  • the unbalance of the floating bush body realized in the form of an internal groove 6 or external groove counteracts an imbalance of the shaft during operation of the radial bearing in the entire rotational speed range of the shaft, in particular in the range of high rotational speeds, so that instabilities of the radial bearing and the probability of destruction of the bearing are reduced ,
  • FIG. 7 shows a perspective sketch of a floating ⁇ socket body, whose unbalance is formed by a deformation of the Au ⁇ . .mantels of the floating bushing body.
  • This swimming pool body 1 is also substantially hollow-cylindrical or tubular. He also has a total of six evenly distributed over the circumference ⁇ introduced oil supply holes 2 with matching diameters.
  • the deformation of the outer shell of the swimming pool bush body can be realized for example by a material removal in the form of one or more chamfers or flats.
  • the imbalance of the floating bush body realized by a deformation of the outer jacket of the Wegbüch- body acts against the operation of the radial bearing in the entire Drehgeschwindig ⁇ keits Scheme the shaft, especially in the range of high rotational speeds, an imbalance of the shaft, so that instabilities of the radial bearing and the probability of destruction of the warehouse are reduced.
  • FIG. 8 shows a frontal view of a floating bush body whose imbalance is formed by the eccentric arrangement of the inner diameter of the floating bush body relative to the outer diameter of the floating bush body.
  • the relative position deviation E between the center ⁇ ⁇ of the inside diameter and the center Z A of the Au ⁇ z is greatly oversubscribed. This measure also causes a deliberately uneven mass distribution of the floating bush body over the circumference and thus an unbalance defined in magnitude and location.
  • An imbalance equipped swimming pool body as shown in Figures 3 to 8 and described above, is part of a radial bearing having a shaft mounted in a housing, the Wegbüchseneffort is positioned between the housing and the shaft, wherein between the Shaft and the swimming pool body an inner lubrication gap and between the floating body and the housing is an outer lubrication gap.
  • swimming pool body transmitted and basically causes a deflection of the swimming pool body relative to

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

La présente invention concerne un palier radial qui présente un arbre monté dans un boîtier et un corps de coussinet flottant disposé entre le boîtier et l'arbre. Entre l'arbre et le corps de coussinet flottant est formé un espace de lubrification intérieur. Entre le boîtier et le corps de coussinet flottant est formé un espace de lubrification extérieur. Le corps de coussinet flottant présente un déséquilibre qui permet de contrecarrer un déséquilibre de l'arbre.
PCT/EP2013/060806 2012-05-29 2013-05-24 Palier lisse radial comprenant un corps de coussinet flottant Ceased WO2013178558A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012208960A DE102012208960A1 (de) 2012-05-29 2012-05-29 Radiallager
DE102012208960.8 2012-05-29

Publications (1)

Publication Number Publication Date
WO2013178558A1 true WO2013178558A1 (fr) 2013-12-05

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PCT/EP2013/060806 Ceased WO2013178558A1 (fr) 2012-05-29 2013-05-24 Palier lisse radial comprenant un corps de coussinet flottant

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DE (1) DE102012208960A1 (fr)
WO (1) WO2013178558A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2015190364A1 (ja) * 2014-06-12 2017-04-20 株式会社Ihi 軸受構造、および、過給機
CN107178557A (zh) * 2016-03-09 2017-09-19 西南石油大学 一种能实现稳定转动的螺旋套浮环轴承

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3064721B1 (fr) * 2015-03-03 2020-08-12 BorgWarner Inc. Turbocompresseur à gaz d'échappement comprenant un ensemble palier anisotrope
DE102017213492A1 (de) 2017-08-03 2019-02-07 Continental Automotive Gmbh Schwimmbuchsenlager für einen Abgasturbolader
DE102017213502A1 (de) 2017-08-03 2019-02-07 Continental Automotive Gmbh Schwimmbuchsenlager für einen Abgasturbolader

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS50104044U (fr) * 1974-02-05 1975-08-27
JPS58142014A (ja) * 1982-02-17 1983-08-23 Hitachi Ltd 浮動ブツシユ軸受
EP1550812A1 (fr) * 2004-01-02 2005-07-06 BorgWarner Inc. Turbomachine
JP2008111502A (ja) * 2006-10-31 2008-05-15 Toyota Motor Corp 軸受構造
JP2008190680A (ja) * 2007-02-07 2008-08-21 Ihi Corp 浮動ブッシュ軸受構造
DE102007036913A1 (de) * 2007-08-06 2010-12-02 Voith Patent Gmbh Abgasturbolader für eine Brennkraftmaschine
DE102010040158A1 (de) * 2010-09-02 2012-03-08 Federal-Mogul Wiesbaden Gmbh Strukturierte Schmutzdepots in Gleitlageroberflächen
WO2012132586A1 (fr) * 2011-03-29 2012-10-04 三菱重工業株式会社 Turbocompresseur et procédé de fabrication d'un coussinet flottant

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS50104044U (fr) * 1974-02-05 1975-08-27
JPS58142014A (ja) * 1982-02-17 1983-08-23 Hitachi Ltd 浮動ブツシユ軸受
EP1550812A1 (fr) * 2004-01-02 2005-07-06 BorgWarner Inc. Turbomachine
JP2008111502A (ja) * 2006-10-31 2008-05-15 Toyota Motor Corp 軸受構造
JP2008190680A (ja) * 2007-02-07 2008-08-21 Ihi Corp 浮動ブッシュ軸受構造
DE102007036913A1 (de) * 2007-08-06 2010-12-02 Voith Patent Gmbh Abgasturbolader für eine Brennkraftmaschine
DE102010040158A1 (de) * 2010-09-02 2012-03-08 Federal-Mogul Wiesbaden Gmbh Strukturierte Schmutzdepots in Gleitlageroberflächen
WO2012132586A1 (fr) * 2011-03-29 2012-10-04 三菱重工業株式会社 Turbocompresseur et procédé de fabrication d'un coussinet flottant

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2015190364A1 (ja) * 2014-06-12 2017-04-20 株式会社Ihi 軸受構造、および、過給機
CN107178557A (zh) * 2016-03-09 2017-09-19 西南石油大学 一种能实现稳定转动的螺旋套浮环轴承

Also Published As

Publication number Publication date
DE102012208960A1 (de) 2013-12-05

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