WO2008128833A1 - Dispositif pour la compensation de déplacements relatifs axiaux consécutifs à des effets thermiques - Google Patents

Dispositif pour la compensation de déplacements relatifs axiaux consécutifs à des effets thermiques Download PDF

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Publication number
WO2008128833A1
WO2008128833A1 PCT/EP2008/053270 EP2008053270W WO2008128833A1 WO 2008128833 A1 WO2008128833 A1 WO 2008128833A1 EP 2008053270 W EP2008053270 W EP 2008053270W WO 2008128833 A1 WO2008128833 A1 WO 2008128833A1
Authority
WO
WIPO (PCT)
Prior art keywords
compensating
drive element
compensating part
compensation
thermally induced
Prior art date
Application number
PCT/EP2008/053270
Other languages
German (de)
English (en)
Inventor
Tomas Smetana
Thorsten Biermann
Original Assignee
Schaeffler Kg
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 Schaeffler Kg filed Critical Schaeffler Kg
Publication of WO2008128833A1 publication Critical patent/WO2008128833A1/fr

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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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • 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
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F16C25/08—Ball or roller bearings self-adjusting
    • 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
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B2200/00—Constructional details of connections not covered for in other groups of this subclass
    • F16B2200/97—Constructional details of connections not covered for in other groups of this subclass having differing thermal expansion coefficients
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F16C19/525—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to temperature and heat, e.g. insulation

Definitions

  • the invention relates to a device for compensating for thermally induced relative axial displacements between two components with two compensating parts which convert a thermally induced relative radial movement of the active surfaces in an axial temperature compensating movement of at least one compensating part on cooperating active surfaces.
  • the gearbox housing is generally made in aluminum diecasting and the gearbox shafts are made of steel and mounted by means of an engaged cone roller bearing.
  • the approximately twice as high thermal expansion of the aluminum housing in comparison to the steel shafts significantly noticeable and changes the set preload or the set clearance of the tapered roller bearing. This leads to a significantly reduced bearing life, at worst to an axial Wei- and not ideal meshing with appropriate noise.
  • thermal expansion compensating ring is made of a material - e.g. the elastomer marketed under the trade name VITON® by Dupont - with a significantly higher temperature coefficient than the components subjected to thermal fluctuations.
  • VITON® elastomer marketed under the trade name VITON® by Dupont - with a significantly higher temperature coefficient than the components subjected to thermal fluctuations.
  • the thermal expansion compensating ring transmits the required axial prestressing to the bearing outer ring and is thus exposed to a considerable mechanical load leading to a long-term unstable setting behavior.
  • DE 42 21 802 A1 proposes a compensation device in which two concentric bathdehnungsaus GmbHsringe be serially connected in a mounting ring with a partial longitudinal section approximately S-shaped in shape.
  • an object of the present invention is to provide a device for the compensation of thermally induced axial relative displacements between two components, which compensates for a very small axial space requirement by simple means comparatively large thermally induced relative changes in length between two components.
  • At least one compensation part is provided with a drive element which has a higher coefficient of thermal expansion than the compensation part.
  • the drive element acts as a kind of reinforcing element and amplifies the radial movement - that is, the expansion or contraction of the compensating part in the radial direction - the compensating part beyond the movement of the compensating part, which is in any case due to the thermal and temperature-coefficient behavior.
  • the compensation part is designed as a steel or aluminum ring
  • the mechanical coupling with the drive element causes an additional Radialwars- component with temperature change, which is based solely on the elongation / contraction of the drive element and causes an elastic radial springing of the compensating part and thus its active surface.
  • a first advantage of the invention is that with very simple and few additional components compared to the state of the art significantly less expensive compensation even comparatively large relative changes in length between components is realized.
  • Another advantage of the invention is that these properties are ensured long-term stability even at high operating loads, because the mechanically loaded parts (balancing parts) in their material selection can be optimized independently of the responsible for the compensation movement drive element.
  • the mechanically highly loaded compensating parts can thus consist of inexpensive and robust materials such as steel, while the drive element is made of a material with a much higher temperature coefficient.
  • a preferred embodiment of the invention provides that the compensating part has at its periphery a separation point which has an increased radial mechanical Auffederungsl. Contractility causes.
  • the compensating part can experience orders of magnitude larger radial expansions than the compensating part known from the initially mentioned DE 41 18 933 A1 in the form of a metal disc.
  • the separation point can be formed by telescoping ends of the compensation part.
  • the compensation part always has an outwardly closed shape.
  • the separation point is formed by a slot.
  • an axial material recess may be provided, so that the compensation part can expand mechanically resiliently radially under enlargement of the slot and vice versa while reducing the slot is radially compressible.
  • This embodiment has an off elastic material existing compensating part the further advantage that this with radial bias - can be mounted - for example in a housing bore.
  • a particularly simple embodiment of the drive element provides that this is designed annular.
  • the drive element can be accommodated in particular in likewise annularly shaped compensation parts of this.
  • a particularly advantageous variant of the invention provides that the compensation part is hollow and filled with a material forming the drive element.
  • the advantageously hollow ring-shaped compensating part can be produced by corresponding folding, for example a steel strip, and filled with the material of the drive element.
  • the drive element can also be formed only by solidification or connection, for example polymerization, of the material introduced into the cavity of the compensating part.
  • the drive element is axially slotted and is supported with its slot boundary surfaces on a counterpart.
  • the counterpart may preferably be formed as an integral part of a holding element on which the drive element is applied.
  • the holding element holds the balancing parts together to form a structural unit.
  • the counterpart may be according to a preferred variant of the invention, a piston which is mounted in the compensating part.
  • FIG. 1 shows a first embodiment of the invention in longitudinal section
  • FIG. 2 is an exploded view of essential elements of the device according to the invention, and the arrangement of the elements in the region of a separation point is greatly enlarged;
  • Figure 3 shows a second embodiment of a device according to the invention in longitudinal section
  • Figure 4 in an exploded view of essential elements of the device of Figure 3 and greatly enlarged representation of these elements in the region of a separation point.
  • the devices shown in the figures are used for example to ensure or maintain a set bearing clearance or a bearing preload for a tapered roller bearing, in particular in a differential or a transmission of a motor vehicle.
  • the device acts on a so-called X-arrangement tapered roller bearing 1 on the outer ring 2 a.
  • the outer ring 2 is received in a bore 3 of an aluminum die-cast housing 4.
  • a bearing cage 5 holds spaced a plurality of tapered rollers 6.
  • the tapered rollers roll on the tread 7 of the outer ring 2 and on the running surface 8 of the bearing inner ring 9 from.
  • the inner ring 9 is pressed onto one end 10 of a gear shaft 11.
  • the device comprises a first compensating part 12 with a conical bore 14.
  • the cone forms a first active surface or sliding surface 15.
  • the compensating part 12 is made of steel and is therefore mechanically highly loadable and inexpensive to produce.
  • the device comprises a second compensating part 18, which in this embodiment is configured as a compensating ring and made of a multiply bent steel disc. Of course, however, other cross sections for the compensation part 18 can be selected.
  • the compensation part 18 has a circumferential cavity 19, which is filled with a plastic material 20 - for example an elastomer.
  • the plastic can already be prefabricated in a corresponding ring shape or first filled into the cavity 19 and then by suitable manufacturing methods - for example, a heat treatment - obtained in the balancing part of its solid form.
  • the material 20 forms a ring 21 (drive ring) whose temperature coefficient is material-related by a multiple greater than the temperature coefficient of the compensation part 18.
  • the ring 21 thereby forms a drive element 22.
  • drive element is in the context of the present invention, a component to understand the Reinforcement of the radial expansion or radial contraction of the compensating part 18 is used.
  • the compensation part 18 completely surrounds the drive element 22, so that there is a close mechanical coupling here.
  • the drive element 22 expands significantly more than the compensation part 18, with the result that it imparts its radial extent to the compensation part 18. This would basically be complete circumferential compensating part 18 possible.
  • the compensation part 18 has an axially extending slot or a recess 24.
  • the compensation part 18 can spring up mechanically much more strongly - driven by the drive element - than it would allow the material elasticity of the compensation part 18 alone.
  • the slot 24 forms a defined separation point 25 in the compensation part 18.
  • a steel piece is received in the form of a circular segment, which forms a piston 26.
  • the piston 26 is matched to the inner contour 28 of the cavity 19 and thus displaceably mounted in the compensation part 18 along the circumference.
  • FIG. 2 Details of this arrangement are shown more clearly in FIG. 2, in which the compensation element 18, also referred to as inner ring, with the separation point 25 (slot 24) is shown.
  • the open ends 30, 31 of the split-off compensation part 18 can also engage in one another in the manner of a telescope and thus form a closed shape in the circumferential direction U.
  • the drive ring 21 which acts as a drive element 22 in the previously described manner. Furthermore, the first compensating part 12 can be seen, which forms an outer ring insofar.
  • the plastic ring 21 also has at its periphery a recess or a slot 32 into which the piston 26 is inserted. As shown in particular in the lower part of Figure 2 greatly enlarged partially illustrated region of the separation point 25, the slot 32 of the drive member 22 is filled by the piston 26.
  • the drive element is supported with its slot boundary surfaces 35, 36 on the corresponding end faces 37, 38 of the piston 26.
  • This construction has the advantage that a significantly increased radial mobility of the compensating part 18 is realized by the slot 24, without the drive element 22 being exposed to unwanted external influences due to the slit 24, which changes its width according to its operation.
  • the compensation part 18 With an expansion of the drive element 22 due to temperature increase or a contraction due to temperature reduction, the compensation part 18 is forcibly imposed on the radial expansion or contraction of the drive member 22, ie, the compensation member 18 is moved radially accordingly. It slides with the formed on its outside, the first drive element 12 facing active surface 40 having a corresponding cone angle ⁇ , on the corresponding active surface 15 of the first equalizer 12. This results in a significant increase in length ⁇ H the device length H.
  • ⁇ T temperature difference between the initial state and the compensation state
  • ⁇ half angle of the conical cone of the active surface 15 or 40
  • the axial displacement .DELTA.H which can be compensated in this way is measured using typical bearing geometries and a drive element made of VITON®
  • the drive element is made of a material optimized with regard to the temperature coefficient, which has 30 to 45 times higher thermal expansion compared to steel.
  • the compensating parts which are mechanically stressed during operation are produced from a material (for example steel) optimized in terms of manufacturing technology and material strength.
  • FIGS. 3 and 4 show a further device according to the invention, wherein already described in the figure 1, functionally identical components are provided with the same reference numerals.
  • the exemplary embodiment according to FIGS. 3 and 4 differs from the exemplary embodiment according to FIGS. 1 and 2 essentially in that the second compensation part 48 (inner part) is designed as a partially open steel molded part which has an approximately V-shaped cross-section.
  • the first compensating part 65 (outer part) is designed substantially like that shown in FIG.
  • a drive element 52 is inserted in the form of an elastomeric ring.
  • the compensation part 48 On its outer side 53, the compensation part 48 is matched with an effective surface 54 on the cone angle or the orientation of the active surface 15 of the compensating part 65.
  • the active surfaces or sliding surfaces 15, 54 act as before described together so that the drive element 52 acts as a drive device which causes an axial displacement when the temperature increases.
  • the compensation part 48 has a slot or a recess 55 through which, as already described, the radial deformability of the compensation part 48 is extended far beyond its thermal or material-elastic limits.
  • a holding element 58 is provided, which has a piston 59 as an integral part.
  • the piston 59 penetrates into a slot 60 of the drive element 52 in such a way that the slot boundary surfaces 62, 63 are supported on the piston 59 (FIG. 4).
  • the first compensating part 65 covers the drive element 52 from the other side.
  • the compensating part 48 which is also referred to as an inner ring, is designed as a steel part and has the advantage, due to the radial spring property imparted by the slot 55, under bias into the bore 3 of the housing 4 (FIG. Figure 3) can be used.
  • the steel piston 59 also prevents here that the material of the drive element 52 evades due to thermal expansion.
  • the space occupied by the plastic of the drive element 52 changes considerably in the radial direction, which leads to the desired greater expansion or, on cooling, contraction of the compensation part 48.
  • holding element 58 can additionally hold together the compensating parts and drive element 52 as structural unit 72 via an engagement 70 in lateral surface 71 of compensating part 65. This is easier to handle and mount;
  • the material of the drive member 52 in either radial direction in the region of the slot (filled by the piston 59) dodge.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)

Abstract

L'invention concerne un dispositif pour la compensation de déplacements relatifs axiaux consécutifs à des effets thermiques entre deux composants avec deux parties de compensation (12, 18) qui, par l'intermédiaire de surfaces actives coopérantes (15, 40) transforment un déplacement radial relatif consécutif à des effets thermiques des surfaces actives (15, 40) en un déplacement compensé en température, axial, d'au moins une partie de compensation (18). Pour doter le dispositif, en cas de besoin d'espace de montage axial très faible, avec des moyens simples, d'une capacité de compensation thermique relativement grande, une partie de compensation (18) est couplée avec un élément d'entraînement (22), qui présente un coefficient de dilatation thermique supérieur à la partie de compensation (18), de telle sorte que l'élément d'entraînement (22) imprime ses changements de géométrie consécutifs à des effets thermiques à la partie de compensation avec renforcement de son mouvement radial.
PCT/EP2008/053270 2007-04-21 2008-03-19 Dispositif pour la compensation de déplacements relatifs axiaux consécutifs à des effets thermiques WO2008128833A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007018929.1 2007-04-21
DE102007018929A DE102007018929A1 (de) 2007-04-21 2007-04-21 Vorrichtung zur Kompensation von thermisch bedingten axialen Relativverschiebungen

Publications (1)

Publication Number Publication Date
WO2008128833A1 true WO2008128833A1 (fr) 2008-10-30

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PCT/EP2008/053270 WO2008128833A1 (fr) 2007-04-21 2008-03-19 Dispositif pour la compensation de déplacements relatifs axiaux consécutifs à des effets thermiques

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DE (1) DE102007018929A1 (fr)
WO (1) WO2008128833A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012006390A1 (de) 2012-03-30 2013-10-02 Johann Singer Vorrichtung zum Einstellen und Aufrechterhalten einer optimalen Wälzlagervorspannkraft

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010014453A1 (de) * 2010-04-09 2011-06-09 Aktiebolaget Skf Lageranordnung und Getriebe einer Windkraftanlage
DE102011083508A1 (de) * 2011-09-27 2013-03-28 Zf Friedrichshafen Ag Einheit mit Außenteil und darin zentriert gelagertem Innenteil aus Materialien mit verschiedener Wärmeausdehnung
DE102013215558B4 (de) * 2013-08-07 2020-08-06 Aktiebolaget Skf Vorrichtung zur Kompensation einer temperaturbedingten radialen Vorspannungsänderung in einer Wälzlageranordnung
DE102014219730A1 (de) 2014-09-29 2016-03-31 Aktiebolaget Skf Lageranordnung
DE102016209997A1 (de) 2016-06-07 2017-12-07 Audi Ag Getriebeanordnung für ein Kraftfahrzeug

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5028152A (en) 1990-03-21 1991-07-02 The Timken Company Machine with thermally compensated bearings
DE4118933A1 (de) 1991-06-08 1992-12-10 Zahnradfabrik Friedrichshafen Vorrichtung zum ausgleich axialer waermedehnungen
DE4221802A1 (de) 1992-07-03 1994-01-05 Kugelfischer G Schaefer & Co Wärmedehnungsausgleichsring
DE19534003A1 (de) * 1995-09-14 1997-03-20 Zahnradfabrik Friedrichshafen Segmentiertes Wärmedehnungsausgleichselement
DE102006053731A1 (de) * 2006-11-15 2008-05-21 Schaeffler Kg Vorrichtung mit einem auf Temperaturwechsel reagierenden Kompensationselement

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5028152A (en) 1990-03-21 1991-07-02 The Timken Company Machine with thermally compensated bearings
DE4118933A1 (de) 1991-06-08 1992-12-10 Zahnradfabrik Friedrichshafen Vorrichtung zum ausgleich axialer waermedehnungen
DE4221802A1 (de) 1992-07-03 1994-01-05 Kugelfischer G Schaefer & Co Wärmedehnungsausgleichsring
DE19534003A1 (de) * 1995-09-14 1997-03-20 Zahnradfabrik Friedrichshafen Segmentiertes Wärmedehnungsausgleichselement
DE102006053731A1 (de) * 2006-11-15 2008-05-21 Schaeffler Kg Vorrichtung mit einem auf Temperaturwechsel reagierenden Kompensationselement

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012006390A1 (de) 2012-03-30 2013-10-02 Johann Singer Vorrichtung zum Einstellen und Aufrechterhalten einer optimalen Wälzlagervorspannkraft

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DE102007018929A1 (de) 2008-10-23

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