WO1992014072A1 - Accouplement de corps de serrage - Google Patents

Accouplement de corps de serrage Download PDF

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Publication number
WO1992014072A1
WO1992014072A1 PCT/EP1991/002299 EP9102299W WO9214072A1 WO 1992014072 A1 WO1992014072 A1 WO 1992014072A1 EP 9102299 W EP9102299 W EP 9102299W WO 9214072 A1 WO9214072 A1 WO 9214072A1
Authority
WO
WIPO (PCT)
Prior art keywords
cage
rotation
clamping
sprag
coupling according
Prior art date
Application number
PCT/EP1991/002299
Other languages
German (de)
English (en)
Inventor
Johann Stark
Original Assignee
Ina Wälzlager 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 Ina Wälzlager Schaeffler Kg filed Critical Ina Wälzlager Schaeffler Kg
Publication of WO1992014072A1 publication Critical patent/WO1992014072A1/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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D15/00—Clutches with wedging balls or rollers or with other wedgeable separate clutching members
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D27/00—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor
    • F16D27/02—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with electromagnets incorporated in the clutch, i.e. with collecting rings

Definitions

  • the invention relates to a sprag coupling with a coupling outer part and a coupling inner part, with clamping bodies designed as rolling elements and arranged between two for torque transmission and guided in a cage, with one of the two coupling parts assigned clamping surfaces which, seen in cross section, at least to one of the two Rotation directions towards the cylindrical running surface of the other coupling part form a narrowing clamping gap, and with means for transferring the clamping bodies into contact with the clamping surfaces.
  • Such sprag couplings are known, for example, from US Pat. No. 4,030,581 and GB Pat. No. 1,200,690.
  • the clamping bodies are designed as rollers.
  • the freewheel is switched depending on the direction of rotation.
  • the invention is based on the object of proposing a sprag clutch which is not only intended to achieve a torque transmission position in one of the two directions of rotation, but which enables the pre-run function to be canceled, that is to say a rigid clutch is achieved for both directions of rotation , but at the same time it is ensured that an axial displacement of the coupling components relative to one another remains ensured in an axial direction.
  • This object is achieved in that, in addition to the clamping gap (s) formed in the direction of rotation, the clamping surfaces at least to one of the two axial displacement directions to block the displacement form a narrowing gap to the running surface, and that the cage leading the rolling elements in Axial direction is shiftable.
  • the advantage of this design is that a torsionally rigid connection can be achieved in both directions of rotation.
  • the freewheel position can be canceled.
  • the arrangement ensures, however, that a displacement of the two coupling components in an axial direction is nevertheless ensured.
  • Such a function can be important, for example, in steering devices for the steerable wheels of a motor vehicle, where these are normally adjusted by means of an auxiliary power steering system, but if the auxiliary power fails, a rigid coupling should still be possible in order to control the steering of Hand operated. At the same time, however, it must be ensured for safety reasons that the components can be pushed into one another in the sense of shortening in the event of an accident.
  • the clamping surfaces in the coupling part to which they are assigned form a recess, the cross section of which decreases along the axis of rotation towards a direction of displacement.
  • the recesses can either be assigned to the outer coupling part or to the inner coupling part.
  • the Clamping surfaces in the coupling part to which they are assigned form a recess, the cross section of which decreases along the axis of rotation toward both directions of displacement.
  • the cage can be displaced to a limited extent in the direction of rotation with respect to the coupling part having the clamping surfaces.
  • a latching position is provided in which the balls can be brought into contact with one of the corresponding clamping surfaces exclusively for torque transmission in one of the two directions of rotation. In this position, the sprag freewheel acts purely as a freewheel for the two directions of rotation. A shift from this detent position is required for the transition to the blocked state for both directions of rotation.
  • the cage should be acted upon by a spring towards the release position. Accordingly, the rolling elements are out of contact with the running surface and thus in a position in which no torque can be transmitted in either direction of rotation and also no axial fixation of the two coupling parts with respect to one another can take place. So it's the free one Mobility guaranteed in this position.
  • the transfer into one of the other positions has to be carried out by a corresponding displacement of the rolling elements counter to the force of the spring.
  • the clamping surfaces are preferably flat surfaces which, seen in cross-section, form a triangular recess with a cross-sectional surface that changes in the axial direction, in particular changes linearly.
  • An electromagnet can be provided to displace the cage in the axial direction. It is also possible to adjust the cage in the direction of rotation using an electromagnet.
  • the electromagnet is permanently assigned to one of the two coupling parts, while the cage carries a ferromagnetic disk opposite the electromagnet. In the case of rotation adjustment, the electromagnet generates a braking force when excited, which transmits a driving force to the cage in the direction of rotation.
  • FIG. 1 shows a longitudinal section through a first embodiment of a sprag coupling, which is held by a spring in the blocking position as a preferred position for both directions of rotation and a direction of sliding,
  • FIG. 2 shows a section A-A in the right half and a section B-B of FIG. 1 in the left half
  • FIG. 3 shows a variant of FIG. 1,
  • FIG. 4 shows a longitudinal section through an embodiment in which the clamping body coupling is in a preferred position by a spring, in which there is no clamping effect in the axial displacement directions, but a clamping effect can be brought about in the two possible directions of rotation,
  • FIG. 5 shows a further embodiment of the clamping body coupling in longitudinal section, in which the clamping surfaces are assigned to the inner coupling part and which can be locked in one direction of rotation and in both possible axial displacement directions,
  • FIG. 5a shows the design of the clamping surfaces of the exemplary embodiment according to FIG. 5 as a single unit, enlarged
  • Figure 6 shows a section CC according to Figure 5 and 7 shows an embodiment as shown in FIG. 5, but with tons instead of balls as rolling elements,
  • the sprag freewheels shown in the various figures each consist of a clutch outer part 1, a clutch inner part 3 coaxially accommodated therein and between the two roller bodies 4.
  • the clutch outer part 1 can additionally be in a receiving sleeve 2, which is part of a machine or another unit can be included.
  • the rolling elements 4 are designed according to the exemplary embodiments according to FIGS. 1 to 6 as balls and in the exemplary embodiment according to FIG. 7 as tons.
  • the rolling elements 4 are held in the cage 5.
  • the cage 5 is arranged in the axial direction, that is, one of the two directions X or Y and in one of the two directions of rotation N and N, at least to a limited extent displaceable or rotatable.
  • the rolling elements 4 can be transferred into a clamping position which is effective in one of the directions of rotation or one of the directions of displacement.
  • clamping recesses 11 are formed either in the inner surface 6 of the outer coupling part 1 or the outer surface 7 of the inner coupling part 3, which are formed by clamping surfaces 9, 10.
  • the clamping recesses 11 form together with the respective counter surface of the opposite part; thus either the outer surface 7 of the inner coupling part 3 or the inner surface 6, 6a of the outer coupling part 3 has a clamping gap 8.
  • the outer coupling part 1 is provided with an inwardly directed section which forms guide lugs 13 which engage between guide recesses 14 of the cage 5. It can be seen from FIG. 2 that a limited rotation of the cage 5 relative to the guide projection 13 is possible. Between the radially inward surface of the clutch outer part 1 and a support disc 15 assigned to the cage 5, one or more support springs ' 16 are arranged, which the cage 5 and thus the circumferentially distributed rolling elements 4 in the sliding direction X in the clamping gap 8, which between the Clamping recesses 11 and the cylindrical outer surface 7 of the clutch inner part 3 is formed, push it in. It can be seen from FIGS.
  • the clamping gap 8 is reduced in the sliding direction X, so that, for example when the inner coupling part 3 moves in the sliding direction X, jamming between the outer coupling part 1 and the inner coupling part 3 is brought about, both for the sliding direction X as well as for the two directions of rotation N 1 and N.
  • the two adhesive surfaces 9, 10 are roof-shaped and thus also cause a clamping in the direction of rotation N and N about the axis of rotation 12. Contrary to the sliding direction X, that is to say in the Y direction, however, a movement of the inner coupling part 3 can take place while the clamping effect on the outer coupling part 1 is canceled.
  • an electromagnet 17 is attached in the receiving sleeve 2 and, when excited, attracts a ferromagnetic disk 18 assigned to the cage 5.
  • the cage 5 together with the rolling elements 4 is pulled out of the clamping gap 8 in the Y direction.
  • This has the effect that, on the one hand, a free axial movement in the two displacement directions Y and X of the clutch inner part 3 relative to the clutch outer part 1 is possible, but also, depending on the direction of rotation N., or N, one of the two clamping surfaces 9 or 10 comes into effect.
  • the outer coupling part moves 1 in the direction of rotation N the clamping surface 9 to effect and a torque in the direction of rotation N is transmitted to the clutch inner part 3.
  • an overhaul function is then given because the rolling elements 4 are brought out of contact with the clamping surface 9.
  • FIG. 3 in contrast to that according to FIG. 1, only a different arrangement for the support spring 16, which shifts the cage 5, is selected.
  • the support disk 15 is not assigned to the cage 5, but rather to the receiving sleeve 2.
  • the support spring 16 is arranged between this support disc 15 and the end face of the cage 5.
  • the embodiments shown in FIGS. 1 to 3 could, for example, be used in devices in which the outer coupling part 1 and the inner coupling part 3 are normally moved independently of one another by a power drive. As long as the power drive works and is switched on, the electromagnet cancels the clamping action of the clamping body coupling, while when the circuit is interrupted, for example, a mechanical coupling occurs, so that manual operation is possible, for example.
  • Auxiliary power steering in motor vehicles is an example of an application, although manual operation is ensured in the case of a mechanical clutch. Nevertheless, for example in the event of an impact, the inner clutch part 3 can be moved in the Y direction relative to the outer clutch part 1 to shorten the steering column.
  • FIG. 4 shows an embodiment which is basically constructed from the same components as that according to FIG. 3, specifically with regard to the arrangement of the support spring 16.
  • FIG. 4 shows an embodiment which is basically constructed from the same components as that according to FIG. 3, specifically with regard to the arrangement of the support spring 16.
  • the support spring 16 acts on the cage 5 and thus the rolling elements 4 in the release direction, so that in the normal position only the torque transmission and freewheeling functions for the two directions of rotation N and N are given, as described in connection with these, but in order to achieve a blockage in the two directions of rotation and jamming with respect to one Sliding direction, namely the sliding direction Y, it is necessary to move the cage 5 by exciting the electromagnet 17 into the position shifted to the left and thus the rolling elements 4 deeper into the clamping gap 8.
  • the inner clutch part 3 can, however, be moved in relation to the outer clutch part 1 in the sliding direction X to cancel the clamping effect.
  • the cage 5 furthermore has a radially outwardly resilient collar 22 on the inside of the outer surface 7 of the inner coupling part 3, at the openings which receive the rolling elements 4, which collar holds the rolling elements 4 in their radially outer position. He lifts it from the cylindrical outer surface 7.
  • FIGS. 5 to 7 show embodiments in which the clamping recesses 11 and the clamping surfaces 9, 10 forming them are assigned to the inner coupling part 3.
  • the inner coupling part 3 has clamping recesses 11 distributed circumferentially in its outer surface 7 in accordance with the distribution of the rolling elements 4 in the cage 5. It can be seen that due to the course of the clamping surfaces 9, 10 with a decreasing depth, starting from the outer surface 7 in the direction of rotation N .. according to FIG. 6 for the opposite direction of rotation N when driving the clutch inner part 3, a clamping effect is generated.
  • the clamping gap 8 between the inner surface 6 of the coupling outer part 1 and the clamping surfaces 9, 10 narrows namely.
  • the springs 20 are supported at one end on the rolling elements 4 and at their other end on resilient tongues 19 which are part of the cage 5 and are intended to facilitate assembly of the cage.
  • the rolling elements 4 would only be effective as a plain bearing. So you can not take precise guidance of the inner clutch part 3 and outer clutch part 1 against each other. For this reason, a support bearing 21 is additionally arranged between the two, which takes over the function of centering.
  • the rolling elements 4, which are designed as balls according to FIG. 5, can also, as shown in the example according to FIG. 7, be designed as barrels 4.
  • a design of the clamping surfaces 9, 10 according to FIG. 5 is possible.
  • the load-bearing capacity is increased again, so that the already particularly suitable suitability of the barrel for high moments to be transmitted is improved.
  • an embodiment is also possible which is similar to that according to FIGS. 1 to 4 is designed.
  • the cage 5 can therefore also be acted upon by an electromagnet or a permanent magnet in order to be adjusted.

Abstract

Un accouplement de corps de serrage permet de bloquer une pièce extérieure d'accouplement (1) par rapport à une pièce intérieure d'accouplement en trois directions parmi les deux directions axiales de déplacement et les deux directions de rotation possibles, alors que dans la quatrième direction (direction de rotation ou de déplacement) une fonction de course libre est assurée. A cet effet, une fente supplémentaire de serrage pour au moins une des deux directions de déplacement axial Y ou X est prévue, outre la fente de serrage (8) en forme de faces de serrage (9, 10) ménagée dans la direction de rotation.
PCT/EP1991/002299 1991-02-02 1991-12-03 Accouplement de corps de serrage WO1992014072A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP4103136.9 1991-02-02
DE19914103136 DE4103136A1 (de) 1991-02-02 1991-02-02 Klemmkoerperkupplung

Publications (1)

Publication Number Publication Date
WO1992014072A1 true WO1992014072A1 (fr) 1992-08-20

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1991/002299 WO1992014072A1 (fr) 1991-02-02 1991-12-03 Accouplement de corps de serrage

Country Status (2)

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DE (1) DE4103136A1 (fr)
WO (1) WO1992014072A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999028645A1 (fr) * 1997-11-26 1999-06-10 John Hugh Kerr Manchon multidirectionnel complet
WO1999045281A1 (fr) 1998-03-04 1999-09-10 INA Wälzlager Schaeffler oHG Systeme d'encliquetage cuneiforme, notamment a action lineaire
US6409001B1 (en) 1997-11-26 2002-06-25 Ker-Train Holdings Ltd Full-complement multi-directional coupling
US6691847B2 (en) 1998-11-26 2004-02-17 Ker-Train Holdings Ltd. Power transfer device
EP1955971A1 (fr) * 2007-02-08 2008-08-13 Jurmet Sp. z o.o. Dispositif de serrage pour une connexion rotative d'un arbre avec un manchon à paroi intérieure cylindrique
US7441642B2 (en) * 2005-10-19 2008-10-28 Honeywell International Inc. Low inertia ball brake/clutch

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19805211A1 (de) * 1998-02-10 1999-08-12 Schaeffler Waelzlager Ohg Spannvorrichtung zum Verbinden zweier umeinander angeordneter Bauteile
ATE526509T1 (de) 2008-05-05 2011-10-15 Jurmet Sp Z O O Spannvorrichtung zur drehmomentübertrragung zwischen einer angetriebenen welle und einer die welle koaxial umgebenden, zylindrischen hülse
DE102019220047B4 (de) * 2019-12-18 2021-08-12 Zf Friedrichshafen Ag Schaltbare Freilaufkupplung

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB131309A (en) * 1917-04-21 1920-11-04 Wolfgang Magg Improvements in clutches
FR42465E (fr) * 1932-10-25 1933-07-31 Roue libre pour automobiles
GB458213A (en) * 1935-12-20 1936-12-15 Henry Martin Kesterton Improvements relating to clutches
US3279571A (en) * 1963-05-02 1966-10-18 Wassilieff Victor Rational coupling device
US4030581A (en) * 1975-08-25 1977-06-21 Facet Enterprises, Inc. Electromagnetic roller clutch
FR2413580A1 (fr) * 1977-12-29 1979-07-27 Vernier Sa G Systeme d'embrayage

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB131309A (en) * 1917-04-21 1920-11-04 Wolfgang Magg Improvements in clutches
FR42465E (fr) * 1932-10-25 1933-07-31 Roue libre pour automobiles
GB458213A (en) * 1935-12-20 1936-12-15 Henry Martin Kesterton Improvements relating to clutches
US3279571A (en) * 1963-05-02 1966-10-18 Wassilieff Victor Rational coupling device
US4030581A (en) * 1975-08-25 1977-06-21 Facet Enterprises, Inc. Electromagnetic roller clutch
FR2413580A1 (fr) * 1977-12-29 1979-07-27 Vernier Sa G Systeme d'embrayage

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999028645A1 (fr) * 1997-11-26 1999-06-10 John Hugh Kerr Manchon multidirectionnel complet
US6409001B1 (en) 1997-11-26 2002-06-25 Ker-Train Holdings Ltd Full-complement multi-directional coupling
WO1999045281A1 (fr) 1998-03-04 1999-09-10 INA Wälzlager Schaeffler oHG Systeme d'encliquetage cuneiforme, notamment a action lineaire
DE19809078A1 (de) * 1998-03-04 1999-09-16 Schaeffler Waelzlager Ohg Insbesondere linear wirkendes Klemmgesperre
DE19980346B4 (de) * 1998-03-04 2010-11-18 Schaeffler Technologies Gmbh & Co. Kg Insbesondere Linear wirkendes Klemmgesperre
US6691847B2 (en) 1998-11-26 2004-02-17 Ker-Train Holdings Ltd. Power transfer device
US7441642B2 (en) * 2005-10-19 2008-10-28 Honeywell International Inc. Low inertia ball brake/clutch
EP1955971A1 (fr) * 2007-02-08 2008-08-13 Jurmet Sp. z o.o. Dispositif de serrage pour une connexion rotative d'un arbre avec un manchon à paroi intérieure cylindrique

Also Published As

Publication number Publication date
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