EP3853489A2 - Arrangement de palier - Google Patents

Arrangement de palier

Info

Publication number
EP3853489A2
EP3853489A2 EP19768831.0A EP19768831A EP3853489A2 EP 3853489 A2 EP3853489 A2 EP 3853489A2 EP 19768831 A EP19768831 A EP 19768831A EP 3853489 A2 EP3853489 A2 EP 3853489A2
Authority
EP
European Patent Office
Prior art keywords
bearing
bearing arrangement
extension
braking
counter surface
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.)
Withdrawn
Application number
EP19768831.0A
Other languages
German (de)
English (en)
Inventor
Nicolas Stroop
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.)
Ondal Medical Systems GmbH
Original Assignee
Ondal Medical Systems 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 Ondal Medical Systems GmbH filed Critical Ondal Medical Systems GmbH
Publication of EP3853489A2 publication Critical patent/EP3853489A2/fr
Withdrawn legal-status Critical Current

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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating 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
    • 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
    • F16C19/38—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 two or more rows of rollers
    • F16C19/383—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • 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
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • F16C41/001—Integrated brakes or clutches for stopping or coupling the relatively movable parts
    • 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
    • F16D59/00—Self-acting brakes, e.g. coming into operation at a predetermined speed
    • F16D59/02—Self-acting brakes, e.g. coming into operation at a predetermined speed spring-loaded and adapted to be released by mechanical, fluid, or electromagnetic means
    • 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
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F16D65/186—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes with full-face force-applying member, e.g. annular

Definitions

  • the invention relates to a bearing arrangement, in particular with a braking device.
  • an anchor plate with an applied friction lining is pressed against a counter surface, for example a pressure plate, by prestressed compression springs in order to inhibit movement, in particular rotation, of the respective bearing elements relative to one another.
  • the armature plate is connected in a rotationally fixed manner to a first housing part, which can be designed as a stator.
  • the pressure plate is rotationally fixed to a second housing part, which can also be designed as a rotor.
  • the friction lining can be attached to both the anchor plate and the pressure plate.
  • the friction generated by the pressure force of the compression springs generates a braking torque.
  • the braking torque prevents, for example, an unintentional movement of a support arm system, which is kept movable by means of the bearing unit at least with respect to a rotational degree of freedom.
  • a strong electromagnet which is, for example, firmly connected to the stator, is supplied with a current.
  • the resulting magnetic field counteracts the compressive force of the springs and attracts the anchor plate. This stops the pressing of the friction lining and the stator and rotor can then be rotated against each other with little effort.
  • the contact pressure which causes the braking torque corresponds to the force which the electromagnet has to generate to release the brake. If the braking torque is high, the electromagnet must be dimensioned accordingly strong and the currents within a coil of the electromagnet are correspondingly large. Likewise, the gap between the electromagnet and the armature plate is crucial for the function at high braking torques, since the magnetic force decreases sharply with the distance to the magnet. This places high demands on the manufacturing accuracy and the assembly effort, in particular to keep the gap small. For example, to set the gap, a fine thread, which is difficult to manufacture, is provided with a small pitch between the pressure plate and the housing.
  • the position of the pressure plate on the fine thread is fixed after setting a position with an adhesive, which makes maintenance very complex.
  • the position setting itself must also be very precise so that the gap is a perfect fit. Otherwise, the magnetic force generated by the magnet may be too weak due to an excessively large distance in order to be able to counteract the spring force sufficiently to cancel the braking effect. If the distance is too small, on the other hand, an undesired sliding contact can occur, which damages the bearing.
  • the anchor plate may then no longer be able to lift far enough from a counter surface corresponding to the brake lining and thus, even when the brake is released, there is still too high a frictional force with relative rotation of the respective bearing elements.
  • Another known constructive solution for fixing or braking a bearing unit is the use of an elastic pressure hose, which expands when an internal pneumatic pressure is applied. The expansion leads to a pressing force on the rotor and stator and creates a frictional force on the active surfaces, which inhibits the rotary movement.
  • the pressure hose can therefore take over the function of the springs and the electromagnet, for example.
  • the disadvantage of this solution is that when a support arm system mounted by means of the bearing unit is moved and the brake is not released, abrasive wear occurs on the relatively moving active surfaces of the pressure hose, which is also referred to as the pneumatic hose. This abrasive wear can lead to a leak in the pressure hose, also known as the brake hose.
  • the service life of the bearing unit can thus be short and / or the respective maintenance intervals can be short. A similar effect can occur due to cracks in the respective crimping points of the elastic tube to which it is attached.
  • the maintenance of a defective brake hose is a complex service operation.
  • a third known constructive solution for fixing or braking a bearing unit is a friction brake unit, which cannot be released. This creates a permanent braking torque between the rotor and stator, which the operator cannot release.
  • the braking torque is chosen so high that a movement of a support arm system mounted with the bearing unit is still possible, but undesired movements are prevented relatively reliably. In some embodiments, this is braking torque cannot be adjusted, changes with increasing wear of the friction surfaces and is then no longer correctable.
  • the storage units described also have in common that they are characterized by a wide variety of components and assemblies. This also makes these storage units expensive and time-consuming to maintain.
  • DE 10 2008 01 7 262 A1 describes a roller bearing slewing ring with an integrated direct drive and with an optionally integrated brake, for example a friction brake.
  • a pin is attached to an inner surface of an outer ring.
  • the friction brake also has integrated springs for its pretensioning, which are spaced radially from the anti-rotation device. The springs and pin are located on axially opposite sides of the friction brake. Accordingly, the springs are not guided through the pin.
  • JP 2002 005 205 A describes a bearing arrangement in which spring elements and guide elements are positioned at different diameters. Accordingly, the spring elements are not guided through the guide elements.
  • EP 2 631 127 A1 describes an industrial truck with braked load rollers.
  • An anchor plate is mounted on a trunnion or a central shaft or on an electromagnetic actuator.
  • a spring device is arranged in the electromagnetic actuator. An arrangement outside the actuator is not possible due to the respective springs. The springs are not guided.
  • the object of the present invention is to provide a bearing arrangement which is particularly inexpensive to manufacture and in particular simple to assemble.
  • the invention relates to a bearing arrangement with at least a first bearing element and a second bearing element, which are connected to one another in a relatively rotatable manner along a common longitudinal axis.
  • the bearing arrangement can comprise a braking device which inhibits the relative rotation of the two bearing elements from one another by means of a frictional force generated by the braking device.
  • the braking device can comprise a brake element connected to the first bearing element, a counter surface connected to the second bearing element and at least one spring element.
  • the spring element can be designed to press the brake element against the counter surface with a spring force in order to produce a frictional connection.
  • the at least one spring element is preferably installed preloaded. The frictional force results from the frictional engagement when the bearing elements move relative to one another.
  • the counter surface can also be connected to the second bearing element such that it is formed on or as one of the surfaces thereof.
  • the counter surface can move with the second bearing element designed as a rotor when it is moved relative to the stator.
  • the braking element can, for example, remain in position together with the first bearing element designed as a stator.
  • the brake element and the counter surface can slide frictionally against one another and thus generate the frictional force counteracting the rotation due to the frictional engagement.
  • the respective bearing element connected to the braking element or connected to the counter surface can also be referred to as an associated bearing element.
  • the counter surface can be designed simply as a surface of the second bearing element facing the braking element or as a separate part fixed to it, for example also as a braking element.
  • Respective brake elements can be designed, for example, as brake linings in order to have a high coefficient of friction when sliding off.
  • the brake pads can be connected, for example, to the respective bearing elements by means of an adhesive or screw connection.
  • the bearing arrangement can preferably also comprise an actuatable adjustment device.
  • the adjusting device By means of the adjusting device, a contact pressure with which the brake element is pressed against the counter surface due to the spring element can be reduced. The braking force acting on the relative rotation of the two bearing elements can thus be modified.
  • the adjusting device can only reduce the contact pressure in order to adjust the degree of inhibition of the rotation of the respective bearing elements.
  • the adjusting device can also function as a clutch which provides the frictional connection cancels and thus deactivates the inhibition. Then the two bearing elements can be rotated quickly and easily relative to one another with little effort. For example, only the inherent friction of the bearing arrangement then has to be overcome.
  • the bearing arrangement is designed, for example, as a rolling bearing, only the rolling friction of the bearing elements on the rolling bodies has to be overcome. Due to the pretensioning by the at least one spring element, the frictional engagement can be restored automatically as soon as the adjusting device is no longer actuated.
  • the adjusting device can comprise, for example, an actuator by means of which the contact pressure is reduced, which is therefore counteracted by the spring force of the at least one spring element.
  • the actuator can comprise an electromagnet or a pressure hose.
  • the brake of the bearing arrangement can then be released, for example, electrically or pneumatically.
  • the maximum contact pressure and / or friction can be predetermined by the contact pressure of the respective spring elements and the material pairing of the friction element and the counter surface.
  • the adjusting device is used to temporarily reduce the braking force or temporarily release the braking and can be dimensioned accordingly in accordance with the pressing force of the respective spring elements.
  • the friction element can correspond to the braking element.
  • the brake element can also comprise a friction element, for example in the form of a brake lining, which can also be referred to as a friction lining.
  • a friction element can correspond to a brake pad.
  • the brake element can comprise a plate, in particular an anchor plate, on which the friction lining or the friction element is arranged.
  • the friction lining can be permanently or releasably attached, for example with an adhesive or screw connection.
  • the friction element or the friction lining can form a friction surface, in particular on a side facing the counter surface.
  • the spring element can be designed, for example, as a compression spring, in particular as a coil spring or plate spring.
  • the spring force preferably acts essentially normal to the counter surface and / or to a friction surface of the friction element, which is in contact with the counter surface in the case of a frictional engagement.
  • the counter surface and the friction element can form plane parallel corresponding friction surfaces.
  • the counter surface is preferably formed on an extension of the second bearing element which is oriented transversely, in particular at right angles to the direction of action of the pressing force.
  • the orientation of the extension results, for example, from a main direction of extension of the extension and is preferably parallel to the counter surface.
  • the extension can be recognized, for example, by the fact that it serves no other purpose in the bearing arrangement except for the formation of the counter surface.
  • the Bearing arrangement also form a fully functional bearing without the extension, apart from inhibiting rotation.
  • the extension is preferably formed in one piece with the second bearing element.
  • the extension means that there is no need for a separate pressure plate. In particular, this eliminates the complex assembly on a fine thread, the setting of the gap between the armature plate and the electromagnet, and the gluing after this setting.
  • the throughput time during production can be greatly reduced, in particular due to the elimination of an adhesive's curing times. Assembly and manufacturing can be particularly cost-effective.
  • the production of a thread in one of the respective bearing elements is also unnecessary.
  • the bearing arrangement can also be easily assembled without special training, since the gap is essentially given by design and does not have to be adjusted. This makes installing the bearing arrangement particularly easy for its buyers.
  • the diameter in the area of the frictional engagement of the bearing arrangement that is to say in the area of the counter surface and the friction element, can be particularly large.
  • the respective friction surfaces in contact with frictional engagement can be particularly large.
  • the contact pressure required can be particularly low with an otherwise constant friction torque compared to conventional bearing arrangements.
  • the surface pressure between the counter surface and the friction element can be particularly low. This can reduce abrasive wear.
  • Respective spring elements can be dimensioned weaker, as a result of which the installation space required can be reduced.
  • the adjusting device can also require less force to counteract the pressing force.
  • an actuator can be dimensioned weaker and correspondingly small and inexpensive.
  • an electromagnet can be dimensioned smaller, as a result of which a required length of enamelled copper wire can also be reduced.
  • the power required to release the brake can also be lower, which means that, for example, a power supply unit can be dimensioned smaller.
  • the exact observance of the minimum gap is also less relevant.
  • the electromagnet can also be dimensioned so strongly that the brake can be reliably released even in the case of a gap that is unusually large due to manufacturing tolerances.
  • the electromagnet can nevertheless be just as strong or weaker than in the case of a bearing arrangement in which the gap can be adjusted by means of a pressure plate and fine thread due to the lower pressing force required.
  • An axial direction of the bearing arrangement can be predetermined by its longitudinal axis.
  • a radial direction can, for example, cross a direction, in particular at right angles, to Longitudinal axis must be defined.
  • Radially inwards can be defined radially in the direction towards the longitudinal axis and radially outwards in the direction away from the longitudinal axis.
  • the brake element comprises an armature disk and a friction surface formed thereon, the armature disk being connected to the first bearing element in a rotationally fixed but axially movable manner along the longitudinal axis by means of at least one guide element.
  • the friction surface can be designed in the form of a friction lining on the armature disk. Due to the design with armature plate, the brake of the bearing arrangement can be released easily and reliably, in particular with simple actuators such as an electromagnet.
  • the friction surface can be formed here, for example, by a friction lining glued or screwed onto the armature disk, so that it can be easily replaced when worn.
  • each guide element can be designed, for example, as guide bolts which are arranged in corresponding through openings in the armature disk.
  • the guide bolts can also be designed as dowel pins.
  • the main extension direction of the guide pin is preferably aligned in the axial direction along the longitudinal axis. The guide bolts thus guide the movement of the armature disk in the axial direction along the longitudinal axis.
  • the armature disk can for example also be designed as an anchor plate.
  • the adjusting device comprises an electromagnet, by means of which the armature disk can be moved axially against the spring force.
  • An electromagnet is a particularly low-maintenance, robust and cost-effective actuator.
  • the armature disk is preferably made of a material which is attracted by the magnetic field that can be generated by the electromagnet.
  • the electromagnet is preferably arranged axially spaced from the armature disk on a side facing away from the counter surface.
  • the electromagnet is switched on, the armature disk is then pulled toward the electromagnet and the armature disk is thus axially pulled away from the counter surface.
  • the frictional engagement can be released or the contact pressure of the friction element on the counter surface can be reduced in order to remove or reduce an inhibition of the relative rotation of the two bearing elements with respect to one another.
  • the at least one spring element is arranged essentially on the same diameter as the at least one guide element.
  • respective guide elements can also serve as respective guides for respective spring elements.
  • a helical spring can be protected against kinking by a guide bolt arranged in its center.
  • the diameter can be defined in relation to the longitudinal axis, in particular the radial distance from it.
  • the respective spring elements can therefore have essentially the same radial distance from the longitudinal axis as the respective guide elements.
  • the respective spring elements and respective guide elements are preferably also arranged in the circumferential direction at corresponding positions, which can then result in the support or guidance of the spring elements already described.
  • a guide element is preferably provided for each spring element.
  • the guide elements are preferably designed as pins or guide pins, around which the spring elements designed as helical springs are arranged
  • one of the two bearing elements is designed as an inner ring and the other of the two bearing elements is designed as an outer ring.
  • the bearing arrangement can be designed as a roller or slide bearing.
  • the second bearing element is preferably designed as an inner ring, since the radial size of the bearing arrangement does not have to be increased in spite of the extension.
  • the extension can be formed, for example, as a partial region of the inner ring, which extends axially further than the outer ring and projects radially there beyond the remaining inner ring. This results in an at least partial axial overlap between the extension and the outer ring.
  • the extension preferably extends essentially at most as far radially as the outer ring.
  • the extension is designed as a shoulder on the second bearing element, in particular on the second bearing element designed as an inner ring.
  • a paragraph can be particularly inexpensive and easy to manufacture, for example if the second bearing element is a turned part.
  • a transition between the extension and the remaining second bearing element is curved or angled.
  • the extension formed as a shoulder can be curved into the rest of the second bearing element or can transition with a sharp edge, notch and / or chamfer.
  • the angled transition is particularly inexpensive to manufacture, especially on a lathe. In addition, this is very space-saving.
  • the angled transition can also be designed in the manner of a chamfer.
  • the curved transition can take particularly high loads.
  • the extension can be thinner in the axial direction, for example, so that the bearing arrangement can be particularly compact, in particular in the axial direction.
  • the extension and / or the counter surface extend radially, in particular at right angles to the longitudinal axis, with their main extension surface. This results in a particularly advantageous flow of force and also alignment with respect to the respective frictional forces.
  • the bearing arrangement can be particularly compact.
  • the counter surface and / or a corresponding friction surface of the friction element are arranged in a radially outer region of the bearing arrangement.
  • the extension and / or the respective friction surfaces can be particularly small.
  • the necessary contact pressure can be particularly small with the same inhibiting torque, which results in advantages with regard to the dimensioning of the braking device and the adjusting device, in particular its actuator and the gap.
  • the counter surface and / or the corresponding friction surface of the friction element are preferably arranged in a radially outermost region of the bearing arrangement.
  • the second bearing element in particular its extension, extends essentially radially outward at most as far as the first bearing element and / or the braking element, in particular its armature disk.
  • the inner ring preferably extends radially outwards as far as the outer ring.
  • the inner ring can extend radially further inwards than the outer ring.
  • the adjustment device comprises a display device which is designed to indicate actuation of the adjustment device.
  • the display device is preferably arranged together with the electromagnet of the adjustment device on the first bearing element. With the display device, a user can easily recognize whether the rotation is currently inhibited or not or whether the brake is released or not.
  • the display device can comprise a lamp, in particular an LED, which lights up when the adjustment device is actuated.
  • the LED can be integrated in the circuit of the electromagnet and can be automatically supplied with current and therefore light up as soon as the electromagnet is supplied with current.
  • the non-actuation can be indicated, for example, by the fact that the LED is not lit or by a different color.
  • the actuator of the adjusting device and the display device By mounting the actuator of the adjusting device and the display device together on the same bearing element, they can be coupled to one another in a particularly simple manner to display the actuation.
  • a coil of the electromagnet and the display device can easily be installed together in the outer ring, so that the display device can be arranged on the outside of the bearing arrangement without extensive wiring on an outside.
  • the two electrical components are in the same rotary reference system. If, on the other hand, the two electrical components are located in different bearing elements, they must either be contacted individually and independently of one another or be electrically connected with a complex sliding contact. In the present case, however, it is possible to incorporate both electrically controlled components in or on a component.
  • the wiring effort is reduced and the assembly of sensitive electronic components is reduced to a single assembly or one of the two bearing elements.
  • Bearing arrangement (10) with at least a first bearing element (12) and a second bearing element (14) which are connected to one another in a relatively rotatable manner along a common longitudinal axis (1 6), the bearing arrangement (10)
  • a braking device (24) which inhibits the relative rotation of the two bearing elements (12, 14) from one another by means of a frictional force generated by the braking device (24), wherein
  • the braking device (24) comprises a braking element (26) connected to the first bearing element (12), a counter surface (34) connected to the second bearing element (14) and at least one spring element (44) which generates the braking element (26) Friction against the counter surface (34) with a spring force, and
  • the counter surface (34) is formed on an extension (38) of the second bearing element (14) oriented transversely, in particular at right angles, to the direction of action of the contact pressure, the extension (38) being formed in one piece with the second bearing element (14).
  • the brake element (26) comprises an armature disk (28) and a friction surface formed thereon, the armature disk (28) being connected to the first bearing element (12) in a rotationally fixed but axially movable manner along the longitudinal axis (16) by means of at least one guide element (32) .
  • the adjusting device (42) comprises an electromagnet (36), by means of which the armature disk (28) can be moved axially against the spring force.
  • the at least one spring element (44) is arranged essentially on the same diameter as the at least one guide element (32).
  • the extension (38) is designed as a shoulder on the second bearing element (14), in particular on the second bearing element (14) designed as an inner ring.
  • a transition between the extension (38) and the rest of the second bearing element (1 4) is curved or angled.
  • the extension (38) and / or the counter surface (34) extend radially, in particular at right angles to the longitudinal axis (1 6), with their main extension surface.
  • the counter surface (34) and / or a corresponding friction surface of a friction element, in particular a friction lining (30), and / or the braking element (26) are arranged in a radially outer region of the bearing arrangement (10).
  • the second bearing element (14), in particular its extension (38), extends essentially radially outward at most as far as the first bearing element (12) and / or the braking element (26), in particular its armature disk (28).
  • Bearing arrangement (10) according to one of the preceding items, wherein
  • the adjustment device (24) comprises a display device which is designed to indicate actuation of the adjustment device (24), the display device preferably being arranged on the first bearing element (12) together with the electromagnet of the adjustment device.
  • the single figure shows a sectional view of a bearing arrangement.
  • the figure shows in a sectional view a part of a bearing arrangement 10, which comprises a first bearing element 12 designed as an outer ring and a second bearing element 14 designed as an inner ring.
  • the bearing arrangement 10 is designed as an axial inclined roller bearing, but can also be designed as another bearing design.
  • the first bearing element 12 also forms at least part of a bearing housing.
  • a cover can also be provided. Alternatively or additionally, the housing is completely formed by the cover, in which the first bearing element 10 is then completely or almost completely accommodated. This can reliably prevent accidental contact with the bearing arrangement 10.
  • the bearing arrangement 10 is designed as a roller bearing in which the two bearing elements 12, 14 can be rotated relative to one another about the longitudinal axis 16.
  • the two bearing elements 12, 14 roll on each other on respective rolling elements 18, which are designed here as cylindrical bodies and are surrounded by respective bearing rings 20, which can also be referred to as running disks.
  • the outer ring forms a stator, which is fastened, for example, to a floor or a ceiling, in the present case by means of a connecting structure 22.
  • the inner ring forms a rotor, to which a further connecting structure 22 is fastened, for example in the form of a cantilever.
  • the respective connection structures 22 are detachably connected to the respectively associated bearing element 12, 14 by means of respective screw connections.
  • a reverse construction is also possible, in which the inner ring forms the stator and the outer ring the rotor.
  • the bearing arrangement 10 also has a braking device 24 which can inhibit the relative rotation of the two bearing elements 12, 14 from one another.
  • the brake device 24 has a brake element 26, which in the present case comprises an anchor plate 28 and a brake pad 30 glued thereon.
  • the anchor plate 28 is axially movable by means of respective guide bolts 32 in a rotationally fixed manner with the first bearing element 12 but axially movable connected to this.
  • the guide boices 32 are, for example, screwed and pressed into holes in the first bearing element 12 and extend through corresponding through openings in the anchor plate 28. This results in an axial movement of the anchor plate 28.
  • the guide bolts 32 are arranged uniformly over the circumference.
  • the axial direction is predetermined by the longitudinal axis 16
  • the radial direction is defined at right angles to the longitudinal axis 16.
  • a spring element 44 which presses the anchor plate 28 with the friction lining 30 against a counter surface 34 of the second bearing element 14.
  • the spring element 44 is designed as a helical compression spring. The contact pressure causes a frictional engagement, which counteracts the relative rotation of the two bearing elements 12, 14.
  • the counter surface 34 is simply the surface of a portion of the second bearing element 14 that faces the friction lining 30 and contacts it in the state shown in the figure.
  • the bearing arrangement 10 or the braking device 24 preferably comprises a plurality of spring elements 44, which are arranged distributed over the circumference are, in particular regularly spaced from each other.
  • the respective spring elements 44 can each be arranged around an associated respective guide pin 32 in order to protect them against kinking and to keep both the number of receiving bores required and the overall space requirement of the bearing arrangement 10 low.
  • the bearing arrangement 10 also includes an adjusting device 42.
  • the adjusting device 42 comprises an electromagnet 36, which is arranged in a recess in the first bearing element 12. When current is applied, this electromagnet 36 pulls the armature plate 28 axially toward it against the pressing force of the spring elements 44, this movement being guided by the guide bolts 32. As a result, the frictional engagement between the friction lining 30 and the counter surface 34 is eliminated and the two bearing elements 12, 14 can rotate relative to one another essentially uninhibitedly.
  • the armature plate 28 can be lifted off the counter surface 34 by the electromagnet 36 and the inner ring and outer ring are freely movable relative to one another. This is also known as electromagnetic brake ventilation.
  • the counter surface 34 is formed on an integral extension 38 of the inner ring or the second bearing element 14.
  • the extension 38 forms a shoulder relative to the rest of the bearing element 14. This shoulder extends axially beyond the first bearing element 12 or the outer ring. As a result, the extension 38 or this shoulder can extend further radially in this axial region than the rest of the inner ring. In the present case, the extension 38 extends radially at least as far as the rolling elements 18.
  • the extension 38 can also extend, for example, up to a central region of the anchor plate 28 or even up to its radially outer edge. Likewise, the extension can also extend, for example, radially as far as a screw connection of the outer ring to the connecting structure 22 or also like the outer ring itself. There is therefore an axial overlap between the extension 38 and the anchor plate 28 and an outermost partial area of the first bearing element 12.
  • the bearing arrangement 10 is thus particularly compact and, in addition, an advantageous arrangement and size of the respective friction surfaces contacted in the frictional engagement can be achieved.
  • a particularly large friction surface is thus provided between the friction lining 30 and the counter surface 34, which also has a particularly large lever arm with respect to the longitudinal axis 16.
  • a particularly high friction torque or braking torque which inhibits rotation can be provided with the same contact force of the spring elements 44, or only a small contact force is required with the same inhibiting friction torque.
  • the electromagnet 36 can be particularly small and weak and / or the requirements for the accuracy of maintaining a size of a gap 40 between the electromagnet 36 and the armature plate 28 in the state in which there is a frictional connection can be particularly low.
  • the gap 40 is a decisive parameter for how strong the electromagnet 36 must be in order to be able to overcome the contact force of the spring elements 44 in order to release the frictional engagement.
  • the gap 40 is only a few tenths of a millimeter in size.
  • the extension 38 formed in one piece with the rest of the second bearing element 14 makes it possible, for example, to dispense with a separate thrust washer.
  • This thrust washer is usually connected to the second bearing element 14 by means of a thread in order to be able to adjust the gap 40. After the setting, the thread is glued to determine the position of the thrust washer. Both this setting and the production of the respective thread and the mounting of separate thrust washers can therefore be dispensed with in the bearing arrangement 10. As a result, the bearing arrangement 10 can be manufactured and assembled particularly cost-effectively and quickly. Maintenance is also easier.
  • the arrangement of the bearing arrangement 10 can also be reversed in such a way that the inner ring is connected to the jib located below.
  • a fastening nut can be screwed in from above.
  • a bearing housing is then connected at the top to a ceiling tube or to an extension arm above it.
  • the In this case, braking device 24 can be integrated at the bottom in the outer bearing ring or the bearing housing.
  • first bearing element 14 second bearing element

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Braking Arrangements (AREA)
  • Support Of The Bearing (AREA)

Abstract

L'invention concerne un arrangement de palier (10) comprenant au moins un premier élément de palier (12) et un deuxième élément de palier (14), qui sont reliés l'un à l'autre le long d'un axe longitudinal commun (16) de manière à pouvoir tourner relativement l'un par rapport à l'autre. L'arrangement de palier (10) comporte un dispositif de freinage (24) qui empêche la rotation relative des deux éléments de palier (12, 14) l'un par rapport à l'autre. Le dispositif de freinage (24) comprend un élément de frein (26) relié au premier élément de palier (12), une surface homologue (34) reliée au deuxième élément de palier (14) et au moins un élément ressort (44) qui presse l'élément de frein (26) contre la surface homologue (34) avec une force de ressort en vue de générer une liaison par friction, et un dispositif de positionnement (42) actionnable, au moyen duquel une force de pressage avec laquelle l'élément de frein (26) est pressé contre la surface homologue (34) peut être réduite. La surface homologue (34) est formée sur un prolongement (38) du deuxième élément de palier (14) qui est orienté transversalement, en particulier perpendiculairement, à la direction d'action de la force de pressage, le prolongement (38) étant formé d'une seule pièce avec le deuxième élément de palier (14).
EP19768831.0A 2018-09-17 2019-09-17 Arrangement de palier Withdrawn EP3853489A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP18194937.1A EP3623655A1 (fr) 2018-09-17 2018-09-17 Palier avec dispositif de freinage
PCT/EP2019/074911 WO2020058292A2 (fr) 2018-09-17 2019-09-17 Arrangement de palier

Publications (1)

Publication Number Publication Date
EP3853489A2 true EP3853489A2 (fr) 2021-07-28

Family

ID=63637810

Family Applications (2)

Application Number Title Priority Date Filing Date
EP18194937.1A Withdrawn EP3623655A1 (fr) 2018-09-17 2018-09-17 Palier avec dispositif de freinage
EP19768831.0A Withdrawn EP3853489A2 (fr) 2018-09-17 2019-09-17 Arrangement de palier

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP18194937.1A Withdrawn EP3623655A1 (fr) 2018-09-17 2018-09-17 Palier avec dispositif de freinage

Country Status (4)

Country Link
US (1) US20210356004A1 (fr)
EP (2) EP3623655A1 (fr)
CN (1) CN112805483A (fr)
WO (1) WO2020058292A2 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3604839A1 (fr) * 2018-08-03 2020-02-05 Ondal Medical Systems GmbH Palier

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1046421B (de) * 1952-11-21 1958-12-11 Johann Vollenbroich Elektromagnetisch betaetigte Scheibenreibungskupplung oder -bremse
SE439050B (sv) * 1981-09-29 1985-05-28 Asea Ab Elektromagnetisk skivbroms med manuell efterjusteringsanordning av luftgap
DE3402522A1 (de) * 1984-01-26 1985-08-01 INA Wälzlager Schaeffler KG, 8522 Herzogenaurach Waelzlager mit drehwinkelabhaengigem drehwiderstand
DE19500589A1 (de) * 1995-01-11 1996-07-18 Koersgen Heinz Norbert Dipl In Elektrischer Radnabenmotor ohne Getriebe, mit außen laufendem Rotor und elektromagnetisch gelüfteter Federdruckbremse insbesondere zum Antrieb von Rollstühlen und anderen Kleinfahrzeugen
DE19943209C2 (de) * 1999-09-09 2002-01-24 Walterscheid Gmbh Gkn Kupplungsanordnung für landwirtschaftliche Geräte
JP2002005205A (ja) * 2000-06-23 2002-01-09 Shinko Electric Co Ltd スプリングクローズ型電磁ブレーキ及びその電磁ブレーキ内蔵型モータ
DE102006004065A1 (de) * 2006-01-28 2007-08-02 Jungheinrich Ag Federspeicherbremse für ein Flurförderzeug
DE102007013164A1 (de) 2007-03-20 2008-09-25 Schaeffler Kg Wälzlager mit einer Bremseinrichtung
DE102007028688A1 (de) * 2007-06-21 2008-12-24 Jungheinrich Aktiengesellschaft Automatische Federspeicherbremse für Flurförderzeug (FFZ)
DE102007057780A1 (de) * 2007-11-30 2009-06-04 Schaeffler Kg Wälzlager mit einer Bremseinrichtung
DE102008017262B4 (de) * 2008-04-04 2016-06-09 Schaeffler Technologies AG & Co. KG Wälzlager-Drehverbindung mit integriertem Direktantrieb und mit integrierter Bremse
DE102012101530A1 (de) * 2012-02-27 2013-08-29 Kion Warehouse Systems Gmbh Flurförderzeug mit gebremsten Lastrollen
DE102015100178A1 (de) * 2015-01-08 2016-07-14 Linde Material Handling Gmbh Fahrantrieb eines Flurförderzeugs mit einem Elektromotor und mit einer Federspeicherbremseinrichtung
DE102015215835A1 (de) * 2015-08-19 2017-02-23 Schaeffler Technologies AG & Co. KG Drehverbindung

Also Published As

Publication number Publication date
CN112805483A (zh) 2021-05-14
US20210356004A1 (en) 2021-11-18
WO2020058292A2 (fr) 2020-03-26
WO2020058292A3 (fr) 2020-05-14
EP3623655A1 (fr) 2020-03-18

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