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
  • 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
  • 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
  • F16C19/361—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 cylindrical rollers
  • F16C19/362—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 cylindrical rollers the rollers being crossed within the single row
• • 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
• • 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
  • F16C2300/00—Application independent of particular apparatuses
  • F16C2300/10—Application independent of particular apparatuses related to size
  • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
• • 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
  • F16D2121/00—Type of actuator operation force
  • F16D2121/18—Electric or magnetic
  • F16D2121/20—Electric or magnetic using electromagnets
  • F16D2121/22—Electric or magnetic using electromagnets for releasing a normally applied brake

Definitions

• the invention relates to a rolling bearing with a braking device, in particular rotary joint, consisting of a bearing outer ring and a bearing inner ring, between which roll on corresponding raceways rolling elements, wherein for generating a braking effect by frictional engagement connected to one of the bearing rings displaceable brake element against one with the zugehö- other bearing ring connected counter-surface is pressed and the frictional connection can be canceled by means of an electromagnet.
• Rolling bearings with braking devices have been known for some time. So there is a risk in rolling bearing rotations of wind turbines that they fail after a relatively short time by corrugation in the raceways. This phenomenon is generated in particular by small pivoting movements to compensate for the wind direction, which leads to a sliding of the rolling elements on the track. To eliminate this wear, it is known to increase by various measures, the low rotational resistance of bearings.
• DE 37 25 972 A1 and DE 41 04 137 A1 suggest in this context, to use an additional peripheral braking device. The braking force and thus the desired rotational resistance can then be set from the outside.
• the disadvantage here is that in the first case the brake element can only be canceled when the wind turbine is shut down.
• the braking device consists of many mechanical niche parts and is therefore complex to manufacture and complicated to handle.
• a non-rotating pivot connection for excavators, cranes or the like for supporting a pivoting superstructure on a substructure is known.
• These rotary joints each consist of a one-piece rotating ring and a two-piece, composed of two profile rings further rotary ring.
• the two rotary rings are each supported by the balls of a double-row ball bearing against each other and equipped with a braking device.
• the brake devices each comprise one or more brake pad carriers, which are fastened to a component which is connected to the one-piece rotary ring. In this arrangement, it is disadvantageous that the braking devices are arranged outside the actual bearing arrangement and therefore require additional space.
• the radial bearing arrangement according to FIG. 1 has a deep groove ball bearing configured as a radial bearing and a braking device arranged axially next to it.
• the deep groove ball bearing consists of the inner ring, the outer ring and between both arranged in a cage bearing balls. Furthermore, the deep groove ball bearing has two sealing rings, which seal the annulus on both sides against the environment.
• the braking device has an inner retaining ring and outer retaining ring. On a radially outwardly directed flange of the inner retaining ring via a flat wire spring a brake disc is attached, which consists of a ferromagnetic material and on its side facing away from the flange has a brake pad.
• the brake disc By fixing by means of the flat wire spring, the brake disc is rotatably connected to the inner retaining ring and slidable in the axial direction. Opposite the brake pad, a counter surface is formed on the outer retaining ring, against which the brake pad is pressed during braking.
• the outer retaining ring further comprises an electric coil and one or more permanent magnets, each in the region between the brake disc and the deep groove ball bearing and are mechanically connected to the outer retaining ring and thus also connected to the counter surface.
• the disadvantage here is that the braking device must be flanged in the axial direction as an external part of the bearing and therefore requires additional space.
• the retaining rings are relatively complicated and must be connected only in a complex manner by pins with the bearing rings.
• Another disadvantage is due to the fact that the braking effect is triggered by a permanent magnet, which attracts the brake disc. In certain applications, however, a steady magnetic field is disadvantageous, since under certain circumstances iron-containing dirt is attracted to the bearing.
• the invention is therefore based on the object to avoid the disadvantages mentioned and to provide an easy-to-manufacture braking device that takes up minimal space and realizes a brake application adapted to the particular application.
• this object is achieved according to the characterizing part of claim 1 in conjunction with the preamble in that the brake element is arranged as an integral bearing component within one of the bearing rings, pressed by spring force against the counter surface, wherein the spring force is variably adjustable and the electromagnet one of the bearing rings as a soft iron core and one of these enclosing coil consists.
• a bearing assembly is provided with braking device in which the braking device requires almost no additional space, since it is an integral part of the camp.
• the brake element in one of the bearing rings, normally in the rotating bearing ring, it is possible in this way to realize the rolling bearing with a braking device to save space.
• Another advantage is that the arrangement of the Braking device as an integral rolling bearing component this is not to be connected in an additional and complex manner with the actual bearing assembly.
• the braking force can be easily canceled by the use of the electromagnet, so that in this case, the rolling bearing can be moved smoothly.
• a generic trained rolling bearing with braking device can always be used particularly advantageous if a steady friction torque is desired, but also under certain circumstances, a very fast release of this friction torque must be achieved. This is the case, for example, in the medical field, when the rolling bearing assembly is used in a rotary joint, for example in a ceiling stand, which is connected to differently designed medical equipment. It is advantageous that an unwanted twisting of the rotary joint is on the one hand prevented by the ever-present friction, on the other hand, however, the rotary joint is easily adjusted by releasing the braking device. In an emergency, if an immediate twisting of both rings against each other is required, this must also be possible with effective braking device.
• the braking force is adjusted so that a rotation of the two bearing rings against each other by human muscle power is still possible.
• Another essential advantage of the invention is that an integrated, adjustable brake concept is realized, which can be individually adjusted by the end customer during assembly of the bearing assembly. Since the friction pairing after Monday of the brake unit can be influenced as little as the number of compression springs, the present invention is based on the adjustability of the spring length, since this is proportional to the spring constant in the spring force. Thus, springs of the same geometric dimensions can be used for multiple applications, but the spring force can be set almost as desired. As is known, the spring force acts on the friction lining and thus defines the holding moment of the bearing arrangement. In other words, the holding torque is determined by the number of feet the and the geometry of which is initially fixed, but is variable by the position of the adjusting ring.
• the braking element consists of a ferromagnetic armature plate, a pressure plate and a arranged in one of the bearing rings coil, between the armature plate and Druckplat- te a brake pad is arranged, which connected to one of the bearing rings anchor plate over a plurality of circumferentially spaced apart guide pins held axially displaceable and can be acted upon by a plurality of circumferentially spaced spring elements with a variable bias such that the spring elements are supported on a freely movable in the axial direction annular adjustment ring.
• the adjusting ring is received via a thread of an associated thread of the bearing rings and that the pressure plate is received via a thread of an associated thread of the bearing rings.
• the rolling elements are designed as cross rollers whose rollers roll with approximately square cross-section with alternately offset axes on raceways.
• the advantage of this arrangement is, in particular, that the alternately arranged rolling elements in X-arrangement roll on the raceways, so that can be loads from all directions - axial, radial and Kippmomentbelastung - record with only a cross roller bearing.
• the braking element and the rolling elements are separated by a sealing element arranged in one of the bearing rings, which is preferably formed as a sliding seal. In this way, it is realized that the braking device can not be contacted with lubricant originating from the rolling elements, which would significantly impair their effect.
• one of the bearing rings to be provided at least one circumferential location with a radially extending lubricant passage bore.
• the rolling bearing should be usable in medical devices.
• a first example are ceiling stands, which have been known for some time and are described in DE 36 27 517 A1, DE 43 06 803 A1 and DE 199 63 512 C1.
• the ceiling stand described in the last pre-publication is also provided with a braking device, which consists of two brake rings, which surround the bearing assembly radially from the outside.
• the braking device is shown in addition to be manufactured and outside the actual storage to be arranged component, which in turn includes the disadvantages listed in the prior art.
• a second example is patient beds or patient tables, which can take different positions for medical examinations by rotation of the table top about a vertical axis in the circumferential direction.
• the tables are securely but movably supported at one end via a rotary joint, since the other end during rotation in the circumferential direction more or less freely oscillates, that is, is not supported.
• FIG. 2 shows a longitudinal section along the line M-II in FIG. 1,
• FIG. 2a shows a longitudinal section along the line M-II in FIG. 1 in a perspective view
• FIG. 3 shows a partial longitudinal section along the line IM-III in Figure 1 and 4 shows a partial longitudinal section along the line IV-IV in Figure 1.
• rolling bearing 1 shown in Figures 1 to 4 consists of the bearing outer ring 2 and the bearing inner ring 3, which are arranged concentrically about the bearing axis 4 with each other.
• rolling elements 5 are housed in the form of cross rollers, roll the rollers with approximately square cross-section with alternately offset axis on non-designated careers.
• Both bearing rings 2, 3 have mounting holes 6, 7 for connection to connection structures, not shown.
• the bearing inner ring 3 is provided at two opposite peripheral points, each with a radially extending lubricant passage bore 8, which opens into the rolling bodies 5 receiving annular space and is closed at the other end by a respective lubricating nipple 9.
• Bearing inner ring 3 and bearing outer ring 2 are connected in the upper region by a sealing element 10 which is fixed in an unspecified recess of the bearing inner ring 3 and is designed to be abrasive.
• the brake element 11 consists of the ferromagnetic armature plate 11.1, which is formed like an annular ring and is axially slidably held in the bearing outer ring 2 with a plurality of guide pins 11.2 spaced apart in the circumferential direction, as FIG. 3 shows.
• the guide pins 11.2 engage in unspecified holes in the anchor plate 11.1, these holes are slightly larger in diameter than the diameter of the guide pins 11.2.
• the armature plate 11.1 is acted upon by an axial force on a front side of spring elements 11.3 at a plurality of equally spaced peripheral points.
• the spring elements 11.3 are received in an unspecified bore of the bearing outer ring 2 and opposite to the anchor plate 11.1.
• the adjusting ring 11.4 is held with its not provided with a reference numeral internal thread on the bearing outer ring 2 on the likewise not designated external thread in the axial direction displaceable.
• brake element 11 further includes the pressure plate 11.5, which is also formed like an annular and is held on her non-designated internal thread on the bearing inner ring 3 via its unspecified external thread. Between the pressure plate 11.5 and anchor plate 11.1, the brake pad is arranged 11.6, which is firmly connected in the embodiment with the pressure plate 11.5.
• the bearing outer ring 2 is provided with an unspecified recess, in which the coil 11.7 is arranged, which is provided with the supply line 11.8.
• the air gap 11.9 can be set very precisely by the pressure plate 11.5 by changing its axial positioning by turning relative to the bearing inner ring 3.
• the adjustability of the length of the spring elements 11.3 is influenced in such a way that they are more or less compressed by turning the position of the adjusting ring 11.4 relative to the bearing outer ring 2.
• their expansion or their compression in the axial direction via a thread of the adjusting ring 11.4 is variable.
• the spring length goes over the Spring constant in the spring force, wherein the spring force is increased with an axial shortening of the spring elements.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Braking Arrangements (AREA)
• Rolling Contact Bearings (AREA)

Priority Applications (3)

Applications Claiming Priority (2)

Publications (1)

Family

ID=40158569

Family Applications (1)

Country Status (5)

Families Citing this family (16)

Citations (3)

Family Cites Families (12)

• 2007
  • 2007-11-30 DE DE102007057780A patent/DE102007057780A1/de not_active Withdrawn
• 2008
  • 2008-10-22 EP EP08855453.0A patent/EP2217817B1/de active Active
  • 2008-10-22 WO PCT/EP2008/064298 patent/WO2009068375A1/de not_active Ceased
  • 2008-10-22 US US12/745,445 patent/US8479893B2/en active Active
  • 2008-10-22 JP JP2010535316A patent/JP2011505524A/ja active Pending

Patent Citations (3)

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