WO2023025342A1 - Ensemble palier à fonction roue libre, actionneur linéaire et procédé de fonctionnement d'un actionneur linéaire - Google Patents

Ensemble palier à fonction roue libre, actionneur linéaire et procédé de fonctionnement d'un actionneur linéaire Download PDF

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Publication number
WO2023025342A1
WO2023025342A1 PCT/DE2022/100537 DE2022100537W WO2023025342A1 WO 2023025342 A1 WO2023025342 A1 WO 2023025342A1 DE 2022100537 W DE2022100537 W DE 2022100537W WO 2023025342 A1 WO2023025342 A1 WO 2023025342A1
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WO
WIPO (PCT)
Prior art keywords
bearing
cage
bearing arrangement
overrunning clutch
arrangement
Prior art date
Application number
PCT/DE2022/100537
Other languages
German (de)
English (en)
Inventor
Mario Kreutzer
Andreas Krome
Original Assignee
Schaeffler Technologies AG & Co. 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 Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2023025342A1 publication Critical patent/WO2023025342A1/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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • F16C33/4605—Details of interaction of cage and race, e.g. retention or centring
    • 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
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/18—Freewheels or freewheel clutches with non-hinged detent
    • 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
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • F16H25/2204—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls
    • 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
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/24—Elements essential to such mechanisms, e.g. screws, nuts
    • F16H25/2454—Brakes; Rotational locks
    • 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
    • F16C19/30—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 axial load mainly
    • F16C19/305—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 axial load mainly consisting of rollers held in a cage

Definitions

  • the invention relates to a bearing arrangement which has a freewheel function. Furthermore, the invention relates to a linear actuator and a method for operating a linear actuator.
  • DE 1 145 446 A discloses a bearing designed as an overrunning clutch, namely a radial ball bearing.
  • the well-known bearing which is also intended to provide a freewheel function, comprises an inner and an outer race, as well as balls rolling between the races, which also interact with a locking device with inclined surfaces.
  • a split cage with asymmetrically designed pockets is provided as a blocking device, both parts of which are axially spread apart by the rolling elements, i.e. balls, during relative rotation of the races in the blocking direction and pressed against conical surfaces of the bearing rings.
  • the locking ring is moved by the balls in the freewheeling direction.
  • the arrangement according to DE 1 145 446 A is a frictionally engaged freewheel.
  • EP 2 895 772 B1 discloses a combined vehicle brake which includes a hydraulically actuable service brake and an electromechanically actuable parking brake device.
  • the electromechanically actuable parking brake device has a spindle drive in the form of a ball screw drive.
  • a collar can be formed on a threaded spindle of the spindle drive, which collar is encompassed by a cup-shaped torque transmission element, with a freewheel mechanism acting between the torque transmission element and the collar, which can be designed as a ramp-roller element arrangement.
  • a braking device described in DE 102014 202 189 A1 which also includes a service brake and a parking brake, has a pawl that acts between a spindle nut and a brake caliper housing.
  • the pawl is intended to engage a wall of the caliper housing such that movement of the spindle nut away from a brake disc of the parking brake is blocked.
  • the pawl has a function within an automatic wear adjustment of the braking device according to DE 10 2014 202 189 A1.
  • braking devices which include self-locking gears, are described in the documents DE 103 20 907 B4 and DE 10 2005 055 085 B4.
  • Braking devices comprising worm gears are disclosed, for example, in the documents EP 2 207 982 B1, EP 2 069655 B1 and EP 1 945 966 B1.
  • the invention is based on the object of specifying bearing-freewheel arrangements which are more advanced than the prior art and which are particularly suitable for use in linear actuators, for example in electromechanically actuated brakes, and which are characterized by a particularly favorable ratio between outlay in terms of equipment, space requirement and if a motor drive is provided, mark the energy consumption.
  • this object is achieved by a bearing arrangement having the features of claim 1 .
  • the object is also achieved by a linear actuator comprising such a bearing arrangement according to claim 8.
  • the object is also achieved by a method for operating a linear actuator according to claim 9.
  • the embodiments and advantages of the invention explained below in connection with the operating method also apply accordingly to Devices, i.e. the bearing assembly and the linear actuator, and vice versa.
  • the bearing arrangement has a freewheel function and comprises a roller bearing which has two bearing elements which can rotate relative to one another and which contact the roller bodies of the bearing.
  • the bearing elements can be formed by rings or disks or directly by a housing or a shaft.
  • the rolling elements of the bearing or a subset of the rolling elements are guided in a cage, which at the same time represents a component of an overrunning clutch.
  • the bearing can be an axial bearing, a radial bearing or an angular roller bearing or angular ball bearing, ie a bearing provided both for the transmission of axial forces and for the transmission of radial forces.
  • the one-way clutch which includes the cage, can be designed as either a positive clutch or a friction clutch. At least that part of the cage which locks as part of the one-way clutch is inherently rigid. This means that the cage is either designed in one piece or the cage parts forming the cage, which have a function within the overrunning clutch, are firmly connected to one another.
  • the rotating component of the roller bearing i.e. typically the rotating bearing ring, the rotating bearing disk or a shaft coupled in a rotationally fixed manner to the relevant ring or said disk, is therefore not directly locked when the overrunning clutch is locked, but rather indirectly, namely via the cage of the roller bearing.
  • This freewheel function comes into effect when the bearing is mechanically loaded. If, on the other hand, there is no power flow from the first bearing element via at least part of the rolling elements to the second bearing element, there is no freewheel function. This is particularly the case when all rolling bodies are arranged between the bearing elements with play.
  • the roller bearing is an axial bearing, the rotating bearing disk, i.e.
  • the shaft disk which can be held in place by means of the overrunning clutch, is typically coupled to other rotatable components in such a way that a torque can be transmitted between the shaft disk and the other components, This means that the additional components mentioned can also be prevented from rotating in a specific direction by means of the overrunning clutch. Separate means for stopping the other components directly are not required for this. This also applies in an analogous manner to other designs of roller bearings with an integrated overrunning clutch partially formed by the cage.
  • one of the two bearing elements of the bearing arrangement which in all cases represents a combined bearing-freewheel arrangement, is rotatable, while the other bearing element is a component arranged in a rotationally fixed manner in a surrounding structure.
  • both bearing elements are rotatable.
  • the housing represents a machine component that can be rotated as a whole.
  • a particular advantage of blocking not the shaft or shaft washer, but the cage of the rolling bearing, in particular axial rolling bearing, is that when the overrunning clutch is loaded in the blocking direction, it is possible to overcome the holding torque generated by the blocked cage, so that the overrunning clutch in a certain operating range, namely below the holding torque, fulfills a blocking function and acts as a brake at higher torques. In the latter state, the axial roller bearing has been converted into a plain bearing.
  • the holding torque which in various possible configurations is in a range that can be overcome by a motor drive, thus sets a possible chen switchover point between using the bearing-freewheel arrangement as a roller bearing with freewheel function on the one hand and using the same arrangement as a plain bearing on the other hand, with use in the latter case with the opposite direction of rotation compared to the first case. It is not necessary to have a separate slide bearing ready for one of two possible directions of rotation.
  • the axial bearing, radial bearing or other roller bearing which also functions as a freewheel, can be constructed as a single-row or multi-row bearing. If there is a multi-row, in particular two-row, structure, the rolling bodies of the different rows of rolling bodies can be guided either through a common cage or through separate cages. In the latter case, for example, only the outermost cage or a cage adjacent to an end face of the bearing arrangement is designed as a freewheel component, while the at least one other cage exclusively has a function within the roller bearing. With this structure, a distribution of axial and/or radial loads as well as a reduction of the braking torque during operation in the blocking direction can be achieved.
  • the overrunning clutch is effective between the housing disc and the cage.
  • the one-way clutch can be connected directly between the housing washer and the cage.
  • the freewheel disk can be connected between the housing, on which the housing disk is held, and the cage of the axial roller bearing.
  • Another design principle provides that the overrunning clutch is connected between the shaft washer and the cage.
  • the overrunning clutch is between the cage on the one hand and a rotating or non-rotating machine element on the other side, i.e. typically a shaft or a housing in which the shaft is mounted, effective.
  • a rotating or non-rotating machine element on the other side
  • the operation of the rolling bearing Relative rotation between the cage and said, either rotating or non-rotating machine element occur.
  • the rotational speed of this relative rotation which means operation of the overrunning clutch in the freewheeling direction, corresponds to approximately half the rotational speed of the shaft in conventional bearing constructions, assuming a stationary housing. This applies both to variants in which the rolling elements roll on separate bearing rings or bearing discs and in cases in which the rolling elements roll directly on a shaft and/or on a surface of a more complex component, in particular the housing surface.
  • the bearing arrangement that absorbs forces in the axial direction includes an additional axial bearing that does not have a freewheel function, it being possible for both axial bearings to have a common shaft washer.
  • the bearing arrangement is suitable for the transmission of axial forces in both directions.
  • a spring element in particular in the form of a plate spring, can be provided to generate a prestressing force acting in the axial direction.
  • a freewheel bearing arrangement that absorbs forces exclusively or predominantly in the radial direction can also be loaded by spring force, with the spring force only acting on part of the rolling elements in the case of a purely radial bearing.
  • the overrunning clutch can be effective between the inner ring of the roller bearing and the cage.
  • the bearing-freewheel arrangement can include a freewheel mechanism which acts either between the cage of the roller bearing and its outer ring or directly between the cage and a housing surrounding the outer ring.
  • the component of the overrunning clutch provided by the cage is also used, without loss of generality, as an inner freewheel component, and the second component of the overrunning clutch that interacts directly with the cage is also used as an outer one called freewheel component.
  • the outer freewheel component can engage, for example, on the outer circumference and/or on an end face of the cage.
  • variants can be implemented in which the outer freewheel component contacts contours on the outer peripheral surface of the essentially annular disk-shaped cage.
  • a bearing is designed as a single-row or multi-row radial bearing, in particular one end face of the cage, which in this case can have a cylindrical basic shape, is available for the outer freewheel component to engage.
  • outer freewheel components interact with the cage on both end faces of the cage are also possible.
  • the cage of the radial bearing extends beyond the rolling elements in the axial direction of the bearing, with the freewheel mechanism being located in the section of the cage that protrudes beyond the rows of rolling elements.
  • the second freewheel component can act on the inner and/or outer peripheral surface of the cage, wherein an attack on the inner peripheral surface can be constructed in a particularly space-saving manner, whereas an attack on the outer peripheral surface has the advantage of longer effective lever arms and thus higher torques that can be absorbed. All explanations given in this paragraph regarding the various freewheel components apply to both frictional and positive-locking freewheels.
  • the overrunning clutch of the bearing arrangement is designed, for example, as a ratchet lock.
  • the pawls of the overrunning clutch can interact directly with external teeth or with teeth on the face of the roller bearing cage.
  • the pawls or other latching elements for example displaceable, spring-loaded latching bolts, can engage, for example, in holes that are located in the cage.
  • the pawl has a detent geometry provided by the cage.
  • the rolling elements, in particular balls, needles or rollers, of the axial roller bearing, radial roller bearing or other roller bearing are typically guided individually in pockets in the cage, which at the same time represents a component of the overrunning clutch.
  • the retaining element, which can be accommodated by the overrunning clutch in the blocking direction, can be influenced with a specifically different pocket play in the circumferential direction of the cage.
  • the holding torque is largely dependent on the loads acting on the bearing arrangement, in the case of an axial bearing in particular on the axial force acting between the bearing disks.
  • a radial bearing there is a relationship between the radial force acting on the bearing and the locking effect that occurs when the bearing is under load.
  • the axial force and/or radial force can inevitably result from the operation of a machine comprising the bearing arrangement and/or can be set in a controlled manner, in particular by applying hydraulic pressure. Configurations are also possible in which a mechanical load, which ensures that the one-way clutch is ready for operation, is at least partially predetermined by a passive element, in particular a spring element.
  • the bearing arrangement is particularly suitable for use in a linear actuator, in which case it can be provided in particular for supporting a spindle of a screw drive.
  • the spindle represents the rotating spindle drive component.
  • the spindle nut can form the rotating spindle drive component, while the associated spindle can be displaced in a manner secured against rotation.
  • the spindle drive can be designed, for example, as a simple movement thread, in particular in the form of a non-self-locking trapezoidal thread with a large pitch, as a ball screw drive or as a planetary roller screw drive, with the latter two screw drives having rolling elements being able to have a comparatively small pitch.
  • the linear actuator can be operated with a particularly low drive power, which is to be applied in particular by an electric motor drive of the screw drive.
  • the locking effect of the freewheel of the bearing arrangement comes into operation automatically as soon as forces are exerted on the spindle, which act in the sense of turning back.
  • the transmission ratio of the spindle drive and the locking effect of the freewheel are selected in an advantageous embodiment, taking into account given frictional forces such that the screw drive cannot be reset by a purely axial load on the threaded spindle when forces occur during normal operation. This means that a reset of the screw drive, ie an adjustment against the freewheeling direction, is only possible with a rotary drive of the threaded spindle, through which the roller bearing locking effect of the overrunning clutch is overcome.
  • the linear actuator is suitable, for example, for use in an electromechanical parking brake, ie parking brake, of a vehicle.
  • This can either be a purely electromechanical brake or a brake which, in a manner known per se, can also be actuated hydraulically as a service brake.
  • the overrunning clutch is a friction-locking clutch, it can be designed, for example, as a wrap spring clutch, as a clamping roller freewheel or as a sprag freewheel.
  • a wrap spring clutch as a clamping roller freewheel or as a sprag freewheel.
  • the rolling elements of the bearing arrangement which also acts as a freewheel, are selected depending on the requirements given in the individual case and can have any known shape, in particular the shape of cylindrical rollers, tapered rollers, needles or balls.
  • the cage which is both a component of the rolling bearing and a component of the overrunning clutch, is in typical configurations around a metal part. All metal parts of the bearing assembly can be heat treated as required.
  • the cage which has a multiple function, namely a function as a component of a roller bearing and a function as a freewheel component, can be produced efficiently, in particular using metal forming processes, with machining processes and shaping by archetypes, for example casting, sintering or 3D, also being possible - Pressure, come into consideration.
  • the surface of the cage can be coated to reduce wear and/or friction and/or the surface layer can be hardened. The same applies to the rolling elements and the bearing washers or other bearing elements of the bearing arrangement.
  • FIG. 1 shows a first exemplary embodiment of a bearing arrangement with a freewheel function in a schematic sectional view
  • FIG. 4 shows a bearing arrangement with a freewheel function, which can be used in a reduction gear and comprises two axial roller bearings, in a simplified sectional view,
  • FIG. 5 shows a front, sectional view of the bearing arrangement according to FIG. 4,
  • FIG. 6 shows the arrangement according to FIG. 4 in an exploded view
  • 7 shows a brake actuator which includes a spindle drive with a bearing arrangement with a freewheel function
  • FIG. 9 shows a detail from FIG. 8,
  • FIG. 10 shows a further exemplary embodiment of a bearing arrangement with a freewheel function in a representation analogous to FIG. 1,
  • a bearing arrangement 1 is installed in a housing 2 and comprises a thrust roller bearing 3, namely a thrust roller or needle bearing, with a freewheel function.
  • the housing 2 is a non-rotating machine element. Embodiments with a rotating housing 2 can also be implemented.
  • a housing washer 4 is used, which is attributable to the axial roller bearing 3 .
  • a shaft washer 5 which is connected to a shaft 6 , is also to be attributed to the axial roller bearing 3 .
  • the central axis of the shaft 6 and thus of the entire bearing assembly 1 is denoted by MA.
  • an axial force Fax can act on the shaft washer 5.
  • the rolling bodies, ie needles or rollers, of the axial roller bearing 3 are denoted by 7 and are guided in pockets 9 of a cage 8 , which at the same time represents an inner coupling part of an overrunning clutch 10 .
  • An associated outer clutch part of the overrunning clutch 10 is denoted by 11 .
  • the outer coupling part 11 is fastened in the housing 2.
  • the functionally identical arrangement of the outer clutch part 11 is given in the arrangement according to FIG.
  • the outer clutch part 11 is connected in a rotationally fixed manner to the shaft washer 5 and thus represents a rotatable component of the bearing arrangement 1.
  • the overrunning clutch 10 is designed as a positively acting clutch which interacts directly with the cage 8 as the inner clutch part.
  • the outer clutch part 11 comprises a plurality of pawls 12 which are spring-loaded by means of coil springs 13, the coil springs 13 being supported on support blocks 14, i.e. spring support blocks, which are provided by the outer clutch part 11.
  • the pawls 12 engage in an external toothing 26 of the cage 8, which is generally referred to as a locking geometry.
  • the cage 8 can be produced using forming methods.
  • bearing assembly 1 is installed in a rotary rotary gear, which is designed as a reduction gear and the represents the first gear stage of a two-stage gear arrangement of an electromechanical actuator.
  • a second axial bearing 18 in addition to the axial roller bearing 3 functioning as a freewheel, with both axial bearings 3 , 18 sharing a common shaft washer 5 .
  • a cage guiding a rolling body 20 is denoted by 19 and a housing washer by 22 .
  • An axial force Fax is exerted on the housing disk 22 with the aid of a plate spring 23, which loads the bearing arrangement 1 as a whole and thus determines the maximum holding torque of the overrunning clutch 10.
  • the outer clutch part 11 comprises a sleeve component 15 which is fixed to the housing and is also referred to as the lock housing and in which there are recesses 16 which can be used for mounting the coil springs 13 .
  • a spring support cover 21 Next to the sleeve component 15 fixed to the housing there is a spring support cover 21.
  • the outside diameter of the externally toothed cage 8 is larger than the outside diameter of the second axial bearing 18.
  • the two axial roller bearings 3, 18 have the same pitch circle diameter.
  • the shaft 6 is provided with a connection contour 17 for the transmission of a torque.
  • the housing 2 is composed of several housing parts 24, 25.
  • the term cage lock is also used for the one-way clutch 10 .
  • the bearing arrangement 1 with the freewheel function is part of a linear actuator 27 for actuating the brakes in a motor vehicle.
  • the shaft 6 is firmly connected to a threaded spindle 29 of a spindle drive 28 or formed directly by the threaded spindle 29 .
  • An associated spindle nut 32 is arranged on a brake piston 30, which can also be actuated hydraulically in a manner known per se.
  • a bellows 31 is provided.
  • the brake disc that can be fixed with the help of the linear actuator 27 is denoted by 35 .
  • the spindle drive 28 is designed as a ball screw drive, with balls (not shown) rolling in a thread turn 34 of the threaded spindle 29 , which balls contact the spindle nut 32 at the same time.
  • the spindle drive 28 is a non-self-locking gear for converting a rotation into a linear movement.
  • a shaft-fixed element designated 33 that is to say an element rigidly connected to the shaft 6, exerts an axial force Fax on the bearing arrangement 1, which in this case is single-row.
  • the function of a second row of bearings supporting in the opposite direction is taken over by the rolling bodies, ie balls, which roll between the threaded spindle 29 and the spindle nut 32 .
  • the brake disk 35 is fixed by means of the linear actuator 27, the axial force Fax increases continuously up to a maximum value. In this position, ie when the parking brake is applied, the axial roller bearing 3 is blocked by the overrunning clutch 10 .
  • the blockage of the linear actuator 27 is positive only insofar as there is a positive fit between the cage 8 as the inner coupling part and the pawls 12 . In contrast, there is no form fit between the bearing disks 4 , 5 of the axial roller bearing 3 . The consequence of this is that the lock effected by the one-way clutch 10 can be canceled by introducing a sufficiently large torque into the shaft 6 in the direction of reverse rotation. This is possible with the help of an electric motor, not shown, which is used to actuate the linear actuator 27 in both directions. Since the overrunning clutch 10 remains locked when the shaft 6 rotates in the release direction, the axial roller bearing 3 is used as a plain bearing in this operating phase.
  • the overrunning clutch 10 is again operated in the overrunning direction, with the pawls 12 only applying a small braking torque is exerted on the cage 8.
  • the linear actuator is in the middle of all operating phases 27 can thus be operated in an energy- and material-saving manner, in particular as far as the electric motor used to drive the shaft 6 is concerned.
  • FIG. 10 the structure of a bearing arrangement 1 is illustrated, which represents a modification of the exemplary embodiment according to FIG.
  • the axial bearing 3 is constructed in two rows, with an inner row of rolling elements being denoted by 36 and an outer row of rolling elements by 37.
  • the designated 38 cage of the inner row of rolling elements 36 represents a pure roller bearing cage and has no freewheel function.
  • the freewheeling function is only taken over by the cage 8, which surrounds the inner cage 38 in a ring and has the same function as in the exemplary embodiment according to FIG.
  • the inner row of rolling elements 36 retains its roller bearing function in every operating state.
  • the blocking effect and braking effect of the freewheel 10 is therefore less pronounced in the case of FIG. 10 than in the case of FIG. 1 .
  • a possible bearing assembly 1 is outlined, which is constructed as a combined radial bearing-freewheel assembly.
  • the rolling bodies 7 of the radial bearing roll directly on an inner peripheral surface of the housing 2 .
  • a separate bearing ring 4, ie outer ring could be present in a manner not shown, in which the rolling elements 7 roll.
  • a rolling body play is shown in Fig. 11 exaggerated.
  • the inner ring 5 is fixedly connected to an inner ring 42 of the overrunning clutch 10 via the shaft 6, not shown here, the rings 5, 42 being offset relative to one another in the axial direction in this case.
  • the overrunning clutch 10 of the bearing arrangement 1 according to FIG. 11 is designed as a clamping roller freewheel and is effective between the inner ring 42 and the cage 8 .
  • the cage 8 is firmly connected or made in one piece with cage elements 39, which individually cushion the rollers designated 40, ie pinch rollers.
  • the inner ring 42 has a ramp contour 43, which ensures that a relative rotation between the cage 8 and the inner ring 42 is only possible in a defined direction and thus the desired freewheeling effect is given.
  • Figures 12 to 14 each relate to three operating phases Ph1, Ph2, Ph3 of the bearing arrangement 1, wherein in the first operating phase Ph1, referred to as the forward stroke, the linear actuator 27 is actuated in the freewheeling direction, i.e.
  • FIG. 12 shows the adjustment path SW, ie the stroke of the linear actuator 27, in the three operating phases Ph1, Ph2, Ph3, and
  • FIG. 13 shows the axial force Fax acting in the bearing arrangement 1.
  • the diagram according to FIG. 15 shows basic possibilities for varying a holding torque Mh, which can be absorbed by the overrunning clutch 10, and applies in principle to all exemplary embodiments.
  • a mechanical load on the bearing arrangement 1 is generally denoted by FL.
  • the holding torque Mh can be determined, among other things, by a constant load (Fconst), which is independent of the current operating status.
  • the bearing arrangement 1 can be loaded with a spring element 23 for this purpose.
  • variable loads (Fvar) occur on the one-way clutch 10, which linearly from the depend on the bearing load FL.
  • Bearing element housing washer, bearing, outer ring
  • Bearing element shaft washer, bearing, inner ring

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

Abstract

L'invention concerne un ensemble palier (1) qui peut être utilisé en particulier dans un actionneur linéaire (27) et qui présente une fonction roue libre. Ledit ensemble palier comprend un palier à roulement (3) doté de deux éléments de palier (4, 5) qui peuvent tourner l'un contre l'autre et des éléments de roulement de contact (7). Une cage (8) guidant les éléments de roulement (7) du palier à roulement (3) est conçue sous la forme d'un composant d'un embrayage à roue libre (10) effectif dans l'état chargé mécaniquement du palier à roulement (3), au moins la partie de verrouillage de la cage (8) étant intrinsèquement rigide.
PCT/DE2022/100537 2021-08-26 2022-07-26 Ensemble palier à fonction roue libre, actionneur linéaire et procédé de fonctionnement d'un actionneur linéaire WO2023025342A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021122104.8 2021-08-26
DE102021122104.8A DE102021122104B3 (de) 2021-08-26 2021-08-26 Lageranordnung mit Freilauffunktion, Linearaktuator und Verfahren zum Betrieb eines Linearaktuators

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WO2023025342A1 true WO2023025342A1 (fr) 2023-03-02

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PCT/DE2022/100537 WO2023025342A1 (fr) 2021-08-26 2022-07-26 Ensemble palier à fonction roue libre, actionneur linéaire et procédé de fonctionnement d'un actionneur linéaire

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DE102022121851A1 (de) 2022-08-30 2024-02-29 Schaeffler Technologies AG & Co. KG Lageranordnung mit schaltbarem Freilauf, Linearaktuator und Verfahren zum Betrieb eines Linearaktuators

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DE1145446B (de) 1958-06-10 1963-03-14 Daimler Benz Ag Als Freilaufkupplung ausgebildetes Radialkugellager
DE3612046A1 (de) * 1986-04-10 1987-10-15 Ford Werke Ag Rollen- oder klemmkoerper-freilauf, insbesondere fuer automatik-getriebe fuer kraftfahrzeuge
US5074393A (en) * 1989-05-19 1991-12-24 Ntn Corporation Clutch-bearing assembly
DE4219143A1 (de) 1992-06-11 1993-12-16 Schaeffler Waelzlager Kg Freilaufeinheit
DE4442404C2 (de) 1994-11-30 1999-07-01 Schaeffler Waelzlager Ohg Verdrehsicherung für einen Kunststoffkäfig eines Freilaufs
DE102006004491A1 (de) 2006-02-01 2007-08-02 Schaeffler Kg Klemmkörperfreilauf
DE10320907B4 (de) 2003-05-09 2007-11-15 Lucas Automotive Gmbh Elektrohydraulisch betätigbare Fahrzeugbremse
US20080093189A1 (en) * 2004-08-24 2008-04-24 Schaeffler Kg Device For Damping Rotary Oscillations
DE102007040029A1 (de) 2007-08-24 2009-02-26 Schaeffler Kg Dreiringlager
EP1945966B1 (fr) 2005-11-04 2010-01-13 Continental Teves AG & Co. oHG Frein de véhicule hydraulique avec frein d'immobilisation intégré à commande électromécanique
WO2010051785A1 (fr) 2008-11-10 2010-05-14 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Attn. Overdiek, Gerhard Roue libre à corps de serrage
DE102009022206B3 (de) 2009-05-20 2010-12-02 Schaeffler Technologies Gmbh & Co. Kg Lagerung mit einer Brems- und/oder Klemmvorrichtung
EP2207982B1 (fr) 2007-10-27 2011-03-02 Continental Teves AG & Co. oHG Frein de véhicule combiné avec frein de stationnement à actionnement électromécanique
EP2069655B1 (fr) 2006-09-27 2012-11-14 Continental Teves AG & Co. oHG Frein combine pour vehicule presentant un frein de stationnement actionnable de maniere electromecanique, et transmission pour la transformation d'un mouvement de rotation en un mouvement de translation
FR3002603A1 (fr) * 2013-02-27 2014-08-29 Akliebolaget Skf Roulement systeme mecanique a embrayage unidirectionnel comprenant un tel roulement et alternateur comprenant un tel systeme
DE102014202189A1 (de) 2014-02-06 2015-08-06 Robert Bosch Gmbh Bremsvorrichtung und Verfahren zum Betätigen einer Bremsvorrichtung für eine automatische Feststellbremse
EP2895772B1 (fr) 2012-09-17 2016-11-09 Continental Teves AG & Co. OHG Frein combiné pour véhicule
WO2020164652A1 (fr) 2019-02-11 2020-08-20 Schaeffler Technologies AG & Co. KG Dispositif de course libre de rouleaux de serrage
DE102005055085B4 (de) 2005-09-29 2020-09-24 Robert Bosch Gmbh Kombinierte Betriebs- und Feststellbremseinrichtung sowie Verfahren zur Durchführung einer Notbremsung

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Publication number Priority date Publication date Assignee Title
DE1145446B (de) 1958-06-10 1963-03-14 Daimler Benz Ag Als Freilaufkupplung ausgebildetes Radialkugellager
DE3612046A1 (de) * 1986-04-10 1987-10-15 Ford Werke Ag Rollen- oder klemmkoerper-freilauf, insbesondere fuer automatik-getriebe fuer kraftfahrzeuge
US5074393A (en) * 1989-05-19 1991-12-24 Ntn Corporation Clutch-bearing assembly
DE4219143A1 (de) 1992-06-11 1993-12-16 Schaeffler Waelzlager Kg Freilaufeinheit
DE4442404C2 (de) 1994-11-30 1999-07-01 Schaeffler Waelzlager Ohg Verdrehsicherung für einen Kunststoffkäfig eines Freilaufs
DE10320907B4 (de) 2003-05-09 2007-11-15 Lucas Automotive Gmbh Elektrohydraulisch betätigbare Fahrzeugbremse
US20080093189A1 (en) * 2004-08-24 2008-04-24 Schaeffler Kg Device For Damping Rotary Oscillations
DE102005055085B4 (de) 2005-09-29 2020-09-24 Robert Bosch Gmbh Kombinierte Betriebs- und Feststellbremseinrichtung sowie Verfahren zur Durchführung einer Notbremsung
EP1945966B1 (fr) 2005-11-04 2010-01-13 Continental Teves AG & Co. oHG Frein de véhicule hydraulique avec frein d'immobilisation intégré à commande électromécanique
DE102006004491A1 (de) 2006-02-01 2007-08-02 Schaeffler Kg Klemmkörperfreilauf
EP2069655B1 (fr) 2006-09-27 2012-11-14 Continental Teves AG & Co. oHG Frein combine pour vehicule presentant un frein de stationnement actionnable de maniere electromecanique, et transmission pour la transformation d'un mouvement de rotation en un mouvement de translation
DE102007040029A1 (de) 2007-08-24 2009-02-26 Schaeffler Kg Dreiringlager
EP2207982B1 (fr) 2007-10-27 2011-03-02 Continental Teves AG & Co. oHG Frein de véhicule combiné avec frein de stationnement à actionnement électromécanique
WO2010051785A1 (fr) 2008-11-10 2010-05-14 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Attn. Overdiek, Gerhard Roue libre à corps de serrage
DE102009022206B3 (de) 2009-05-20 2010-12-02 Schaeffler Technologies Gmbh & Co. Kg Lagerung mit einer Brems- und/oder Klemmvorrichtung
EP2895772B1 (fr) 2012-09-17 2016-11-09 Continental Teves AG & Co. OHG Frein combiné pour véhicule
FR3002603A1 (fr) * 2013-02-27 2014-08-29 Akliebolaget Skf Roulement systeme mecanique a embrayage unidirectionnel comprenant un tel roulement et alternateur comprenant un tel systeme
DE102014202189A1 (de) 2014-02-06 2015-08-06 Robert Bosch Gmbh Bremsvorrichtung und Verfahren zum Betätigen einer Bremsvorrichtung für eine automatische Feststellbremse
WO2020164652A1 (fr) 2019-02-11 2020-08-20 Schaeffler Technologies AG & Co. KG Dispositif de course libre de rouleaux de serrage

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