WO2023186211A1 - Dispositif de roue libre et ensemble embrayage comprenant le dispositif de roue libre - Google Patents

Dispositif de roue libre et ensemble embrayage comprenant le dispositif de roue libre Download PDF

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Publication number
WO2023186211A1
WO2023186211A1 PCT/DE2023/100203 DE2023100203W WO2023186211A1 WO 2023186211 A1 WO2023186211 A1 WO 2023186211A1 DE 2023100203 W DE2023100203 W DE 2023100203W WO 2023186211 A1 WO2023186211 A1 WO 2023186211A1
Authority
WO
WIPO (PCT)
Prior art keywords
freewheel
locking
rotation
sleeve
intermediate sleeve
Prior art date
Application number
PCT/DE2023/100203
Other languages
German (de)
English (en)
Inventor
Erik Orel
Luboslav Slezák
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 WO2023186211A1 publication Critical patent/WO2023186211A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/12—Freewheels or freewheel clutches with hinged pawl co-operating with teeth, cogs, or the like
    • F16D41/14—Freewheels or freewheel clutches with hinged pawl co-operating with teeth, cogs, or the like the effective stroke of the pawl being adjustable

Definitions

  • the invention relates to a freewheel device for a drive train of a vehicle with the features of the preamble of claim 1.
  • the invention further relates to a clutch arrangement with the freewheel device.
  • Friction clutches are very common in internal combustion engines, and positive clutches and/or claw clutches are often used as drive motors in electric motors.
  • one-way clutches are also widely used, with a torque-transmitting connection being opened or closed depending on the speed of rotation and the direction of rotation of two shafts connected via the open-air clutch.
  • a one-way clutch comprising: an inner race with a plurality of pawl receiving recesses, a plurality of spring receiving recesses, an outer race surrounding the inner race, the outer race and the inner race are fixed relative to one another in a drive direction and are rotatable relative to one another about an axis in a freewheeling direction, a plurality of pawls between the inner race and the outer race, each pawl being received in a corresponding pawl receiving recess of the plurality of pawl receiving recesses and each pawl having a front one section and a rear section, and a plurality of band springs between the inner race and the outer race, with adjacent band springs secured together with integral clasps and bridges, each pawl being disposed between two clasps to form a circumferential retaining ring .
  • the subject of the invention is a freewheel device which is designed and/or suitable in particular for a drive train of a vehicle.
  • the freewheel device is designed as an overrunning clutch and/or as a direction-dependent clutch.
  • the freewheel device transmits a torque between the two freewheel partners depending on the direction of rotation.
  • the freewheeling device has a first freewheeling partner and a second freewheeling partner.
  • the freewheel partners can be rotated about a common main axis of rotation.
  • the first freewheel partner can be connected and/or connected in a torque-transmitting manner to a first rotating component, for example a first shaft
  • the second freewheel partner can be connected and/or connected in a torque-transmitting manner with a second rotating component, for example a second shaft.
  • the two freewheel partners are preferably arranged coaxially and/or concentrically with respect to the main axis of rotation.
  • the freewheel device has a plurality of locking bodies, which are arranged, in particular fixed, in the radial direction to the main axis of rotation on one freewheel partner and which interact in a form-fitting manner with a ramp-shaped locking contour arranged on the other freewheel partner depending on the direction of rotation and / or the speed of rotation.
  • the locking bodies engage the locking contour in a fixed direction of rotation, preferably in a form-fitting manner
  • the freewheel device When the freewheel device is in a freewheeling state, they slide off the locking contour in a direction opposite to the direction of rotation.
  • the locking contour is preferably formed by a circumferential toothed ramp geometry, in particular a sawtooth ramp.
  • the toothed ramps are aligned in particular in the radial direction.
  • the locking bodies are preferably designed as radially movable locking pawls.
  • pivot axes or pivot areas of the locking bodies extend parallel to the main axis of rotation.
  • the freewheel device has an intermediate sleeve.
  • the intermediate sleeve comprises a sleeve section surrounding the main axis of rotation and a plurality of spring sections.
  • the intermediate sleeve has the shape of a hollow cylinder.
  • the spring sections are arranged and/or designed to implement a spring load on the locking bodies.
  • the locking bodies are spring-loaded in the radial direction with respect to the main axis of rotation.
  • the sleeve section and the spring sections are formed in one material and/or in one piece from a common, coherent base material.
  • the spring sections are designed as sections that are only partially and not completely separated from the sleeve section and are connected to the sleeve section in one material and/or in one piece via a fastening area.
  • the sleeve section and the spring sections are realized together in a monolithic manner.
  • the assembly of the freewheel device is significantly simplified due to the joint design of the sleeve section and the spring sections. It is no longer necessary to assemble a large number of individual parts for spring loading of the locking bodies, but the intermediate sleeve has the spring sections integrated, so that the intermediate sleeve can be installed as a single component in the freewheel device.
  • the spring sections are connected undivided to the sleeve section, so that the intermediate sleeve is formed from a process sequence and/or process combination, in particular from cutting and forming, but the individual spring sections do not have to be assembled separately.
  • the intermediate sleeve can thus be manufactured as a component from a common base material in one piece and in high quality.
  • the simplified structure simplifies both the production and assembly of the freewheel device.
  • the spring sections are each designed as a leaf spring section.
  • the respective leaf spring section is connected to the sleeve section in one material and/or in one piece via a fastening area running parallel to the main axis of rotation.
  • the leaf spring section preferably has a rectangular shape, with a side edge of the rectangular shape forming the connecting fastening area.
  • the leaf spring section can be bent in the radial direction, either radially inwards or radially outwards, to generate and/or increase the spring load, for example, so that it runs, for example, in a tangential direction to the pitch circle diameter of the sleeve section.
  • the spring sections are designed as biasing spring sections, with the biasing spring sections biasing the locking bodies against the locking contour.
  • each locking body is assigned such a biasing spring section.
  • the spring sections are designed as control spring sections, the control spring sections blocking the radial deflection of the locking bodies, so that the locking bodies are separated from the locking contour.
  • each locking body is assigned such a control spring section.
  • the intermediate sleeve is designed as a control sleeve, wherein the intermediate sleeve can assume different control positions in the direction of rotation around the main axis of rotation to control the locking bodies.
  • the intermediate sleeve can be rotated in the direction of rotation in order to assume the different control positions.
  • the intermediate sleeve releases the locking bodies for engagement in the locking contour.
  • the freewheeling device is now switched on.
  • a passive position as a control position the intermediate sleeve keeps the locking bodies out of engagement with the locking contour. In this control position, the freewheeling device is switched off.
  • the two freewheeling partners can rotate independently of each other in both directions when the freewheeling device is switched off.
  • the preload spring sections pretension the locking bodies against the locking contour.
  • any control organs can in principle keep the locking bodies out of engagement with the locking contour.
  • the control spring sections preferably block the radial deflection of the locking bodies, so that they are arranged without interference with the locking contour.
  • the locking bodies are pressed in a first radial direction by the control spring sections in the passive position of the intermediate sleeve and/or in an opposite second radial direction, in particular in the direction of the locking contour, in the active position of the intermediate sleeve by the biasing spring sections.
  • the active position is set as a control position and when the intermediate sleeve is rotated in a direction opposite to the first direction of rotation, the passive position is set as a control position. It follows that when the intermediate sleeve is rotated into the active position, the preload spring sections are moved to the locking bodies and when rotated in the opposite direction, the preload spring sections are moved away and the control spring sections are moved to the locking bodies. At a Rotation in the original direction, the control spring sections are moved away again and the preload spring sections are closed.
  • This configuration results in a component for the intermediate sleeve that is comparatively easy to manufacture, but highly integrated in terms of functions, which can be easily installed in the freewheel device and can switch it in a simple manner.
  • the intermediate sleeve has a plurality of opening areas, with the control spring sections and the preload spring sections being arranged opposite one another in the opening areas in the circumferential direction.
  • the opening areas are each designed to be rectangular in the development of the intermediate sleeve, with the control spring sections and the biasing spring sections facing each other with the free spring areas, with particularly preferably a spacing in the circumferential direction between the control spring section and the preloading spring section in a common opening area, the spacing being at least the Extension of the control spring section or the preload spring section in the direction of rotation corresponds.
  • the intermediate sleeve is arranged at least in some areas and/or in at least one control position between the locking bodies and the locking contour. This positioning ensures that the intermediate sleeve can keep the locking bodies away from the locking contour. Alternatively or additionally, this ensures that the intermediate sleeve can bias the locking bodies in the direction of the locking contour. This configuration means that the freewheel device can be implemented in a very space-saving manner.
  • the locking bodies are arranged radially on the outside of the locking contour.
  • the control spring sections in the passive position move the locking bodies in the radial direction reach under to block the locking bodies.
  • the respective control spring section presses against the locking body from radially inside in order to push it radially outwards and/or away from the locking contour.
  • the preload spring sections in the active position extend over the locking bodies in the radial direction in order to preload the locking bodies.
  • the respective biasing spring section presses on the locking body from radially outside in order to press it radially inward and/or against the locking contour.
  • the first freewheel partner has a plurality of receiving pockets on an inner circumference for receiving the locking bodies and the second freewheel partner has the locking contour on an outer circumference opposite the locking bodies.
  • the locking bodies are accommodated in a retractable manner within the receiving pockets.
  • the receiving pockets preferably form a negative contour of the blocking body.
  • the locking bodies are movably mounted in the respective receiving pocket. When switched on, the locking bodies are partially moved out of the respective receiving pocket, so that they are in torque-transmitting engagement with the locking contour on the one hand and with the receiving pocket on the other. When switched off, the locking bodies are completely or largely driven into the respective receiving pocket, so that they are disengaged or arranged at a distance from the locking contour. Due to the concentric arrangement of the freewheel partners, the locking bodies can be moved in and out of the receiving pockets in a simple and space-saving manner.
  • the clutch arrangement also has a sliding sleeve arranged coaxially to the two clutch partners and/or freewheel partners for controlling the clutch arrangement and for the rotationally fixed connection of the freewheel partners as clutch partners positive coupling.
  • the sliding sleeve is motion-coupled with the intermediate sleeve, so that the intermediate sleeve can be switched between the passive position and the active position by the sliding sleeve.
  • the sliding sleeve is coupled to the intermediate sleeve in such a way that it is pivoted in the circumferential direction when the sliding sleeve is axially displaced.
  • the sliding sleeve is preferably displaceable in the axial direction with respect to the main axis of rotation relative to the two freewheel partners and is non-rotatably connected or connectable in the circumferential direction to the first and/or the second freewheel partner.
  • the two freewheel partners are accommodated or receivable radially within the sliding sleeve.
  • the sliding sleeve can have a groove running in the circumferential direction on its outer circumference for connecting an actuating actuator.
  • the groove serves to accommodate a shift fork, in particular to accommodate a sliding block.
  • the sliding sleeve is displaceable in the axial direction with respect to the main axis of rotation between a locking position, a freewheeling position and a neutral position.
  • the sliding sleeve is displaceable in an axial direction relative to the main axis of rotation from the locking position to the freewheeling position and then to the neutral position and in reverse order in an axial opposite direction.
  • the two freewheel partners are connected to each other in a rotationally fixed manner in one direction of rotation and in a counter-rotation direction as coupling partners via the sliding sleeve.
  • the sliding sleeve positively engages with the first and second freewheel partners in the circumferential direction in order to connect the two freewheel partners to one another in a rotationally fixed manner during rotation in the direction of rotation and the opposite direction of rotation.
  • the two freewheeling partners are connected to one another in a rotationally fixed manner via the freewheeling device in exactly one direction of rotation.
  • the sliding sleeve controls the active position of the intermediate sleeve.
  • the locking bodies positively engage with the first and second freewheeling partners in the direction of rotation in order to connect the two freewheeling partners to one another in a rotationally fixed manner during rotation in the direction of rotation.
  • the two freewheel partners can be rotated relative to each other when rotating in a counter-rotating direction or one of the two freewheel partners remains stationary.
  • the freewheel device is switched off by axially moving the sliding sleeve into the neutral position.
  • the locking bodies are held out of engagement with the locking contour by the control of the intermediate sleeve by the sliding sleeve, so that the two freewheel partners can be rotated relative to one another in the direction of rotation and in the opposite direction of rotation.
  • the sliding sleeve controls the intermediate sleeve so that it is in the passive position.
  • the advantage of the clutch arrangement is that it is characterized by simple actuation, particularly under load, due to the axial displacement of the sliding sleeve.
  • an additional actuator for the freewheel device can be dispensed with, so that the clutch arrangement requires significantly fewer components and at the same time can be designed to be particularly cost-effective.
  • Another advantage is that the clutch arrangement can be designed to be particularly robust and is suitable for transmitting high torques.
  • the first freewheel partner has external teeth and the second freewheel partner has locking teeth.
  • the sliding sleeve is rotatably connected to the external toothing via internal teeth Engagement, wherein the internal toothing can also be brought into rotationally fixed engagement with the locking teeth when shifted into the locking position in order to couple the two freewheel partners to one another in a rotationally fixed manner.
  • the external, internal and locking teeth are each designed as a straight toothing aligned in the axial direction with respect to the main axis of rotation, so that the sliding sleeve and the first or second freewheel partner are displaceable relative to one another in the axial direction to the main axis of rotation and are rotationally fixed to one another in the circumferential direction are coupled.
  • the internal toothing of the sliding sleeve and the external toothing of the first freewheel partner are formed by webs or teeth or grooves that extend axially to the main axis of rotation.
  • the sliding sleeve preferably has a roof toothing axially on the side of the internal toothing directed towards the second freewheel partner.
  • the second freewheel partner has a roof toothing axially on the side of the locking toothing directed towards the sliding sleeve.
  • the intermediate sleeve has a link element and the sliding sleeve has a link on or in which the link element can move.
  • the backdrop organ and the backdrop together form a backdrop control. The movement coupling between the sliding sleeve and the intermediate sleeve takes place via the link control, so that when the sliding sleeve is axially displaced via the link control, the intermediate sleeve is pivoted.
  • a possible subject of the invention relates to a drive train with a first and a second shaft and with the clutch arrangement as already described previously.
  • the first shaft is non-rotatably connected to the first freewheel partner and the second shaft is non-rotatably connected to the second freewheel partner, with torque transmission between the two shafts being controllable by axially displacing a sliding sleeve of the clutch arrangement.
  • the first freewheel partner has a first driving toothing for a rotationally fixed connection of the first shaft and the second freewheel partner has a second driving toothing for a rotationally fixed connection of the second shaft.
  • the powertrain is preferred designed and/or suitable for driving a vehicle, in particular a motor vehicle.
  • the drive train is designed and/or suitable for an electric axle of the vehicle.
  • the clutch arrangement can be part of a connection or disconnection unit (“connect or disconnect unit”), for example to release an electric drive from the drive shafts of the vehicle.
  • one shaft can be designed as a motor-side drive shaft and the other shaft as a wheel-side output shaft.
  • Figure 1 is an exploded view of a coupling arrangement as an exemplary embodiment of the invention
  • Figure 2 is a cross-sectional view of the coupling arrangement in Figure 1;
  • Figure 3 is a side plan view of the coupling arrangement of the previous figures in a locked position
  • Fig. 4 a, b a side plan view and a cross-sectional view
  • Fig. 5 a, b a side plan view and a cross-sectional view
  • Figure 1 shows a clutch arrangement 1 with a freewheel device 11 in an exploded view as an exemplary embodiment of the invention.
  • the freewheel device 11 has a first and a second freewheel partner 2, 3, which, depending on the relative rotation to one another, are coupled to one another in a rotationally fixed manner in a locked state in a direction of rotation or are arranged to rotate freely relative to one another in a freewheeling state.
  • the clutch arrangement 1 is designed as a claw clutch and/or a positive clutch, with the freewheel partners 2, 3 also forming clutch partners in the clutch arrangement 1.
  • the clutch arrangement 1 has a sliding sleeve 4, which is arranged coaxially to the freewheel partners 2, 3 with respect to a common main axis of rotation 100.
  • the first freewheel partner 2 is designed as a hub, in particular as a sleeve carrier, on which the sliding sleeve 4 is arranged in a rotationally fixed manner and is arranged to be displaceable in an axial direction 101 and an axial opposite direction 102 with respect to the main axis of rotation 100.
  • the first freewheel partner 2 has an external toothing 5 on the outer circumference and the sliding sleeve 4 has an internal toothing 6 on the inner circumference, which are each designed as straight teeth extending axially to the main axis of rotation 100.
  • the second freewheel partner 3 is designed as a coupling body which has a locking toothing 7 on its outer circumference, the sliding sleeve 4 being able to be brought into rotationally fixed engagement with the locking toothing 7 during an axial displacement in the axial opposite direction 102 along the main axis of rotation 100 in order to secure the two freewheeling partners 3, 5 to be coupled together in a rotationally fixed manner.
  • the first and second freewheel partners 2, 3 are each designed as a spur gear or a spur-toothed wheel.
  • the sliding sleeve 4 can be connected to an actuating actuator, not shown, which applies an actuating force to the sliding sleeve 4 in the axial direction with respect to the main axis of rotation 100.
  • the sliding sleeve 4 In order to move the sliding sleeve 4 in the axial direction 101 or the axial opposite direction 102 during rotation about the main axis of rotation 100, the sliding sleeve 4 has a circumferential groove 24 on its outer circumference, into which, for example, a shift fork of the actuating actuator can engage.
  • the first and second freewheel partners 2, 3 are each rotatably connected to a rotating component, for example a shaft.
  • the first freewheel partner 2 has a first driving toothing 9 on the inner circumference and the second freewheel partner 3 has a second driving toothing 10 on the inner circumference.
  • the first and second driving teeth 9, 10 are each designed as a plug-in toothing.
  • the first freewheel partner 2 can be arranged on an output side and the second freewheel partner 3 can be arranged on a drive side.
  • the freewheel device is designed as a switchable freewheel device 11.
  • the freewheel device 11 has several, in particular six, locking bodies 12 distributed around the main axis of rotation 100, which are each pivotally arranged in a receiving pocket 14 formed on the first freewheel partner 2.
  • the receiving pockets 14 are each designed as depressions made on the inner circumference of the first freewheel partner 2, which essentially form a negative contour of the locking body 12.
  • the locking bodies 12 can be deflected in the radial direction and are received in a form-fitting manner in the associated receiving pocket 14 in the circumferential direction.
  • the locking bodies each have a pivot axis 13, the pivot axes 13 being aligned parallel to the main axis of rotation and, for example, being fixed to the first freewheel partner 2.
  • the second freewheel partner 3 has a ramp-shaped locking contour 15 on its outer circumference facing the locking bodies 12, which is designed as a spur toothing.
  • the locking contour 15 can interact positively with the locking bodies 15 in a switched-on state of the freewheel 11 in a direction of rotation 103 of the second freewheel partner 3.
  • a counter-rotation direction 104 that is opposite to the direction of rotation 103, the first and second freewheel partners 2, 3 can be rotated relative to one another, with the locking bodies 14 sliding on the locking contour 15 when the freewheel 11 is engaged.
  • the locking bodies 12 are designed as locking pawls and the locking contour 15 is formed by several sawtooth ramps rising in the circumferential direction.
  • the freewheel device 11 also has a circumferentially movable intermediate sleeve 16 for controlling the freewheel 11, which is arranged coaxially to the two freewheel partners 2, 3 with respect to the main axis of rotation 100.
  • the coupling arrangement 1 has a guide ring 17, the guide ring 17 in this exemplary embodiment having three guide webs 18, which extend in the axial direction to the main axis of rotation 100.
  • the guide ring 17 serves to radially guide the intermediate sleeve 16.
  • the intermediate sleeve 16 can assume different control positions in the direction of rotation, in particular a passive position and an active position.
  • the intermediate sleeve 16 has a sleeve section 8 and control spring sections 19, the control spring sections 19 being arranged on the sleeve section 8 and blocking the radial deflection of the locking bodies 12 in the passive position of the intermediate sleeve 16.
  • the control spring sections 19 are designed as leaf spring sections, which are each connected to the sleeve section 8 in one piece and/or in one material via an axially extending fastening area and are bent radially inwards.
  • the intermediate sleeve 16 has biasing spring sections 20, the biasing spring sections 20 being arranged on the sleeve section 8 and biasing the locking bodies 12 against the locking contour 15 in the active position of the intermediate sleeve 16.
  • the biasing spring sections 20 are designed as leaf spring sections, which are each connected in one piece and/or in one material to the sleeve section 8 via an axially extending fastening region and are bent radially outwards.
  • the intermediate sleeve 16 in particular the sleeve section 8, has opening areas 21, each opening area 21 being provided in the circumferential direction with a control spring section 19 on one side and with a preload spring section 20 on the other side.
  • a locking body 12 is assigned to each opening area 21 and/or each control spring section 19 and/or each preload spring section 20.
  • the intermediate sleeve 16 can be used, for example Sheet metal ring, in particular sheet metal sleeve, can be formed, wherein the control spring sections 19 and the biasing spring sections 20 are at least partially separated from the sheet metal ring, but are connected to the sleeve section 8 in one piece and / or in one material via the base material of the intermediate sleeve 16.
  • the intermediate sleeve 16 has link elements 22, which are designed as link pins and extend outwards in the radial direction.
  • the intermediate sleeve 16 has three such link elements 22, which are regularly distributed in the direction of rotation.
  • the sliding sleeve 4 has links 23, which together with the link elements 22 each form a link control. When the sliding sleeve 4 is moved axially, the link element 22 is guided along the link 23, so that depending on the axial position of the sliding sleeve 4 relative to the intermediate sleeve 16, the intermediate sleeve 16 is rotated in the circumferential direction in order to achieve the different control positions, in particular the passive position Active position to be taken in order to switch the freewheel device 11 on or off.
  • the sliding sleeve 4 can be moved along the main axis of rotation 100 into a blocking position 105, a freewheeling position 106 and a neutral position 107.
  • the sliding sleeve 4 In the locking position 105, the sliding sleeve 4 is in engagement via the internal toothing 6 on the one hand with the external toothing 5 and on the other hand with the locking toothing 7, so that the two freewheel partners 3, 4 are connected to one another in a rotationally fixed manner in the direction of rotation 103 and the counter-rotation direction 104 and form the coupling partners.
  • the sliding sleeve 4 engages exclusively with the external toothing 5 via the internal toothing 6, with the freewheel device 11 being switched on at the same time, so that the two freewheel partners 2, 3 are connected to one another in a rotationally fixed manner in the direction of rotation 103 and relative to one another in the opposite direction of rotation 104 are twistable.
  • the neutral position 107 the sliding sleeve 4 engages exclusively with the external toothing 5 via the internal toothing 6, with the freewheel device 11 being switched off at the same time, so that the two freewheel partners 2, 3 can be rotated relative to one another in the direction of rotation 103 and in the opposite direction of rotation 104.
  • FIG 2 shows a schematic cross-sectional view through the clutch arrangement 1 in Figure 1, with the freewheel device 11 switched on and/or activated. From the cross-sectional view it can be seen that the intermediate sleeve 16 is in the active position, with the biasing spring sections 20 resting on the locking bodies 12, in particular on a free, pivotable end of the locking bodies 12, in an elastically resilient and/or spring-loaded manner, so that the locking bodies 12 is pressed radially inwards onto the locking contour 15. Depending on the direction of rotation, the freewheeling device 11 can then assume a freewheeling state or a locked state.
  • the intermediate sleeve 16 is rotated counterclockwise in this illustration, the preload spring sections 20 are moved away from the locking bodies 12, so that the preload and/or spring loading is canceled.
  • the control spring sections 19 are moved to the locking bodies 12, so that the control spring sections 19 block the locking bodies 12 so that they cannot come into contact with the locking contour 15.
  • the freewheel device 11 is in a switched off state and the intermediate sleeve 16 is in the passive position.
  • the intermediate sleeve 16 is arranged at least in some areas between the locking bodies 12 and the locking contour 15.
  • the biasing spring sections 20 engage over the locking bodies 12 when viewed in the radial direction and the control spring sections 19 engage under the locking bodies 12 in the radial direction.
  • the clutch arrangement 1 is shown in the locking position 105.
  • the sliding sleeve 4 engages over the first freewheeling partner 2 and the second freewheeling partner 3, the internal toothing 6 of the sliding sleeve 4 being in engagement with both the external toothing 5 of the first freewheeling partner 2 and with the locking toothing 7 of the second freewheeling partner 3, so that it is rotationally fixed over the Sliding sleeve 4 are connected to each other.
  • the link element 22 is located at the beginning of the link 23.
  • the sliding sleeve 4 becomes axial in the direction of the first Freewheel partner 2 and / or shifted in the axial direction 101.
  • the intermediate sleeve 16 is not actuated via the link guide due to the transition from the locking position 105 to the freewheel position 106.
  • Figure 4a shows the clutch arrangement 1 in the freewheel position 106.
  • the sliding sleeve 4 is moved to such an extent that the second freewheel partner 3 and/or the locking teeth 7 are released.
  • the positive connection between the first and second freewheel partners 2, 3 is released via the sliding sleeve 4.
  • the intermediate sleeve 16 is in the active position, so that the biasing spring sections 20 press the locking bodies 12 against the locking contour 15.
  • the freewheel device 11 is thus activated and a torque is transmitted between the freewheel partners 2, 3 depending on the relative direction of rotation.
  • 5a shows the clutch arrangement 1 in the neutral position 107.
  • the sliding sleeve 4 is further displaced, with the second freewheel partner 3 and/or the locking teeth 7 being released as in the freewheel position 106.
  • the positive connection between the first and second freewheel partners 2, 3 via the sliding sleeve 4 is still broken. Due to the further axial displacement of the sliding sleeve 4 in the axial direction 101, the link member 22 is displaced in the circumferential direction by the link 23, which is aligned obliquely to the axial extension in the end region. By moving the link member 22, the intermediate sleeve 16 is rotated in the direction of rotation and transferred from the active position to the passive position.
  • the intermediate sleeve 16 is in the passive position, with the preload spring sections 20 having moved away from the locking bodies 12 in the circumferential direction and, on the other hand, the control spring sections 19 being in contact with the locking bodies 12 and pushing them outwards in the radial direction , so that the locking bodies 12 are separated and/or spaced apart from the locking contour 15.
  • the freewheel device 11 is in a switched off state.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)

Abstract

Afin d'obtenir une mise en prise et un désengagement automatisés dans divers états d'entraînement d'un véhicule, des embrayages à roue libre sont largement utilisés, une liaison de transmission de couple étant ouverte ou fermée en fonction de la vitesse de rotation et du sens de rotation de deux arbres reliés par l'intermédiaire de l'embrayage à roue libre. L'invention concerne un dispositif de roue libre (11) comprenant : un premier et un second partenaire de roue libre (2, 3), les partenaires de roue libre (2, 3) définissant un axe de rotation principal (100) ; une pluralité d'éléments de verrouillage (12) qui peuvent être déviés radialement et et qui sont situés sur un partenaire de roue libre (2) et interagissent par complémentarité de forme, en fonction du sens de rotation, avec un contour de verrouillage de type rampe (15) situé sur l'autre partenaire de roue libre (3) afin d'accoupler les deux partenaires de roue libre (2, 3) ensemble en fonction du sens de rotation ; et un manchon intermédiaire (16), le manchon intermédiaire (16) ayant une partie manchon circonférentielle (8) et une pluralité de parties ressort destinées à charger par ressort l'élément de verrouillage (12), la partie manchon (8) et les parties ressort étant formées à partir d'un matériau et/ou d'un seul tenant à partir d'un matériau de base continu commun.
PCT/DE2023/100203 2022-03-29 2023-03-16 Dispositif de roue libre et ensemble embrayage comprenant le dispositif de roue libre WO2023186211A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022107408.0 2022-03-29
DE102022107408.0A DE102022107408B3 (de) 2022-03-29 2022-03-29 Freilaufeinrichtung sowie Kupplungsanordnung mit der Freilaufeinrichtung

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WO2023186211A1 true WO2023186211A1 (fr) 2023-10-05

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PCT/DE2023/100203 WO2023186211A1 (fr) 2022-03-29 2023-03-16 Dispositif de roue libre et ensemble embrayage comprenant le dispositif de roue libre

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DE (1) DE102022107408B3 (fr)
WO (1) WO2023186211A1 (fr)

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WO2024061862A1 (fr) * 2022-09-21 2024-03-28 Magna Pt B.V. & Co. Kg Embrayage à roue libre à prise automatique pour une chaîne cinématique de véhicule automobile

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US5855263A (en) * 1996-12-20 1999-01-05 Eaton Corporation One-way clutch and torque converter stator
US20090145718A1 (en) 2005-09-02 2009-06-11 Chiesa Alfred J Overrunning Clutch
US20100181157A1 (en) * 2007-06-27 2010-07-22 Schaeffler Kg Freewheel coupling
US10871194B2 (en) * 2019-01-31 2020-12-22 Schaeffler Technologies AG & Co. KG Switchable ratcheting wedge clutch

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US5205386A (en) * 1992-03-05 1993-04-27 United Technologies Corporation Pawl and ratchet clutch with pawl holdback
US5855263A (en) * 1996-12-20 1999-01-05 Eaton Corporation One-way clutch and torque converter stator
US20090145718A1 (en) 2005-09-02 2009-06-11 Chiesa Alfred J Overrunning Clutch
US20100181157A1 (en) * 2007-06-27 2010-07-22 Schaeffler Kg Freewheel coupling
US10871194B2 (en) * 2019-01-31 2020-12-22 Schaeffler Technologies AG & Co. KG Switchable ratcheting wedge clutch

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024061862A1 (fr) * 2022-09-21 2024-03-28 Magna Pt B.V. & Co. Kg Embrayage à roue libre à prise automatique pour une chaîne cinématique de véhicule automobile

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