WO2011023157A1 - Schwungrad mit anlasserzahnkranz - Google Patents
Schwungrad mit anlasserzahnkranz Download PDFInfo
- Publication number
- WO2011023157A1 WO2011023157A1 PCT/DE2010/000896 DE2010000896W WO2011023157A1 WO 2011023157 A1 WO2011023157 A1 WO 2011023157A1 DE 2010000896 W DE2010000896 W DE 2010000896W WO 2011023157 A1 WO2011023157 A1 WO 2011023157A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- flywheel
- spring
- clamping body
- ring gear
- starter
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
- F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
- F02N15/022—Gearing between starting-engines and started engines; Engagement or disengagement thereof the starter comprising an intermediate clutch
- F02N15/025—Gearing between starting-engines and started engines; Engagement or disengagement thereof the starter comprising an intermediate clutch of the friction type
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- 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
-
- 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
- F16D43/00—Automatic clutches
- F16D43/02—Automatic clutches actuated entirely mechanically
- F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
- F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D43/00—Automatic clutches
- F16D43/02—Automatic clutches actuated entirely mechanically
- F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
- F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
- F16D43/18—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members with friction clutching members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D45/00—Freewheels or freewheel clutches combined with automatic clutches
-
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
- F16F15/13114—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses characterised by modifications for auxiliary purposes, e.g. provision of a timing mark
Definitions
- the invention relates to a flywheel which is accommodated on an output shaft of an internal combustion engine and has a starter ring gear for starting the internal combustion engine by means of a starter.
- flywheels are known from the prior art.
- a starter ring gear is rotatably attached to these, in which a pinion of a starter engages and drives the output shaft via the flywheel.
- frequent engagement of the starter may be uncomfortable.
- An object of the invention is therefore to propose a flywheel with starter ring gear in which frequent starting operations of the internal combustion engine can be achieved in a comfortable manner.
- a flywheel which is firmly held on an output shaft of an internal combustion engine, with a starter ring gear for starting the engine by means of a starter, the starter ring gear is rotatably mounted axially between a housing of the internal combustion engine and the flywheel on the housing and depending on the direction of a transmitted from the starter via the starter ring gear on the output shaft torque and / or depending on the speed of the output shaft is fixedly coupled to the drive output shaft.
- starter ring gear and drive shaft thus acts a direction-dependent freewheel and / or a speed-dependent centrifugal clutch.
- the starter ring gear is rotatably mounted on the housing by means of a sliding bearing.
- a sliding bearing usually requires less space than a rolling bearing and is also cheaper.
- the sliding bearing comprises a bearing bush with a cylindrical bearing ring and a housing-side bearing collar.
- a stop ring or locking ring may be provided so that an axial fixing of the starter ring is ensured.
- the sliding bearing comprises a bearing bush which is molded onto the housing. This ensures a secure connection between the bearing bush and housing, as an axial fuse z. B. an undercut is possible.
- the starter ring gear is rotatably mounted on the housing by means of at least three wheels, which are in contact with the outer circumference of the starter ring gear.
- One of the wheels is preferably the starter pinion.
- the other wheels are preferably free-running pinions which are rotatably mounted on the motor housing and are in engagement with the starter ring gear.
- the bearing of the starter ring gear is arranged outside of the starter ring gear, so that the space can be used elsewhere within.
- a torque from the starter to the output shaft is transferable and is decoupled after overhauling the idle speed by the internal combustion engine, the starter ring gear from the output shaft.
- the starter ring gear can be decoupled from the output shaft by means of a freewheel.
- the freewheel is arranged radially between the starter ring gear and the bearing of the starter ring gear.
- the freewheel is arranged radially between the starter ring gear and means for coupling the freewheel to an input part of a clutch.
- the freewheel is a sprag freewheel clutch, wherein clamping body speed-dependent effect a torque transfer between the starter ring gear and the output shaft.
- an inner surface of an axial projection of a gear rim bearing disc part forms a contact surface for clamping surfaces of the clamping body of the sprag freewheel. It is preferably provided that the clamping body distributed over the circumference on a support shaft connected to the support member and against the action of energy storage are arranged radially limited rotatable.
- the clamping body are braced by the energy storage against the inner surface and flyweights have, depending on the speed of the flywheel cause a lifting of the inner surface by rotating the clamping body.
- the energy storage are bias springs.
- the carrier part encompasses a sheet metal cage and an inner ring, which are essentially disc-shaped and form a circumferential intermediate space for receiving the clamping body.
- Both the sheet metal cage and the inner ring can be made as a stamped part or deep-drawn part of a metal sheet.
- the sheet metal cage is formed from segments which are connected to each other with spring elements. This causes a high elasticity in the circumferential direction and-depending on the design of the spring elements- also in the radial direction.
- the sheet-metal cage comprises a cage ring, on which carrier elements are arranged radially outside.
- the inner portion of the sheet metal cage, namely the inner ring, is very rigid, the suspension of the clamping body is relatively elastic in both the circumferential direction and in the radial direction.
- the carrier elements are connected by means of substantially radially extending webs with the cage ring.
- the suspension of the clamping body is relatively elastic in the circumferential direction and relatively stiff in the radial direction.
- the carrier elements are connected by means of curved spring webs with the cage ring.
- the suspension of the clamping body is relatively elastic in the circumferential direction as well as in the radial direction.
- the spring bars are arranged in pairs. - A -
- the inner ring has a toothing which is in engagement with a primary mass. The teeth so worried the torque transfer to the primary mass with coupled freewheel.
- the sheet-metal cage is connected axially and in the circumferential direction frictionally engaged with a guide ring, wherein the guide ring is rotatably connected to the primary mass.
- the sheet metal cage has axial guide surfaces, which bear against an axial annular surface of the guide ring.
- a frictional connection in the axial direction and in the circumferential direction is effected, which is mounted by simple axial impressions of the sheet metal cage in the guide ring.
- the sheet metal cage comprises storage means on which the clamping bodies are rotatably mounted by means of a mounting hole. It is preferably provided that the storage means is a sheet metal nose, which is further preferably stamped out of the sheet metal cage.
- the storage means is a circumferential or split ring approach.
- the storage means is a bush which is pressed into an opening of the sheet metal cage.
- the mounting of the clamping lever comprises an opening through which the biasing spring is guided. It is preferably provided that the biasing spring is fixed with a first spring lever in a groove of the clamping lever and a second spring lever on a stop of the sheet metal cage, wherein a central part of the biasing spring protrudes through the mounting hole of the clamping body.
- a stop limits the rotation of the clamping body.
- the clamping body are set from a dependent of the mass of the flyweights of the clamping body and the spring stiffness of the biasing spring speed by the stop. This reduces wobble and rotational movements of the clamping body with changes in the speed of the drive shaft and thereby reduces vibrations generated.
- the clamping bodies have a notch into which the stop engages upon rotation of the clamping body in an end position. The notch defines the clamping body also in the radial direction with respect to their rotation about the suspension to the sheet metal cage.
- the freewheel is a band spring freewheel with at least one band spring.
- the primary mass has a fastening element for fastening at least one band spring.
- the fastening element is a circumferential or split ring.
- the band spring is arranged spirally in the radial direction between the fastening element and an axial projection which is non-rotatably connected to the starter ring gear.
- the band spring freewheel comprises three band springs, which engage spirally in one another.
- the clamping body by means of a spring which is clamped between the respective clamping body and the sheet metal cage, are braced against the inner surface.
- At least one axial tab is formed on the sheet metal cage.
- an axially resilient element is additionally provided. This should also be installed between the two cage washers and provide for axial springing of the clamp body. This is targeted against a cage disc created and the risk of oblique curling is minimized.
- the spring can be positioned both to the right and left of the clamp body.
- a resilient element for example, a corrugated spring or a plate spring can be used.
- the clamping body are fastened by means of fastening holes on bolts, wherein between the bolts and the surface of the mounting holes, a spring is arranged, which faces a radial displacement of the clamping body allows the bolt against the spring force of the springs.
- the clamp body is mounted on the bolt with a relatively large amount of play. For an exact positioning of the clamp body is not possible.
- the clamping body is only positioned by spring and centrifugal forces. If vibrations in the vehicle are added, it can happen that the individual clamp bodies are different with respect to the cage and, under the moment, roll up differently. This leads to tension of the system and can lead to very high forces that exert individual clamp body on the cage. To prevent this, the clamping body are resiliently mounted on the bolt.
- plastic discs can be inserted between the clamping body and the cage in the area around the bolt on both sides of the clamping body.
- the diameter of the discs should remain as small as possible.
- FIGS 1 to 16 Showing:
- FIG. 1 shows an embodiment of a flywheel with a decoupled by means of a freewheel starter ring gear
- Figure 2 shows a starter ring gear with a storage means of a disc part
- Figure 3 shows another embodiment of a flywheel in section
- Figure 4 is a schematic diagram of Figure 3;
- Figure 5 shows the slide bearing according to Figure 4 in an enlarged view
- Figure 6 shows an embodiment of a freewheel
- FIG. 7 shows a clamping body in a three-dimensional view
- Figure 8 shows the mounting position of a clamping body on a sheet metal cage
- Figure 9 shows a section of the sheet metal cage
- Figure 10 is a rear view of the sheet metal cage of Figure 9;
- Figure 11 is an inner ring
- Figure 12 is a section through an embodiment of a flywheel
- FIG. 13 is an enlarged detail of FIG. 12;
- Figure 14 shows a detail of a guide ring
- Figure 15 shows another embodiment of a flywheel according to the invention.
- Figure 16 is a schematic diagram of an alternative embodiment of the freewheel
- Figure 17 is an enlarged detail of Figure 16;
- Figure 18 is a plan view of the embodiment according to Figures 16 and 17;
- FIG. 19 shows an enlarged detail of FIG. 19
- Figure 20 is a band spring in a three-dimensional view
- Figure 21 shows another embodiment of a flywheel according to the invention
- Figure 22 is a perspective view of the sheet metal cage and other components
- FIG. 23 shows a detail of the sheet metal cage according to FIGS. 21 and 22;
- Figure 24 shows another embodiment of a sheet metal cage
- Figure 25 shows another embodiment of a sheet metal cage
- Figure 26 shows an embodiment of a biasing spring
- Figure 27 shows another embodiment of a sheet metal cage
- Figure 28 shows another embodiment of a sheet metal cage
- Figure 29 shows another embodiment of a sheet metal cage and a clamping body
- FIG. 30 shows the clamping body in FIG. 29
- Figure 31 shows another embodiment of a freewheel
- Figure 32 shows a sheet metal cage with axially flared tab
- Figure 33 shows another embodiment of a freewheel
- Figure 34 embodiments of springs for mounting the clamp body on a
- the flywheel 1 shows an embodiment of a flywheel 1, which is driven by an output shaft 2 of an internal combustion engine, not shown.
- the axis of rotation is designated by the reference numeral 13.
- the flywheel 1 comprises a primary mass 3, which is formed in the example shown from a sheet metal part 3, which may consist of die-cast or forged material in further embodiments.
- the Flywheel 1, for example, record a clutch that connect to a hydrodynamic torque converter or serve as a primary-side input part of a dual mass flywheel.
- a clutch unit which is already mounted on the transmission input shaft of a subsequent transmission, are connected.
- such clutch units may be double clutches of a dual-clutch transmission.
- the flywheel 1 is driven by the output shaft 2.
- the flywheel 1 is firmly connected to the output shaft 2, for example by means not shown connecting means such as screws.
- a starter not shown, which has a pinion which meshes with the toothing of the starter ring gear 4.
- the pinion can be in permanent engagement with the starter ring gear.
- the starter ring gear 4 is centered by means of a rolling bearing 5 on the housing 6 of the internal combustion engine and rotatably received.
- the housing 6 may have an axial projection 7 on which the rolling bearing 5 is accommodated.
- the axial projection 7 also has a stop edge and a locking ring, so that the rolling bearing 5 is axially fixed.
- a disc part 8 Radially between the starter ring gear 4 and the rolling bearing 5, a disc part 8 is provided which has an axial projection 9 for receiving the starter ring gear 4 and an axial projection 10, by means of which the disc part 8 is received on the rolling bearing 5. Furthermore, the disc part 8 is axially secured by means of the axial projection 10 on the rolling bearing 5, for example by means of a locking ring.
- the freewheel 11 may be designed, for example, centrifugally dependent switching, so that after exceeding a predetermined speed, the centrifugal force is used and the freewheel 11 is released so that no more torque is transmitted via the starter ring gear 4 and this is decoupled together with the support member 8 and the rolling bearing 5.
- the freewheel 11 is supported radially on a projection 12 of the sheet metal part 3, wherein the projection 12 may be formed as an annular groove or by means of several distributed over the circumference segments or characteristics.
- FIG. 2 shows the arrangement of the disk part 8 of FIG. 1 in detail.
- the disk part 8 may be made of sheet metal and be brought by means of appropriate punching and sheet metal forming in the appropriate form.
- the configured in the form of a ring disc part 8 has two lugs 9, 10, on which radially outside of the starter ring gear 4 and radially inside the rolling bearing 5 is arranged. It has proved to be particularly advantageous if the rolling bearing 5 and the starter ring gear 4 are arranged at the same axial height. In terms of optimizing the installation space, it may also be advantageous if the roller bearing 5 and the starter ring gear 4 are not aligned when the surface of the housing is not small.
- FIG. 4 shows an alternative embodiment of a flywheel 1, in which compared to the embodiment of Figures 1 and 2, the rolling bearing 5 (see Figure 1) is replaced by a plain bearing.
- Figure 3 shows the embodiment in section
- Figure 4 shows a schematic representation in section. Identical components or components with the same function are as indicated in Figures 1 and 2. Illustrated in FIG. 4 is, inter alia, the housing 6 and the starter ring gear 4, which is fastened on the axial ring gear 9 of the disk part 8.
- the radially inner axial projection 10 forms with a bearing bush 14 which is fixed to the housing in the housing 6, a sliding bearing.
- FIG. 5 shows the sliding bearing according to FIG. 4 in an enlarged view.
- the bearing bush 14 is L-shaped in section and comprises a hollow cylindrical bearing ring 15 and a bearing collar 16 protruding therefrom in the radial direction.
- a retaining ring 17 is arranged in an annular groove 18 of the housing 6 and prevents the bearing ring 15 from sliding axially between the locking ring 17 and the bearing ring 15 is a thrust washer 19 is arranged.
- the bearing collar 16 and the thrust washer 19 form axial fixings for the disc part 8.
- the bearing bush 14 is a plastic component, for example of an injection-molded thermoplastic.
- the thrust washer 19 is also a plastic component made of an injection-molded plastic, but may also be made of a different material such as sheet iron or the like.
- FIG. 6 shows an exemplary embodiment of a freewheel 11. This comprises a sheet-metal cage 21, an inner ring 22 and a plurality of clamping bodies 23 arranged over the circumference of the freewheel 11.
- the sheet-metal cage 21 and the inner ring 22 are firmly connected to one another and form two rings as a carrier part. between which a circumferential gap remains.
- the clamping body 23 are each rotatably mounted about an axis.
- the biasing springs 24 urge the clamp bodies into a position as shown in FIG.
- a clamping body 23 is shown in a spatial view in FIG. 7; FIG. 8 shows the insertion position on the sheet metal cage 21.
- the clamping body 23 is substantially disc-shaped and comprises a receiving area 25 in which a mounting hole 26 is introduced, and a clamping lug 27 with a clamping surface 52 and a flyweight 28.
- the moment of inertia of the flyweight 28 to the mounting hole 26 is greater than the moment of inertia of the Clamp 27 around the mounting hole 26.
- this application of force can be effected, for example, by moving the clamping body 23 on a circular path in the installation position, for example according to FIG. 6, and the centrifugal force in the direction of the directional arrow 29, a torque is generated in the counterclockwise direction about the line of the mounting hole 26.
- FIG. 8 shows the clamping body 23 in the installed position on the sheet metal cage 21. Shown in FIG. 8 is only the area around a clamping body 23, the rest of the sheet metal cage 21 is cut off. Likewise, the inner ring 22 (see Figure 6) is not shown. Compared to Figure 6, the representation of Figure 8 from the opposite direction, in Figure 6 so the clamping body 23 are shown in the plane behind the sheet metal cage 21, in Figure 8, this is exactly the opposite.
- FIG. 9 shows a section of the sheet metal cage 21 without additional attachments, ie in particular without a clamping body 23.
- the view of FIG. 9 corresponds approximately to the view of FIG. 8.
- the upper side 31 of the sheet metal nose 30 is bent in each case in the manner of a circular cutout, so that the inner surface of the fastening bore 26 can slide on the sheet metal nose 30 and the sheet metal sen-30 so form a journal for the clamp body 23.
- the sheet nose 30 are respectively stamped out of the sheet metal cage 21, so that an opening 32 is formed.
- the contour of the opening 32 is in the rear view of the sheet metal cage 21 according to FIG.
- the sheet metal cage 21 comprises individual segments 33, these being designated in FIG. 9 by reference numerals 33a, 33b and 33c.
- the segments 33 are connected to each other with spring elements 34.
- the spring elements 34 allow deformation of the sheet metal cage 21 in the circumferential direction.
- the segments 33 comprise radial guide surfaces 35 which extend in the axial direction with respect to the axis of rotation 13 (see FIG. 1).
- the two peripherally arranged edges 36a and 36b are stepped radially inwardly.
- the segments 33 On their radial inner side, the segments 33 have T-shaped wings 37.
- the biasing springs 39 (see Figure 8) have a first spring lever 40 which lies in a groove 41 of the clamping body 23.
- a cylindrical spring wire wound middle part 42 of the biasing springs 39 protrudes through the opening 32, so that a shown in Figure 12 and 13 second spring lever 43 extends along the respective segments 33 of the opening 32 in the direction of the stop 38 and is determined by the stop 38 ,
- the biasing springs 39 thus generate a torque on the clamping body 23 about the axis formed by the mounting hole 26 in the clockwise direction of Figure 8, this direction is indicated by an arrow 44.
- the inner ring 22 is shown. This includes a disc-shaped annular surface 45, which serves for the axial guidance of the clamping body 23, and an inner race 46. In the raceway 46, an axial toothing 47 is introduced, which makes it possible to transmit a moment.
- FIGS. 12 and 13 show a section through a flywheel according to the invention.
- Figure 13 shows the essential parts of the flywheel in an enlarged view.
- the identical parts with respect to FIGS. 1 and 2 are denoted here in the same way.
- the ring gear 4 is rotatably mounted on the engine block as shown with reference to Figures 4 and 5.
- an outer ring 49 is arranged and fixedly connected to the disc part 8.
- the outer ring 49 has an inner surface 67.
- the raceway 46 of the inner ring 22 is by means of the toothing 47 with an unspecified counter-toothing of the primary mass 3 in engagement and so with respect to the rotation fixedly connected thereto.
- a guide ring 50 is firmly connected to the primary mass 3.
- the guide ring 50 carries a sheet metal cage 21.
- the guide surfaces 35 of the sheet metal cage 21 abut against a circumferential annular surface 51 of the guide ring 50.
- the sheet metal cage 21 and the inner ring 22 are thus rotatably connected to the primary mass 3verbunden.
- the biasing springs 39 By the biasing springs 39, the first driving lugs 27 of their clamping surface 52 are pressed against the inside of the outer ring 49.
- Figure 14 shows a section of the guide ring 50 in an enlarged view.
- the guide ring 50 includes a mounting washer 55 which is fixedly connected to the primary mass 3. This can be done for example by riveting or the like.
- a bead 56 circulating in the axial direction with respect to the primary mass 3 convex in conjunction with an envelope 57 introduced in the opposite direction causes an increased elasticity of the guide ring 50 in the radial direction.
- the envelope 57 is shaped so that it runs with a constant diameter in the axial direction and thus forms the annular surface 51.
- FIG. 15 shows a further exemplary embodiment of a flywheel 1 according to the invention.
- the entire assembly is supported by supporting the starter toothed crane 4 on its outer circumference by three rollers distributed around the outer circumference, or better yet gears.
- One of the gears is a sprocket gear 58 of the starter, the other two gears are mounted fixed to the gear wheels 59a and 59b.
- the bearing through the roller bearing 5 according to FIG. 1 or the plain bearing according to FIG. 4 is replaced by a bearing on the outer circumference of the starter toothed ring 4.
- the primary mass 3 of a dual-mass flywheel here comprises an axially extending circumferential ring 60 to which the open ends of a plurality of spirally arranged band springs 61 are fastened, for example, by rivets 62.
- the starter ring gear 4 has a disc-shaped part 63 which rests with an axial projection 64 on the axial projection 9 of the disc part 8 and is firmly connected thereto.
- the bearing of the disk part 8 is selected in the embodiment of Figure 16 as in the embodiment of Figure 4, but here also can be done a storage in the outer periphery as in the embodiment of Figure 15 or a bearing with a rolling bearing according to the embodiment of Figure 1.
- FIG. 17 shows a section around the ring 60 and the band springs 61 according to FIG. 16 in an enlarged view.
- FIG. 18 shows a plan view of the exemplary embodiment according to FIGS. 16 and 17,
- FIG. 19 shows the region of the band springs 61 and their attachment to the ring 60 in an enlarged detail
- FIG. 20 shows one of the band springs 61 in a three-dimensional view.
- An open end 65 of the band springs 61 is fixedly connected to the ring 60 by means of a rivet 62.
- the other open end 66 of the band springs 60 is located on the axial projection 64.
- the resulting from the bias of the band springs 61 contact force is reduced to the axial extension 64 by the centrifugal force exerted on the band springs 61, so that from a speed that depends on the geometry and the Material properties of the band springs 61 depends, no frictional force is transmitted from the band springs 61 more on the axial projection 64, so that the starter ring gear 4 is free to run relative to the primary mass 3.
- three identical band springs are provided, but any other number of band springs can be used here. It is only important that the band springs have sufficient radial distance from each other, so that they can deform in radial.
- the ring gear 4 takes the free ends 66 of the band springs 61 with. Due to the frictional force between the free ends 66 of the band springs 61 and the axial extension 64, the band springs 61 are further rotated, so that their frictional force is increased. This leads to a self-reinforcing the frictional force. Consequently, a moment can be transmitted between the starter ring gear 4 and the primary mass 3. If the crankshaft rotates below the take-off speed of the band springs and the starter ring gear cranking speed is less than the crankshaft speed, the band springs 61 slide on the ring gear with only a small amount of braking force applied to the crankshaft. As a result, the function of a freewheel is already achieved.
- the band springs 61 lift off the axial shoulder 64. There is then no moment transfer between the primary mass 3 and the starter ring gear 4.
- the Abhebenchiere can be varied by the geometry of the band springs 61, their number, the outer diameter of the axial extension 64 and the like.
- FIG. 21 shows a further exemplary embodiment of a flywheel 1 according to the invention.
- the disk part 8 is in turn mounted with a roller bearing 5.
- the rolling bearing 5 is in turn fixed with a unspecified circlip on the bearing seat of the housing 6.
- An annular recess 68 ensures an axial distance between the roller bearing 5 and the housing 6. This remains a circumferential shoulder 69, which serves as an axial stop for the inner cage of the rolling bearing 5.
- a bearing protection 70 is connected to rivets 71 with the disc part 8.
- a peripheral edge 72 of the disc part 8 surrounds the outer cage of the rolling bearing 5 on the side facing the coupling, the bearing protection 70 engages around the bearing outer ring on the other side, so that the disc part 8 is fixed axially to the rolling bearing 5.
- the sheet-metal cage 21 of the freewheel 11 is embodied here as a closed ring, compare FIG. 22.
- the further construction of the freewheel 11 corresponds to the exemplary embodiment of FIGS. 12 and 13, apart from the configuration of the sheet-metal cage 21.
- FIG. 22 shows a three-dimensional representation of the sheet metal cage 21 and the inner ring 22 with clamping bodies 23 arranged therein.
- the pretensioning springs 39 can also be seen. Further details are not indicated in FIG.
- FIG. 23 shows a section of the sheet-metal cage 21 according to the embodiment of FIGS. 21 and 22.
- the sheet-metal cage 21 comprises a circumferential cage ring 73 into which fastening bores 74 distributed over the circumference are introduced.
- the mounting holes 74 of the cage ring 73 can be connected to the inner ring 22, for example by means of rivets.
- carrier elements 76 are respectively arranged on the cage ring 73.
- the support elements 76 are approximately disk-shaped and each have an opening 32.
- the function of the carrier elements corresponds to that of the segments 33 (see FIG. 9) in previous exemplary embodiments and serve for fastening the clamping bodies 23.
- an annular shoulder 83 circulating in two subregions is provided here two parts 83a and 83b of the annular shoulder is formed. Spacing lugs 84 serve for connection to the guide ring 50 (see FIG. 21).
- the cage of the freewheel 11 is designed in this construction as a closed cage ring 73 (see Figure 22).
- This closed ring can be secured either against rotation with the inner ring 22 and guide plate. This is indicated in the figure by the holes 74.
- Another option is to dispense with the connection and allow the cage to rotate.
- the suspension of the clamping body 23 in the cage by means of a spring bar 75a, 75b (or a web 77, see Figure 24) must be connected to the closed cage ring 73.
- This (spring) web must be made both radially and tangentially soft. The tangential softness is needed in order to be able to join in the tangential movement of the clamping body 23 when rolling in under moment. The stiffer this web is, the higher the forces exerted by the forced movement of the clamp body 23 on the cage.
- FIG. 24 shows a variant of a sheet metal cage 21, in which the carrier elements 76 are arranged on the cage ring 73 by means of a web 77.
- the connection between the carrier element 76 and the cage ring 73 has a large radial rigidity.
- This variant provides a radially stiff cage. This can absorb the centrifugal forces themselves.
- 21 instead of a completely closed ring as a sheet metal cage, 21 this can also be composed of individual segments. This allows for easier production and handling. The individual segments are then either riveted together in the assembly of the freewheel 11, or connected directly to the guide plate or inner ring.
- FIG. 25 shows a variant of the spring webs 75 which is slightly different from the exemplary embodiment in FIG. 23 and in which they have a shorter length and less bending, so that the connection between the cage ring 73 and the carrier elements 76 becomes stiffer.
- FIG. 25 additionally clarifies the fixing of the pretensioning spring 39 (see also FIGS. 8, 9, 10).
- One leg 78 of the prestressing springs 39 engages behind a web 79 on one of the spring webs 75, this being the spring web 75a.
- Spring turns 80 project through the opening 32.
- FIG. 26 shows an exemplary embodiment of a leg spring as the pretensioning spring 39.
- a second, short leg 81 with an axially folded nose 82 engages in a corresponding recess, for example a spring. B.
- FIG. 27 shows the fastening of the leg 79 on the basis of the sheet metal cage according to FIG. 23 in an assembled view in a three-dimensional section.
- FIG. 25 shows the suspension of the leg spring both on the cage and on the clamping body.
- the biasing force of the leg spring can be used to bias the cage.
- the curling of the clamp body under moment forces the cage to tangential deformation.
- This deformation causes high stresses in the resilient area of the cage. These stresses are reduced by introducing the force of the leg spring into the cage at a suitable location.
- FIG. 25 shows a force introduction which fulfills these conditions. Due to the selected support points there is a tangential deformation of the cage (without engine torque), which is directed in the opposite direction to the subsequent deformation by the rolling-in process. When rolling in, therefore, this deformation is first reduced. The tensions in the rolled-up state are correspondingly lower. As already mentioned, the cage is secured against rotation. This allows that the envelope contour of the permanently starter starter may deviate from a rotationally symmetrical contour, if this brings space advantages. This can be achieved by, for example, dispense with individual clamp body and thus locally less axial space is required.
- a torsion-resistant cage brings another advantage.
- the clamping body may only turn up to a predetermined angle. This angle is determined on the one hand by the geometry (collision with other components) and on the other hand by the maximum permissible stress in the leg spring. Since the centrifugal forces of the clamp body for lifting take care about idling speed, the angle of rotation would be too large without additional stop for the clamp body. If the cage is rotationally fixed with respect to the inner ring and thus the clamping bodies are thus quasi stationary, then this stop can be formed on the relatively solid inner ring. This is advantageous over a stop directly on the soft cage. Another possibility is the attachment of the stop on the guide plate.
- the inner ring does not have to be rotationally symmetrical.
- imprints and bores may be applied as long as they do not obstruct the movement of the clamping bodies.
- holes can be made in extension of the leg springs.
- the leg spring can then be longer and is correspondingly flatter in their characteristic. A flat characteristic brings clear advantages for the design of the freewheel.
- the sheet metal cage 21 is designed as a deep-drawn part, so that the annular shoulder 83 is formed directly on the sheet metal cage 21.
- a bush 84 is inserted into the opening 32 instead.
- the bush 84 is guided through the mounting hole 26 of the respective clamping body 23.
- the bush 84 can then be made of a lower quality material and much easier deep drawn.
- Figure 29 shows an embodiment in which the rotation of the clamping body 23 is limited by centrifugal force against the force of the biasing spring 39 by a stop 86.
- the abutment 86 for centrifugal force support abuts in a notch 85 of the clamp body 23 (see FIG. 29).
- the shape of the notch can be configured differently. In addition to the wedge shape, other shapes are conceivable. Among other things, a shape with a larger wedge angle or a circular notch would be possible. Alternatively, notch 85 (both wedge and circular) can be widened.
- This embodiment has the consequence that only a coarse positioning of the clamping body 23 takes place through the notch 85.
- the stop prevents in this case excessive swinging movements of sheet metal cage 21 and clamp body 23 and thus serves as overload protection.
- the web 79 is arranged projecting in the circumferential direction directly on the carrier element 76.
- FIG. 31 shows a further exemplary embodiment of a freewheel according to the invention in a plan view.
- the axial projections 9 and 10 are shown as lines.
- the clamping body 23 are rotatably mounted on bolts 87 of the sheet metal cage 21.
- Each clamping body 23 is associated with a tension spring 88, which surrounds a nose 90 of the clamping body 23 with a first spring hook 89 and with a second spring hook 91, a pin 92 which is arranged on the sheet metal cage 21 surrounds.
- the tension spring is mounted on one side on the clamping body and at the other end in the pin 91 on the cage.
- the tension spring 88 are alternatively a compression spring, a plate spring or leaf spring or a seated outside of the clamping body leg spring possible.
- the suspension of the tension spring 88 on the sheet metal cage 21 can be performed differently.
- the cage plate is designed so that two identical sheets can be used on the two sides of the sprag, so that the inner ring 22 and the sheet metal cage 21 are identical.
- the spring suspensions for example, the pins 92, are alternately issued from one of the two sheets. If pins are used as spring suspension, they can be made of steel or of plastic. The use of plastic as a pin material minimizes the friction between the spring and pin and thus the load on the spring.
- guide elements 93 are inserted on both sides. These are triangular in the sectional view of FIG. 31 and stepped in the axial direction.
- the task of the guide elements is the radial guidance of the sheet metal cage 21 and the clamping body 23, after they have lifted. From this point on, so if the clamp body 23 have lifted from the axial projection 9 and 10, the radial forces based on the Sheet metal cage 21 act on the guide elements 93 on the inner ring.
- the guide elements 93 are preferably made of plastic, but other friction-minimizing materials such as brass or bronze may be used.
- centering is a centering collar, which is mounted in the inner ring.
- the centering collar can be mounted on one or both sides of the inner ring.
- the cage plates are then centered on the inner diameter directly on the inner ring.
- the sheet metal cage 21 should rotate at the speed of the inner ring (the crankshaft speed). Due to the inertia of the cage and the clamping body and the engine vibrations but it will temporarily come to speed differences between the inner ring 22 and the sheet-metal cage 21. This can be changed by an additional friction device, which acts between cage and inner ring.
- One way to create the friction is a diaphragm spring between the cage and inner ring, which axially braces these two parts.
- a spring integrated in the sheet metal cage 21 is also possible. In this case, 21 tabs are punched out on the inner diameter of the sheet metal cage, which are positioned axially.
- the spring tongues 95 On the radial inside 94 is one or more spring tongues 95 punched out, which are cranked in the axial direction.
- the spring tongues 95 comprise a region 95a which lies in the same plane as the remaining parts of the sheet metal cage 21, and a region 95b which is bent by a small angle in the axial direction and which is in a part 95c which in turn lies parallel to the remaining part of the sheet metal cage 21 passes.
- the part 95c is thus effectively shifted relative to the part 95a by an offset in the axial direction.
- the spring tongue 95 is punched out of the base material of the sheet metal cage 21.
- Figure 33 shows a modified embodiment of Figure 31 with additional end stops for the clamping body 23.
- the end stop for each clamp body 23 includes a stop pin 96 which is fixedly connected to the sheet metal cage 21. Instead of a stop pin 96 in the manner of a bolt, the stop can also be formed directly from the cage plate.
- the engaged position of the clamping body 23 is shown by solid lines, the disengaged end position of the central clamping body is shown with a dashed line.
- the maximum diameter of the tension spring 88 is determined by the distance between the two cage plates, ie the distance of the sheet metal cage 21 from the inner ring 22. To increase the maximum possible spring diameter, beads are introduced to the cage plates in the region of the springs. The beads must include the entire pivoting range of the springs. Instead of the beads, windows can also be punched out of the sheet metal cage 21 in the region of the springs.
- Figure 34 shows an alternative attachment of the clamping body 23 to the bolt 87 by means of springs.
- the clamp body is usually mounted on the bolt 87 with a relatively large amount of play. For an exact positioning of the clamp body is not possible.
- the clamping body 23 is positioned only by spring or centrifugal force. Now come vibrations in the vehicle added, it may happen that the individual clamping body 23 are different based on the sheet metal cage 21 and roll under different circumstances. This leads to tension of the system and can lead to very high forces exerting individual clamp body on the sheet metal cage 21. To prevent this, the clamping body are resiliently mounted on the bolt 87.
- Figure 34 shows two possible embodiments of such a spring 97, which is arranged between the bolt 87 and the mounting hole 26 (see, for example, Figure 7).
- FIG. 34a shows a spring 97 in which spring elements 99 are exposed in the radial direction from a substantially cylindrical basic body 98.
- the spring 97 has an opening 100 which allows compression of the spring 97.
- FIG. 34b shows an alternative spring 97, which is designed to be wavy in the radial direction. Both springs have the purpose to reduce the radial play of the clamping body 23 on the bolt 87 and to fix the clamping body 23 in the radial direction, which can be moved against the force of the springs 97 continue in the radial direction.
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112010003447T DE112010003447A5 (de) | 2009-08-28 | 2010-07-29 | Schwungrad mit Anlasserzahnkranz |
JP2012525883A JP2013503282A (ja) | 2009-08-28 | 2010-07-29 | スタータリングギヤを備えるフライホイール |
CN201080038388.4A CN102483028B (zh) | 2009-08-28 | 2010-07-29 | 包括启动器齿环的飞轮 |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009039059 | 2009-08-28 | ||
DE102009039059.6 | 2009-08-28 | ||
DE102009041466 | 2009-09-14 | ||
DE102009041466.5 | 2009-09-14 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011023157A1 true WO2011023157A1 (de) | 2011-03-03 |
Family
ID=43016522
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2010/000896 WO2011023157A1 (de) | 2009-08-28 | 2010-07-29 | Schwungrad mit anlasserzahnkranz |
Country Status (4)
Country | Link |
---|---|
JP (1) | JP2013503282A (de) |
CN (1) | CN102483028B (de) |
DE (2) | DE112010003447A5 (de) |
WO (1) | WO2011023157A1 (de) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2015501398A (ja) * | 2011-10-19 | 2015-01-15 | シェフラー テクノロジーズ ゲー・エム・ベー・ハー ウント コー. カー・ゲーSchaeffler Technologies GmbH & Co. KG | 車両始動装置 |
WO2016119786A1 (de) * | 2015-01-30 | 2016-08-04 | Schaeffler Technologies AG & Co. KG | Fliehkraftkupplung |
EP2855958A4 (de) * | 2012-06-01 | 2016-08-31 | Borgwarner Inc | Freilaufanordnung |
DE102020121909A1 (de) | 2020-08-21 | 2022-02-24 | Bayerische Motoren Werke Aktiengesellschaft | Klemmkörperfreilauf mit Stützelement zum Begrenzen einer Kippbewegung eines Klemmkörpers und Verbrennungskraftmaschine mit einem Klemmkörperfreilauf |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2015032398A1 (de) * | 2013-09-04 | 2015-03-12 | Schaeffler Technologies Gmbh & Co. Kg | Fliehkraftpendel-anschlagfederelement, fliehkraftpendeleinrichtung sowie komponentenanordnung |
DE102013020327B4 (de) | 2013-12-05 | 2022-05-25 | Borgwarner Inc. | Starterfreilauf und Freilaufanordnung mit einem solchen Starterfreilauf |
DE102015202527B3 (de) * | 2015-02-12 | 2016-04-21 | Schaeffler Technologies AG & Co. KG | Riemenscheibenentkoppler |
DE102015202531B3 (de) | 2015-02-12 | 2015-12-17 | Schaeffler Technologies AG & Co. KG | Riemenscheibenentkoppler |
CN106286703B (zh) * | 2015-05-29 | 2018-06-15 | 上海汽车集团股份有限公司 | 单质量飞轮总成 |
CN111043240B (zh) * | 2019-12-31 | 2021-07-20 | 潍柴动力股份有限公司 | 双质量飞轮及机动车的驱动系 |
DE102021001566A1 (de) | 2020-05-29 | 2021-12-02 | Borgwarner Inc. | Freilauf-Dämpfer-Anordnung für ein Kraftfahrzeug |
DE102020005657A1 (de) | 2020-09-16 | 2022-03-17 | Borgwarner Inc. | Freilauf-Dämpfer-Anordnung für ein Kraftfahrzeug und Antriebsstrang für ein Kraftfahrzeug mit einer solchen Freilauf-Dämpfer-Anordnung |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19642147A1 (de) * | 1996-10-12 | 1998-04-23 | Mannesmann Sachs Ag | Kraftfahrzeugkupplung |
DE19752667A1 (de) * | 1997-11-27 | 1999-06-02 | Mannesmann Sachs Ag | Drehschwingungsdämpfer |
DE10019593A1 (de) * | 2000-04-20 | 2001-10-25 | Bayerische Motoren Werke Ag | Anlasserfreilauf |
DE102005021161A1 (de) * | 2004-05-12 | 2005-12-15 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Anlasserzahnkranz sowie Schwungrad mit einem derartigen Anlasserzahnkranz |
EP1936218A2 (de) * | 2006-11-30 | 2008-06-25 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Drehmomentbegrenzer und Montageverfahren für einen Drehmomentbegrenzer |
WO2009103267A2 (de) * | 2008-02-20 | 2009-08-27 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Schwungrad mit anlasserzahnkranz |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4449852B2 (ja) * | 2005-07-29 | 2010-04-14 | トヨタ自動車株式会社 | 内燃機関始動回転力伝達機構 |
JP2009047075A (ja) * | 2007-08-20 | 2009-03-05 | Denso Corp | エンジン始動装置 |
-
2010
- 2010-07-29 CN CN201080038388.4A patent/CN102483028B/zh not_active Expired - Fee Related
- 2010-07-29 DE DE112010003447T patent/DE112010003447A5/de not_active Ceased
- 2010-07-29 WO PCT/DE2010/000896 patent/WO2011023157A1/de active Application Filing
- 2010-07-29 DE DE102010032655A patent/DE102010032655A1/de not_active Withdrawn
- 2010-07-29 JP JP2012525883A patent/JP2013503282A/ja not_active Withdrawn
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19642147A1 (de) * | 1996-10-12 | 1998-04-23 | Mannesmann Sachs Ag | Kraftfahrzeugkupplung |
DE19752667A1 (de) * | 1997-11-27 | 1999-06-02 | Mannesmann Sachs Ag | Drehschwingungsdämpfer |
DE10019593A1 (de) * | 2000-04-20 | 2001-10-25 | Bayerische Motoren Werke Ag | Anlasserfreilauf |
DE102005021161A1 (de) * | 2004-05-12 | 2005-12-15 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Anlasserzahnkranz sowie Schwungrad mit einem derartigen Anlasserzahnkranz |
EP1936218A2 (de) * | 2006-11-30 | 2008-06-25 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Drehmomentbegrenzer und Montageverfahren für einen Drehmomentbegrenzer |
WO2009103267A2 (de) * | 2008-02-20 | 2009-08-27 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Schwungrad mit anlasserzahnkranz |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2015501398A (ja) * | 2011-10-19 | 2015-01-15 | シェフラー テクノロジーズ ゲー・エム・ベー・ハー ウント コー. カー・ゲーSchaeffler Technologies GmbH & Co. KG | 車両始動装置 |
EP2855958A4 (de) * | 2012-06-01 | 2016-08-31 | Borgwarner Inc | Freilaufanordnung |
WO2016119786A1 (de) * | 2015-01-30 | 2016-08-04 | Schaeffler Technologies AG & Co. KG | Fliehkraftkupplung |
US10302157B2 (en) | 2015-01-30 | 2019-05-28 | Schaeffler Technologies AG & Co. KG | Centrifugal clutch |
DE102020121909A1 (de) | 2020-08-21 | 2022-02-24 | Bayerische Motoren Werke Aktiengesellschaft | Klemmkörperfreilauf mit Stützelement zum Begrenzen einer Kippbewegung eines Klemmkörpers und Verbrennungskraftmaschine mit einem Klemmkörperfreilauf |
Also Published As
Publication number | Publication date |
---|---|
DE112010003447A5 (de) | 2012-10-25 |
CN102483028B (zh) | 2014-12-17 |
DE102010032655A1 (de) | 2011-03-10 |
JP2013503282A (ja) | 2013-01-31 |
CN102483028A (zh) | 2012-05-30 |
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