CN101970852B - Flywheel comprising starter ring gear - Google Patents
Flywheel comprising starter ring gear Download PDFInfo
- Publication number
- CN101970852B CN101970852B CN200980105735.8A CN200980105735A CN101970852B CN 101970852 B CN101970852 B CN 101970852B CN 200980105735 A CN200980105735 A CN 200980105735A CN 101970852 B CN101970852 B CN 101970852B
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- China
- Prior art keywords
- flywheel
- ring gear
- idle running
- output shaft
- running device
- Prior art date
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Images
Classifications
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- 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
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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
- 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
- F16D43/16—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 clutching members having interengaging parts
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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
- 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
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- 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
- F02N15/023—Gearing between starting-engines and started engines; Engagement or disengagement thereof the starter comprising an intermediate clutch of the overrunning type
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- 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
-
- 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
- F02N15/026—Gearing between starting-engines and started engines; Engagement or disengagement thereof the starter comprising an intermediate clutch of the centrifugal type
Abstract
The invention relates to a flywheel on an output shaft of an internal combustion engine, said output shaft being driven by a starter in order to start the internal combustion engine. According to the invention, the starter ring gear that is driven by the starter is located axially between the housing of the internal combustion engine and the flywheel. The starter ring gear is only driven whilst torque is transmitted from the starter to the starter ring gear.
Description
Technical field
The present invention relates to a kind of flywheel, this flywheel is received on the output shaft of internal-combustion engine and has flywheel ring gear, and this flywheel ring gear is for starting this internal-combustion engine by means of Starter.
Background technique
This flywheel is known by prior art.Flywheel ring gear is fixed on this flywheel without relative rotation, and the small gear of Starter coordinates with this flywheel ring gear and output shaft drives by flywheel.Especially in mixing application and start/stop system, the frequent joint of Starter is uncomfortable.
Summary of the invention
Therefore, task of the present invention is, a kind of flywheel with flywheel ring gear is provided, and in this flywheel, can cosily realize the frequent starting process of internal-combustion engine.
This task solves by a kind of flywheel, this flywheel is received on the output shaft of internal-combustion engine regularly, this flywheel has flywheel ring gear, this flywheel ring gear is used for by means of Starter starting apparatus combustion engine, wherein, flywheel ring gear is bearing in the axial direction between the housing of internal-combustion engine and flywheel and according to the direction of the moment that is passed to output shaft by Starter by flywheel ring gear and is coupled with output shaft regularly on driving.Can make in this way internal combustion engine, and the small gear of Starter does not separate with flywheel ring gear, because Starter takes off coupling in the case of the rotating speed of Starter is exceeded by internal-combustion engine.For example also be interpreted as driving plate for flywheel, for example, for connecting torque-converters or being assemblied in the clutch of transmission side and the flexible disk of the elementary quality of double mass flywheel.
Flywheel ring gear advantageously can reverse and be bearing on housing, thus, due to this flywheel ring gear centering on housing, can follow with respect to the narrow gap of housing and can save thus structure space.At this, in the time that moment no longer passes to internal-combustion engine from Starter, flywheel ring gear can take off coupling with output shaft or flywheel and be connected.Flywheel ring gear also can reverse and be bearing on output shaft or flywheel in a similar manner, and thus, this flywheel ring gear is centrally received and can under the condition being proposed, be coupled with output shaft or flywheel by corresponding coupling mechanism.At this, in the time of starting apparatus combustion engine, flywheel ring gear is by flywheel and output shaft coupling, and this startup is by being undertaken by Starter driver output axle.
Can make Starter keep engaging with the tooth portion of flywheel ring gear constantly by means of its small gear by the flywheel ring gear of de-coupling in a beneficial way, can advantageously cancel thus the magnetic switch for engaging small gear.From the predetermined rotating speed of internal-combustion engine, make the de-coupling of Starter carry out together with the bearing of flywheel ring gear in a beneficial way, thus need to be because pivot friction additionally drops into energy with other frictional work.The rotating speed predetermined in order to throw off Starter for example can be in the scope of the idling speed of internal-combustion engine, and thus, in the time of this rotating speed, moment no longer passes to output shaft and flywheel ring gear and the de-coupling of output shaft in the time that idling speed is exceeded by internal-combustion engine from Starter.
Flywheel ring gear and output shaft or with the de-coupling of flywheel in a beneficial way by means of one side flywheel, output shaft or the member being fixedly connected with them and carry out by means of idle running device between flywheel ring gear on the other hand, thus, de-coupling directly after driving component, carry out and bearing device together with the receiving member between flywheel ring gear and the coilable bearing device on output shaft, flywheel or housing in the time that idling speed is exceeded or static in the time that idle running device is surmounted.Be proved advantageously at this, idle running device is arranged on large as far as possible diameter.This makes the confining force of idle running device less, thus, the part that forms idle running device can construct simply and can lower cost ground for example by forming by means of the working of plastics of pressure injection method manufacture.It is favourable that for example idle running device is positioned between flywheel ring gear and the bearing device of flywheel ring gear diametrically, is preferably directly positioned at the inner radial of flywheel ring gear to the acceptance division of its bearing device.Can be provided with some mechanisms at this, for example rivet, be welded to connect device, kayser or buckle connecting device, to idle running device is connected with flywheel.Fixing or the connection of idle running device on flywheel advantageously carried out in the inner radial of idle running device, thus, this idle running device can be placed in flywheel ring gear or this flywheel ring gear for reversing the inner radial that is bearing in the acceptance division on housing or output shaft in the situation that diameter is large as far as possible.
Flywheel ring gear can be carried by the dish of for example making with plate or load-bearing member at this, and this dish or load-bearing member receive and form in the inner radial of the bead for receiving flywheel ring gear a part for an idle running device on housing by means of bearing device.The inner face of for example radial flange can be formed for the setting face of the clamping body of clamping body idle running device.At this, the clamping body effect that is received on the load-carrying ring being connected with output shaft and can resist energy storage device that distributes on circumference arranges to restricted torsion diametrically, and this load-carrying ring regularly for example riveted joint ground is connected with the flywheel that can be made up of plate.At this, clamping body is pressed on setting face at the rotating speed hour of flywheel by energy storage device.In addition, clamping body has governor weight, and these governor weights cause lifting from the setting face of clamping body according to the rotating speed of flywheel by the torsion of clamping body.In this way, in the time that rotating speed is higher, for example, when rotating speed is during higher than idling speed, between setting face and clamping body, form gap, thus, flywheel ring gear together with load-bearing member and bearing device and if desired with the ingear Starter of flywheel ring gear almost without frictionally with the de-coupling of output shaft.
Can process preferably by load-bearing member or the load-carrying ring of the correspondingly configured reception clamping body of plate punching for the energy storage device that loads clamping body, its mode is for example to put on display corresponding camber member and differential hardening at least if desired from load-carrying ring.By being placed in major diameter, the load of clamping body can reduce, and thus, these clamping bodies for example can be made up of plastics by simple mode.
The configuration form as an alternative solution of idle running device can be wind spring idle running device.For this reason, the axial setting face of wind spring and the setting face of inner radial that the load-bearing member being connected with flywheel of idle running device can have for receive wind spring idle running device at radially outer are made up of the axial bead of the dish for supporting flywheel ring gear, and this dish receives flywheel ring gear at radially outer.The axial bead by dish compresses and is only connected with the axial bead of the load-bearing member of flywheel in the axial direction in the axial direction and without relative rotation and with another end on an end at this to be arranged on diametrically wind spring between these setting faces.In the time that flywheel ring gear is activated machine driving during start-up course, due to the friction of Ai Teerwan rope, wind spring tension and to form the friction of self intensification sealed with the axial bead of dish, the straight maintenance of this friction lock unification, until output shaft exceedes flywheel ring gear and occurs radial clearance with respect to axial bead, thus, as described before, the low frictionally de-coupling of flywheel ring gear and part below.
Particularly advantageously, for fear of by means of large diameter rolling bearing supporting flywheel ring gear, point type bearing device can be set on housing.For this reason can be on housing distribute on circumference ground and three or more is centrally set axially from the outstanding pin of housing with respect to the rotation axis of output shaft, these pins can reverse respectively the dish receiving for receiving flywheel ring gear.For this reason, on pin, also can arrange little, thus lower cost and drop into technically not too high rolling bearing, dish rolls on these rolling bearings.Self-evident, dish insures in the axial direction and rolls on pin.
Accompanying drawing explanation
Describe the present invention in detail by means of Fig. 1 to Figure 16.Accompanying drawing represents:
Fig. 1 has the embodiment by means of the flywheel of the flywheel ring gear of the de-coupling of idle running device,
The flywheel ring gear that Fig. 2 supports by means of dish,
Fig. 3 has the embodiment's of the flywheel of clamping body idle running device cut-away section,
The details of Fig. 4 clamping body idle running device,
Fig. 5 receives the load-carrying ring of clamping body,
The clamping body of Fig. 6 in installment state,
The description of the working method of Fig. 7 and Fig. 8 clamping body,
View and the details of Fig. 9 and Fig. 9 a load-carrying ring,
The section of Figure 10 clamping body idle running device,
The section of Figure 11 load-carrying ring fixing details on load-bearing member,
Figure 12 has the embodiment's of the flywheel of wind spring idle running device cut-away section,
The details of Figure 13 Figure 12,
The description of the working method of the wind spring idle running device of Figure 14 Figure 12 and Figure 13,
Figure 15 and Figure 16 flywheel ring gear be the cut-away section on internal-combustion engine housing and partial view at acceptance point upper support.
Embodiment
Fig. 1 shows the embodiment of flywheel 1, and this flywheel is driven by the output shaft 2 of the internal-combustion engine not being shown specifically.Flywheel 1 is made up of plate 3 in the example shown, and this plate also can form by pressed article or by the material forging in other configuration example.Flywheel 1 for example can receive being connected of clutch, foundation and fluid torque converter or the primary side input component as double mass flywheel.In addition, the clutch assembly being assemblied on the transmission input shaft of speed changer below can be connected with flywheel 11.This clutch assembly can be for example the double clutch of dual-clutch transmission.Flywheel 1 is driven by output shaft 2.For this reason, flywheel 1 and output shaft 2 are for example fixedly connected with as screw by means of the bindiny mechanism not being shown specifically.
Internal-combustion engine is from the state of rest of this internal-combustion engine by means of unshowned Starter, and this Starter has small gear, and this small gear engages with the tooth portion of flywheel ring gear 4.For this reason, small gear can coordinate in continuing with flywheel ring gear.Flywheel ring gear 4 at this by means of rolling bearing 5 centrally and can reverse on the housing 6 that is received in internal-combustion engine.For this reason, housing 6 can have axial bead 7, and rolling bearing 5 is received in this axial bead.In order to limit the diameter of rolling bearing 5, advantageously, axially bead 7 is equipped with as far as possible little radius.In addition, axially bead 7 has backstop seamed edge and guard ring, thus, and rolling bearing 5 axial restraints.Between flywheel ring gear 4 and rolling bearing 5, be provided with dish 8 diametrically, this dish has axial bead 9 for receiving flywheel ring gear 4 and for making dish 8 be received in the axial bead 10 on rolling bearing 5.In addition, dish 8 for example fixes by means of guard ring in the axial direction by means of its axial bead 10 on rolling bearing 5.
Idle running device 11 works between flywheel ring gear 4 or dish 8 and plate 3, and this idle running device is taken member 3 and surmounted in the time that the rotating speed of the internal-combustion engine having started exceedes in the time that Starter is worked.Idle running device 11 for example can be configured to change according to centrifugal force, thus, after predetermined rotating speed exceedes, centrifugal action comes into force and idle running device 11 is thrown off, thus, moment no longer transmit by flywheel ring gear 4 and this flywheel ring gear together with load-bearing member 8 and the de-coupling of rolling bearing 5.Idle running device 11 is supported on the protuberance 12 of plate 3 diametrically at this, and wherein, protuberance 12 can be used as circular groove or forms by means of multiple section or belling portions that are distributed on circumference.Meanwhile, between idle running device 11 and plate 3, on this position, the angular misalignment between flywheel ring gear 4 and the flywheel 1 of internal-combustion engine and coupling has obtained compensation.
Fig. 2 shows the details of the structure of the dish 8 of Fig. 1.Dish 8 can be manufactured and be reached suitable shape by means of corresponding punching and plate mould-forming method by plate.Be configured to annular dish 8 and have two beads 9,10, flywheel ring gear 4 is arranged in these beads in inner radial at radially outer and rolling bearing 5.Be proved particularly advantageously, rolling bearing 5 and flywheel ring gear 4 are arranged on identical axial height.Favourablely in the meaning in space of optimizing structure can be also that, in the no small situation in surface of the wall of housing, rolling bearing 5 and flywheel ring gear 4 do not line up.
Fig. 3 shows the cross section view of the structure of the flywheel 1 with flywheel ring gear 4, and wherein, the lower part of spin axis 13 belows is omitted.In addition, idle running device 11 is at length expressed as clamping body idle running device 14.This clamping body idle running device consists of clamping body 15, and these clamping bodies are by means of being arranged on without relative rotation that load-bearing member 16 on plate 3 is connected with flywheel 1 and inner face 17 frictional fit of the axial bead 9 that is provided with flywheel ring gear 4 of visual transition state and fixed and dish 8.
Fig. 4 shows the details of clamping body idle running device 14.Clamping body 15 distributes to reverse and is for example arranged on load-bearing member 16 by means of rivet 18 on circumference.By the restricted torsion of clamping body 15, these clamping bodies form rubbing contact according to reversing with its fitting surface 19 with inner face 17, and wherein, rubbing contact additionally regulates by being separately positioned on an energy storage device 20 on clamping body 15.In this way, in the time that internal-combustion engine is static or during the internal combustion engine start being driven by Starter, between clamping body 15 and inner face 17, form rubbing contact, thus, the torsion of being undertaken by Starter of flywheel ring gear 4 causes flywheel 1, the thus driving to output shaft 2 and internal-combustion engine is started in this way.Clamping body 15 has respectively about its run-on point 21 and fitting surface 19 or the opposed governor weight 22 of acting surface that loaded by energy storage device 20, thus, in the time that flywheel 1 accelerates to the rotating speed being conditioned, clamping body 15 reverses like this due to centrifugal action, and fitting surface 19 is lifted forming gap from inner face 17.For make clamping body 15 due to centrifugal force restricted displacement, in load-bearing member 16, be provided with backstop 23.This backstop for example can be put on display from load-bearing member 16.By clamping body, at the configuration aspect its fitting surface 19 and governor weight 22, the conversion of idle running device can be coordinated mutually with the predetermined conditioned disjunction idling speed of internal-combustion engine.
Fig. 5 shows the details of the load-bearing member 16 of Fig. 3 and Fig. 4.Load-bearing member is configured to two-piece type in the embodiment shown, comprises real load-bearing member 16 and load-carrying ring 24, and this load-carrying ring can be made and be had energy storage device 18 and backstop 23 by thinner material.Load-carrying ring 24 is received on load-bearing member 16 by means of rivet 18, and these rivets also can reverse and receive clamping body 15.
Fig. 6 at length shows load-bearing member 16 and load-carrying ring 24, the backstop 23 that this load-carrying ring has energy storage device 20 and puts on display.Energy storage device 20 is configured at this camber member 25 going out from load-carrying ring 24 punching in a circumferential direction, and for spring force is radially provided, these camber members are crimped and form.Camber member 25 on its end with the nose 26 of clamping body 15 in coordinating and these clamping bodies being pressed on the unshowned inner face of flywheel ring gear 4 (Fig. 3), thus, on fitting surface 19, form the rubbing contact with this fitting surface.Due to clamping body 15, in the side that deviates from nose 26 of clamping body 15, by governor weight 22 is set, quality is larger, in the time that load-bearing member 16 accelerates or reverses, the effect of clamping body 15 antagonistic spring storages 20 is reversed until backstop 23 around the run-on point 21 of rivet 18, thus, the rubbing contact between fitting surface 19 and the inner face 17 (Fig. 4) of flywheel ring gear 4 (Fig. 4) is cancelled.
Fig. 7 and Fig. 8 have explained the working method of the clamping body idle running device 14 being shown specifically.For this reason, Fig. 7 shows the state that the frictional fit between the fitting surface 19 of clamping body 15 and the inner face 17 of the axial bead 9 of dish 8 forms.Due to the spring force F (E) of energy storage device 20, clamping body is rotated towards the direction of inner face 17 around run-on point 21.Because the central point 27 of the radius of fitting surface is in run-on point 21 outsides, when during start-up course, dish 9 reverses, work to self intensification.As shown in Figure 8, if the part of rotation is the rotating speed increase of dish 9 and load-bearing member 16 together, governor weight 22 due to centrifugal force F (F) increase stand radially outer acceleration and when spring force F (E) is exceeded clamping body 15 start torsion, thus, the rubbing contact on inner face 17 is cancelled and clamping body only rests in backstop 23.
In order to get across, Fig. 9 shows the load-carrying ring 24 as single, Fig. 9 a shows another detailed view in load-carrying ring 24 inside, has backstop 23, camber member 25 and for through for making load-carrying ring be fixed on the hole 28 (Fig. 3) of the rivet on load-bearing member 16.
Figure 10 shows the detailed assembling of clamping body idle running device 14 with cross section view, the axial bead 9 of inner face that has dish 8 and receive flywheel ring gear 4 and be formed for the rubbing contact of clamping body idle running device 14 is as the part of input side, and the part of these input sides passes torque to flywheel 1.The plate 3 of flywheel 1 and load-bearing member 16 form the part of outlet side, and the moment of being transmitted the idle running means for engaging in the situation that by Starter is passed to unshowned output shaft by the part of this outlet side.For this reason, plate 3 is fixedly connected with load-bearing member 16, for example riveted joint or engage with tooth.Load-bearing member is riveted by means of rivet 18 with load-carrying ring 24 again and also can restrictedly be reversed and receive clamping body 15 at this.At this, in jointing state, between the fitting surface 19 being arranged on clamping body 15, form rubbing contact, this rubbing contact after internal combustion engine start because centrifugal action is cancelled.
Figure 11 shows the details of the configuration that load-bearing member 16, load-carrying ring 24 and clamping body 15 rivet by means of rivet 18.In order to receive regularly load-bearing member 16, rivet 18 is configured to stair-stepping special-shape rivet, and thus, during riveting, clamping body 15 and load-carrying ring 24 do not clamp with load-bearing member.For this reason, be provided with backstop 29, load-bearing member 16 rests in this backstop in the time compressing, and clamping body 15 and load-carrying ring 24 are compacted with the axial distance regulating regularly on larger diameter, and this axial distance allows clamping body 15 with respect to load-carrying ring relative torsion.
Figure 12 shows the idle running device 11 of Fig. 1 as the details of the replacement configuration of wind spring idle running device 114.Except the configuration of idle running device, this structure can be compared with the clamping body idle running device 14 of Fig. 3 and Figure 10.Also can be configured to sliding bearing for the rolling bearing 5 that dish 108 is received on the housing 6 of internal-combustion engine at other configuration example.Dish 108 radially outer receive flywheel ring gear 4 and different from the dish 8 of Fig. 2 diametrically between flywheel ring gear 4 and rolling bearing 5 inside forming section 130 or the indentation portion by means of axial ring-type form an axial bead 131 radially staggering with axial bead 9, this axial bead has the fitting surface 132 of radially outer, and wind spring 133 is arranged on this fitting surface.Corresponding therewith, the load-bearing member 116 being arranged on the plate 3 of flywheel 1 overlaps diametrically axial bead 131 and forms an axial bead 134, this axial bead has the inner face 135 parallel with respect to fitting surface 132, and wherein, wind spring 133 is arranged between two beads 131,134 diametrically.Wind spring 133 this in the state not rotating on an end in the axial direction and in a circumferential direction regularly and in being only suspended at regularly bead 134 in the axial direction with another end and with respect to bead 131 pre-pressings on fitting surface 132.If the torsion of carrying out by means of Starter by dish carrys out starting apparatus combustion engine, wind spring 133 is strained and is rubbed sealed with wind spring 133 formation that are suspended in load-bearing member 116 on fitting surface.When speed discrepancy is pulled and changes to output shaft and drive when flywheel from output shaft, sealed cancel and wind spring is shifted in the situation that forming radial clearance with respect to fitting surface 132 of rubbing.Thus, dish 108, flywheel ring gear 4 and with the de-coupling of Starter of this flywheel ring gear coupling.
Figure 13 forms the details that shows wind spring idle running device 114 radial clearance 136 in the time that rotating speed is high in the time of the frictional fit without wind spring 133 between the axial bead 131 of dish 108 and wind spring 133, this wind spring is resisted the pre-pressing of this wind spring by centrifugal force in the time that rotating speed is high and on the axial bead 134 of load-bearing member 116, in this axial bead, this wind spring suspends in the hole 138 of axial bead 134 by means of free end 137 and be only fixing in the axial direction with another free end.In this view, rub sealed by form radial clearance 136 flywheel 1 of cancelling and for example rotating rapidly and the de-coupling of dish 108 for example stopping more than idling speed.If rotating speed reduces again, the pre-pressing force of wind spring 133 exceedes centrifugal force and radial clearance 136 closures, and this sets up the rubbing contact between wind spring 133 and the fitting surface 132 of axial bead 131, and this rubbing contact allows the internal-combustion engine stopping to start again.
The formation of the rubbing contact of self intensification is described by means of Figure 14.Produce frictional force by wind spring 133 pre-pressing in axial bead 131, in the time of internal combustion engine start, in the time that this axial bead is reversed by Starter, this frictional force is taken wind spring 133.By the bending of bead 131 and wind spring, wind spring 133 is nipped because Ai Teerwan rope rubs also self intensification.Because free end 137 is received in the hole 138 of axial bead 134 of the load-bearing member 116 being connected with flywheel regularly, power passes to live axle from Starter, until rubbing contact is by the centrifugal forces affect and the disengagement that improve during higher than idling speed at rotating speed.
Figure 15 shows the bearing device of the alternative of the flywheel 1 as Fig. 1 of flywheel ring gear 4.Replace a unique rolling bearing 5 (Fig. 1), three or more is preferably set on the housing 206 of internal-combustion engine and is distributed in the acceptance division 239 on circumference, the forming section 239 being arranged in housing 206 can arrange and for example in the time manufacturing housing by means of pressure injection method, pour into a mould in the time manufacturing housing 206.As an alternative solution, correspondingly can machining shaft to outstanding pin.Dish 208 can reverse and be received on these outside forming sections 239.At this, around the forming section 239 centrally arranging with respect to spin axis 13, a rolling bearing 240 can be set respectively, dish 208 rolls on described rolling bearing.The radial location of forming section 239 can be carried out under major diameter because from use a concentric rolling bearing different, this configuration is technically and aspect the cost for rolling bearing, drop into not high.Therefore can in the comparable radial position of idle running device 11, arrange bearing device.In this way, the node configuration of dish 208 is simplified, and in addition, materials'use can reduce, especially when dish 208 is by bar manufacture, roll extrusion with while sealing on end.
Figure 16 shows the view of the detailed expression of the structure of Figure 15, have idle running device 11, the dish 208 only schematically showing and be distributed in the bearing 240 on circumference, these bearings are received on housing 206 by means of forming section 239 and are formed for the bearing device of dish 208.Be advantageously provided an element of construction 241 in order to assemble, this element of construction comprises the complete flywheel 1 of the bearing device with idle running device 11 and flywheel ring gear 4.For this reason, idle running device 11 is received on the plate 3 of flywheel 1 anti-loosely.In addition, the anti-loose ground of idle running device 11 and dish 208 receives mutually.The common mode of flywheel ring gear 4 use is fixed for example welding, ca(u)lk or pyrocondensation on dish 208.Rolling bearing 240 is arranged on dish 208 anti-loosely, and thus, this element of construction only must be sleeved on forming section 239 in the time of final assembling and flywheel 1 is connected with output shaft.The axial relief of dish 208 on forming section 239 by by flywheel 1 axial restraint be threaded on live axle 2 and produce.
Reference number inventory
1 flywheel
2 output shafts
3 plates
4 flywheel ring gears
5 rolling bearings
6 housings
7 axial beads
8 dish
9 axial beads
10 axial beads
11 idle running devices
12 protuberances
13 spin axiss
14 clamping body idle running devices
15 clamping bodies
16 load-bearing members
17 inner faces
18 rivets
19 fitting surfaces
20 energy storage devices
21 run-on points
22 governor weights
23 backstops
24 load-carrying rings
25 camber members
26 noses
27 central points
28 holes
29 backstops
108 dish
114 wind spring idle running devices
116 load-bearing members
130 inside forming sections
131 axial beads
132 fitting surfaces
133 wind springs
134 axial beads
135 inner faces
136 radial clearances
137 free ends
138 holes
206 housings
208 dish
239 forming sections
240 rolling bearings
241 element of construction
F (E) spring force
F (F) centrifugal force
Claims (16)
1. flywheel (1), this flywheel is received on the output shaft (2) of internal-combustion engine regularly, this flywheel has flywheel ring gear (4), this flywheel ring gear is for starting this internal-combustion engine by means of Starter, wherein, this flywheel ring gear (4) is bearing in the housing (6 of this internal-combustion engine in the axial direction, 206) and between this flywheel (1) and according to the direction of the moment that is passed to this output shaft (2) by this Starter by this flywheel ring gear (4) on driving, be coupled with this output shaft (2) regularly, this flywheel ring gear (4) can reverse and be bearing in this housing (6, 206) on, it is characterized in that: this flywheel ring gear (4) is by dish (8, 108, 208) carrying, this dish is at this housing (6, 206) upper by means of bearing device carrying and in the axial bead (9 for receiving this flywheel ring gear (4), 131) inner radial forms a part for an idle running device.
2. according to the flywheel of claim 1 (1), it is characterized in that: this flywheel ring gear (4) is by this flywheel (1) and this output shaft (2) coupling.
3. according to the flywheel (1) of claim 1 or 2, it is characterized in that: the tooth portion of this Starter constantly with this flywheel ring gear (4) in engaging.
4. according to the flywheel (1) of claim 1 or 2, it is characterized in that: until the rotating speed of this internal-combustion engine reaches idling speed, can give this output shaft (2) carry-over moment from this Starter; After the rotating speed of this internal-combustion engine exceedes this idling speed, this flywheel ring gear (4) and the de-coupling of this output shaft (2).
5. according to the flywheel (1) of claim 1 or 2, it is characterized in that: this flywheel ring gear (4) can be by means of the de-coupling of idle running device (11) and this output shaft (2).
6. according to the flywheel of claim 5 (1), it is characterized in that: this idle running device (11) is arranged between flywheel ring gear (4) and the bearing device of this flywheel ring gear (4) diametrically.
7. according to the flywheel of claim 5 (1), it is characterized in that: this idle running device (11) is arranged on this flywheel ring gear (4) and diametrically for making between the mechanism of this idle running device (11) and this flywheel (1) coupling.
8. according to the flywheel (1) of claim 1 or 2, it is characterized in that: the inner face (17) of this axial bead (9) is formed for the setting face of the clamping body (15) of clamping body idle running device (14).
9. flywheel (1) according to Claim 8, is characterized in that: the quantity of described clamping body (15) is multiple and is arranged in the mode distributing effect restricted the torsions ground setting diametrically that the load-bearing member (16) being connected with this output shaft (2) is upper and can resist energy storage device (20) on circumference.
10. according to the flywheel of claim 9 (1), it is characterized in that: the quantity of described energy storage device is multiple, these clamping bodies (15) are pressed on this inner face (17) above and are had governor weight (22) by these energy storage devices (20), and the quantity of described governor weight is multiple and these governor weights cause lifting from this inner face (17) according to the rotating speed of this flywheel (1) by the torsion of these clamping bodies (15).
11. according to the flywheel (1) of claim 9 or 10, it is characterized in that: described energy storage device (20) is formed by the member that receives these clamping bodies (15).
12. according to the flywheel (1) of claim 9 or 10, it is characterized in that: these clamping bodies (15) are made up of plastics.
13. according to the flywheel (1) of claim 1 or 2, it is characterized in that: this idle running device (11) is wind spring idle running device (114).
14. according to the flywheel of claim 13 (1), it is characterized in that: this dish (108) has the axial setting face (131) of the wind spring (133) for receive this wind spring idle running device (114) in inner radial.
15. according to the flywheel of claim 13 (1), it is characterized in that: the setting face for the radially outer of this wind spring (133) forms by the load-bearing member (116) being connected with this output shaft (2).
16. according to the flywheel (1) of claim 1 or 2, it is characterized in that: this flywheel ring gear (4) can be reversed to be received at least three forming sections (239) that are distributed on housing on circumference, that be arranged on this internal-combustion engine (206).
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102008010257 | 2008-02-20 | ||
| DE102008010257.1 | 2008-02-20 | ||
| DE102008016440.2 | 2008-03-31 | ||
| DE102008016440 | 2008-03-31 | ||
| PCT/DE2009/000197 WO2009103267A2 (en) | 2008-02-20 | 2009-02-12 | Flywheel comprising a starter ring gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101970852A CN101970852A (en) | 2011-02-09 |
| CN101970852B true CN101970852B (en) | 2014-05-14 |
Family
ID=40671368
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200980105735.8A Expired - Fee Related CN101970852B (en) | 2008-02-20 | 2009-02-12 | Flywheel comprising starter ring gear |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP5473947B2 (en) |
| CN (1) | CN101970852B (en) |
| DE (2) | DE102009008599A1 (en) |
| WO (1) | WO2009103267A2 (en) |
Families Citing this family (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010130058A1 (en) | 2009-05-15 | 2010-11-18 | Litens Automotive Partnership | Engine starter |
| WO2011023157A1 (en) * | 2009-08-28 | 2011-03-03 | Schaeffler Technologies Gmbh & Co. Kg | Flywheel comprising a starter ring gear |
| DE102010033503B4 (en) * | 2009-08-28 | 2020-02-13 | Schaeffler Technologies AG & Co. KG | Starter with dry freewheel |
| WO2011038707A2 (en) * | 2009-09-29 | 2011-04-07 | Schaeffler Technologies Gmbh & Co. Kg | Freewheel, in particular for permanently meshed starters |
| DE102010054287B4 (en) | 2009-12-17 | 2020-08-06 | Schaeffler Technologies AG & Co. KG | Flywheel for permanent starter |
| DE102010012514B4 (en) * | 2010-03-24 | 2016-08-25 | Audi Ag | Device for starting an internal combustion engine |
| DE102011014095A1 (en) * | 2010-03-29 | 2011-12-15 | Schaeffler Technologies Gmbh & Co. Kg | Freewheel system |
| DE102011101500A1 (en) | 2010-05-25 | 2011-12-15 | Schaeffler Technologies Gmbh & Co. Kg | Dual-mass flywheel for torsional vibration attenuation in crankshaft of internal combustion engine of motor car, has secondary pane designed such that frictional engagement of bolting spring with primary pane is voidable |
| DE112011102513A5 (en) | 2010-07-26 | 2013-05-29 | Schaeffler Technologies AG & Co. KG | freewheel |
| DE102010032318A1 (en) * | 2010-07-27 | 2012-02-02 | Gm Global Technology Operations Llc (N.D.Ges.D. Staates Delaware) | Auxiliary unit for combustion engine of motor system, has control unit controlling combustion engine during turning off combustion engine, and auxiliary motor setting combustion engine into movement in predetermined phase |
| DE102011013233A1 (en) | 2011-03-07 | 2012-09-13 | Schaeffler Technologies Gmbh & Co. Kg | Freewheel for permanently engaged starter of motor vehicle, has compression spring for providing radially outwardly directed compressive force on clamping portion against outer ring, which is provided in radially outward closed groove |
| DE102012205270A1 (en) | 2011-04-20 | 2012-10-25 | Schaeffler Technologies AG & Co. KG | Freewheel for a permanently interlocked starter of a motor vehicle |
| JP6086919B2 (en) * | 2011-10-19 | 2017-03-01 | シェフラー テクノロジーズ アー・ゲー ウント コー． カー・ゲーＳｃｈａｅｆｆｌｅｒ Ｔｅｃｈｎｏｌｏｇｉｅｓ ＡＧ ＆ Ｃｏ． ＫＧ | Vehicle starter |
| ITBO20120363A1 (en) * | 2012-07-03 | 2014-01-04 | Ferrari Spa | AUTOMATIC MANUAL TRANSMISSION FOR A HYBRID CAR PROVIDED WITH AN INTERNAL COMBUSTION ENGINE AND AN ELECTRIC MACHINE |
| DE102015207321A1 (en) | 2014-04-24 | 2015-10-29 | Schaeffler Technologies AG & Co. KG | flywheel |
| DE102014216803A1 (en) | 2014-08-25 | 2016-02-25 | Schaeffler Technologies AG & Co. KG | Flywheel and method of making a flywheel |
| DE102015220599A1 (en) | 2014-12-18 | 2016-06-23 | Schaeffler Technologies AG & Co. KG | Permanently meshed starter with a freewheel |
| DE102016202138A1 (en) | 2016-02-12 | 2017-08-17 | Bayerische Motoren Werke Aktiengesellschaft | Method for starting an internal combustion engine and drive train for a motor vehicle |
| DE102020116098B3 (en) * | 2020-06-18 | 2021-07-01 | Schaeffler Technologies AG & Co. KG | Starter device with a compensating device |
| DE102020116099A1 (en) | 2020-06-18 | 2021-12-23 | Schaeffler Technologies AG & Co. KG | Starter device with a radial offset compensation device |
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| CN1264000A (en) * | 1999-01-13 | 2000-08-23 | 易通公司 | Automatic regulating friction lutch with overregulate protection |
| DE10019593A1 (en) * | 2000-04-20 | 2001-10-25 | Bayerische Motoren Werke Ag | Starter's overrunning clutch has outer ring coupled to starter shaft and inner ring coupled to crankshaft, and in overrun phase clamping components are deflected by centrifugal force action so that they are separated from outer ring |
| WO2007012943A1 (en) * | 2005-07-29 | 2007-02-01 | Toyota Jidosha Kabushiki Kaisha | Startup torque transmitting mechanism of an internal combustion engine |
| WO2007012946A1 (en) * | 2005-07-29 | 2007-02-01 | Toyota Jidosha Kabushiki Kaisha | Startup torque transmitting mechanism of an internal combustion engine |
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| DE3241245A1 (en) * | 1982-11-09 | 1984-05-10 | Stieber Division Der Borg-Warner Gmbh, 6900 Heidelberg | Sprag |
| JP2534150Y2 (en) * | 1990-05-22 | 1997-04-30 | 日本精工株式会社 | One-way clutch |
| JPH1037984A (en) * | 1996-07-19 | 1998-02-13 | Paatonaa Sangyo Kk | Innerless one-way clutch, and simplified clutch attaching and detaching and their combination |
| DE19847769A1 (en) * | 1998-10-16 | 2000-04-20 | Mannesmann Sachs Ag | Wrap spring clutch has first and second components, rotary coupling of wrap spring coupling part and counter coupling part |
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| JP2008106834A (en) * | 2006-10-25 | 2008-05-08 | Jtekt Corp | One-way clutch, sprag for one-way clutch, and method of manufacturing the sprag |
| JP2008121737A (en) * | 2006-11-09 | 2008-05-29 | Ntn Corp | One-way clutch |
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2009
- 2009-02-12 DE DE102009008599A patent/DE102009008599A1/en not_active Withdrawn
- 2009-02-12 DE DE112009000236.6T patent/DE112009000236B4/en not_active Expired - Fee Related
- 2009-02-12 JP JP2010547039A patent/JP5473947B2/en not_active Expired - Fee Related
- 2009-02-12 WO PCT/DE2009/000197 patent/WO2009103267A2/en active Application Filing
- 2009-02-12 CN CN200980105735.8A patent/CN101970852B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1264000A (en) * | 1999-01-13 | 2000-08-23 | 易通公司 | Automatic regulating friction lutch with overregulate protection |
| DE10019593A1 (en) * | 2000-04-20 | 2001-10-25 | Bayerische Motoren Werke Ag | Starter's overrunning clutch has outer ring coupled to starter shaft and inner ring coupled to crankshaft, and in overrun phase clamping components are deflected by centrifugal force action so that they are separated from outer ring |
| WO2007012943A1 (en) * | 2005-07-29 | 2007-02-01 | Toyota Jidosha Kabushiki Kaisha | Startup torque transmitting mechanism of an internal combustion engine |
| WO2007012946A1 (en) * | 2005-07-29 | 2007-02-01 | Toyota Jidosha Kabushiki Kaisha | Startup torque transmitting mechanism of an internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2011514487A (en) | 2011-05-06 |
| DE112009000236B4 (en) | 2020-11-26 |
| WO2009103267A2 (en) | 2009-08-27 |
| CN101970852A (en) | 2011-02-09 |
| DE102009008599A1 (en) | 2009-08-27 |
| WO2009103267A3 (en) | 2009-12-30 |
| DE112009000236A5 (en) | 2010-10-28 |
| JP5473947B2 (en) | 2014-04-16 |
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