CN101970852A - Flywheel comprising a starter ring gear - Google Patents
Flywheel comprising a starter ring gear Download PDFInfo
- Publication number
- CN101970852A CN101970852A CN2009801057358A CN200980105735A CN101970852A CN 101970852 A CN101970852 A CN 101970852A CN 2009801057358 A CN2009801057358 A CN 2009801057358A CN 200980105735 A CN200980105735 A CN 200980105735A CN 101970852 A CN101970852 A CN 101970852A
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- CN
- China
- Prior art keywords
- flywheel
- ring gear
- idle running
- output shaft
- running device
- Prior art date
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- 239000007858 starting material Substances 0.000 title claims abstract description 36
- 238000002485 combustion reaction Methods 0.000 claims abstract description 39
- 239000011324 bead Substances 0.000 claims description 43
- 230000008878 coupling Effects 0.000 claims description 21
- 238000010168 coupling process Methods 0.000 claims description 21
- 238000005859 coupling reaction Methods 0.000 claims description 21
- 238000004146 energy storage Methods 0.000 claims description 13
- 230000007246 mechanism Effects 0.000 claims description 4
- 230000000694 effects Effects 0.000 claims description 3
- 229920003023 plastic Polymers 0.000 claims description 3
- 239000004033 plastic Substances 0.000 claims description 3
- 238000005096 rolling process Methods 0.000 description 24
- 238000000034 method Methods 0.000 description 8
- 230000005540 biological transmission Effects 0.000 description 4
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- 230000001133 acceleration Effects 0.000 description 1
- 230000003042 antagnostic effect Effects 0.000 description 1
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- 238000006243 chemical reaction Methods 0.000 description 1
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- 239000012530 fluid Substances 0.000 description 1
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- 238000002156 mixing Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
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- 230000000007 visual effect Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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
-
- 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
-
- 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
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
- Mechanical Operated Clutches (AREA)
- Gear Transmission (AREA)
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 used for starting this internal-combustion engine by means of Starter.
Background technique
This flywheel is known by prior art.Flywheel ring gear does not have and is fixed on this flywheel with relatively rotating, and the small gear of Starter cooperates with this flywheel ring gear and output shaft drives by flywheel.Especially in mixing application and startup/halt 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 the Starter starting apparatus combustion engine, wherein, flywheel ring gear is bearing in the axial direction between the housing of internal-combustion engine and the flywheel and is coupled with output shaft regularly on driving according to the direction of the moment that is passed to output shaft by Starter by flywheel ring gear.Can make internal combustion engine in this way, and the small gear of Starter does not separate with flywheel ring gear, because Starter takes off coupling under the situation that the rotating speed of Starter is surpassed by internal-combustion engine.For example also be interpreted as driving plate for flywheel, for example be used to connect torque-converters or be assemblied in the clutch of transmission side and the flexible disk of the elementary quality of double mass flywheel.
Flywheel ring gear advantageously can be bearing on the housing with reversing, thus, because this flywheel ring gear centering on housing, can follow with respect to the narrow gap of housing and can save structure space thus.At this, when moment no longer when Starter passes to internal-combustion engine, flywheel ring gear can take off coupling ground with output shaft or flywheel and be connected.Flywheel ring gear also can be bearing on output shaft or the flywheel in a similar manner with reversing, and thus, this flywheel ring gear is centrally received and can be coupled with output shaft or flywheel under the condition that is proposed by corresponding coupling mechanism.At this, when starting apparatus combustion engine, flywheel ring gear is by flywheel and output shaft coupling, and this startup is undertaken by driving output shaft by Starter.
Available favourable mode makes Starter keep engaging with the tooth portion of flywheel ring gear constantly by means of its small gear by the flywheel ring gear that takes off coupling, can advantageously cancel the magnetic switch that is used to engage small gear thus.Make Starter take off coupling from the predetermined rotating speed of internal-combustion engine and carry out, do not need thus because pivot friction and other frictional work and additionally drop into energy with the bearing of favourable mode together with flywheel ring gear.Predetermined rotating speed for example can be in the scope of idling speed of internal-combustion engine in order to throw off Starter, thus, when this rotating speed, moment no longer from Starter pass to output shaft and when idling speed is surpassed by internal-combustion engine flywheel ring gear and output shaft take off coupling.
Flywheel ring gear and output shaft or with flywheel take off coupling with favourable mode by means of one side flywheel, output shaft or the member of fixedlying connected and carry out by means of the idle running device between the flywheel ring gear on the other hand with them, thus, take off that coupling directly carries out in the driving component back and bearing device together with being in flywheel ring gear and the receiving member between the coilable bearing device on output shaft, flywheel or the housing when idling speed is exceeded or static when the idle running device is surmounted.Be proved advantageously at this, the idle running device is arranged on the big as far as possible diameter.This makes that the confining force of idle running device is less, and thus, but the part of formation idle running device can be constructed simply and lower cost ground for example is made of the working of plastics by means of the manufacturing of pressure injection method.For example the idle running device is positioned between the bearing device of flywheel ring gear and flywheel ring gear to be favourable, preferably directly to be positioned at the inner radial of flywheel ring gear to the acceptance division of its bearing device diametrically.Can be provided with some mechanisms at this, for example rivet, be welded to connect device, kayser or buckle connection set, so that the 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 the inner radial that flywheel ring gear or this flywheel ring gear are being used for being bearing in the acceptance division on housing or the output shaft with reversing under the big as far as possible situation of diameter.
Flywheel ring gear can be by dish of for example making with plate or load-bearing member carrying at this, and this dish or load-bearing member receive and form in the inner radial of the bead that is used to receive flywheel ring gear the part of an idle running device by means of bearing device on housing.For example the inner face of radial flange can be formed for clamping body idle running device clamping body by putting face.At this, clamping body be received in with distributing on the circumference with load-carrying ring that output shaft is connected on and the restricted diametrically setting of effect that can resist energy storage device with reversing, this load-carrying ring for example rivet regularly and can be connected by the flywheel that plate constitutes.At this, clamping body hour is pressed on by putting on the face at the rotating speed of flywheel by energy storage device.In addition, clamping body has governor weight, these governor weights according to the rotating speed of flywheel by reversing of clamping body cause from clamping body by putting lifting of face.In this way, when rotating speed is higher, for example when rotating speed is higher than idling speed, forming the gap by putting between face and the clamping body, thus, flywheel ring gear is together with load-bearing member and bearing device and almost do not have frictionally with the ingear Starter of flywheel ring gear in case of necessity and take off coupling with output shaft.
The energy storage device that is used for loading clamping body can be processed preferably by the load-bearing member or the load-carrying ring of the correspondingly configured reception clamping body of plate punching out, and its mode for example is to put on display corresponding camber member and differential hardening at least in case of necessity from load-carrying ring.By being placed on the major diameter, the load of clamping body can reduce, and thus, for example available simple mode of these clamping bodies is made of plastics.
The configuration form of the scheme as an alternative of idle running device can be a wind spring idle running device.For this reason, the load-bearing member that is connected with flywheel of idle running device can have wind spring axial by putting being made of the axial bead of the dish that is used to support flywheel ring gear by putting face of face and inner radial that is used for receiving at radially outer wind spring idle running device, and this dish receives flywheel ring gear at radially outer.Be arranged on diametrically these by put between the face wind spring this axial bead by dish compress and on an end in the axial direction and do not have and to relatively rotate ground and only be connected with the axial bead of the load-bearing member of flywheel in the axial direction with another end.When flywheel ring gear is activated the machine driving during start-up course, because Ai Teerwan rope friction, wind spring tension and with the axial bead of dish to form the friction of self intensification sealed, the straight maintenance of this friction lock unification, surpass flywheel ring gear and radial clearance occurs up to output shaft with respect to axial bead, thus, such as described before, the low coupling that frictionally takes off of the part of flywheel ring gear and back.
Particularly advantageously, the point type bearing device can be set on housing for fear of by means of large diameter rolling bearing supporting flywheel ring gear.Can distribute ground and three or more centrally is set axially from the outstanding pin of housing with respect to the rotation axis of output shaft on the housing on circumference, these pins can receive the dish that is used to receive flywheel ring gear respectively with reversing for this reason.For this reason, on pin, also can be provided with little, thus lower cost and drop into not too high rolling bearing technically, dish rolls on these rolling bearings.Self-evident, dish rolls on pin with insuring in the axial direction.
Description of drawings
Describe the present invention in detail by means of Fig. 1 to Figure 16.Accompanying drawing is represented:
Fig. 1 has the embodiment of flywheel who takes off the flywheel ring gear of coupling by means of the idle running device,
The flywheel ring gear that Fig. 2 supports by means of dish,
Fig. 3 has embodiment's the cut-away section of the flywheel of clamping body idle running device,
The details of Fig. 4 clamping body idle running device,
Fig. 5 receives the load-carrying ring of clamping body,
Fig. 6 is in the clamping body in the installment state,
The description of the working method of Fig. 7 and Fig. 8 clamping body,
The 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 embodiment's the cut-away section of the flywheel of wind spring idle running device,
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 are at cut-away section and the partial view of acceptance point upper support on the internal-combustion engine housing.
Embodiment
Fig. 1 shows the embodiment of flywheel 1, and this flywheel is driven by the output shaft 2 of the internal-combustion engine that is not shown specifically.Flywheel 1 is made of plate 3 in the example shown, and this plate also can constitute by pressed article or by the material that forges in other configuration example.Flywheel 1 for example can receive being connected of clutch, foundation and fluid torque converter or as the primary side input component of double mass flywheel.In addition, the clutch assembly that has been assemblied on the transmission input shaft of speed changer of back can be connected with flywheel 11.This clutch assembly for example can be the double clutch of dual-clutch transmission.Flywheel 1 is driven by output shaft 2.For this reason, flywheel 1 for example is connected by means of bindiny mechanism that is not shown specifically such as screw with output shaft 2.
By means of unshowned Starter, this Starter has small gear to internal-combustion engine from the state of rest of this internal-combustion engine, the tooth portion engagement of this small gear and flywheel ring gear 4.For this reason, small gear can be in flywheel ring gear and continue to cooperate.Flywheel ring gear 4 at this by means of rolling bearing 5 centrally and can be received on the housing 6 of internal-combustion engine with reversing.For this reason, housing 6 can have axial bead 7, and rolling bearing 5 is received on 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.Be provided with dish 8 diametrically between flywheel ring gear 4 and rolling bearing 5, this dish has the axial bead 9 that is used to receive flywheel ring gear 4 and is used to make dish 8 to be received in axial bead 10 on the rolling bearing 5.In addition, dish 8 for example fixes by means of guard ring on rolling bearing 5 in the axial direction by means of its axial bead 10.
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 when the rotating speed of the internal-combustion engine that has started surpasses when Starter is worked.Idle running device 11 for example can be configured to change according to centrifugal force, thus, centrifugal action comes into force and 11 disengagements of idle running device after predetermined rotating speed surpasses, and thus, moment no longer transmits by flywheel ring gear 4 and this flywheel ring gear takes off coupling together with load-bearing member 8 and 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 constitutes by means of a plurality of section or belling portions that are distributed on the circumference.Simultaneously, on this position, the flywheel ring gear 4 of internal-combustion engine and coupling and the angular misalignment between the flywheel 1 have obtained compensation between idle running device 11 and plate 3.
Fig. 2 shows the details of structure of the dish 8 of Fig. 1.Dish 8 can reach suitable shape by the plate manufacturing and by means of corresponding punching out and plate mould-forming method.Be configured to annular dish 8 and have two beads 9,10, flywheel ring gear 4 is arranged on these beads in inner radial at radially outer and rolling bearing 5.Being proved particularly advantageous is that rolling bearing 5 is arranged on the identical axial height with flywheel ring gear 4.Favourablely on the meaning in space of optimizing structure also can be that under the surperficial no small situation 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 bottom of spin axis 13 belows is omitted.In addition, idle running device 11 at length is expressed as clamping body idle running device 14.This clamping body idle running device constitutes by clamping body 15, and these clamping bodies are arranged on by means of nothing that load-bearing member 16 on the plate 3 is connected with flywheel 1 and visual transition state and calmly and inner face 17 frictional fit of the axial bead 9 that is provided with flywheel ring gear 4 of dish 8 with relatively rotating.
Fig. 4 shows the details of clamping body idle running device 14.Clamping body 15 can for example be arranged on the load-bearing member 16 by means of rivet 18 on the circumference with distributing with reversing.Reverse by the restricted of clamping body 15, these clamping bodies form rubbing contact according to reversing with its fitting surface 19 and inner face 17, and wherein, rubbing contact is additionally regulated by being separately positioned on an energy storage device 20 on the clamping body 15.In this way, when internal-combustion engine is static or between by the Starter internal combustion engine driven starting period, form rubbing contact between clamping body 15 and the inner face 17, thus, flywheel ring gear 4 pass through that Starter carries out reverse cause flywheel 1, driving and the internal-combustion engine to output shaft 2 starts in this way thus.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, when flywheel 1 accelerates to the rotating speed that is conditioned, clamping body 15 reverses like this owing to centrifugal action, makes fitting surface 19 lift under the situation that forms the gap from inner face 17.For clamping body 15 is shifted owing to centrifugal force restrictedly, in load-bearing member 16, be provided with backstop 23.This backstop for example can be put on display from load-bearing member 16.At the configuration aspect its fitting surface 19 and the governor weight 22, the conversion of idle running device can be coordinated mutually with the predetermined conditioned disjunction idling speed of internal-combustion engine by clamping body.
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 had energy storage device 18 and backstop 23 by thin material.Load-carrying ring 24 is received on the load-bearing member 16 by means of rivet 18, and these rivets also can receive clamping body 15 with reversing.
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 to the camber member 25 that goes out from load-carrying ring 24 punching out in a circumferential direction at this, and for spring force radially is provided, these camber members are crimped and form.Camber member 25 cooperates and these clamping bodies is pressed on the unshowned inner face of flywheel ring gear 4 (Fig. 3) being in the nose 26 of clamping body 15 on its end, thus, forms the rubbing contact with this fitting surface on fitting surface 19.Quality is bigger by governor weight 22 is set on the side that deviates from nose 26 of clamping body 15 owing to clamping body 15, when load-bearing member 16 quickens or reverses, the effect of clamping body 15 antagonistic spring storages 20 is reversed up to backstop 23 around the run-on point 21 of rivet 18, thus, the rubbing contact between the inner face 17 (Fig. 4) of fitting surface 19 and 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 that is shown specifically.For this reason, Fig. 7 shows the state that the frictional fit between the inner face 17 of axial bead 9 of the fitting surface 19 of clamping body 15 and dish 8 forms.Because the spring force F (E) of energy storage device 20, clamping body is rotated motion around run-on point 21 towards the direction of inner face 17.Because the central point 27 of the radius of fitting surface is in run-on point 21 outsides, works to self intensification when dish 9 reverses during start-up course.As shown in Figure 8, if Xuan Zhuan part is the rotating speed increase of dish 9 and load-bearing member 16 together, then governor weight 22 stand owing to centrifugal force F (F) increases radially outer acceleration and when spring force F (E) when being exceeded clamping body 15 begin to reverse, thus, the rubbing contact on the inner face 17 is cancelled and clamping body only rests on the 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 be used to pass to be used to make load-carrying ring to be fixed on the hole 28 (Fig. 3) of the rivet on the 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 of rubbing contact that has dish 8 and receive flywheel ring gear 4 and be formed for 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 sides, and the part of this outlet side will be given unshowned output shaft by the transmission of torque that Starter transmits under the situation of idle running means for engaging.For this reason, plate 3 is fixedlyed connected with load-bearing member 16, for example rivets or meshes with tooth.Load-bearing member also can restrictedly receive clamping body 15 with load-carrying ring 24 by means of rivet 18 riveted joints and at this again with reversing.At this, in jointing state, between the fitting surface 19 that is arranged on the clamping body 15, form rubbing contact, this rubbing contact after internal combustion engine start owing to centrifugal action is cancelled.
Figure 11 shows load-bearing member 16, load-carrying ring 24 and clamping body 15 details by means of the configuration of rivet 18 riveted joints.In order to receive load-bearing member 16 regularly, rivet 18 is configured to stair-stepping special-shaped 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 on when compressing on this backstop, and clamping body 15 and load-carrying ring 24 are compacted with the axial distance of regulating regularly on bigger diameter, and this axial distance allows clamping body 15 to reverse relatively with respect to load-carrying ring.
Figure 12 shows the details of the idle running device 11 of Fig. 1 as 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.Be used for the rolling bearing 5 that dish 108 is received on the housing 6 of internal-combustion engine also can be configured to sliding bearing at other configuration example.Dish 108 radially outer receive flywheel ring gear 4 and different with 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 that radially staggers 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 that is arranged on the plate 3 of flywheel 1 overlaps axial bead 131 diametrically 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 that does not rotate on an end in the axial direction and in a circumferential direction regularly and with another end only be suspended in the bead 134 in the axial direction regularly and with respect to bead 131 prestressing on fitting surface 132.If by dish reverse starting apparatus combustion engine by means of what Starter carried out, then wind spring 133 is strained on fitting surface and to form friction sealed with being suspended at wind spring 133 in the load-bearing member 116.When speed discrepancy is pulled when changing to output shaft and driving flywheel from output shaft, sealed cancel and wind spring is shifted under the situation with respect to fitting surface 132 formation radial clearances of rub.Thus, dish 108, flywheel ring gear 4 and take off coupling with the Starter of this flywheel ring gear coupling.
Figure 13 shows the details of wind spring idle running device 114 under the situation that forms radial clearance 136 between the axial bead 131 of dish 108 and the wind spring 133 when the frictional fit of no wind spring 133 when rotating speed is high, this wind spring is resisted the prestressing of this wind spring by centrifugal force when rotating speed is high and on the axial bead 134 of load-bearing member 116, 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 on this axial bead.In this view, rub and sealedly take off coupling by forming radial clearance 136 flywheel 1 of cancelling and for example more than idling speed, rotating apace and the dish 108 that for example stops.If rotating speed reduces again, then the pre-pressing force of wind spring 133 surpasses centrifugal force and radial clearance 136 closures, and this makes the rubbing contact foundation between the fitting surface 132 of wind spring 133 and axial bead 131, and the internal-combustion engine that this rubbing contact allows to stop 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 prestressing on axial bead 131, this frictional force is taken wind spring 133 when this axial bead is reversed by Starter when internal combustion engine start.By the bending of bead 131 and wind spring, wind spring 133 is nipped owing to the Ai Teerwan rope with rubbing also self intensification.Because free end 137 is received in the hole 138 of axial bead 134 of the load-bearing member 116 that is connected with flywheel regularly, power passes to live axle from Starter, up to centrifugal forces affect and the disengagement of rubbing contact by improving when rotating speed is higher than idling speed.
Figure 15 shows the bearing device as the alternative of the flywheel 1 of Fig. 1 of flywheel ring gear 4.Replace a unique rolling bearing 5 (Fig. 1), three or more preferably is set on the housing 206 of internal-combustion engine is distributed in acceptance division 239 on the circumference, the forming section 239 that is arranged in the housing 206 can be provided with when making housing 206 and for example pour into a mould when making housing by means of the pressure injection method.Scheme correspondingly can be processed axially outstanding pin as an alternative.Dish 208 can be received on these outside forming sections 239 with reversing.At this, wind the forming section 239 that centrally is provided with respect to spin axis 13 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 with use a concentric rolling bearing different, this configuration is not technically and in that to be used for aspect the cost of rolling bearing input 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 obtains simplifying, and in addition, material uses and can reduce, especially when dish 208 by bar manufacturing, roll extrusion with when on the end, sealing.
Figure 16 shows the view of detailed expression of the structure of Figure 15, have idle running device 11, the dish 208 that only schematically shows and be distributed in bearing 240 on the circumference, these bearings are received on the 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 for assembling, 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, idle running device 11 and dish 208 anti-loose ground receive mutually.The common mode of flywheel ring gear 4 usefulness is fixed for example welding, ca(u)lk or pyrocondensation on dish 208.Rolling bearing 240 is arranged on the dish 208 anti-loosely, and thus, this element of construction only must be sleeved on the forming section 239 when final assembling and flywheel 1 is connected with output shaft.Dish 208 the axial relief on the forming section 239 by with flywheel 1 axial restraint be threaded on the live axle 2 and produce.
The 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 rotations
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 (19)
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 used for starting this internal-combustion engine by means of Starter, it is characterized in that: this flywheel ring gear (4) is bearing in the axial direction between the housing (6,206) of this internal-combustion engine and this flywheel (1) and is coupled with this output shaft (2) regularly on driving according to the direction of the moment that is passed to this output shaft (2) by this Starter by this flywheel ring gear (4).
2. according to the flywheel (1) of claim 1, it is characterized in that: this flywheel ring gear (4) can be bearing on this housing (6,206) with reversing.
3. according to the flywheel (1) of claim 1, it is characterized in that: this flywheel ring gear (4) can be bearing on this output shaft (2) with reversing.
4. according to the flywheel (1) of one of claim 1 to 3, it is characterized in that: this flywheel ring gear (4) is by this flywheel (1) and this output shaft (2) coupling.
5. according to the flywheel (1) of one of claim 1 to 4, it is characterized in that: the tooth portion of this Starter is in engagement with this flywheel ring gear (4) constantly.
6. according to the flywheel (1) of one of claim 1 to 5, it is characterized in that: up to the idling speed of this internal-combustion engine, moment can pass to this output shaft (2) from this Starter, and after this idling speed was surpassed by this internal-combustion engine, this flywheel ring gear (4) took off coupling with this output shaft (2).
7. according to the flywheel (1) of one of claim 1 to 6, it is characterized in that: this flywheel ring gear (4) can take off coupling by means of idle running device (11) and this output shaft (2).
8. according to the flywheel (1) of claim 7, it is characterized in that: this idle running device (11) is arranged between the bearing device of flywheel ring gear (4) and this flywheel ring gear (4) diametrically.
9. according to the flywheel (1) of claim 7 or 8, it is characterized in that: this idle running device (11) be arranged on this flywheel ring gear (4) diametrically and be used to make this idle running device (11) and the mechanism of this flywheel (1) coupling between.
10. according to the flywheel (1) of one of claim 2 to 9, 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) go up by means of the bearing device carrying and form the part of an idle running device in the inner radial of the axial bead (9,131) that is used to receive this flywheel ring gear (4).
11. the flywheel (1) according to claim 10 is characterized in that: the inner face (17) of this axial bead (9) be formed for clamping body idle running device (14) clamping body (15) by putting face.
12. the flywheel (1) according to claim 11 is characterized in that: these clamping bodies (15) are arranged on the restricted diametrically setting of effect that energy storage device (20) was gone up and can be resisted to the load-bearing member (16) that is connected with this output shaft (2) with distributing with reversing on circumference.
13. flywheel (1) according to claim 12, it is characterized in that: these clamping bodies (15) are pressed on this inner face (17) by these energy storage devices (20) and have governor weight (22), and these governor weights cause lifting from this inner face (17) according to the rotating speed of this flywheel (1) by reversing of these clamping bodies (15).
14. the flywheel (1) according to claim 12 or 13 is characterized in that: these energy storage devices (20) are formed by the member that receives these clamping bodies (15).
15. the flywheel (1) according to one of claim 12 to 14 is characterized in that: these clamping bodies (15) are made of plastics.
16. the flywheel (1) according to one of claim 7 to 10 is characterized in that: this idle running device (11) is a wind spring idle running device (114).
17. the flywheel (1) according to claim 16 is characterized in that: this dish (108) has wind spring (133) axial by putting face (131) that is used for receiving in inner radial this wind spring idle running device (114).
18. the flywheel (1) according to claim 16 or 17 is characterized in that: the forming by the load-bearing member (116) that is connected with this output shaft (2) of radially outer that is used for this wind spring (133) by putting face.
19. the flywheel (1) according to one of claim 1 to 18 is characterized in that: this flywheel ring gear (4) can be received on three forming sections (239) that are distributed on the housing on the circumference, that be arranged on this internal-combustion engine (206) at least with reversing.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102008010257 | 2008-02-20 | ||
| DE102008010257.1 | 2008-02-20 | ||
| DE102008016440 | 2008-03-31 | ||
| DE102008016440.2 | 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 true CN101970852A (en) | 2011-02-09 |
| CN101970852B 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) | DE112009000236B4 (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 |
| DE102010033503B4 (en) * | 2009-08-28 | 2020-02-13 | Schaeffler Technologies AG & Co. KG | Starter with dry freewheel |
| WO2011023157A1 (en) * | 2009-08-28 | 2011-03-03 | Schaeffler Technologies Gmbh & Co. Kg | Flywheel comprising a starter ring gear |
| 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 |
| WO2011120491A2 (en) * | 2010-03-29 | 2011-10-06 | 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 |
| WO2012055383A2 (en) | 2010-07-26 | 2012-05-03 | 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 |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| US6062365A (en) * | 1999-01-13 | 2000-05-16 | Eaton Corporation | Automatically adjusting friction clutch with over adjustment 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 |
| JP4508027B2 (en) * | 2005-07-29 | 2010-07-21 | トヨタ自動車株式会社 | Internal combustion engine starting torque transmission mechanism |
| JP4449852B2 (en) * | 2005-07-29 | 2010-04-14 | トヨタ自動車株式会社 | Internal combustion engine starting torque transmission mechanism |
| JP2007120474A (en) * | 2005-10-31 | 2007-05-17 | Denso Corp | Engine starting device |
| JP4179349B2 (en) * | 2006-06-23 | 2008-11-12 | トヨタ自動車株式会社 | Ring gear, internal combustion engine starting rotational force transmission mechanism, and ring gear manufacturing method |
| 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 |
-
2009
- 2009-02-12 DE DE112009000236.6T patent/DE112009000236B4/en not_active Expired - Fee Related
- 2009-02-12 WO PCT/DE2009/000197 patent/WO2009103267A2/en active Application Filing
- 2009-02-12 JP JP2010547039A patent/JP5473947B2/en not_active Expired - Fee Related
- 2009-02-12 CN CN200980105735.8A patent/CN101970852B/en not_active Expired - Fee Related
- 2009-02-12 DE DE102009008599A patent/DE102009008599A1/en not_active Withdrawn
Also Published As
| Publication number | Publication date |
|---|---|
| WO2009103267A2 (en) | 2009-08-27 |
| DE102009008599A1 (en) | 2009-08-27 |
| JP2011514487A (en) | 2011-05-06 |
| JP5473947B2 (en) | 2014-04-16 |
| DE112009000236B4 (en) | 2020-11-26 |
| WO2009103267A3 (en) | 2009-12-30 |
| DE112009000236A5 (en) | 2010-10-28 |
| CN101970852B (en) | 2014-05-14 |
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| C53 | Correction of patent of invention or patent application | ||
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Address after: German Herzogenaurach Applicant after: SCHAEFFLER TECHNOLOGIES AG & CO. KG Address before: German Herzogenaurach Applicant before: Schaeffler Technologies GmbH |
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