CN101328854A - Starter for engines - Google Patents
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- CN101328854A CN101328854A CNA2008101249675A CN200810124967A CN101328854A CN 101328854 A CN101328854 A CN 101328854A CN A2008101249675 A CNA2008101249675 A CN A2008101249675A CN 200810124967 A CN200810124967 A CN 200810124967A CN 101328854 A CN101328854 A CN 101328854A
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- armature shaft
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Abstract
The present invention provides a starter for an engine, including a motor; a planetary reduction gear including a sun gear and a planet wheel; clutch outer and clutch inner, wedge shape cam chamber and one-way clutch of roller locating in the cam chamber; a planet wheel stand driven by orbital motion of the planet wheel and formed as a whole body with the clutch outer; an outer adjusting component, having a round hole formed in the central part of the planet wheel stand along the diameter direction; a concave section, formed by drilling in the central part of the clutch inner supported with rotary mode through an inner bearing from a central shell; the anti-motor side of an armature shaft is inserted through the round hole, the end part of the armature shaft is inserted into the inside of the concave section that passes through the round hole provided on the outer adjusting component, and the armature shaft bearing that is press fit in the inner circumference of the concave section supports the armature shaft relatively rotatably.
Description
Technical field
The present invention relates to a kind of starter motor that is used to pilot engine.
Background technique
Open 2005-130753 number with shown in Figure 9 as the Japanese patent gazette spy, wherein show the starter motor that is used to pilot engine that is provided with retarder 105 and overrunning clutch 115, retarder 105 reduces the rotational speed of armatures 100, and the rotation of the armature 100 that overrunning clutch 115 will slow down by retarder 105 is delivered to output shaft 110.
The end enclosure (not shown) supports an end (side opposite with retarder) of the armature shaft 120 that the rotating force (moment of torsion) of armature 100 is exported by the bearing (not shown).Dust guard 140 supports the other end of armature shaft 120 by bearing 130.
Retarder 105 is planetary reducers and comprises: be arranged on the sun gear 150 on the armature shaft 120; Internal gear 160 with the coaxial setting of sun gear; The a plurality of planet wheels 170 that mesh simultaneously with gear 150 and 160; And bear because the planetary wheel carrier 180 of the active force that causes around orbiting of planet wheel 170.
Overrunning clutch 115 forms in planetary wheel carrier 180.Overrunning clutch 115 comprises clutch Outside 200, clutch inner 210 and a plurality of roller 220, clutch Outside 200 is sentenced relatively by bearing 190 at an end of armature shaft 120, and free rotation mode supports, clutch inside 210 is formed on the output shaft 110 as a whole, and roller 220 is arranged between clutch Outside 200 and the clutch inside 210.
According to above-mentioned structure, can control the deflection of the clutch Outside 200 that the rotation by armature 100 causes, even and clutch Outside 200 disequilibriums still might transfer torque to overrunning clutch 115 reposefully.
Another aspect, open 9-88780 number with shown in Figure 9 as the Japanese patent gazette spy, wherein show the conventional starter motor that comprises output shaft 110, output shaft 110 rotatably supports by being arranged on bearing 250 on the front shell 240 and the bearing 270 that is arranged on the center housing 260.Output shaft 110 has the small gear 230 of coaxial setting and integrally forms in the clutch inside 210 of overrunning clutch 115.
Yet above-mentioned starter motor is the deflection of controlling armature 100 by an end that bearing 130 is set to armature shaft 120 (the anti-clutch side of sun gear 150).In this case, owing to must guarantee to be used between armature 100 and retarder 105, being provided with the space (Fig. 9 is " X " shape) of bearing 130, therefore there is the elongated problem of starter motor length.
Further, after motor is by the starter motor starting, when the speed of motor surpassed the speed of starter motor and causes small gear 230 to enter overspeed condition, such problem can take place as shown in figure 10: promptly the slight instability owing to atwirl clutch inside 210 was easy to take place the deflection of output shaft 110 under deflected condition.
In addition, if this deflection of output shaft 110 following problem will occur so: for example cause that by vibrations the rotational instability of generation, the clutch inside 210 of noise is delivered to clutch Outside 200 by roller 220 and makes the idling performance variation of overrunning clutch 115.
Reason for this reason, bearing play must make very for a short time and also rotary component for example the balance of output shaft 11 0 or clutch Outside 200 must reach enough accurate.
Summary of the invention
Make and the objective of the invention is to address the above problem, and purpose of the present invention exactly can be for motor provides a kind of like this starter motor, the deflection that it can the solenoidoperated cluthes outside can be shortened the length of starter motor simultaneously.
Thereby another object of the present invention is to provide the starter motor that can prevent the idling performance deterioration by the deflection of adjusting output shaft with simple structure for motor.
At the starter motor that is used for motor aspect first, the starter motor that is used for motor comprises:
Motor, it produces moment of torsion and has armature shaft;
Planetary reducer, it has sun gear and planet wheel, and described sun gear is arranged on the described armature shaft, and described planet wheel rotation time is around the circumgyration of described sun gear, to reduce the rotating speed of described armature shaft;
Overrunning clutch, it is delivered to output shaft by described planetary reducer with the moment of torsion that is increased by described planetary reducer of described motor, and described overrunning clutch has: be arranged to the clutch Outside and the clutch inside that can relative to each other rotate; Be formed at the wedge cams chamber between described clutch Outside and the described clutch inside; And be contained in roller in the described cam chamber;
Planetary wheel carrier, its orbiting by described planet wheel drives, and forms as a whole with described clutch Outside;
Outer adjusting component, its have in the core of described planetary wheel carrier, form along diametric circular hole; And
Recessed portion, its core internal drilling in the described clutch inside of being supported in rotatable mode by inner bearing by center housing forms;
Wherein, with the part that described sun gear is set away from and an end being arranged on the described armature shaft of described overrunning clutch side pass the described circular hole of described outer adjusting component and insert in the inner circumferential of the female part, and described end is supported in the mode that relative to each other can rotate by the armature shaft bearing by described clutch inside.
According to above-mentioned structure, housing supports clutch inside by inner bearing, and the end of armature shaft is inner by the armature shaft bearings by clutch.That is to say that housing is proofreaied and correct clutch inside by inner bearing, and the end of armature shaft is inner by the armature shaft bearings by clutch, therefore can control the deflection of armature shaft.
In addition, by the armature shaft bearing being set in the inner circumferential of the recessed portion that in clutch inside, forms, just will the armature shaft bearing be set to a side opposite of sun gear with clutch.Therefore, can shorten the length of starter motor.
In addition, pass the circular hole of the outer adjusting component in the core that is arranged on planetary wheel carrier by the end that makes armature shaft, make the deflection that armature shaft can the solenoidoperated cluthes outside.
According to the starter motor that is used for motor aspect second, the circular hole internal diameter of case of external adjustment component and the dimension difference of passing between the external diameter of armature shaft of circular hole are 2a, in described inner circumferential or in the bearing play of the outer circumferential side of described armature shaft is 2b, and the maximum deviation amount that roller can depart from from the outer circumferential side of clutch inside when overrunning clutch exceeds the speed limit is set at c, then satisfies the given condition of formula c＞a+b.
According to the starter motor that is used for motor aspect the 3rd, suppose when two rollers along the circumferential direction adjacent one another are pierce cam chamber than narrow side the time clutch Outside maximum eccentric value that produces amount be set at d, then satisfy the given condition of formula a+b＞d.
According to the starter motor that is used for motor aspect the 4th, clutch Outside is provided with the through hole that forms in the diametric core of planetary wheel carrier, and the outer adjusting component with form of ring is inserted in the inner circumferential of through hole.
According to the starter motor that is used for motor aspect the 5th, inner bearing is set to can contact with clutch inside.
According to the starter motor that is used for motor aspect the 6th, the end face of inner bearing is towards the end face of clutch inside and be set to can contact with the end face of clutch inside.
According to the starter motor that is used for motor aspect the 7th, inner bearing is arranged on the overlapping part with the inboard of packing ring, can prevent that like this clutch inside from throwing off vertically against clutch Outside and withdraw from.
According to the starter motor that is used for motor aspect the 8th, suppose under output shaft is arranged at state in the motor side of center housing, gap width between the edge surface of clutch inside and the edge surface of inner bearing is set at e, and the thickness setting of packing ring is f, then satisfies by the given condition of formula e＜f.
According to the starter motor that is used for motor aspect the 9th, be provided with along the outwards outstanding flange portion of diametric(al) in the end that is arranged in motor side of described inner bearing.
According to the starter motor that is used for motor aspect the tenth, the internal surface of flange portion is provided with chamfering.
According to the starter motor that is used for motor aspect the 11, be provided with groove in the side opposite of clutch inside along the periphery of described output shaft, and the part of inner bearing is installed in the groove of clutch inside at least with motor.
Description of drawings
In the accompanying drawings:
Fig. 1 is the axial, cross-sectional view that illustrates according to the starter motor of first embodiment of the invention;
Fig. 2 is the axial, cross-sectional view that the major component of starter motor shown in Figure 1 is shown;
Fig. 3 is the sectional view of the amplification of overrunning clutch shown in Figure 1;
Fig. 4 is the axial, cross-sectional view of amplification that the circumference of overrunning clutch shown in Figure 1 is shown;
Fig. 5 A and 5B are the sectional view of the cam chamber of overrunning clutch shown in Figure 1;
Fig. 6 is the axial, cross-sectional view that illustrates according to the major component of the starter motor of second embodiment of the invention;
Fig. 7 is the axial, cross-sectional view that illustrates according to the circumference of the clutch of third embodiment of the invention;
Fig. 8 illustrates according to the bearing of four embodiment of the invention and the axial, cross-sectional view of clutch inside;
Fig. 9 relates to the sectional view of the starter motor of conventional art; And
Figure 10 is the simulation drawing that is used for explaining in the circumferential deflection of conventional art output shaft.
Embodiment
Below with reference to accompanying drawing first mode of execution of the present invention is described.
Fig. 1 is the axial, cross-sectional view that illustrates according to the starter motor of first mode of execution, and Fig. 2 is the axial, cross-sectional view that the major component of starter motor is shown.
The starter motor 1 of this mode of execution comprises armature shaft 2, motor 3, output shaft 4, small gear 5, planetary reducer 6 (hereinafter referred retarder), overrunning clutch 7, shift rod 8 and magnetic switch 9.
The moment of torsion that motor 3 produces corresponding to energy armature shaft 2.Output shaft 4 and the armature shaft 2 coaxial front sides (left side of Fig. 1 and Fig. 2) that are arranged on motor 3.Small gear 5 is engaged on the periphery of output shaft 4 in the mode of spline.Retarder 6 reduces the rotational speed of motor 3.Overrunning clutch 7 is delivered to output shaft 4 with the moment of torsion of retarder 6.And magnetic switch 9 disconnects and the closed power-on circuit (not shown) that is arranged on motor 3 in the main contact (not shown) and via the mobile vertically small gear 5 of shift rod 8.
Motor 3 is known commutator motors, has the rectifier (not shown) in an end of armature shaft 2 (side opposite with retarder).Motor 3 comprises the armature 10 with armature shaft 2, the fixed magnetic pole 11 that is arranged on armature 10 peripheries and fixed magnetic pole 11 is fixed on cylindric yoke 12 on the internal surface.When the starter switch (not shown) being switched to " connection " and make the contact (not shown) that places magnetic switch 9 closed, armature 10 energisings also begin rotation.
The front end of output shaft 4 (side opposite with motor) is freely rotatably supported by bearing 13 by an end of front shell 14.The rear end of output shaft 4 (motor side) is rotatably supported by inner bearing 15 by center housing 16.Inner bearing 15 is fixed as and makes its rear end put in to be arranged in the internal surface of small diameter cylinders shape part 16a at center housing 16 front end places.Inner bearing 15 is made by for example metal or resin.
When above-mentioned starter switch switched to " connection ", the coil (not shown) was switched on, and made the plunger 20 that is contained in the magnetic switch 9 be sucked into coil by the magnetic that produces in coil.Therefore the contact of motor 3 close and, and shift rod 8 carries out shifting functions by bar 19, produces the extruding force of small gear 5 then.
Retarder 6 is known planetary reducer types, and retarder 6 is reduced in the rotational speed of the motor 3 on the armature shaft 2 and is increased in output torque on the same axle.As shown in Figure 3, retarder 6 planetary wheel carrier 24 that is included in the sun gear 21 that forms on the periphery of an end (side opposite) of armature shaft 2, is rotated with the planet wheel 23 of the coaxial internal gear 22 of sun gear 21, a plurality of for example three whiles and sun gear 21 and internal gear 22 engagements and the motion by these planet wheels 23 around track with the annular setting with motor.Sun gear 21 is by being delivered to three planet wheels 23 with armature shaft 2 rotations with the rotation of armature shaft 2.
Each of three planet wheels 23 is rotatably supported by the bearing (not shown) by the pin 25 that is fixed to planetary wheel carrier 24 separately.Planet wheel 23 meshes and turns round around the periphery of sun gear 21 with sun gear 21 and internal gear 22.In addition, internal gear 22 forms in the internal surface of the circular cylindrical wall of center housing 16.The planetary wheel carrier 24 and clutch Outside 24 one of overrunning clutch 7 are finished (planetary wheel carrier 24 also is endowed same reference character), and when transmitting the turning power of planet wheel 23, planetary wheel carrier 24 rotates.In addition, three pins 25 are fixed to planetary wheel carrier 24.
As shown in Figure 3, overrunning clutch 7 comprises and is arranged to the clutch Outside 24 that becomes one with planetary wheel carrier 24, the clutch inside 26 that is set to output shaft 4 and a plurality of not only at the roller 27 and the spring 28 of transmitting torque among the clutch Outside 24 but also among clutch inside 26.Center housing 16 coats the periphery of retarders 6 and overrunning clutch 7 and by yoke 12 lock rings forwardly between housing 14 and the end enclosure 29.Whole center housing 16 is fixed by a plurality of through bolts 30.
Fig. 4 is the axial, cross-sectional view of amplification that the circumference of overrunning clutch 7 is shown.As shown in Figure 4, overrunning clutch 7 is provided with packing ring 31, to prevent that clutch inside 26 from coming off and lubricant oil flows out.The outer peripheral portion that the end face with clutch Outside 24 of packing ring 31 contacts is fixing by clutch cover 32, and the inner periphery contact clutch inside 26 of packing ring 31 can prevent that like this clutch inside 26 from coming off in (among the figure to left-hand) and prevent that lubricant oil from flowing out.
Its end nipple of being arranged to the above-mentioned inner bearing 15 of this paper stretches in the small diameter cylinders part that is arranged on center housing 16 front end places, be arranged to kiss the earth to the side margins surface of the end face 26A of clutch inside 26 15A but inner bearing 15 has, and inner bearing 15 is arranged to overlap with the internal diameter sidepiece of packing ring 31.
With regard to clutch Outside 24, outer adjusting component 33 promptly forms in the central part office of planetary wheel carrier 24 at the core of clutch Outside 24, and is controlled along its diametric departing from by outer adjusting component 33.As shown in Figure 3, the circular hole 33a externally core of adjustment component 33 forms along its diametric(al), and insert in the circular hole 33a end of armature shaft 2.Further, a plurality of wedge cams chamber 24a that are formed in the clutch Outside 24 and equidistantly form along the circumferencial direction of clutch Outside 24 are arranged between the periphery sidepiece of clutch inside 26, and in cam chamber 24a, hold roller 27.
Clutch inside 26 is provided with inner shaft parts 26a, its external diameter less than when moment of torsion transmits the contact roller 27 its in all sides.Spindle unit 26a is arranged on integratedly on the output shaft 4 and by center housing 16 and rotatably supports by the inner bearing 15 on the periphery of spindle unit 26a in being installed in being somebody's turn to do.In addition, center housing 16 is installed within the inner circumferential of the front shell 14 that is attached to motor and is non-rotatably fixing.
As shown in Figure 3, hollow tubular recessed portion 26b is that the axial drilling along clutch inside 26 forms in the core of clutch inside 26.Further, armature shaft bearing 34 press fits of supporting the fore-end of armature shaft 2 are advanced in the inner circumferential of recessed portion 26b.That is to say that the side opposite with motor of armature shaft 2 passed the circular hole 33a of outer adjusting component 33 and inserted the inner circumferential of recessed portion 26b and can be supported with the relative rotation by armature shaft bearing 34 by clutch inside 26.In addition, the motor side of armature shaft 2 is rotatably supported by the bearing (not shown) by end enclosure 29.
Herein, explain with reference to figure 3, Fig. 4 and Fig. 5 A and 5B and be used to control the situation that the moment of torsion via clutch Outside 24 transmits.
The internal diameter of the circular hole 33a of case of external adjustment component 33 and the dimension difference of passing between the external diameter of armature shaft 2 of circular hole 33a are 2a, dimension difference between the external diameter of the internal diameter of armature shaft bearing 34 and armature shaft 2 (bearing play) is 2b, the maximum deviation amount that roller 27 can depart from from the perimeter sides of clutch inside 26 when overrunning clutch 7 hypervelocities is c, and when two rollers along the circumferential direction adjacent one another are pierce cam chamber 24a than narrow side 24b the time clutch Outside 24 that produces the amount of maximum eccentric value be d, then
c＞a+b............(1)
a+b＞d............(2)
Satisfy by above-mentioned formula (1) and the given condition of formula (2).
Herein, bearing play 2b is the dimension difference between the external diameter of the internal diameter of armature shaft bearing 34 when 34 press fits of armature shaft bearing are advanced in the inner circumferential of recessed portion 26b and armature shaft 2.Bearing play 2b is the dimension difference between the internal diameter of the external diameter of armature shaft bearing 34 and recessed portion 26b when armature shaft bearing 34 is press fit on the periphery of armature shaft 2 still.
In addition, as shown in Figure 4, suppose that the gap width between the edge surface 26A of clutch inside 26 and the edge surface 15A of inner bearing 15 is e under output shaft 4 is arranged at state in the rear side of center housing 16, and the thickness of packing ring 31 is f,
E＜f............ (3) then
Satisfy by the given condition of formula (3).
Hereinafter explain the operation of starter motor 1.
When starter switch is switched " on ", then the contact of motor 3 is by magnetic switch 9 closures and armature 10 energisings, thereby produces moment of torsion in armature 10.Therefore, by armature shaft 2, sun gear 21 rotates and then drives three small gears 23 and rotates.Although each planet wheel 23 all meshes with sun gear 21 and internal gear 22, but, thereby make each planet wheel 23 turn round around the periphery of sun gear 21 simultaneously be that center self is rotating with pin 25 because the internal gear 22 that forms in center housing 16 is configured to and can not rotates.Rotating power is delivered to planetary wheel carrier 24 (being clutch Outside 24) by pin 25 then, and the rotation of clutch Outside 24 is delivered to clutch inside 26 by roller 27, so output shaft 4 rotations.
On the other hand, by starter switch being switched to " connection ", place the magnetic coil (not shown) energising of magnetic switch 9 and form electromagnet.Because plunger 20 (with reference to figure 1) is drawn in electromagnet, make splined tube 17 be shifted bar 8 and promote (left side of Fig. 1) and small gear 5 and gear ring 18 engagements forward, thereby the moment of torsion of motor 3 is delivered to gear ring 18 and pilots engine along the axis of output shaft 4 with being installed to small gear 5 on the output shaft 4.
Rotated to after the high speed rotating by gear ring 18 at engine start and small gear 5, it is faster than the rotation of clutch Outside 24 that the rotation of clutch inside 26 can become.Yet roller 27 moves on to the more spacious side 24c of the cam chamber 24a between clutch inner 26 and the clutch Outside 24, and the locking of clutch inner 26 and clutch Outside 24 is eliminated like this.Thereby make moment of torsion can not be delivered to clutch Outside 24, therefore can prevent armature 10 hypervelocities from clutch inside 26.
In addition, piloting engine by rotating crank and starter switch becomes " disconnection " afterwards, magnetic coil stops energising, and when the gravitation disappearance of electromagnet, the reaction force of return spring (not shown) pushes back plunger 20.When plunger 20 was pushed back, small gear 5 was owing to shift rod 8 edges and the side that is used to the pilot engine mobile gear ring 18 that breaks away from the opposite direction.Small gear 5 is returned to the precalculated position (position shown in Figure 1) on output shaft 4 and stops then.And main contact is opened and the electric energy from the battery (not shown) to motor stops, so the rotation of armature 10 slows down gradually and stops.
As mentioned above, the starter motor 1 of present embodiment obviously can be controlled the deflection of armature shaft 2, because inner bearing 15 alignments are passed through by center housing 16 in clutch inside 26, and the fore-end of armature shaft 2 is supported by armature shaft bearing 34 by clutch inner 26.In addition, because needn't allocation space in order to armature shaft bearing 34 is set to a side opposite of sun gear 21 by the inner circumferential that armature shaft bearing 34 is set to the recessed portion 26b that is formed in the clutch inside 26, so the length of starter motor 1 can shorten with clutch.And, because formula (1) above satisfying and the relation between the formula (2), thus can be under the situation of the moment of torsion smooth transfer of overrunning clutch 7 the alignment adjustment of realization clutch Outside 24.
That is to say, by satisfying the condition of formula (1), can be in the deflection of the rotating speed of working as clutch inside 26 above solenoidoperated cluthes outside 24 in the rotating speed of (hypervelocity) clutch Outside 24.
In addition, by satisfying the condition of formula (2), make can to prevent that in situation following time of off-centre two rollers 27 are lockable when clutch Outside 24 because when roller 27 pierce cam chamber 24a than narrow space 24b the time outer adjusting component 33 can not become adverse effect.In other words, because the operation of overrunning clutch 7 is not subjected to the obstruction of outer adjusting component 33, therefore can carry out moment of torsion transmission stably.
In addition, according to this mode of execution since the end face 15A of inner bearing 15 towards and be set to can contact with the end face 26A of clutch inside 26, therefore will reply power and be applied on the small gear 5 by the reverse power of helical spline when the hypervelocity.In addition, make the end face 26A of clutch inside 26 contact the end face 15A of inner bearing 15 by this reaction of replying power, therefore the deflection of output shaft 4 can be adjusted in moving clutch inside 26 by the end face 15A that follows inner bearing 15, thereby can prevent the idling performance deterioration when high speed rotary.
In addition, because inner bearing 15 is arranged on the inboard overlapping part of itself and packing ring 31, can prevent that like this clutch inside 26 from throwing off vertically against clutch Outside 24 and withdraw from, thereby between the external diameter of the internal diameter of packing ring 31 and output shaft 4, can form and play the space of collecting the lubricant oil effect.Therefore, can prevent to be full of lubricant oil between the end face 26A of the end face 15A of inner bearing 15 and clutch inside 26 and be subjected to action of centrifugal force and outwards disperse, thereby improve the anti-sticking ability.
At last, make packing ring 31 and inner bearing 15 overlap all the time by the condition that satisfies formula (3), and irrelevant with the axial position of output shaft 4.Therefore, can keep lubricant oil can outwards not disperse because of being subjected to action of centrifugal force.
Yet the present invention is not limited to above-mentioned mode of execution, let alone, can provide various variation in the scope that does not deviate from main points of the present invention.
Fig. 6 is the axial, cross-sectional view of major component that the starter motor of second embodiment of the invention is shown, and this mode of execution is the example that constitutes outer adjusting component 40 by the planetary wheel carrier 24 of clutch Outside 24 and another member.
As shown in Figure 6, clutch Outside 24 is provided with the through hole 41 in the diametric core that is formed at planetary wheel carrier 24.Outer adjusting component 40 with annular form is inserted the inner circumferential of through hole 41.According to this structure, outer adjusting component 40 can be made by the material that is different from clutch Outside 24.
In addition, although have following structure, wherein be not that output shaft 4 moves against overrunning clutch 7, but small gear 5 is along the peripheric movement of output shaft at the starter motor 1 shown in first mode of execution and second mode of execution.Yet the present invention can be applicable to the starter motor 1 with following structure equally, and wherein output shaft 4 and small gear 5 move against overrunning clutch 7 together as parts.Although be not shown specifically, but the interior shaft portion 26a of clutch inside 26 can be with the shape setting of cylinder type, and output shaft 4 can inject in the circumference of interior shaft portion 26a, thereby makes output shaft 4 be connected by for example helical splined joint part with interior shaft portion 26a.
Fig. 7 is the axial, cross-sectional view that is illustrated in the clutch circumference in the third embodiment of the invention.As shown in Figure 7, can be arranged on the end of inner bearing 15 along the outwards outstanding flange portion 15a of diametric(al).According to this mode of execution, can control the deflection of output shaft 4 more definitely with the contact diameter of the end face of clutch inside 26 by increase.
In addition, outwards the internal surface of outstanding flange portion 15a is provided with chamfering 15b, therefore in this embodiment, can further improve the effect of collecting lubricant oil by the size that increases inner bearing 15 and chamfering 15b.In addition, by the size of the bight R on the border of output shaft 4 and clutch inside 26 being established to such an extent that the bigger processing that makes output shaft 4 becomes easily and can improve the intensity of output shaft 4.
Although in the above-described embodiment, the end face 15A of inner bearing 15 is towards the end face 26A of clutch inside 26, and be arranged to contact the end face 26A of clutch inside 26, but still can in the fore-end of clutch inside 26, be provided with along the groove 26c of output shaft 4 peripheries as shown in Figure 8, thereby make that the part of inner bearing 15 (being specially the rear end part of inner bearing 15) can be installed among the groove 26c of clutch inside 26 at least.
In addition, Fig. 8 is illustrated in the inner bearing 15 in the 4th mode of execution and the axial, cross-sectional view of clutch inside 26.According to this mode of execution, adjust the deflection of output shaft 4 by the rear end part of the inner bearing 15 that contacts with the internal surface of the wall of groove 26c.Therefore, can prevent the deflection of output shaft 4 when high speed rotary, and can prevent the idling performance variation.Can also improve the effect that the lubricant oil that is full of between inner bearing 15 and the clutch inside 26 is kept.
In brief, if starter motor 1 has following structure, be that inner bearing 15 is set to can contact with clutch inside 26, to reply power by the reverse power of helical spline when exceeding the speed limit is applied on the small gear 5, and clutch inner 26 is owing to the reaction of replying power contacts inner bearing 15, so just can adjust the deflection of output shaft 4, and can prevent output shaft 4 deflection when high speed rotary, therefore can prevent the idling performance deterioration.
Claims (11)
1. starter motor that is used for motor, described starter motor comprises:
Motor, it produces moment of torsion and has armature shaft;
Planetary reducer, it has sun gear and planet wheel, and described sun gear is arranged on the described armature shaft, and described planet wheel rotation time is around the circumgyration of described sun gear, to reduce the rotating speed of described armature shaft;
Overrunning clutch, its moment of torsion that is increased by described planetary reducer with described motor is delivered to output shaft, and described overrunning clutch has: be arranged to the clutch Outside and the clutch inside that can relative to each other rotate; Be formed at the wedge cams chamber between described clutch Outside and the described clutch inside; And be contained in roller in the described cam chamber;
Planetary wheel carrier, its orbiting by described planet wheel drives, and forms as a whole with described clutch Outside;
Outer adjusting component, its have in the core of described planetary wheel carrier, form along diametric circular hole; And
Recessed portion, its core internal drilling in described clutch inside forms, and described core is rotatably supported by inner bearing by center housing;
Wherein, with the part that described sun gear is set away from and an end being arranged on the described armature shaft of described overrunning clutch side pass the described circular hole of described outer adjusting component and insert in the inner circumferential of the female part, and described end is supported in the mode that relative to each other can rotate by the armature shaft bearing by described clutch inside.
2. the starter motor that is used for motor as claimed in claim 1, wherein, suppose that the internal diameter of described circular hole of described outer adjusting component and the dimension difference of passing between the external diameter of described armature shaft of described circular hole are 2a, in described inner circumferential or in the bearing play of the outer circumferential side of described armature shaft is 2b, and the maximum deviation amount that described roller can depart from from the outer circumferential side of described clutch inside when described overrunning clutch exceeds the speed limit is set at c, then satisfies by the given condition of formula c＞a+b.
3. the starter motor that is used for motor as claimed in claim 2, wherein, suppose when two rollers along the circumferential direction adjacent one another are pierce described cam chamber than narrow side the time the described clutch Outside maximum eccentric value that produces amount be set at d, then satisfy by the given condition of formula a+b＞d.
4. the starter motor that is used for motor as claimed in claim 1, wherein, described clutch Outside is provided with the through hole that forms in the diametric core of described planetary wheel carrier, and the described outer adjusting component with form of ring is inserted in the inner circumferential of described through hole.
5. the starter motor that is used for motor as claimed in claim 1, wherein, described inner bearing is set to can contact with described clutch inside.
6. the starter motor that is used for motor as claimed in claim 5, wherein, the end face of described inner bearing is towards the end face of described clutch inside and be set to can contact with the end face of described clutch inside.
7. the starter motor that is used for motor as claimed in claim 5, wherein, described inner bearing is arranged on the inside overlapping part with packing ring, can prevent that so described clutch inside from throwing off vertically against described clutch Outside and withdraw from.
8. the starter motor that is used for motor as claimed in claim 7, wherein, suppose under described output shaft is arranged at state in the described motor side of described center housing, gap width between the edge surface of described clutch inside and the edge surface of described inner bearing is set at e, and the thickness setting of described packing ring is f, then satisfies the given condition of formula e＜f.
9. the starter motor that is used for motor as claimed in claim 5 wherein, is provided with along the outwards outstanding flange portion of its diametric(al) in the end of the described motor side of described inner bearing.
10. the starter motor that is used for motor as claimed in claim 9, wherein, the internal surface of described flange portion is provided with chamfering.
11. the starter motor that is used for motor as claimed in claim 5, wherein, be provided with groove in the side opposite of described clutch inside along the periphery of described output shaft, and the part of described at least inner bearing is installed in the described groove of described clutch inside with motor.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2007-164061 | 2007-06-21 | ||
| JP2007164061A JP4572912B2 (en) | 2007-06-21 | 2007-06-21 | Starter |
| JP2007164061 | 2007-06-21 | ||
| JP2007269125A JP4831045B2 (en) | 2007-10-16 | 2007-10-16 | Starter |
| JP2007-269125 | 2007-10-16 | ||
| JP2007269125 | 2007-10-16 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101328854A true CN101328854A (en) | 2008-12-24 |
| CN101328854B CN101328854B (en) | 2010-11-17 |
Family
ID=40204827
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008101249675A Expired - Fee Related CN101328854B (en) | 2007-06-21 | 2008-06-20 | Starter for engines |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4572912B2 (en) |
| CN (1) | CN101328854B (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102297254A (en) * | 2010-06-23 | 2011-12-28 | 博格华纳公司 | Electromagnetic clutch disconnecting device used for accessory drive |
| CN102734036A (en) * | 2011-03-30 | 2012-10-17 | 德昌电机(深圳)有限公司 | Vehicle engine starting system |
| CN103032237A (en) * | 2011-10-06 | 2013-04-10 | 株式会社电装 | Starter |
| CN103216373A (en) * | 2013-04-24 | 2013-07-24 | 浙江远邦台技汽车电器有限公司 | Isolator device |
| CN104214036A (en) * | 2013-04-29 | 2014-12-17 | 罗伯特·博世有限公司 | Starting device for an internal combustion engine |
| CN104948372A (en) * | 2014-03-26 | 2015-09-30 | 株式会社电装 | Engine starter with torque variator |
| CN102734036B (en) * | 2011-03-30 | 2016-11-30 | 德昌电机(深圳)有限公司 | Start system for vehicle engine |
| CN110566390A (en) * | 2018-06-06 | 2019-12-13 | 通用汽车环球科技运作有限责任公司 | Vehicle engine electric starter motor with multiple speed ratios |
| CN111120175A (en) * | 2018-10-30 | 2020-05-08 | 浙江星月实业有限公司 | Gasoline engine |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4912501Y1 (en) * | 1970-10-28 | 1974-03-27 | ||
| US5898229A (en) * | 1995-09-18 | 1999-04-27 | Denso Corporation | Starter with improved one-way clutch structure |
| JP3550818B2 (en) * | 1995-09-18 | 2004-08-04 | 株式会社デンソー | Starter |
| JP3713800B2 (en) * | 1996-04-10 | 2005-11-09 | 株式会社デンソー | Starter |
| JP4161070B2 (en) * | 2003-06-11 | 2008-10-08 | 三菱電機株式会社 | Engine starter |
| JP4249596B2 (en) * | 2003-10-30 | 2009-04-02 | 澤藤電機株式会社 | Starter |
| JP4247683B2 (en) * | 2004-12-17 | 2009-04-02 | 株式会社デンソー | Planetary gear mechanism reduction starter |
-
2007
- 2007-06-21 JP JP2007164061A patent/JP4572912B2/en not_active Expired - Fee Related
-
2008
- 2008-06-20 CN CN2008101249675A patent/CN101328854B/en not_active Expired - Fee Related
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102297254A (en) * | 2010-06-23 | 2011-12-28 | 博格华纳公司 | Electromagnetic clutch disconnecting device used for accessory drive |
| CN102297254B (en) * | 2010-06-23 | 2015-12-02 | 博格华纳公司 | Magnetic clutch for accessory drive departs from connection set |
| CN102734036A (en) * | 2011-03-30 | 2012-10-17 | 德昌电机(深圳)有限公司 | Vehicle engine starting system |
| CN102734036B (en) * | 2011-03-30 | 2016-11-30 | 德昌电机(深圳)有限公司 | Start system for vehicle engine |
| CN103032237A (en) * | 2011-10-06 | 2013-04-10 | 株式会社电装 | Starter |
| CN103216373A (en) * | 2013-04-24 | 2013-07-24 | 浙江远邦台技汽车电器有限公司 | Isolator device |
| CN103216373B (en) * | 2013-04-24 | 2016-12-28 | 浙江远邦台技汽车电器有限公司 | Isolator device |
| CN104214036A (en) * | 2013-04-29 | 2014-12-17 | 罗伯特·博世有限公司 | Starting device for an internal combustion engine |
| CN104948372A (en) * | 2014-03-26 | 2015-09-30 | 株式会社电装 | Engine starter with torque variator |
| CN104948372B (en) * | 2014-03-26 | 2018-04-20 | 株式会社电装 | Engine starter with torque converter |
| CN110566390A (en) * | 2018-06-06 | 2019-12-13 | 通用汽车环球科技运作有限责任公司 | Vehicle engine electric starter motor with multiple speed ratios |
| CN111120175A (en) * | 2018-10-30 | 2020-05-08 | 浙江星月实业有限公司 | Gasoline engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4572912B2 (en) | 2010-11-04 |
| JP2009002237A (en) | 2009-01-08 |
| CN101328854B (en) | 2010-11-17 |
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Granted publication date: 20101117 |