CN202080114U - Variable speed transmission unit - Google Patents
Variable speed transmission unit Download PDFInfo
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- CN202080114U CN202080114U CN 201120168014 CN201120168014U CN202080114U CN 202080114 U CN202080114 U CN 202080114U CN 201120168014 CN201120168014 CN 201120168014 CN 201120168014 U CN201120168014 U CN 201120168014U CN 202080114 U CN202080114 U CN 202080114U
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Abstract
The utility model provides a variable speed transmission unit, which can not cause the problems of poor meshing of a speed change mechanism and interference on other parts when overlarge external input results in inclination of an output shaft. Parts of an input and an output shafts (8, 9) away from bearing embedded parts between the input and the output shafts (8a, 9a) along the axis direction are respectively supported by bearings on a unit casing (1) of the variable speed transmission unit; and the bearing embedded parts (8a, 9a) between the input and the output shafts are formed by enabling coaxial abutting ends (8a, 9a) to be correspondingly and rotatably inserted into each other; and an abutting face for limiting inclination of the input shaft (8) and the output shaft (9) through the abutting connection with at least one of the input and the output shafts (8, 9), and a gap (33) allowing the inclination of the input and the output shafts (8, 9) is formed between one shaft and the abutting face within the inclination range smaller than the limited inclination.
Description
Technical field
The utility model relates to a kind of speed change gear unit, in the driver element of each wheel that its electronlmobil that is used for travelling utilizing each wheel driving motor uses (be commonly called as and be the wheel hub electric motor unit) etc.
Background technology
As above-mentioned speed change gear unit, the technology of record in the current for example patent documentation 1 that has proposed to constitute as the wheel hub electric motor unit.
This wheel hub electric motor unit can utilize high-revolving small-sized drive motor by using retarder.In the case, use the retarder of compound planet gear formula, so have be coaxial docking the ground input shaft and the output shaft of configuration relatively as retarder.In axis direction one side (body inner side) of above-mentioned retarder, electrical motor is combined with above-mentioned input shaft, in axis direction opposite side (the car body outside), make wheel combine (with reference to patent documentation 1) with above-mentioned output shaft.
Be provided with on each drive wheels in the electronlmobil of above-mentioned wheel hub electric motor unit, when making direct motor drive, it is rotated in and utilizes retarder to slow down the back to the wheel transmission, can make vehicle '.
In addition, but when input shaft that disposes relatively on the ground that is coaxial docking of free rotary ground supporting retarder and output shaft, in order to shorten shaft size, the end that is coaxial docking of input shaft and output shaft can be inserted each other with the relative rotation mutually, thereby bearing fitting portion between the setting input and output shaft, and, will be from bearing fitting portion between this input and output shaft along axis direction away from input shaft and the position of output shaft, bearing is bearing on the wheel hub electric motor unit housing respectively, and carries out the supporting of this input and output shaft.
Patent documentation 1: TOHKEMY 2008-037355 communique (Fig. 1,7)
The utility model content
But, in the supporting construction of above-mentioned retarder input and output shaft, owing to make the end that is coaxial docking of its input shaft and output shaft each other can be chimeric with the relative rotation, will be from bearing fitting portion between this input and output shaft along axis direction away from input shaft and the position of output shaft respectively bearing be bearing on the unit housings, so can produce following problems.
That is, when turning driving etc., if import transverse force (load of overall width direction) from the wheel ground plane to wheel, then producing output shaft is fulcrum bevelled tendency with its unit housings side bearing portion.
The inclination (toppling over) of the output shaft that causes by above-mentioned wheel transverse force, through bearing fitting portion between above-mentioned input and output shaft and to the input shaft transmission, and input shaft is toppled over to cooresponding direction around its unit housings side bearing portion, bearing fitting portion place produces crossed-axes angle between input shaft and output shaft between above-mentioned input and output shaft.
Between input shaft and output shaft, utilize the retarder of following compound planet gear formula and drive combination.Therefore, the over-tilting of input and output shaft worsens the engagement between the rotation key element of retarder, causes durability between the parts to worsen and the generation of noise.
The utility model is exactly to propose in view of the above problems, its purpose is, a kind of speed change gear unit is provided, the problem that engagement between the rotation key element of the retarder iso-variable velocity mechanism of tilting to produce significantly between the input and output shaft worsens even it under the situation that applies excessive outside input such as wheel transverse force to output shaft, also can suppress or relative turning unit such as drive motor contacts with each other and caused.
For this purpose, speed change gear unit of the present utility model is as shown in following and constitute.
At first, illustrating becomes the speed change of prerequisite of the present utility model gear unit, it sets bearing fitting portion between input and output shaft, so that the end that is coaxial docking of input shaft and output shaft can be inserted with the relative rotation mutually, and, on unit housings, respectively bearing supporting input shaft and output shaft from bearing fitting portion between this input and output shaft along axis direction away from the position, utilize speed-changing mechanism to drive combination between input shaft and the output shaft.
Unique point of the present utility model is to constitute, in above-mentioned speed change gear unit, be provided with by with input shaft and output shaft at least one butt limit the bevelled bearing surface of input shaft and output shaft, and in than the little slant range of the inclination of restriction, between a described axle and bearing surface, form the bevelled gap of allowing input shaft and output shaft.
The effect of utility model
According to above-mentioned speed change gear unit of the present utility model, being tilted in the permissible range hour of, output shaft less to the input of the outside of output shaft effect, can utilize above-mentioned gap that input shaft and output shaft are tilted, on the other hand, externally the input become excessive, when output shaft tilts significantly, by be arranged in input shaft and the output shaft at least one on the bearing surface butt, thereby the inclination of restriction input shaft and output shaft.
Therefore, according to the utility model, even under the situation that applies excessive outside input such as wheel transverse force to output shaft, also can suppress because the problem that the relative turning unit of deterioration of the engagement between the rotation key element of the retarder iso-variable velocity mechanism of tilting to produce significantly between the input and output shaft or drive motor etc. contacts with each other and caused.Therefore, can prevent that not only the action of speed-changing mechanism etc. is bad, and can suppress the interference of relative turning unit, improve the durability of speed change gear unit.
Description of drawings
Fig. 1 is the vertical profile lateral plan of the speed change gear unit that constitutes as the wheel hub electric motor unit of the 1st related embodiment of the utility model of expression.
Fig. 2 is that detailed cross sectional view is amplified by the portion that wants of the wheel hub electric motor unit among Fig. 1.
Fig. 3 is the vertical profile lateral plan of the speed change gear unit that constitutes as the wheel hub electric motor unit of the 2nd related embodiment of the utility model of expression.
Fig. 4 is that detailed cross sectional view is amplified by the portion that wants of the wheel hub electric motor unit among Fig. 3.
Fig. 5 is the vertical profile lateral plan of the speed change gear unit that constitutes as the wheel hub electric motor unit of the 3rd related embodiment of the utility model of expression.
Fig. 6 is the amplification front elevation of the metal lining of the expression employed band bearing surface in wheel hub electric motor unit shown in Figure 5.
Fig. 7 is the figure of the inclination situation of input and output shaft of the limit of schematically representing output shaft wheel hub electric motor unit when toppling over, the 1st embodiment～the 3rd embodiment etc.
The specific embodiment
Below, based on embodiment shown in the drawings, describe embodiment of the present utility model in detail.
The structure of＜the 1 embodiment 〉
Fig. 1,2 illustrates the speed change gear unit of the 1st embodiment of the present utility model that constitutes as the wheel hub electric motor unit, and Fig. 1 is its vertical profile lateral plan, and Fig. 2 is that detailed cross sectional view is amplified by its portion that wants.
Shown in above-mentioned accompanying drawing, the wheel hub electric motor unit of present embodiment respectively is provided with one on the wheel all around of vehicles such as electronlmobil, have respectively: unit housings 3, electrical motor 4, compound planet gear formula retarder 5 (being designated hereinafter simply as " retarder ").
Unit housings 3 is made of following part: wheel hub electric motor unit housing main body 1; Back cover 2, its rear side in this housing body 1 (body inner side) utilizes bolt to assemble at a plurality of positions; Sealing element 30, its front side in housing body 1 (the car body outside) utilizes bolt to assemble at a plurality of positions.In the inside of unit housings 3, assemble and accommodate electrical motor 4 and retarder 5.In addition, electrical motor 4 and retarder 5 are equivalent to driver element of the present utility model, and sealing element is equivalent to sealing of the present utility model.
Electrical motor 4 is made of following part, that is: circular stator 6, the chimeric and fastening setting of circular inner peripheral surface of itself and housing body 1; Rotor 7, it has the gap of radial direction with respect to the inner peripheral surface of above-mentioned circular stator 6, rotatably with circular stator 6 concentric arrangement.
Retarder 5 is equivalent to the speed-changing mechanism in the utility model, is made of i.e.: input shaft 8 and output shaft 9, its ground configuration relatively that is coaxial docking in the present embodiment following part; Sun gear 11, the outside face near the end 8a that is coaxial docking of itself and input shaft 8 front sides is integrally formed; Ring gear 12, it is in the radial direction of this sun gear 11 outside, and with vertically near output shaft 9 sides and the state of concentric arrangement is fixed on the housing body 1; A plurality of (being 3 in the present embodiment) ladder planet pinion gears (ladder miniature gears) 13, its by with sun gear 11 ingears big footpath pinion part 13a and integrally formed and constitute with Ring gear 12 ingear path pinion part 13b with this big footpath pinion part 13a; And carriage 14, it can support these ladder planet pinion gears 13 with rotating freely.
On the other hand, the front part of output shaft 9 to extending with the opposite sense (front side) of input shaft 8, from the front side end of housing body 1, be that the opening of sealing element 30 protrudes, is protruded the position at this from retarder 5, combines with wheel 15 shown in as described later.
Above-mentioned input shaft 8 and output shaft 9, by the end 8a that is coaxial docking with input shaft 8, insert among the hole 9b on the end 9a that is coaxial docking that is formed on output shaft 9 rear sides, at them the bearing 16 that can use needle bearing is set between the two, thereby sets bearing fitting portion between the input and output shaft that can support mutually with the relative rotation each other.In addition, in the present embodiment, above-mentioned when chimeric, bearing 16 is carrying out this chimeric connection with the roughly the same axis direction position of sun gear 11 and the engagement of the 13a of large diameter gear portion.
From the bearing 16 that forms bearing fitting portion between this input and output shaft respectively to axis direction rear side, front side away from input shaft 8 and the position separately of output shaft 9, utilization can be used the bearing 17 of ball bearing of main shaft and can use the entad bearing 18 of thrust bearing of multiple row, and bearing is bearing on the unit housings 3.In addition, bearing 18 is arranged between the periphery of interior week of end cap 19 and wheel nave 21, wherein, and chimeric connection of salient of the output shaft 9 that the front opening of these end cap 19 inaccessible housing body 1, this wheel nave 21 and front opening from housing body 1 protrude.
In the present embodiment, the carrier frame plate 14a of front side is in the rear end approaching with input shaft 8 of output shaft 9, and is integrally formed with output shaft 9, as the output rotating member of retarder 5.Therefore, carriage 14 and ladder planet pinion gear 13 combine with output shaft 9 to input shaft 8 sides from output shaft 9 with stretching out.
Below, the combined structure that wheel 15 combines with output shaft 9 is described.
When wheel 15 is installed, in running through the bolt hole of its wheel disc, insert wheel bolt 23 and carry out aligned in position, and make the side closed contact of this wheel disc and brake disc 22, under this state, by making wheel bolt 23 and wheel nut 24 fastening screwing togather, thereby carry out the installation of wheel 15 with respect to output shaft 9.
Between the peripheral end and housing body 1 of the support portion 21a that is disposed at its outside on the wheel nave 21 via bearing 18, utilize the circular sealing element of bolted 30, it extends towards input shaft 8 to the radial direction inboard.Interior all lateral bending of sealing parts 30 is bent and fixing oil sealing 31 makes its front end contact with the outer peripheral face of input shaft 9.Thus, utilize the inside and outside separation of oil sealing 31 with unit housings 3, therefore, will be separated with its exterior bearing 18 by the driver element that electrical motor 4 and retarder 5 constitute, the oil and the grease that can suppress are separately sneaked into.
At interior all side ends of sealing element 30, fastening metal lining 32 cylindraceous.The inner peripheral surface of this metal lining 32 is relative with the outer peripheral face of input shaft 8, has gap 33 along radial direction.The size in the gap 33 of this ring-type as described later shown in, be set at the size in the following permissible range, promptly, this permissible range is, acting on excessive input from the outside to output shaft 9, making output shaft 9 is that fulcrum is when tilting significantly with the bearing 18 of this housing body 1, make the outer peripheral face of output shaft 9 and inner peripheral surface (bearing surface) butt of metal lining 23, make output shaft 9 and input shaft 8 not produce, retarder and other circumferential component are not caused harmful effect than the bigger inclination of the present situation (limit leaning angle).
In the present embodiment, the size in this gap 33 for example is illustrated in figure 7 as about 0.25mm.Under the situation of the 1st embodiment, compare with the 2nd, the 3rd embodiment described later, it is the most approaching that bearing surface and output shaft 9 bear the bearing 18 that becomes fulcrum when the outside is imported, therefore make the radial direction size decreases in gap 33, on this basis, fluctuation from processing, assembling aspect also needs to set lessly.In addition, in Fig. 1,2,, the exaggeration of the size in gap 33 is amplified and describe for easy to understand.
The bearing surface of metal lining 23 is positioned at wheel 15 sides of oil sealing 31 from this figure as can be known.
The wheel hub electric motor unit of formation as noted above works shown in following.
The effect of＜the 1 embodiment 〉
If to stator 6 energising of electrical motor 4, then be used to the rotor 7 of electrical motor 4 is rotated driving from the electromagnetic force of stator, this rotary driving force transmits via the sun gear 11 of input shaft 8 to retarder 5.
Thus, sun gear 11 makes 13 rotations of ladder planet pinion gear via the 13a of large diameter gear portion, but at this moment Gu Ding Ring gear 12 works as the antagonistic force portion of bearing, therefore, and the planet motion that ladder planet pinion gear 13 makes the 13b of small-diameter gear portion roll along Ring gear 12.
The planet motion of above-mentioned ladder planet pinion gear 13 transmits to output shaft 9 via carriage 14, makes output shaft 9 to the direction identical with input shaft 8 rotation of slowing down.
Utilize above-mentioned gearing, retarder 5 makes the rotation that applies to input shaft 8 from electrical motor 4, slows down with the ratio of being determined by the number of teeth of the number of teeth of sun gear 11 and Ring gear 12, and transmits to output shaft 9.
Transmit to wheel 15 via wheel nave 21 that combines with it and wheel bolt 23 to the rotation that output shaft 9 applies, can make vehicle '.
In addition, when car brakeing, by by brake plate 25 from axis direction both sides cramping brake disc 22, thereby make wheel 15 friction brakinges, can realize its intended purposes.
Under the less situation of leaning angle (output shaft 9 is with respect to the straight line angulation that links bearing 17,18) less at common straight-line travelling etc., output shaft 9, utilize the leaning angle (input shaft 8 is with respect to the straight line angulation of binding bearing 17,18) of the input shaft 8 that bearing fitting portion and output shaft 9 link between input and output shaft also less to the transverse force that wheel 15 applies.Therefore, in the case, can not hinder the rotation of retarder and electrical motor 4 etc., can successfully make wheel 15 rotations.
On the other hand, becoming leaning angle big, output shaft 9 in negotiation of bends etc. to the transverse force that wheel 15 applies becomes under the big situation, the outer peripheral face of output shaft 9 not with the scope of the interior all side bearing surface butts that are arranged at the metal lining 32 on the sealing element 30 in, guarantee the gap 33 between them.Therefore, in this scope, can not produce problems such as following, that is, the engagement of reducer gear deteriorates to and exceeds permissible range, or other circumferential component interfere and the effect of wheel hub electric motor unit is caused obstacle, and its durability is worsened.
In addition, under the leaning angle situation that further change is big of output shaft 9, the outer peripheral face of output shaft 9 and the interior all side bearing surface butts that are arranged at the metal lining 32 on the sealing element 30, the gap 33 of the part of their institute's butts becomes zero.Its result, output shaft 9 is crustal inclination by a larger margin, its result, the inclination that has also suppressed the input shaft 8 that links at the end 8a that is coaxial docking, 9a place and output shaft 9 becomes big by a larger margin.Because the inclination limit leaning angle that is suppressed in as noted above of above-mentioned input and output shaft 8,9, so can not produce problems such as following in the case yet, promptly, the engagement of reducer gear deteriorates to and exceeds permissible range, or other circumferential component interfere and the effect of wheel hub electric motor unit are caused obstacle, and its durability is worsened.
Fig. 7 schematically represents to be in the relation of input and output shaft 8,9 under the situation of above-mentioned limit leaning angle etc.The first half at Fig. 7, utilize line chart to describe to represent the relation of input-output line L81, the L91 etc. of the input and output shaft 8,9 among the 1st embodiment, in addition, in the latter half of Fig. 7, utilize line chart to describe not exist the structural element of the wheel hub electric motor unit under the situation of leaning angle.
As shown in the drawing, under the situation of limit leaning angle, go up perk in the figure left by the output shaft 9 that line L91 represents, with the bearing surface butt (shown in this figure A) of the metal lining 32 of sealing element 30, suppress to become bigger leaning angle.At this moment, butt position A is that zero situation begins the about 0.25mm of side shifting outside radial direction from leaning angle.On the other hand, bearing fitting portion place goes up perk to the right in the figure by the input shaft of being represented by line L81 8 that bearing 16 links between input and output shaft, suppresses its allowable angle of inclination.
Therefore, in the wheel hub electric motor unit of the 1st embodiment, following situation can not appear, promptly, the engagement of reducer gear is deteriorated to exceed permissible range, or other circumferential component interfere and the effect of wheel hub electric motor unit is caused obstacle, its durability is worsened.In addition, as shown in the drawing, the center-point G2 of the center-point G1 of bearing 16, sun gear 11, path miniature gears 13a etc., after input and output shaft 8,9 run-off the straights, its result respectively as 16 ', mobile slightly vertically shown in G1 ', the G2 ' etc.
The effect of＜the 1 embodiment 〉
More than, shown in explanation, the speed change gear unit of the 1st embodiment can obtain following cited effect.
(1) owing to constitutes inner peripheral surface at the metal lining 32 at the inner peripheral surface place of the sealing element 30 that is anchored on unit housings 3, formation is by limiting the bevelled bearing surface of this axle with output shaft 9 butts, in than the little slant range of the inclination of this restriction, between output shaft 9 and bearing surface, form the bevelled gap 33 of allowing input shaft 8 and output shaft 9, even so and under the bevelled situation to the excessive outside input of output shaft 9 effect, from input and output shaft 8,9 leaning angle is the radial direction miles of relative movement K1 of zero bearing surface till becoming limit leaning angle, be suppressed to the size in gap 33, can prevent following situation, promptly, the engagement of reducer gear deteriorates to above permissible range, or other circumferential component interfere and the effect of wheel hub electric motor unit are caused obstacle, and its durability is worsened.Therefore, can also do not needed to worry the problems referred to above, correspondingly be increased the additional effect of Design freedom.On the other hand, owing to constitute and between output shaft 9 and bearing surface, form the bevelled gap 33 of allowing input shaft 8 and output shaft 9, so under common motoring condition (not acting on the state of excessive outside input), the axle not with this face butt, therefore, allow toppling over of the axle that causes by the vibration that is produced etc.Therefore, under common motoring condition, can prevent the rotation situation about interfering of axle or produce the situation of abnormal sound.
(2), enter driver element inside so can suppress the impurity that the outer peripheral face butt because of bearing surface and output shaft 9 produced because at the outer setting bearing surface of the driver element that constitutes by retarder and electrical motor 4.
(3) because the oil sealing 31 that will be installed on the sealing element 30 is arranged on the driver element side with respect to bearing surface, so can prevent reliably from bearing surface or the outside impurity that enters to driver element inside.
(4) owing to utilize metal lining 32 to form bearing surfaces, so on one side can allow the rotation of output shaft 9, Yi Bian its allowable angle of inclination is limited in the limit leaning angle.
Therefore, in the 1st embodiment, at the 13a of large diameter gear portion of ladder planet pinion gear 13 and the engaging piece place between the sun gear 11 on the input shaft 8, the shoulder grafting that can produce gear hardly touches (shoulder touch), the worry that the effect to retarder 5 causes obstacle or its durability is reduced can be eliminated, but also the worry that relative turning unit is contacted with each other can be eliminated reliably.
The structure of＜the 2 embodiment 〉
Below, the 2nd embodiment that the utility model is related is described.
The speed change gear unit of the 2nd embodiment of the present utility model that Fig. 3,4 expressions and the 1st embodiment constitute as the wheel hub electric motor unit in the same manner, Fig. 3 is its vertical profile lateral plan, Fig. 4 is that detailed cross sectional view is amplified by its portion that wants.
In these accompanying drawings, for play with Fig. 1,2 in the part of same function, mark same numeral and illustrating, here, the repeat specification of identical component part is avoided in only explanation and the different part of the 1st embodiment shown in Fig. 1,2.
Present embodiment replaces the 1st embodiment on the inner peripheral surface will be arranged on sealing element with the metal lining of bearing surface, bearing surface is arranged on the output shaft side this point different with the 1st embodiment.
Therefore, in the present embodiment, with the 1st embodiment in the same manner, for input shaft 8 and output shaft 9, the hole 9b of end 8a on the end 9a that is coaxial docking that is formed on output shaft 9 rear sides that be coaxial docking of input shaft 8 inserted, by the bearing 16 that can use needle bearing is set at them, thereby set bearing fitting portion between the input and output shaft that can support mutually with the relative rotation each other between the two.
In addition, on the inner peripheral surface that is formed at the hole 9b on the end 9a that is coaxial docking of output shaft 9, circular metal lining 34 is fixed on bearing 16 compares on the forward position.The inner peripheral surface of metal lining 34 constitutes bearing surface, its with the end 8a that is coaxial docking and the front part that above-mentioned bearing 16 is compared of input shaft 8 between, form the gap 33 of ring-type along radial direction.In addition, in the present embodiment, the limit leaning angle of output shaft 9 is compared with the situation of the 1st embodiment and is set greatlyyer.In addition, because bearing surface is compared with bearing 18 near rear side, so the gap 33 among the 2nd embodiment for example is set at about 0.7mm as shown in Figure 7.
The effect of＜the 2 embodiment 〉
In the 2nd embodiment shown in above-mentioned Fig. 3,4, the rotary driving force of electrical motor 4 (rotor 7) transmits to wheel 15 via the sun gear 11 of input shaft 8, retarder 5 and ladder planet pinion gear 13, output shaft 9 successively, can make vehicle '.
Under the less situation of common leaning angles less to the transverse force that wheel 15 applies, output shaft 9 such as straight-line travelling, utilize the leaning angle of the input shaft 8 that bearing fitting portion and output shaft 9 links between input and output shaft also less.Therefore, in the case, can not hinder the rotation of retarder and electrical motor 4 etc., can successfully make wheel 15 rotations.
On the other hand, becoming leaning angle big, output shaft 9 in negotiation of bends etc. to the transverse force that wheel 15 applies becomes under the big situation, on the bearing surface of the metal lining 34 of output shaft 9, the outer peripheral face of the end 8a that is coaxial docking of input shaft 8 not with the scope of bearing surface butt in, guarantee the gap 33 between them.Therefore, in this scope, can not produce problems such as following, that is, the engagement of reducer gear deteriorates to and exceeds permissible range, or other circumferential component interfere and the effect of wheel hub electric motor unit is caused obstacle, and its durability is worsened.
In addition, under the leaning angle of output shaft 9 further becomes big situation, interior all side bearing surface butts of the metal lining 34 in the outer peripheral face of the end 8a that is coaxial docking of input shaft 8 and the hole 9b that is arranged at output shaft 9, the gap 33 of the part of their institute's butts becomes zero.Its result, output shaft 9 is crustal inclination by a larger margin, its result, the inclination that has also suppressed the input shaft 8 that links at the end 8a that is coaxial docking, 9a place and output shaft 9 becomes big by a larger margin.Because the inclination limit leaning angle that is suppressed in as noted above of above-mentioned input and output shaft 8,9, so can not produce problems such as following in the case yet, promptly, the engagement of reducer gear deteriorates to and exceeds permissible range, or other circumferential component interfere and the effect of wheel hub electric motor unit are caused obstacle, and its durability is worsened.
Fig. 7 schematically represents to be in the relation of input and output shaft 8,9 under the situation of above-mentioned limit leaning angle etc., under the situation of limit leaning angle, go up perk in the figure left by the output shaft 9 that line L92 represents, make the bearing surface butt (shown in this figure B) of metal lining 34 of be coaxial docking the end 8a and the output shaft 9 of input shaft 8, suppress to become bigger leaning angle.At this moment, butt position B is that zero situation begins the about 0.7mm of side shifting outside radial direction from leaning angle.On the other hand, bearing fitting portion place goes up perk to the right in the figure by the input shaft of being represented by line L81 8 that bearing 16 links between input and output shaft, suppresses its allowable angle of inclination.In addition, bearing 16 is positioned at by 16 " expression the position.
Therefore, in the wheel hub electric motor unit of the 2nd embodiment, following situation can not appear, promptly, the engagement of reducer gear is deteriorated to exceed permissible range, or other circumferential component interfere and the effect of wheel hub electric motor unit is caused obstacle, its durability is worsened.
The effect of＜the 2 embodiment 〉
From foregoing as can be known, the wheel hub electric motor unit of the 2nd embodiment also has following effect except the above-mentioned effect (1) of the 1st embodiment.
(5) because being coaxial docking between the 8a of end at the input shaft 8 that is coaxial docking end 9a and in being formed at hole 9b, inserts of output shaft 9, comparing the bearing surface that the front side is provided with metal lining 34 with bearing 16, entering driver element inside so can be suppressed at the impurity of bearing surface place generation.
(6) in addition, be coaxial docking between end 8a, the 9a owing to metal lining 34 is configured in, so become compact structure, it is big that the Design freedom of wheel hub electric motor unit becomes.
＜the 3 embodiment 〉
Below, the 3rd embodiment that the utility model is related is described.
Fig. 5 is the vertical profile lateral plan of the speed change gear unit of the 3rd embodiment of the present utility model that constitutes as the wheel hub electric motor unit in the same manner with the 1st embodiment of expression, and Fig. 6 is the amplification front elevation of the metal lining of the band bearing surface that uses in the speed change gear unit of the 3rd embodiment.
In these accompanying drawings, for play with Fig. 1,2 in the part of same function, mark same numeral and illustrating, here, the repeat specification of identical component part is avoided in only explanation and the different part of the 1st embodiment shown in Fig. 1,2.
In the 3rd embodiment, the sun and planet gear and the 1st embodiment that constitute retarder constitute in the same manner.That is, retarder has sun gear 11, Ring gear 12, miniature gears carriage 14, and it can support ladder miniature gears 13 with rotating freely.Miniature gears carriage 14 has: front side carrier frame plate 14a, and it extends from the outer circumferential radial direction outside of the end 9a that is coaxial docking of output shaft 9 in the front side and integrally formed; Rear side carrier frame plate 14b, it is arranged on rear side; And pinion shaft 14c, it links between them, can support ladder miniature gears 13 with rotating freely.The axle that pinion shaft 14c five equilibrium is configured in input and output shaft 8,9 is 3 positions of pivoting at center, has axial oilhole and connected radial direction oilhole, supplies with oil to the needle bearing that supports the ladder miniature gears.In addition, this axial oilhole is connected with radial direction oilhole on being formed on rear side carrier frame plate 14b, and all within it side openings portion accepts from the oil of the ejection oilhole ejection of input shaft 8.
In interior all sides of this rear side carrier frame plate 14b, utilize welding to wait the metal lining 35 of mounting circular ring shape.The inner peripheral surface of this metal lining 35 constitutes bearing surface, between the part of this inner peripheral surface and the input shaft 8 relative with it, forms gap 33 along radial direction.In the 3rd embodiment, in order to obtain the limit leaning angle identical, so the size in gap 33 is set at 0.6mm as shown in Figure 7 with the 2nd embodiment.
Metal lining 35 forms circular as shown in Figure 6, forms oilhole 35a accordingly with the position of pinion shaft 14c.All sides were compared with the oilhole of rear side carrier frame plate 14b and are carried out hole enlargement and acceptant oil in this oilhole 35a made, and along with outside radial direction, undergauge is to the degree of the oilhole diameter of rear side carrier frame plate 14b.In addition, can on metal lining 35, form,, also can form the oil groove of Zhou Fangxiang in order to carry out the supply of oil at the easy oilhole of lateral bracket plate 14b backward of outer circumferential side along the oily dump tank of the circumference of inner peripheral surface.
The effect of＜the 3 embodiment 〉
In the wheel hub electric motor unit of the 3rd embodiment, with the 1st, the 2nd embodiment in the same manner, in the inclination of output shaft 9 hour, between the metal lining 35 of input shaft 8 and rear side carrier frame plate 14b, guarantee gap 33, can successfully move.
On the other hand, if it is big that the inclination of output shaft 9 becomes, then the input shaft 8 that links via the bearing 16 of be coaxial docking end 8a, 9a tilts, when reaching capacity leaning angle, the inner peripheral surface of the metal lining 35 of the periphery of input shaft 8 and rear side carrier frame plate 14b, i.e. bearing surface butt.Thus, suppress input shaft 8 inclination by a larger margin, also suppress the output shaft 9 that links via bearing 16 and input shaft crustal inclination by a larger margin.Its result can prevent the problems such as interference of bad and other parts of the engagement of retarder.
Fig. 7 illustrates this situation, and input shaft of being represented by line L83 8 and the output shaft of being represented by line L93 9 are identical with line L82, the L92 of the 2nd embodiment.From the leaning angle of input and output shaft 8,9 is the radial direction miles of relative movement K3 of zero bearing surface till becoming limit leaning angle, is suppressed in the size in gap 33.In addition, by making the line L93 that is in output shaft 9, thereby determine limit leaning angle to the bearing surface of the metal lining 35 of the rear side carrier frame plate 14b of the position that rear side prolongs and the outer peripheral face butt of input shaft 8.Therefore, in the case, the line L93 of bearing surface upper left perk in Fig. 7 and the line L83 of upper right perk are along position butt that radial direction separates significantly.Relative therewith, in the 1st embodiment, bearing surface is in and bearing 18 immediate positions, in addition, in the 2nd embodiment, bearing surface is in the bearing surface of the 1st embodiment to be compared further from bearing 18, but compares more the position near bearing 18 with the bearing surface of the 3rd embodiment.Therefore, with respect to the identical inclination of output shaft 9, the radial direction distance between the metal lining 32,34,35 of bearing surface and its butt side, maximum in the 3rd embodiment.This expression is maximum in the 3rd embodiment with respect to the bevelled sensitivity of output shaft 9.
The effect of＜the 3 embodiment 〉
From foregoing as can be known, the wheel hub electric motor unit of the 3rd embodiment can also obtain following effect except the above-mentioned effect (1) of the 1st embodiment, (4).
(7) owing on the inner peripheral surface of the metal lining 35 of the inner peripheral surface that is arranged at rear side carrier frame plate 14b, constitute bearing surface, make the outer peripheral face and the bearing surface butt of the input shaft 8 that links via bearing 16 and output shaft 9, so uprise with respect to the bevelled sensitivity of output shaft 9.Therefore, have and advantage such as design easily.
Based on the foregoing description the utility model has been described, but the utility model is not limited to the foregoing description, also comprises and implemented following various examples after changing.
Unit housings 3 is made of housing body 1, back cover 2, sealing element 30 in the various embodiments described above, but does not need to be defined in this, for example can certainly make sealing element 30 and housing body 1 integrally formed.
In addition, metal lining 32,34,35 is arranged on the opposite side (housing body 1 or miniature gears carriage 14 etc.) of axle 8,9 in the position that the outer peripheral face with axle 8,9 separates, but also can be arranged on axle 8,9 sides in contrast, makes its outer peripheral face and opposite side butt.
In addition, in the various embodiments described above, on metal lining 32,34,35, form bearing surface, but also can use other forms of bearing, the outer peripheral face of the inner peripheral surface of its inner ring side or outer ring as bearing surface, also can be adopted the parts outside the bearing.
In the various embodiments described above, all with the speed change gear unit as the wheel hub electric motor unit of electronlmobil and constitute, but be not limited to this, be applicable to all industrial gear units certainly.
In addition, in the various embodiments described above, the situation of using compound planet gear formula retarder as the speed-changing mechanism in the speed change gear unit has been described, but be not limited to this as the speed-changing mechanism in the speed change gear unit, can use all types of speed-changing mechanisms (comprising speed increasing mechanism), in the case, certainly by using above-mentioned design of the present utility model to obtain identical action effect.
Claims (6)
1. speed change gear unit, it sets bearing fitting portion between input and output shaft, so that the end that is coaxial docking of input shaft and output shaft can be inserted with the relative rotation mutually, and, on unit housings, respectively bearing supporting input shaft and output shaft from bearing fitting portion between this input and output shaft along axis direction away from the position
Utilize speed-changing mechanism to drive combination between described input shaft and the described output shaft,
It is characterized in that,
Be provided with by with described input shaft and described output shaft at least one butt limit the bevelled bearing surface of described input shaft and described output shaft, and,
In than the little slant range of the inclination of described restriction, between a described axle and described bearing surface, form the bevelled gap of allowing described input shaft and described output shaft.
2. speed change gear unit according to claim 1 is characterized in that,
Described speed change gear unit has unit housings, and this unit housings is accommodated driver element, and this driver element has described speed-changing mechanism and drives the electrical motor of this speed-changing mechanism,
Described bearing surface is arranged on the sealing of described unit housings, and sealing portion is configured between the hub bearing and described driver element of the wheel nave that can rotate freely the ground support wheel.
3. speed change gear unit according to claim 2 is characterized in that,
The described sealing of described unit housings has oil sealing, and this oil sealing separates described driver element with described hub bearing,
This oil sealing is arranged on described driver element side with respect to described bearing surface.
4. speed change gear unit according to claim 1 is characterized in that,
Being coaxial docking between the end of the described input shaft of described bearing surface bearing fitting portion between described input and output shaft and described output shaft is arranged on in this end that is coaxial docking.
5. speed change gear unit according to claim 1 is characterized in that,
Described speed-changing mechanism has: sun gear, Ring gear, planet pinion gear and the carriage that can support planet pinion gear with rotating freely,
Described bearing surface is arranged on the described carriage.
6. according to each described speed change gear unit in the claim 1 to 5, it is characterized in that,
Described bearing surface is the outer peripheral face or the inner peripheral surface of bearing.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010115907A JP5598085B2 (en) | 2010-05-20 | 2010-05-20 | Variable speed transmission unit |
| JP2010-115907 | 2010-05-20 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202080114U true CN202080114U (en) | 2011-12-21 |
Family
ID=45340764
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201120168014 Expired - Fee Related CN202080114U (en) | 2010-05-20 | 2011-05-20 | Variable speed transmission unit |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP5598085B2 (en) |
| CN (1) | CN202080114U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103375592A (en) * | 2012-04-24 | 2013-10-30 | 西华大学 | External driving type middle rotating ring mechanical seal with speed change gear |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04243751A (en) * | 1991-01-24 | 1992-08-31 | Canon Inc | Device for conveying sheet-shaped member |
| JP3465120B2 (en) * | 1994-08-23 | 2003-11-10 | 日本車輌製造株式会社 | Power transmission device using planetary roller transmission |
| JP5023606B2 (en) * | 2006-08-09 | 2012-09-12 | 日産自動車株式会社 | Electric drive |
| JP5205074B2 (en) * | 2008-02-12 | 2013-06-05 | 本田技研工業株式会社 | In-wheel motor for vehicles |
| JP5111240B2 (en) * | 2008-05-29 | 2013-01-09 | 株式会社不二工機 | Gear support device in planetary gear type reduction gear |
-
2010
- 2010-05-20 JP JP2010115907A patent/JP5598085B2/en not_active Expired - Fee Related
-
2011
- 2011-05-20 CN CN 201120168014 patent/CN202080114U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103375592A (en) * | 2012-04-24 | 2013-10-30 | 西华大学 | External driving type middle rotating ring mechanical seal with speed change gear |
Also Published As
| Publication number | Publication date |
|---|---|
| JP5598085B2 (en) | 2014-10-01 |
| JP2011241936A (en) | 2011-12-01 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20111221 Termination date: 20160520 |