CN104179944B - Power transmission apparatus for vehicle - Google Patents

Power transmission apparatus for vehicle Download PDF

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Publication number
CN104179944B
CN104179944B CN201410174303.5A CN201410174303A CN104179944B CN 104179944 B CN104179944 B CN 104179944B CN 201410174303 A CN201410174303 A CN 201410174303A CN 104179944 B CN104179944 B CN 104179944B
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China
Prior art keywords
output shaft
bearing
ring
parts
connector
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CN201410174303.5A
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CN104179944A (en
Inventor
牧美里
垣内浩树
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Honda Motor Co Ltd
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Honda Motor Co Ltd
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Priority to JP2013111125A priority Critical patent/JP6112661B2/en
Priority to JP2013-111125 priority
Application filed by Honda Motor Co Ltd filed Critical Honda Motor Co Ltd
Publication of CN104179944A publication Critical patent/CN104179944A/en
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Publication of CN104179944B publication Critical patent/CN104179944B/en
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H29/00Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
    • F16H29/02Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts
    • F16H29/04Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts in which the transmission ratio is changed by adjustment of a crank, an eccentric, a wobble-plate, or a cam, on one of the shafts

Abstract

A kind of power transmission apparatus for vehicle.The number of components of the bearing of the surrounding of the output shaft of the power transmission apparatus for vehicle with crank-type variable-speed unit can be cut down.It possesses the output shaft block bearing (27 that output shaft (12) is supported on case of transmission (26), 28), with by each swing connector (22) axial two-side supporting in the swing connector supporting bearing (34 of output shaft (12), 34 '), output shaft block bearing (27, 28) inner ring (41, 44), with swing connector supporting bearing (34 ') with this inner ring (41, 44) adjacent inner ring (36 ') forms as one, therefore, compared with the situation of the inner ring utilizing different parts composition output shaft block bearing and the inner ring of swing connector supporting bearing, number of components can not only be cut down and make the axial dimension of power transmission apparatus for vehicle minimize, output shaft block bearing can also be improved and swing alignment and the rigidity of connector supporting bearing.

Description

Power transmission apparatus for vehicle
Technical field
The present invention relates to the power transmission apparatus for vehicle possessing multiple crank-type variable-speed unit, the plurality of crank-type becomes Speed unit is transferred to output shaft after the rotation speed change of the power shaft being connected with driving source.
Background technology
In order to the rotor of motor is rotatably freely supported on stator, according to such knot known in following patent document 1 Structure: circle is fixed on another circle of the thrust ball bearing of rotor and the radial direction ball axle that the axle of rotor is supported on stator The outer ring held abuts.
Patent document 1: Japanese Patent Publication 3-3155 publication
, around the output shaft of power transmission apparatus for vehicle possessing multiple crank-type variable-speed unit, except Output shaft is supported on outside the bearing of case of transmission, in addition it is also necessary to by axial the two of the swing connector of multiple variable-speed units Side bearing, in each pair bearing of output shaft, owing to so multiple bearing is arranged in the periphery of output shaft, accordingly, there exist portion Number of packages amount increases, the axial dimension of power transmission apparatus for vehicle maximizes such problem.
Summary of the invention
The present invention completes in view of aforesaid situation, its object is to cut down the vehicle with crank-type variable-speed unit Number of components with the bearing of the surrounding of the output shaft of power transmission.
In order to reach above-mentioned purpose, according to the invention described in technical scheme 1, a kind of vehicle power transmission dress is proposed Put, wherein, the axially aligned setting of multiple variable-speed units, described variable-speed unit by with the power shaft that is connected of the source of driving Rotating after speed change and be transferred to output shaft, described variable-speed unit possesses respectively: eccentric part, described eccentric part relative to The eccentricity variable of the axis of described power shaft, and described eccentric part rotates together with this power shaft;Swing connector, Described swing connector is supported on described output shaft in the way of rotating against freely;One-way clutch, described unidirectional from Clutch is arranged between described output shaft and described swing connector;And connecting rod, described connecting rod connects described eccentric part With described swing connector, described power transmission apparatus for vehicle is characterised by, described power transmission apparatus for vehicle Possessing: output shaft block bearing, described output shaft is supported on case of transmission by it;With swing connector supporting bearing, Described swing connector supporting is propped up by it in described output shaft, inner ring and the described swing connector of output shaft block bearing The inner ring adjacent with this inner ring holding bearing forms as one.
It addition, according to the invention described in technical scheme 2, propose a kind of power transmission apparatus for vehicle, its feature exists In, on the basis of the structure of technical scheme 1, described output shaft block bearing is the roller bearing possessing roller, institute The inner ring stating output shaft block bearing possesses: the 1st parts, and it is for described roller rolls;With a pair the 2nd parts, it Be arranged in the axial both sides of described 1st parts, and their end surface supporting is in described roller, described 2nd parts with The inner ring of described swing connector supporting bearing forms as one.
It addition, according to the invention described in technical scheme 3, it is proposed that a kind of power transmission apparatus for vehicle, its feature It is, at least one party and the described 1st on the basis of the structure of technical scheme 2, in the pair of 2nd parts The lubrication groove extending radially through described inner ring it is formed with between parts.
It addition, the eccentric disc 18 of embodiment is corresponding to the eccentric part of the present invention, the ball bearing 27 of embodiment With the output shaft block bearing that roller bearing 28 corresponds to the present invention, the radical-thrust ball bearing 34 ' of embodiment is corresponding In the swing connector supporting bearing of the present invention, the engine E of embodiment is corresponding to the driving source of the present invention.
According to the structure of technical scheme 1, when eccentric part and the power shaft that is connected with driving source rotate integratedly, one The connecting rod that end is connected with eccentric part moves back and forth, and the swing connector being connected with the other end of connecting rod is carried out back and forth Swing.When swinging connector and swinging to a direction, it is arranged in output shaft and the one-way clutch swung between connector Device engages, when swinging connector and swinging in the other direction, and described one-way clutch debonding, thus, input The rotation of axle is transferred to output shaft off and on.Multiple variable-speed units alternately transmit driving force with separating the time difference, thus Output shaft rotates continuously.When the offset making eccentric part changes, the reciprocating stroke change of connecting rod, thus Make the stroke change of the oscillating motion of swing connector, thus, the anglec of rotation change of output shaft, power shaft and output shaft Between gear ratio be changed.
Due to possess the output shaft block bearing that output shaft is supported on case of transmission and will swing connector supporting in The swing connector supporting bearing of output shaft, the inner ring of output shaft block bearing and swing connector supporting bearing with The inner ring that this inner ring is adjacent forms as one, therefore, from utilize different parts constitute output shaft block bearing inner ring and The situation of the inner ring swinging connector supporting bearing is compared, and can not only cut down number of components and make vehicle power transmit The axial dimension miniaturization of device, additionally it is possible to improve output shaft block bearing and swing the alignment of connector supporting bearing And rigidity.
It addition, according to the structure of technical scheme 2, output shaft block bearing is the roller bearing possessing roller, output shaft The inner ring of block bearing possesses: the 1st parts, and it is for roller rolls;With a pair the 2nd parts, they are arranged in the 1st The axial both sides of parts, and their end surface supporting is in roller, the 2nd parts and the inner ring swinging connector supporting bearing Forming as one, therefore, the inner ring being in the past made up of two parts becomes three parts, and number of components adds one Individual, but, swing the inner ring of connector supporting bearing owing to need not adjacent two, therefore, it is possible to altogether make portion Number of packages amount cuts down one.
It addition, according to the structure of technical scheme 3, due at least one party in a pair the 2nd parts and the 1st parts it Between be formed with the lubrication groove extending radially through inner ring, therefore, can not only be through the lubrication groove rolling to output shaft block bearing Son supply lubricating oil, additionally it is possible to be readily formed lubrication groove.
Accompanying drawing explanation
Fig. 1 is the skeleton drawing of power transmission apparatus for vehicle.
Fig. 2 is the detailed figure of 2 of Fig. 1.
Fig. 3 is the sectional view (OD state) of the 3-3 line along Fig. 2.
Fig. 4 is the sectional view (GN state) of the 3-3 line along Fig. 2.
Fig. 5 is the Action Specification figure under OD state.
Fig. 6 is the Action Specification figure under GN state.
Fig. 7 is the detailed figure of 7 of Fig. 2.
Fig. 8 is 8 enlarged drawings of Fig. 7.
Fig. 9 is the sectional view of the 9-9 line along Fig. 8.
Figure 10 is 10 enlarged drawings of Fig. 7.
Figure 11 is the enlarged drawing of the direction observation of the arrow 11 along Fig. 8.
Figure 12 is the explanatory diagram that radical-thrust ball bearing acts on the load of roller.
Label declaration
11: power shaft;12: output shaft;18: eccentric disc (eccentric part);19: connecting rod;21: one-way clutch Device;22: swing connector;26: case of transmission;27: ball bearing (output shaft block bearing);28: roller Bearing (output shaft block bearing);34 ': radical-thrust ball bearing (swings connector supporting bearing);36 ': inner ring; 41: inner ring;44: inner ring;44a: the 1 parts;44b: the 2 parts;44c: lubrication groove;45: roller;E: Engine (driving source);U: variable-speed unit.
Detailed description of the invention
Below, based on Fig. 1~Figure 12, embodiments of the present invention are illustrated.
As it is shown in figure 1, the driving force of the engine E axletree 10,10 through left and right is transferred to driving wheel W, W Power transmission apparatus for vehicle possesses crank-type buncher T and differential mechanism D.
It follows that the structure of buncher T is illustrated based on Fig. 2~Fig. 6.
As shown in Figures 2 and 3, the buncher T of present embodiment is mutually isostructural multiple (in reality by having Execute in mode is 6) variable-speed unit U ... axially overlap, these variable-speed units U ... possess and join abreast The power shaft 11 shared put and the output shaft 12 shared, being rotated in of power shaft 11 is transmitted after being decelerated or accelerating To output shaft 12.
Hereinafter, as representative, the structure of a variable-speed unit U is illustrated.It is connected with engine E and rotates Power shaft 11 in the way of rotating against freely, run through the rotation of hollow of the such shifting actuator of electro-motor 14 The inside of axle 14a.The rotor 14b of shifting actuator 14 is fixed on rotary shaft 14a, and stator 14c is fixed on housing. Rotary shaft 14a of shifting actuator 14 can rotate with the speed identical with power shaft 11, and can be relative to defeated Enter axle 11 to rotate against at different rates.
The power shaft 11 of rotary shaft 14a running through shifting actuator 14 is fixed with the 1st little gear 15, crank The planet carrier 16 of shape is connected to rotary shaft 14a of shifting actuator 14 in the way of crossing over the 1st little gear 15. Diameter and identical 2 the 2nd little gears 17,17 of the 1st little gear 15 are respectively by pinion pin 16a, 16a quilt Being bearing in cooperates with the 1st little gear 15 is configured to the position of equilateral triangle, gear ring 18a and these the 1st little gears 15 With the 2nd little gear 17,17 engagement, described gear ring 18a is eccentrically formed the inside of the eccentric disc 18 in circular plate type. Connecting rod 19 bar portion 19a one end arrange ring portion 19b by ball bearing 20 with embedding by the way of rotating against freely Outer peripheral face together in eccentric disc 18.
6 variable-speed unit U ... jointly have the planet carrier 16 of crank-like, are supported on by the 2nd little gear 17,17 The phase place of the eccentric disc 18 of planet carrier 16 differs 60 ° in each variable-speed unit U respectively.
For being arranged at the one-way clutch 21 of the periphery of output shaft 12, to be supported on a pivot on connecting rod 19 via pin 19c Bar portion 19a on the inner peripheral portion swinging connector 22 as exterior part, using the peripheral part of output shaft 12 as inside Part, in the space of the wedge-like being formed between exterior part and inner part, possesses multiple engaged spring 24 ... force Roller 25 ....
It follows that the structure of the periphery of output shaft 12 is illustrated based on Fig. 7~Figure 11.Further, at Fig. 3~ Schematically illustrating one-way clutch 21 in Fig. 6, the structure of its reality is shown in Fig. 7~Figure 11.
A pair of the axial both ends ball bearing 27,27 of output shaft 12 is supported on case of transmission 26, and, defeated The axial central portion of shaft 12 is supported on case of transmission 26 through roller bearing 28.Therefore, at roller bearing 28 Right side is configured with 3 variable-speed unit U ..., 3 variable-speed unit U it are configured with in the left side of roller bearing 28 ....This Sample, by this supporting output shaft 12 in position at 3 of axial both ends and axial central portion, it is possible to reduce this defeated The flexure of shaft 12.
The one-way clutch 21 of the periphery being supported on output shaft 12 is swinging the circular inner peripheral surface 22a of connector 22 And output shaft 12 bend to be configured with between wavy outer peripheral face 12a 12 rollers 25 ..., connecting rod 19 via Pin 19c and clamping element 29,29 are connected with protuberance 22b, the 22b arranged in the periphery swinging connector 22.
One-way clutch 21 possesses for honouring roller 25 ... the engagement spring 24 of force ... cage body 31.Cage body 31 are made up of following part: a pair endless member 32,32, they are made up of circular sheet material;With 12 springs Support rod 33 ..., they circumferentially, equally spaced configure, and make a pair endless member 32,32 be connected with each other, a pair ring Shape parts 32,32 are arranged in 12 rollers 25 ... axial both sides, 12 splinter bars 33 ... be arranged in 12 Individual roller 25 ... between.The inner peripheral portion of endless member 32 is formed as wavy, and it is wavy with output shaft 12 The concavo-convex engaging of outer peripheral face 12a, thus, cage body 31 is combined with output shaft 12 in the way of can not rotating against.
It is that S shape forms that engagement spring 24 makes 1 elastic plate bend to cross section, and its end side is by welding Etc. the splinter bar 33 being fixed on cage body 31.
It addition, be positioned at roller 25 swinging to be configured with between connector 22 and output shaft 12 ... axial both sides double The radical-thrust ball bearing 34 of row ..., swing connector 22 and output shaft 12 by these radical-thrust ball bearings 34 ... Maintain concentric and can connect in the way of rotating against.Each radical-thrust ball bearing 34 is in outer ring 35,35 And by multiple balls 37 between inner ring 36 ... being configured to the bearing of 2 row, outer ring 35,35 is integrally formed in Swinging the axial end portion of connector 22,22, shared inner ring 36 is made up of other parts, and is fixed on output shaft The periphery of 12.
At the axial both ends of outer peripheral face of the inner ring 36 of radical-thrust ball bearing 34, it is configured with storage ball 37 ... 2 row recess 36a ... (with reference to Figure 11).These recesses 36a ... be formed as the axial end of outer peripheral face at inner ring 36 Face is opened wide, and, a row recess 36a of an axial side ... and a row recess 36a of axial the opposing party ... it is configured to phase Stagger mutually.
So, each ball 37 is formed the recess 36a receiving this ball, therefore, is not required in terms of durability Not only to reduce number of components as the retainer of bearing neck, to also improve the durable of radical-thrust ball bearing 34 Property.And, by cancelling retainer, it is possible to configuration ball 37 thick and fast ..., thus add radical-thrust ball axle Hold the capacity of 34.It addition, with general ball 37 is configured at the structure in the endless groove of inner ring 36 compared with, rolling Pearl 37 increases with the contact area of recess 36a, the largest face pressure that therefore ball 37 is born for identical input load Reduce, it is possible to realize raising and the miniaturization of radical-thrust ball bearing 34 of durability.
And, it is also possible to same phase by 2 row recess 36a ... be configured to mutually opposing, replace 2 row recesses 36a ... be configured to mutually stagger.But, if by recess 36a ... be configured to mutually stagger, then can shorten inner ring The axial dimension of 36.
It is configured with axle spring 38 between radical-thrust ball bearing 34 and an endless member 32 of cage body 31, from Multiple projections 38a that the inner circumferential of axle spring 38 is prominent ... through the recess 32a of the inner circumferential of described endless member 32 ... Between and with roller 25 ... end face elasticity abut.
Supporting swing connector 22 ... radical-thrust ball bearing in, except the radical-thrust ball axle of above-mentioned biserial Hold 34 ... in addition, there is also the ball bearing 27,27 being configured to and support output shaft 12 or roller bearing 28 is adjacent Single-row radical-thrust ball bearing 34 '.The ball bearing 27 of supporting output shaft 12 possesses and is supported on case of transmission 26 Outer ring 40, the inner ring 41 being supported on output shaft 12 and the multiple balls being arranged between outer ring 40 and inner ring 41 42 ..., this inner ring 41 is made up of same parts with the inner ring 36 ' of single-row radical-thrust ball bearing 34 '.
It addition, the roller bearing 28 of supporting output shaft 12 possesses is supported on the outer ring 43 of case of transmission 26, supporting In the inner ring 44 of output shaft 12 and multiple rollers 45 of being arranged between outer ring 43 and inner ring 44 ....Inner ring 44 are made up of the 1st parts 44a and a pair the 2nd parts 44b, 44b, and described 1st parts 44a is positioned at axial central authorities, To roller 45 ... outer peripheral face support, the pair of 2nd parts 44b, 44b is combined in the 1st parts 44a's Axially both sides, to roller 45 ... both ends of the surface support, the 2nd parts 44b, 44b with the 1st parts 44a It is formed with multiple lubrication groove 44c on the divisional plane abutted ..., the plurality of lubrication groove 44c ... extend radially through inner ring 44.
It follows that the effect to the embodiments of the present invention possessing said structure illustrates.
First, the effect to a variable-speed unit U of buncher T illustrates.If making shifting actuator Rotary shaft 14a of 14 rotates against relative to power shaft 11, then planet carrier 16 revolves around the axis L1 of power shaft 11 Turn.Now, the center O of planet carrier 16, the i.e. the 1st little gear 15 and two the 2nd little gear 17,17 constitute The center of equilateral triangle rotates around the axis L1 of power shaft 11.
Fig. 3 and Fig. 5 shows that the center O of planet carrier 16 is relative to the 1st little gear 15 (i.e. power shaft 11) place In the state of the side contrary with output shaft 12, now, eccentric disc 18 becomes relative to the offset of power shaft 11 Maximum, the gearratio of buncher T becomes OD (overdrive) state.Fig. 4 and Fig. 6 shows planet carrier The center O of 16 is positioned at the shape of the side identical with output shaft 12 relative to the 1st little gear 15 (i.e. power shaft 11) State, now, eccentric disc 18 is zero relative to the offset of power shaft 11, and the gearratio of buncher T becomes GN (neutral gear) state.
Under the OD state shown in Fig. 5, if make power shaft 11 rotate by engine E and with power shaft 11 Identical speed makes rotary shaft 14a of shifting actuator 14 rotate, then power shaft 11, rotary shaft 14a, planet carrier 16,15, two the 2nd little gears 17,17 of the 1st little gear and eccentric disc 18 when being integrally forming with Centered by power shaft 11, (reference arrow A) carries out eccentric rotary counterclockwise.From (A) warp of Fig. 5 Spending (B) rotation period to the state of (C) of Fig. 5 of Fig. 5, connecting rod 19 makes to be supported on a pivot on this by pin 19c The swing connector 22 (reference arrow B) counterclockwise of the end of the bar portion 19a of connecting rod 19 rotates, wherein Ring portion 19b of this connecting rod 19 is rotated against, by ball bearing 20, the periphery being supported on eccentric disc 18 freely.Figure (A) of 5 and (C) of Fig. 5 show the two ends of the rotation towards described arrow B direction swinging connector 22.
So, when swinging connector 22 and rotating along arrow B direction, roller 25 ... engaging-in one-way clutch 21 The space of the wedge-like between swing connector 22 and output shaft 12, the rotation swinging connector 22 is passed to output Axle 12, therefore, output shaft 12 (reference arrow C) counterclockwise rotates.
If the little gear 15 of power shaft the 11 and the 1st further rotates, then gear ring 18a and the 1st little gear 15 and the 2nd are little Eccentric disc 18 (reference arrow A) eccentric rotary counterclockwise of gear 17,17 engagement.From (C) of Fig. 5 Rotate the period of the state of (A) to Fig. 5 through (D) of Fig. 5, connecting rod 19 makes to be supported on a pivot on this company by pin 19c The swing connector 22 of the end of the bar portion 19a of bar 19 (reference arrow B ') clockwise rotates, and wherein this connects Ring portion 19b of bar 19 is rotated against, by ball bearing 20, the periphery being supported on eccentric disc 18 freely.(C) of Fig. 5 With the two ends that (A) of Fig. 5 shows the rotation towards described arrow B ' direction swinging connector 22.
So, when swinging connector 22 and rotating along arrow B ' direction, roller 25 ... compressive engagement spring 24 ..., While being released by the space of the wedge-like between inner peripheral surface and the outer peripheral face of output shaft 12 swinging connector 22, thus, Swinging connector 22 to skid relative to output shaft 12, output shaft 12 does not rotates.
As described above, when swinging connector 22 reciprocating rotary, when the direction of rotation swinging connector 22 it is only Counterclockwise time (reference arrow B), output shaft 12 (reference arrow C) the most counterclockwise rotates, therefore, Output shaft 12 intermittent rotary.
The figure of effect when Fig. 6 is to be shown under GN state operating buncher T.Now, due to power shaft The position of 11 is consistent with the center of eccentric disc 18, and therefore eccentric disc 18 is zero relative to the offset of power shaft 11. If making power shaft 11 rotate by engine E in this condition and making speed change cause with the speed identical with power shaft 11 Rotary shaft 14a of dynamic device 14 rotates, then power shaft 11, rotary shaft 14a, the little gear 15 of planet carrier the 16, the 1st, Two the 2nd little gears 17,17 and eccentric disc 18 when being integrally forming centered by power shaft 11 around inverse Clockwise (reference arrow A) carries out eccentric rotary., owing to the offset of eccentric disc 18 is zero, therefore The reciprocating stroke of connecting rod 19 is also zero, and output shaft 12 does not rotates.
Therefore, if driving shifting actuator 14 that the position of planet carrier 16 is set in OD state and Fig. 4 of Fig. 3 GN state between, then the operating being capable of under any gearratio between Zero-drive Chain ratio and predetermined transmission ratio.
In buncher T, 6 the variable-speed unit U being set up in parallel ... eccentric disc 18 ... phase place be staggered mutually Open 60 °, therefore, 6 variable-speed unit U ... alternately transmit driving force, i.e. 6 one-way clutch 21 ... in appoint Anticipate one and be necessarily in engagement state, thus enable that output shaft 12 rotates continuously.
It addition, as it is shown in fig. 7, be configured with 27,27,1 Roller Shaft of 2 ball bearings in the periphery of output shaft 12 Hold the radical-thrust ball bearing 34 of 28,4 biserials ... and 4 single-row radical-thrust ball bearings 34 ' ..., therefore, Exist and cause because this amounts to 15 bearings the axial dimension of buncher T to increase such worry.
, parts are utilized to constitute the inner ring 41,41 of a pair ball bearing 27,27 and adjacent with them 2 The inner ring 36 ', 36 ' (with reference to Fig. 8) of single-row radical-thrust ball bearing 34 ', 34 ', and, utilize parts to constitute rolling A pair the 2nd parts 44b, 44b of the inner ring 44 of sub-bearing 28 and adjacent with them 2 single-row radical-thrust ball axles Hold the inner ring 36 ', 36 ' (with reference to Figure 10) of 34 ', 34 ', therefore, number of components can not only be reduced to cut down cost, and The axial dimension that can make buncher T minimizes.It addition, by improving single-row radical-thrust ball bearing 34 ' ... relatively In ball bearing 27,27 and the alignment of roller bearing 28, and make their inner ring 41,44,44,36 ' ... be integrally forming And improve rigidity, thereby, it is possible to supporting output shaft 12 and swing connector 22 securely ....
Particularly, for roller bearing 28, the inner ring 44 being typically divided into 2 parts has been divided into 1 the 1st Parts 44a and 2 the 2nd these 3 parts of parts 44b, 44b, therefore number of components adds one, but, logical Cross the inner ring 36 ', 36 ' of the radical-thrust ball bearing 34 ', 34 ' making the 2nd parts 44b, 44b single-row with adjacent 2 Forming as one, thus, number of components decreases two such that it is able to make number of components altogether reduce one.And, Owing to being formed with lubrication groove 44c on the cooperation face of the 1st parts 44a and the 2nd parts 44b, 44b ..., therefore, Not only lubrication groove 44c ... processing become easy, and lubrication groove 44c can be passed through ... to roller 45 ... supply lubrication Oil is to improve lubricant effect.
It addition, as shown in Figure 8, the roller 25 of one-way clutch 21 is width Wi's (i.e. the total length of roller 25) In the range of abut with the outer peripheral face 12a of output shaft 12, on the other hand, the roller 25 of one-way clutch 21 is with than institute State width Wo little for width Wi and the inner peripheral surface 22a swinging connector 22 to abut.
As Figure 12 (A) schematically shown in, the outer peripheral face as convex surface of roller 25 is connected to output shaft 12 The outer peripheral face as convex surface and swing connector 22 the inner peripheral surface 22a as concave surface, produce at this bearing surface Hertz stress becomes big at the outer peripheral face of convex surface abutting part each other, i.e. output shaft 12, convex surface and concave surface abutting part, The inner peripheral surface i.e. swinging connector 22 diminishes.
As shown in (B) of Figure 12, act on the axial distribution of load of roller 25 edge part at its two ends drastically Increase (edge loading), as shown in (C) of Figure 12, add by convex surface is implemented at the axial both ends of roller 25 Work (Network ラ ウ ニ Application グ), it is possible to reduce edge loading.When in order to the axial dimension making buncher T little Type and when reducing the axial dimension of roller 25, the roller 25 abutted with the outer peripheral face as convex surface of output shaft 12 The load of axial outer end initially will overstep the extreme limit load, therefore, according to the load of the outer peripheral face side of output shaft 12 Determine the minimum of a value of the axial dimension of roller 25.
In the case of determining the minimum of a value of axial dimension of roller 25 as described above, swing the interior of connector 22 The load of side face side is not up to ultimate load, but there are some and have more than needed.In the present embodiment, such as Fig. 8 and Tu Shown in (D) of 12, set by the width Wo of the inner peripheral surface side abutted with roller 25 by swinging connector 22 Must be less than the width Wi of the outer peripheral face side abutted with roller 25 of output shaft 12, thus it is set to that load is in the company of swing The inner peripheral surface side of fitting 22 and the outer peripheral face side of output shaft 12 reach capacity load simultaneously.Thus, it is ensured that roller The durability of 25, exists the width Wo suppression swinging the inner peripheral surface side abutted with roller 25 of connector 22 simultaneously Minimum limit, utilizes configuration radical-thrust ball bearing 34 in space formed here ..., 34 ' ..., it is possible to contracting The axial dimension of short buncher T.
Above, embodiments of the present invention are illustrated, but the present invention can be in the range of without departing from its main points Carry out various design alteration.
Such as, the buncher T of embodiment possesses 6 variable-speed unit U, but the quantity of variable-speed unit U It is not limited to 6.
It addition, the connector supporting bearing that swings of the present invention is not limited to the radical-thrust ball bearing 34 ' of embodiment, Can also be ball bearing or the such other kinds of bearing of roller bearing.
It addition, the output shaft block bearing of the present invention is not limited to ball bearing 27 or the roller bearing 28 of embodiment, It can also be the such other kinds of bearing of needle bearing.
It addition, in embodiments, it is formed with lubrication at a pair the 2nd parts 44b of the inner ring 44 of roller bearing 28 Groove 44c, but it is also possible to only form lubrication groove 44c at a 2nd parts 44b, or at the 1st parts 44a An end face or two end faces form lubrication groove 44c.
It addition, the driving source of the present invention is not limited to the engine E of embodiment, it is also possible to be motor generator this The other kinds of driving source of sample.

Claims (3)

1. a power transmission apparatus for vehicle, wherein,
Multiple variable-speed units (U) axially aligned setting, described variable-speed unit (U) will be connected with the source of driving (E) Power shaft (11) rotation speed change after be transferred to output shaft (12),
Described variable-speed unit (U) possesses respectively: eccentric part (18), and described eccentric part (18) is relative to institute State the eccentricity variable of the axis of power shaft (11), and described eccentric part (18) is together with this power shaft (11) Rotate;Swinging connector (22), described swing connector (22) is supported on described in the way of rotating against freely Output shaft (12);One-way clutch (21), described one-way clutch (21) be arranged in described output shaft (12) and Between described swing connector (22);With connecting rod (19), described connecting rod (19) connects described eccentric part (18) With described swing connector (22),
Described power transmission apparatus for vehicle is characterised by,
Described power transmission apparatus for vehicle possesses: output shaft block bearing (27,28), it is by described output shaft (12) It is supported on case of transmission (26);With swing connector supporting bearing (34 '), it is by described swing connector (22) It is supported on described output shaft (12), the inner ring (41,44) of output shaft block bearing (27,28) and described swing The inner ring (36 ') adjacent with this inner ring (41,44) of connector supporting bearing (34 ') forms as one.
Power transmission apparatus for vehicle the most according to claim 1, it is characterised in that
Described output shaft block bearing (28) is the roller bearing possessing roller (45), described output shaft block bearing (28) inner ring (44) possesses: the 1st parts (44a), and it rolls for described roller (45);With a pair the 2nd Parts (44b), they are arranged in the axial both sides of described 1st parts (44a), and their end surface supporting is in institute State the inner ring (36 ') of roller (45), described 2nd parts (44b) and described swing connector supporting bearing (34 ') Form as one.
Power transmission apparatus for vehicle the most according to claim 2, it is characterised in that
It is formed with edge between at least one party and described 1st parts (44a) in the 2nd parts (44b) described in a pair Extend radially through the lubrication groove (44c) of the described inner ring (44) of described output shaft block bearing (28).
CN201410174303.5A 2013-05-27 2014-04-28 Power transmission apparatus for vehicle Active CN104179944B (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2013111125A JP6112661B2 (en) 2013-05-27 2013-05-27 Power transmission device for vehicle
JP2013-111125 2013-05-27

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Publication Number Publication Date
CN104179944A CN104179944A (en) 2014-12-03
CN104179944B true CN104179944B (en) 2016-08-17

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CN104806705A (en) * 2015-01-08 2015-07-29 长沙艾科瑞齿轮机械有限责任公司 Gear reducer
JP6208790B2 (en) * 2016-02-29 2017-10-04 本田技研工業株式会社 Power transmission device for vehicle

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CN1693737A (en) * 2004-05-08 2005-11-09 王树春 Mochanical versible speed changer
CN101725683A (en) * 2008-10-24 2010-06-09 陈建武 Eccentric three-group linkage reducer
JP4909322B2 (en) * 2008-07-24 2012-04-04 本田技研工業株式会社 transmission

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GB169929A (en) * 1921-01-03 1921-10-13 Bearings Company Improvements in and relating to anti-friction bearings
JP2002339960A (en) * 2001-05-16 2002-11-27 Nsk Ltd Rolling bearing device
DE10294333D2 (en) * 2001-09-26 2004-09-09 Luk Lamellen & Kupplungsbau drive arrangement
JP2014521030A (en) * 2011-07-08 2014-08-25 シェフラー テクノロジーズ アクチエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフト Freewheel especially used for crank CVT transmission

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CN1693737A (en) * 2004-05-08 2005-11-09 王树春 Mochanical versible speed changer
JP4909322B2 (en) * 2008-07-24 2012-04-04 本田技研工業株式会社 transmission
CN101725683A (en) * 2008-10-24 2010-06-09 陈建武 Eccentric three-group linkage reducer

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