CN104179944A - Power transmission device used for vehicle - Google Patents
Power transmission device used for vehicle Download PDFInfo
- Publication number
- CN104179944A CN104179944A CN201410174303.5A CN201410174303A CN104179944A CN 104179944 A CN104179944 A CN 104179944A CN 201410174303 A CN201410174303 A CN 201410174303A CN 104179944 A CN104179944 A CN 104179944A
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- China
- Prior art keywords
- output shaft
- bearing
- inner ring
- parts
- power transmission
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 35
- 238000005461 lubrication Methods 0.000 claims description 15
- 230000002093 peripheral effect Effects 0.000 description 10
- 230000000694 effects Effects 0.000 description 4
- 206010041662 Splinter Diseases 0.000 description 3
- 239000000725 suspension Substances 0.000 description 3
- 238000005520 cutting process Methods 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 238000003860 storage Methods 0.000 description 2
- 230000004075 alteration Effects 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 244000144983 clutch Species 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 238000005755 formation reaction Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
- F16H29/02—Gearings 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
- F16H29/04—Gearings 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2700/00—Transmission housings and mounting of transmission components therein; Cooling; Lubrication; Flexible suspensions, e.g. floating frames
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- General Details Of Gearings (AREA)
- Rolling Contact Bearings (AREA)
- Friction Gearing (AREA)
Abstract
Provided is a power transmission device used for a vehicle. The part number of bearings around an output shaft of a power transmission device used for a vehicle and provided with a crank type speed changing unit can be reduced. The power transmission device used for the vehicle is provided with output shaft support bearings (27, 28) used for supporting an output shaft (12) to a speed changer housing (26), and swinging connector support bearings (34, 34') used for supporting two axial sides of each swinging connector (22) to the output shaft (12). Inner rings (41, 44) of the output shaft support bearings (27, 28) and inner rings (36'), adjacent to the inner rings (41, 44), of the swinging connector support bearings (34') are formed in an integrated manner, so that compared with the condition that the inner rings of the output shaft support bearings and the inner rings of the swinging connector support bearings are formed by different parts, the part number can be reduced to miniaturize the axial size of the power transmission device used for the vehicle, and the coaxality and the rigidness of the output shaft support bearings and the swinging connector support bearings are improved.
Description
Technical field
The present invention relates to possess the power transmission apparatus for vehicle of multiple crank-type variable-speed units, described multiple crank-type variable-speed units will be passed to output shaft after the rotation speed change of the input shaft being connected with driving source.
Background technique
For the rotor of motor is supported on to stator freely, according to the known such structure of following patent documentation 1: a circle is fixed on another circle and the outer ring butt that the axle of rotor is supported on to the radial ball bearing of stator of the thrust ball bearing of rotor.
Patent documentation 1: Japanese Patent Publication 3-3155 communique
; around the output shaft of power transmission apparatus for vehicle that possesses multiple crank-type variable-speed units; except output shaft being supported on the bearing of case of transmission; also need the axial two-side supporting of the swing link of multiple variable-speed units in each pair of bearings of output shaft; because multiple bearing is so configured in the periphery of output shaft; therefore, exist number of components to increase, 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, and its object is the number of components of the bearing of the surrounding of the output shaft of cutting down the power transmission apparatus for vehicle with crank-type variable-speed unit.
In order to reach above-mentioned purpose, the invention of recording according to technological scheme 1, a kind of power transmission apparatus for vehicle is proposed, wherein, multiple variable-speed units spread configuration vertically, described variable-speed unit will be passed to output shaft after the rotation speed change of the input shaft being connected with driving source, and described variable-speed unit possesses respectively: eccentric part, described eccentric part is variable with respect to the offset of the axis of described input shaft, and described eccentric part rotates together with this input shaft; Swing link, described swing link is supported on described output shaft in the mode of relatively rotating freely; Overrunning clutch, described overrunning clutch is configured between described output shaft and described swing link; And connecting rod, described connecting rod connects described eccentric part and described swing link, and described power transmission apparatus for vehicle is characterised in that, and described power transmission apparatus for vehicle possesses: output shaft block bearing, described output shaft is supported on case of transmission by it; With swing connector supporting bearing, it is by described swing connector supporting in described output shaft, and the inner ring adjacent with this inner ring of the inner ring of output shaft block bearing and described swing connector supporting bearing forms as one.
In addition, the invention of recording according to technological scheme 2, a kind of power transmission apparatus for vehicle is proposed, it is characterized in that, on the basis of the structure of technological scheme 1, described output shaft block bearing is the roller bearing that possesses roller, and the inner ring of described output shaft block bearing possesses: the 1st parts, and it rolls for described roller; With a pair of the 2nd parts, they are configured in the axial both sides of described the 1st parts, and their end surface supporting is in described roller, and the inner ring of described the 2nd parts and described swing connector supporting bearing forms as one.
In addition, the invention of recording according to technological scheme 3, has proposed a kind of power transmission apparatus for vehicle, it is characterized in that, on the basis of the structure of technological scheme 2, between at least one party in described a pair of the 2nd parts and described the 1st parts, be formed with the lubrication groove that radially runs through described inner ring.
In addition, the eccentric disc 18 of mode of execution is corresponding to eccentric part of the present invention, the ball bearing 27 of mode of execution and roller bearing 28 are corresponding to output shaft block bearing of the present invention, mode of execution radical-thrust ball bearing 34 ' corresponding to swing connector supporting bearing of the present invention, the motor E of mode of execution is corresponding to driving source of the present invention.
According to the structure of technological scheme 1, in the time that eccentric part rotates integratedly with the input shaft being connected with driving source, the connecting rod that one end is connected with eccentric part moves back and forth, and the swing link being connected with the other end of connecting rod carries out reciprocally swinging.In the time swinging link to a direction swing, the overrunning clutch that is configured in output shaft and swing between link engages, and in the time that swing link swings in the other direction, described overrunning clutch is removed and engaged, thus, the rotation of input shaft is passed to output shaft off and on.Multiple variable-speed units separate the time difference and replace transmission of drive force, thus output shaft continuous rotation.In the time that the offset of eccentric part is changed, the reciprocating stroke of connecting rod changes, thereby the stroke of the oscillating motion that swings link is changed, and thus, the angle of rotation of output shaft changes, and the gear ratio between input shaft and output shaft is changed.
Owing to possessing the output shaft block bearing that output shaft is supported on to case of transmission, with will swing connector supporting in the swing connector supporting bearing of output shaft, the inner ring of output shaft block bearing, form as one with the inner ring adjacent with this inner ring that swings connector supporting bearing, therefore, compare with the situation of the inner ring that swings connector supporting bearing from the inner ring that utilizes different parts to form output shaft block bearing, not only can cut down number of components and make the axial dimension miniaturization of power transmission apparatus for vehicle, can also improve alignment and the rigidity of output shaft block bearing and swing connector supporting bearing.
In addition, according to the structure of technological scheme 2, output shaft block bearing is the roller bearing that possesses roller, and the inner ring of output shaft block bearing possesses: the 1st parts, and it rolls for roller; With a pair of the 2nd parts, they are configured in the axial both sides of the 1st parts, and their end surface supporting is in roller, and the 2nd parts form as one with the inner ring that swings connector supporting bearing, therefore, the inner ring being in the past made up of two parts becomes three parts, number of components has increased by one, still, and owing to not needing the inner ring of two adjacent swing connector supporting bearings, therefore, can altogether make number of components cut down one.
In addition, according to the structure of technological scheme 3, owing to being formed with the lubrication groove that radially runs through inner ring between at least one party in a pair of the 2nd parts and the 1st parts, therefore, not only can be through lubrication groove the roller supplying lubricating oil to output shaft block bearing, can also easily form lubrication groove.
Brief description of the drawings
Fig. 1 is the skeleton drawing of power transmission apparatus for vehicle.
Fig. 2 is the details drawing of 2 of Fig. 1.
Fig. 3 is along the sectional view of the 3-3 line of Fig. 2 (OD state).
Fig. 4 is along the sectional view of the 3-3 line of Fig. 2 (GN state).
Fig. 5 is the Action Specification figure under OD state.
Fig. 6 is the Action Specification figure under GN state.
Fig. 7 is the details drawing of 7 of Fig. 2.
Fig. 8 is 8 enlarged views of Fig. 7.
Fig. 9 is the sectional view along the 9-9 line of Fig. 8.
Figure 10 is 10 enlarged views of Fig. 7.
Figure 11 is the enlarged view of observing along the direction of the arrow 11 in Fig. 8.
Figure 12 is the explanatory drawing that radical-thrust ball bearing acts on the load of roller.
Label declaration
11: input shaft; 12: output shaft; 18: eccentric disc (eccentric part); 19: connecting rod; 21: overrunning clutch; 22: swing link; 26: case of transmission; 27: ball bearing (output shaft block bearing); 28: roller bearing (output shaft block bearing); 34 ': radical-thrust ball bearing (swinging connector supporting bearing); 36 ': inner ring; 41: inner ring; 44: inner ring; 44a: the 1st parts; 44b: the 2nd parts; 44c: lubrication groove; 45: roller; E: motor (driving source); U: variable-speed unit.
Embodiment
Below, based on Fig. 1～Figure 12, embodiments of the present invention are described.
As shown in Figure 1, the power transmission apparatus for vehicle that the driving force of motor E is passed to driving wheel W, W through the axletree 10,10 of left and right possesses crank-type stepless speed variator T and differential mechanism D.
Next, based on Fig. 2～Fig. 6, the structure of stepless speed variator T is described.
As shown in Figures 2 and 3, the stepless speed variator T of present embodiment will have multiple (being 6 in mode of execution) variable-speed unit U of same structure ... overlapping form vertically, these variable-speed units U ... possess abreast the shared input shaft 11 of configuration and shared output shaft 12, being rotated in of input shaft 11 slowed down or accelerate after be passed to output shaft 12.
Below, as representative, the structure of a variable-speed unit U is described.The input shaft 11 connecting with motor E and rotate runs through the inside of the running shaft 14a of the hollow of the such shifting actuator of electric motor 14 in relative mode of rotating freely.The rotor 14b of shifting actuator 14 is fixed on running shaft 14a, and stator 14c is fixed on housing.The running shaft 14a of shifting actuator 14 can rotate with the speed identical with input shaft 11, and can relatively rotate with different speed with respect to input shaft 11.
On the input shaft 11 of running shaft 14a that runs through shifting actuator 14, be fixed with the 1st small gear 15, the planet carrier 16 of crank-like is connected in the running shaft 14a of shifting actuator 14 to cross over the mode of the 1st small gear 15.2 the 2nd small gears 17,17 that diameter is identical with the 1st small gear 15 are supported in the 1st small gear 15 and are cooperated and be configured to the position of equilateral triangle by small gear pin 16a, 16a respectively, gear ring 18a engages with these the 1st small gears 15 and the 2nd small gear 17,17, and described gear ring 18a is formed at the inside of the eccentric disc 18 of circular plate type prejudicially.The ring portion 19b arranging in one end of the 19a of bar portion of connecting rod 19 is embedded in the outer circumferential face of eccentric disc 18 in the mode freely of relatively rotating by ball bearing 20.
6 variable-speed unit U ... jointly have the planet carrier 16 of crank-like, the phase place that is supported on the eccentric disc 18 of planet carrier 16 by the 2nd small gear 17,17 differs respectively 60 ° in each variable-speed unit U.
For the overrunning clutch 21 of periphery that is arranged at output shaft 12, using the interior perimembranous of the swing link 22 on the 19a of bar portion of connecting rod 19 via pin 19c pivot suspension as exterior part, using the peripheral part of output shaft 12 as inner piece, being formed in the space of the wedge-like between exterior part and inner piece, possess multiple engaged springs 24 ... the roller 25 of the application of force ...
Next, based on Fig. 7～Figure 11, the structure of the periphery to output shaft 12 describes.And, in Fig. 3～Fig. 6, schematically illustrating overrunning clutch 21, its actual structure is shown in Fig. 7～Figure 11.
The axial two end part of output shaft 12 are supported on case of transmission 26 through a pair of ball bearing 27,27, and the axial central part of output shaft 12 is supported on case of transmission 26 through roller bearing 28.Therefore, dispose 3 variable-speed unit U on the right side of roller bearing 28 ..., dispose 3 variable-speed unit U in the left side of roller bearing 28 ...Like this, by axially two end part and axially this position, 3 place supporting output shaft 12 of central part, can reduce thus the deflection of this output shaft 12.
The overrunning clutch 21 that is supported on the periphery of output shaft 12 disposes 12 rollers 25 swinging bending to of the circular inner peripheral surface 22a of link 22 and output shaft 12 between wavy outer circumferential face 12a ..., connecting rod 19 is connected with the protuberance 22b, the 22b that arrange in the periphery that swings link 22 with clamping element 29,29 via pin 19c.
Overrunning clutch 21 possesses for propping up honours roller 25 ... the engage spring 24 of the application of force ... cage body 31.Cage body 31 is made up of following part: a pair of ring-shaped member 32,32, and they are made up of circular sheet material; With 12 splinter bars 33 ... they are along circumferentially equally spaced configuration, a pair of ring-shaped member 32,32 is interconnected, and a pair of ring-shaped member 32,32 is configured in 12 rollers 25 ... axial both sides, 12 splinter bars 33 ... be configured in 12 rollers 25 ... between.The interior perimembranous of ring-shaped member 32 is formed as wavy, and it engages with the wavy outer circumferential face 12a of output shaft 12 is concavo-convex, and thus, cage body 31 is with can not counterrotating mode and output shaft 12 combinations.
It is that S word shape forms that engage spring 24 makes 1 elastic plate bend to cross section, the distolateral splinter bar 33 that is fixed on cage body 31 that waits by welding of one.
In addition, between swing link 22 and output shaft 12, dispose and be positioned at roller 25 ... the radical-thrust ball bearing 34 of biserial of axial both sides ..., swing link 22 and output shaft 12 by these radical-thrust ball bearings 34 ... maintain concentric and can counterrotating mode connecting.Each radical-thrust ball bearing 34 is by multiple balls 37 between outer ring 35,35 and inner ring 36 ... be configured to the bearing that 2 row form, outer ring 35,35 is integrally formed in the axial end portion that swings link 22,22, shared inner ring 36 is made up of other parts, and is fixed on the periphery of output shaft 12.
At the axial two end part of the outer circumferential face of the inner ring 36 of radical-thrust ball bearing 34, dispose storage ball 37 ... 2 row recess 36a ... (with reference to Figure 11).These recesses 36a ... be formed as opening wide at the axial end of the outer circumferential face of inner ring 36, and, an axial side's a row recess 36a ... a row recess 36a with axial the opposing party ... be configured to mutually stagger.
Like this, each ball 37 is formed with to the recess 36a of this ball of storage, therefore, aspect durability, does not need the retainer as bearing neck, not only cut down number of components, also improved the durability of radical-thrust ball bearing 34.And, by cancelling retainer, can configure thick and fast ball 37 ... thereby, increased the capacity of radical-thrust ball bearing 34.In addition, compared with structure in the general annular slot that ball 37 is disposed to inner ring 36, ball 37 increases with the area of contact of recess 36a, and the largest face that therefore ball 37 bears for identical input load is pressed and reduced, and can realize the raising of durability and the miniaturization of radical-thrust ball bearing 34.
And, also can be with same phase by 2 row recess 36a ... be configured to mutually opposedly, replace 2 row recess 36a ... be configured to mutually stagger.But, if by recess 36a ... be configured to mutually stagger, can shorten the axial dimension of inner ring 36.
Between a ring-shaped member 32 of radical-thrust ball bearing 34 and cage body 31, dispose axle spring 38, from outstanding multiple projection 38a of the interior week of axle spring 38 ... pass the recess 32a in the interior week of described ring-shaped member 32 ... between and with roller 25 ... end face elasticity butt.
Swing link 22 in supporting ... radical-thrust ball bearing in, except the radical-thrust ball bearing 34 of above-mentioned biserial ... in addition, also exist be configured to the single-row radical-thrust ball bearing 34 adjacent with supporting the ball bearing 27,27 of output shaft 12 or roller bearing 28 '.Supporting output shaft 12 ball bearing 27 possess be supported on case of transmission 26 outer ring 40, be supported on the inner ring 41 of output shaft 12 and be configured in outer ring 40 and inner ring 41 between multiple balls 42 ..., this inner ring 41 and single-row radical-thrust ball bearing 34 ' inner ring 36 ' formed by same parts.
In addition, supporting output shaft 12 roller bearing 28 possess be supported on case of transmission 26 outer ring 43, be supported on the inner ring 44 of output shaft 12 and be configured in outer ring 43 and inner ring 44 between multiple rollers 45 ...Inner ring 44 is made up of the 1st parts 44a and a pair of the 2nd parts 44b, 44b, described the 1st parts 44a is positioned at axial central authorities, to roller 45 ... outer circumferential face support, described a pair of the 2nd parts 44b, 44b are combined in the axial both sides of the 1st parts 44a, to roller 45 ... both ends of the surface support, on the 2nd parts 44b, 44b and parting plane the 1st parts 44a butt, be formed with multiple lubrication groove 44c ..., described multiple lubrication groove 44c ... radially run through inner ring 44.
Next, the effect of the embodiments of the present invention that possess said structure is described.
First, the effect of stepless speed variator T variable-speed unit U is described.If the running shaft 14a of shifting actuator 14 is rotated relatively with respect to input shaft 11, planet carrier 16 is around the axis L1 of input shaft 11 rotation.Now, the center of the equilateral triangle of the center O of planet carrier 16, i.e. the 1st small gear 15 and two the 2nd small gear 17,17 formations is around the axis L1 of input shaft 11 rotation.
The center O that Fig. 3 and Fig. 5 show planet carrier 16 is the state in a side contrary with output shaft 12 with respect to the 1st small gear 15 (being input shaft 11), now, eccentric disc 18 becomes maximum with respect to the offset of input shaft 11, and the velocity ratio of stepless speed variator T becomes OD (overdrive) state.The center O that Fig. 4 and Fig. 6 show planet carrier 16 is positioned at the state of a side identical with output shaft 12 with respect to the 1st small gear 15 (being input shaft 11), now, eccentric disc 18 is zero with respect to the offset of input shaft 11, and the velocity ratio of stepless speed variator T becomes GN (neutral gear) state.
Under the OD state shown in Fig. 5, if input shaft 11 is rotated and made the running shaft 14a rotation of shifting actuator 14 with the speed identical with input shaft 11 by motor E, input shaft 11, running shaft 14a, planet carrier 16, the 1st small gear 15, two the 2nd small gears 17,17 and eccentric disc 18 carry out eccentric rotary around counterclockwise (reference arrow A) under the state becoming one centered by input shaft 11.Rotate through Fig. 5 (B) at (A) from Fig. 5 to during the state of Fig. 5 (C), connecting rod 19 makes to be rotated around counter clockwise direction (reference arrow B) in the swing link 22 of the end of the 19a of bar portion of this connecting rod 19 by pin 19c pivot suspension, and wherein the ring portion 19b of this connecting rod 19 is rotatably freely supported on the periphery of eccentric disc 18 relatively by ball bearing 20.(A) of Fig. 5 and (C) of Fig. 5 show the two ends of the rotation towards described arrow B direction that swings link 22.
Like this, in the time swinging link 22 along arrow B direction rotation, roller 25 ... the space of the wedge-like between swing link 22 and the output shaft 12 of engaging-in overrunning clutch 21, the rotation that swings link 22 is passed to output shaft 12, therefore, output shaft 12 is around counterclockwise (reference arrow C) rotation.
If input shaft 11 and the 1st small gear 15 are further rotated, the eccentric disc 18 that gear ring 18a engages with the 1st small gear 15 and the 2nd small gear 17,17 is around counter clockwise direction (reference arrow A) eccentric rotary.Rotate through Fig. 5 (D) at (C) from Fig. 5 to during the state of Fig. 5 (A), connecting rod 19 makes by pin 19c pivot suspension in (the reference arrow B ') rotation clockwise of the swing link 22 of the end of the 19a of bar portion of this connecting rod 19, and wherein the ring portion 19b of this connecting rod 19 is rotatably freely supported on the periphery of eccentric disc 18 relatively by ball bearing 20.(C) of Fig. 5 and (A) of Fig. 5 show the two ends of the rotation towards described arrow B ' direction that swings link 22.
Like this, in the time swinging link 22 along arrow B ' direction rotation, roller 25 ... compressive engagement spring 24 on one side ... released from the space that swings the wedge-like between the inner peripheral surface of link 22 and the outer circumferential face of output shaft 12 on one side, thus, swing link 22 and skid with respect to output shaft 12, output shaft 12 does not rotate.
As described above, in the time swinging link 22 reciprocating rotary, only have output shaft 12 in the time that the sense of rotation of swing link 22 is counter clockwise direction (reference arrow B) just to rotate around counter clockwise direction (reference arrow C), therefore, output shaft 12 intermittent rotaries.
Fig. 6 is the figure that is illustrated in the effect while turning round stepless speed variator T under GN state.Now, because the position of input shaft 11 is consistent with eccentric disc 18 center, therefore eccentric disc 18 is zero with respect to the offset of input shaft 11.If input shaft 11 rotated by motor E under this state and make the running shaft 14a rotation of shifting actuator 14 with the speed identical with input shaft 11, input shaft 11, running shaft 14a, planet carrier 16, the 1st small gear 15, two the 2nd small gears 17,17 and eccentric disc 18 carry out eccentric rotary around counterclockwise (reference arrow A) under the state becoming one centered by input shaft 11., because 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 rotate.
Therefore, if drive shifting actuator 14 by the set positions of planet carrier 16 between the GN of the OD of Fig. 3 state and Fig. 4 state, can realize the running under any velocity ratio between zero velocity ratio and predetermined transmission ratio.
In stepless speed variator T, 6 variable-speed unit U that are set up in parallel ... eccentric disc 18 ... phase place stagger mutually 60 °, therefore, 6 variable-speed unit U ... alternately transmission of drive force, i.e. 6 overrunning clutchs 21 ... in any one is inevitable in jointing state, can make thus output shaft 12 continuous rotations.
In addition, as shown in Figure 7, dispose the radical-thrust ball bearing 34 of 28,4 biserials of 27,27,1 roller bearings of 2 ball bearings in the periphery of output shaft 12 ... with 4 single-row radical-thrust ball bearings 34 ' ... therefore, exist because this amounts to 15 bearings and cause the axial dimension of stepless speed variator T to increase such worry.
, utilize parts to form a pair of ball bearing 27, 27 inner ring 41, 41, with 2 adjacent with them single-row radical-thrust ball bearings 34 ', 34 ' inner ring 36 ', 36 ' (with reference to Fig. 8), and, utilize parts to form a pair of the 2nd parts 44b of the inner ring 44 of roller bearing 28, 44b, with 2 adjacent with them single-row radical-thrust ball bearings 34 ', 34 ' inner ring 36 ', 36 ' (with reference to Figure 10), therefore, not only can reduce number of components with cutting down cost, and can make the axial dimension miniaturization of stepless speed variator T.In addition, by improve single-row radical-thrust ball bearing 34 ' ... with respect to the alignment of ball bearing 27,27 and roller bearing 28, and make their inner ring 41,44,44,36 ' ... become one and improve rigidity, thus, can support securely output shaft 12 and swing link 22 ...
Particularly, for roller bearing 28, conventionally the inner ring 44 that is divided into 2 parts has been divided into 1 the 1st parts 44a and 2 these 3 parts of the 2nd parts 44b, 44b, therefore number of components has increased by one, but, by make the 2nd parts 44b, 44b and adjacent 2 single-row radical-thrust ball bearings 34 ', 34 ' inner ring 36 ', 36 ' form as one, thus, number of components has reduced two, thereby can make number of components altogether reduce one.And, owing to being formed with lubrication groove 44c on the fitting surface at the 1st parts 44a and the 2nd parts 44b, 44b ... therefore, lubrication groove 44c not only ... processing become easily, and can pass through lubrication groove 44c ... to roller 45 ... supplying lubricating oil is to improve lubrication effect.
In addition, as shown in Figure 8, the roller 25 of overrunning clutch 21 in the scope of width W i (being the total length of roller 25) with the outer circumferential face 12a butt of output shaft 12, on the other hand, the roller 25 of overrunning clutch 21 is with the width W o and the inner peripheral surface 22a butt that swing link 22 less than described width W i.
As Figure 12 (A) schematically as shown in, the outer circumferential face as convex surface of roller 25 is connected to the outer circumferential face as convex surface of output shaft 12 and swings the inner peripheral surface 22a as concave surface of link 22, the hertz stress producing at this bearing surface is at abutting part each other of convex surface, the outer circumferential face of output shaft 12 becomes large, diminishes at the abutting part of convex surface and concave surface, the inner peripheral surface that swings link 22.
As shown in Figure 12 (B), the axial distribution that acts on the load of roller 25 sharply increases (edge loading) at the edge part at its two ends, as shown in Figure 12 (C), implement convex surface processing (Network ラ ウ ニ Application グ) by the axial two end part to roller 25, can reduce thus edge loading.While dwindling the axial dimension of roller 25 when the axial dimension miniaturization in order to make stepless speed variator T, with the load of the axial outer end of the roller 25 of the outer circumferential face butt as convex surface of output shaft 12 load that will overstep the extreme limit at first, therefore, decide the minimum value of the axial dimension of roller 25 according to the load of the outer circumferential face side of output shaft 12.
In the case of the minimum value of axial dimension that has determined as described above roller 25, the load of inner peripheral surface side that swings link 22 load that do not reach capacity, but exist some more than needed.In the present embodiment, as shown in Fig. 8 and Figure 12 (D), by link 22 setting specific output axle 12 littlely with the width W i of outer circumferential face sides roller 25 butts with the width W o of inner peripheral surface sides roller 25 butts by swinging, set thus load for and swinging the inner peripheral surface side of link 22 and the outer circumferential face side of output shaft 12 load that simultaneously reaches capacity.Thus, guarantee the durability of roller 25, be suppressed at minimum limit by swing of link 22 with the width W o of inner peripheral surface sides roller 25 butts simultaneously, utilize the space configuration radical-thrust ball bearing 34 forming herein ..., 34 ' ..., can shorten thus the axial dimension of stepless speed variator T.
Above, embodiments of the present invention are illustrated, but the present invention can carry out various design alterations in the scope that does not depart from its main points.
For example, the stepless speed variator T of mode of execution possesses 6 variable-speed unit U, but the quantity of variable-speed unit U is not limited to 6.
In addition, swing connector supporting bearing of the present invention be not limited to the radical-thrust ball bearing 34 of mode of execution ', can be also the bearing of other such kinds of ball bearing or roller bearing.
In addition, output shaft block bearing of the present invention is not limited to ball bearing 27 or the roller bearing 28 of mode of execution, can be also the bearing of other such kinds of needle bearing.
In addition, in mode of execution, be formed with lubrication groove 44c at a pair of the 2nd parts 44b of the inner ring 44 of roller bearing 28, still, also can only form lubrication groove 44c at a 2nd parts 44b, or form lubrication groove 44c at an end face or two end faces of the 1st parts 44a.
In addition, driving source of the present invention is not limited to the motor E of mode of execution, can be also the driving source of other such kinds of motor generator.
Claims (3)
1. a power transmission apparatus for vehicle, wherein,
Multiple variable-speed units (U) spread configuration vertically, described variable-speed unit (U) will be passed to output shaft (12) after the rotation speed change of the input shaft (11) being connected with driving source (E),
Described variable-speed unit (U) possesses respectively: eccentric part (18), described eccentric part (18) is variable with respect to the offset of the axis of described input shaft (11), and described eccentric part (18) rotates together with this input shaft (11); Swing link (22), described swing link (22) is supported on described output shaft (12) in the mode of relatively rotating freely; Overrunning clutch (21), described overrunning clutch (21) is configured between described output shaft (12) and described swing link (22); And connecting rod (19), described connecting rod (19) connects described eccentric part (18) and described swing link (22),
Described power transmission apparatus for vehicle is characterised in that,
Described power transmission apparatus for vehicle possesses: output shaft block bearing (27,28), and described output shaft (12) is supported on case of transmission (26) by it; With swing connector supporting bearing (34 '), described swing link (22) is supported on described output shaft (12) by it, and the inner ring (36 ') adjacent with this inner ring (41,44) of the inner ring (41,44) of output shaft block bearing (27,28) and described swing connector supporting bearing (34 ') forms as one.
2. power transmission apparatus for vehicle according to claim 1, is characterized in that,
Described output shaft block bearing (28) is the roller bearing that possesses roller (45), the inner ring (44) of described output shaft block bearing (28) possesses: the 1st parts (44a), and it rolls for described roller (45); With a pair of the 2nd parts (44b), they are configured in the axial both sides of described the 1st parts (44a), and their end surface supporting is in described roller (45), and described the 2nd parts (44b) form as one with the inner ring (36 ') of described swing connector supporting bearing (34 ').
3. power transmission apparatus for vehicle according to claim 2, is characterized in that,
Between at least one party in described a pair of the 2nd parts (44b) and described the 1st parts (44a), be formed with the lubrication groove (44c) that radially runs through described inner ring (44).
Applications Claiming Priority (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 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104179944A true CN104179944A (en) | 2014-12-03 |
| CN104179944B CN104179944B (en) | 2016-08-17 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410174303.5A Expired - Fee Related CN104179944B (en) | 2013-05-27 | 2014-04-28 | Power transmission apparatus for vehicle |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6112661B2 (en) |
| CN (1) | CN104179944B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107128170A (en) * | 2016-02-29 | 2017-09-05 | 本田技研工业株式会社 | Power transmission apparatus for vehicle |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
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| US20050039572A1 (en) * | 2001-09-26 | 2005-02-24 | Oswald Friedmann | Drive assembly |
| 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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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| DE102012210100A1 (en) * | 2011-07-08 | 2013-01-10 | Schaeffler Technologies AG & Co. KG | Freewheel, especially for a crank-CVT transmission |
-
2013
- 2013-05-27 JP JP2013111125A patent/JP6112661B2/en not_active Expired - Fee Related
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2014
- 2014-04-28 CN CN201410174303.5A patent/CN104179944B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20050039572A1 (en) * | 2001-09-26 | 2005-02-24 | Oswald Friedmann | Drive assembly |
| 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 |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107128170A (en) * | 2016-02-29 | 2017-09-05 | 本田技研工业株式会社 | Power transmission apparatus for vehicle |
| CN107128170B (en) * | 2016-02-29 | 2019-07-26 | 本田技研工业株式会社 | Power transmission apparatus for vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6112661B2 (en) | 2017-04-12 |
| JP2014228133A (en) | 2014-12-08 |
| CN104179944B (en) | 2016-08-17 |
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