CN106068405B - Power transmission apparatus for vehicle - Google Patents
Power transmission apparatus for vehicle Download PDFInfo
- Publication number
- CN106068405B CN106068405B CN201480076966.1A CN201480076966A CN106068405B CN 106068405 B CN106068405 B CN 106068405B CN 201480076966 A CN201480076966 A CN 201480076966A CN 106068405 B CN106068405 B CN 106068405B
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- Prior art keywords
- clutch
- output shaft
- input
- transmission
- driving source
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 107
- 230000008859 change Effects 0.000 claims abstract description 13
- 230000007246 mechanism Effects 0.000 description 60
- 238000011144 upstream manufacturing Methods 0.000 description 20
- 230000000875 corresponding effect Effects 0.000 description 10
- 230000007935 neutral effect Effects 0.000 description 10
- 230000000694 effects Effects 0.000 description 5
- 238000000926 separation method Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 230000007257 malfunction Effects 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 238000013016 damping Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000008439 repair process Effects 0.000 description 2
- 230000004075 alteration Effects 0.000 description 1
- 230000004888 barrier function Effects 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process 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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
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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
Abstract
Clutch (52) has：Clutch input part (53) is rotated integrally with the input gear (26) of auxiliary power transfer unit (29)；Clutch output block (54) is rotated integrally with transmission input shaft (11A)；And clutch workpiece (55),It makes clutch output block (54) be engaged with clutch input part (53),The driving force of driving source output shaft (11B) is transmitted to transmission input shaft (11A),Due to connecting driving source output shaft (11B) and clutch input part (53) by spring element (51a),Therefore,Driving source output shaft (11B) can not only be passed through,Clutch input part (53) and spring element (51a) constitute damper (51) and are changed to absorb the rotation of driving source (E),And clutch input part (53) is supported on by case of transmission (56) by bearing (57),Therefore,Even if driving source (E) has rotation to change,Also it can prevent bearing (57) from alternately being driven towards negative direction,To improve the durability of the bearing (57).
Description
Technical field
The present invention relates to power transmission apparatus for vehicle, have：Transmission input shaft, by clutch with by driving
The driving source of dynamic source driving exports axis connection；Transmission output shaft is connect with driving wheel；The gear of crank-type, energy
Enough make the driving force speed change of the transmission input shaft and is transferred to the transmission output shaft；And auxiliary power transmits list
Member, relative to the gear side by side configuration and can be between the driving source output shaft and the transmission output shaft
Driving force is transmitted, the auxiliary power transfer unit consists of the following parts：Input element, by spring element with it is described
Driving source output shaft rotates integrally；Element is exported, is connect with the transmission output shaft；And intermediate elements, connect institute
State input element and the output element.
Background technology
There is known a kind of structure in following patent documents 1, be configured at engine bent axle and speed changer input shaft it
Between double mass flywheel (damper) rotated integrally using the primary flywheel rotated integrally with bent axle, with input shaft secondary flywheel, with
And the torsional spring of connection primary flywheel and secondary flywheel is constituted.
Existing technical literature
Patent document
Patent document 1：Japanese Unexamined Patent Publication 2009-115184 bulletins
Invention content
The subject that the invention solves
But in above-mentioned previous double mass flywheel, since the ball bearing for rotatably supporting its secondary flywheel is matched
It is placed between secondary flywheel and primary flywheel, therefore, when torsional spring stretches and absorbs the rotation variation of engine, primary flywheel and secondary flywheel
Alternately towards opposite direction relative rotation, the inner ring for being configured at the ball bearing between primary flywheel and secondary flywheel also replaces with outer ring
Ground is towards opposite direction relative rotation.If inner ring and outer ring alternately towards opposite direction relative rotation, ball bearing it is durable
Property decline, therefore, it is necessary to prevent inner ring and outer ring from alternately improving durability towards opposite direction relative rotation.
The present invention has been made in view of the above-described circumstances, and its object is to improve the vehicle for being configured at driving source and crank-type
With the durability of the bearing of the damper between power transmission.
Means for solving the problems
In order to achieve the above objectives, according to the present invention it is proposed that a kind of power transmission apparatus for vehicle, has：Speed changer
Input shaft exports axis connection by clutch with the driving source driven by driving source；Transmission output shaft, with driving wheel
Connection；The gear of crank-type by the driving force speed change of the transmission input shaft and can pass to the speed changer
Output shaft；And auxiliary power transfer unit, it configures, can be exported in the driving source side by side relative to the gear
Driving force is transmitted between axis and the transmission output shaft, the auxiliary power transfer unit consists of the following parts：Input is wanted
Element is rotated integrally by spring element with the driving source output shaft；Element is exported, is connected with the transmission output shaft
It connects；And intermediate elements, the input element and the output element are connected, the 1st of the power transmission apparatus for vehicle is special
Sign is that the clutch has：Clutch input part is rotated integrally with the input element；Clutch output block,
It is rotated integrally with the transmission input shaft；And clutch workpiece, make the clutch output block with it is described
Clutch input part engages, and the driving force of the driving source output shaft is passed to the transmission input shaft, by described
Spring element connects the driving source output shaft and the clutch input part, also, by bearing that the clutch is defeated
Enter parts carry in case of transmission.
In addition, according to the present invention it is proposed that a kind of power transmission apparatus for vehicle, other than the 1st feature, the 2nd
It is characterized in that, passes through institute using the clutch input part as the 2nd mass using the driving source output shaft as the 1st mass
State the 1st mass, the spring element and the 2nd mass make the driving source rotation change decaying after be transferred to the change
Fast device input shaft.
In addition, according to the present invention it is proposed that a kind of power transmission apparatus for vehicle, other than the 1st or the 2nd feature,
It the 3rd is characterized in that the bearing is ball bearing.
In addition, according to the present invention it is proposed that a kind of power transmission apparatus for vehicle, in addition to any one in the described 1st~the 3rd
Except a feature, the 4th is characterized in that, the hollow portion that the input element has diameter bigger than the bearing, the input is wanted
Element is supported on the case of transmission in the inside of the hollow portion by the bearing.
In addition, the input shaft main part 11A of embodiment with the present invention transmission input shaft it is corresponding, embodiment it is defeated
Enter axis upstream portion 11B and the driving source output shaft of the present invention is correspondings, the output shaft downstream portion 12B of embodiment and change of the invention
Fast device output shaft corresponds to, and the input gear 26 of embodiment is corresponding with the input element of the present invention, the output gear of embodiment
27 is corresponding with the output element of the present invention, and the idler gear 28 of embodiment is corresponding with the intermediate elements of the present invention, embodiment
Torsional spring 51a and the spring element of the present invention it is correspondings, the dry clutch 52 of embodiment is corresponding with clutch of the invention, reality
The ball bearing 57 for applying mode is corresponding with the bearing of the present invention, and the engine E of embodiment is corresponding with the driving source of the present invention, implements
The variable-speed unit U of mode is corresponding with the gear of the present invention.
Invention effect
1st feature according to the present invention, has：Transmission input shaft, by the clutch by with driven by driving source
Driving source exports axis connection；Transmission output shaft is connect with driving wheel；The gear of crank-type, can be by speed changer
The driving force speed change of input shaft simultaneously passes to transmission output shaft；And auxiliary power transfer unit, relative to gear
Configuration side by side, can transmit driving force between driving source output shaft and transmission output shaft, auxiliary power transfer unit by with
Lower part is constituted：Element is inputted, is rotated integrally with driving source output shaft；Element is exported, is connect with transmission output shaft；With
And intermediate elements, connection input element therefore, will be from when transmission input shaft is blocked and can not be rotated with output element
Clutch debonding and driving source output shaft is detached from transmission input shaft, by auxiliary power transfer unit by driving source
Driving force is transmitted from driving source output shaft to transmission output shaft, and thereby, it is possible to so that vehicle is kept out of the way by the driving force of driving source
Drive to repair shop.
Clutch has：Clutch input part is rotated integrally with input element；Clutch output block, with change
Fast device input shaft rotates integrally；And clutch workpiece, so that clutch output block is engaged with clutch input part,
The driving force of driving source output shaft is transmitted to transmission input shaft, driving source output shaft and clutch are connected by spring element
Input part, therefore, can not only by driving source output shaft, clutch input part and spring element constitute damper come
The rotation for absorbing driving source changes, and clutch input part is supported on case of transmission by bearing, therefore, even if driving
Dynamic source has rotation to change, and can also prevent bearing from alternately being driven towards opposite direction, to improve the durability of the bearing.
In addition, the 2nd feature according to the present invention makees clutch input part using driving source output shaft as the 1st mass
For the 2nd mass, transmitted to speed changer after so that the rotation of driving source is changed decaying by the 1st mass, spring element and the 2nd mass
Input shaft realizes the miniaturization of damper therefore, it is possible to which clutch input part is used as the 2nd mass.
In addition, the 3rd feature according to the present invention, since bearing is ball bearing, therefore, it is possible to be effectively prevented because outer ring with
The reciprocal relative rotation of inner ring and cause the durability of ball bearing to decline.
In addition, the 4th feature according to the present invention, the hollow portion that input element has diameter bigger than bearing, input element
Case of transmission is supported on by bearing in the inside of hollow portion, therefore, is configured by using the hollow portion of input element
Bearing can be such that the axial dimension of power transmission apparatus for vehicle minimizes.
Description of the drawings
Fig. 1 is the synoptic diagram of power transmission apparatus for vehicle.(the 1st embodiment)
Fig. 2 is 2 detailed figures of Fig. 1.(the 1st embodiment)
Fig. 3 is the sectional view (OD states) of the 3-3 lines in Fig. 2.(the 1st embodiment)
Fig. 4 is the sectional view (GN states) of the 3-3 lines in Fig. 2.(the 1st embodiment)
Fig. 5 is the Action Specification figure under OD states.(the 1st embodiment)
Fig. 6 is the Action Specification figure under GN states.(the 1st embodiment)
Fig. 7 is that 7 of Fig. 1 scheme in detail.(the 1st embodiment)
Fig. 8 is the table of joint of the 1st, the 2nd engagement switching mechanism.(the 1st embodiment)
Torque flow graph when Fig. 9 is parking shift.(the 1st embodiment)
Torque flow graph when Figure 10 is reverse gear shift.(the 1st embodiment)
Torque flow graph when Figure 11 is neutral gear.(the 1st embodiment)
Torque flow graph (usual transport condition) when Figure 12 is forward gear.(the 1st embodiment)
Torque flow graph (engine-braking condition) when Figure 13 is forward gear.(the 1st embodiment)
Torque flow graph (idle stop state) when Figure 14 is forward gear.(the 1st embodiment)
Torque flow graph (malfunction) when Figure 15 is forward gear.(the 1st embodiment)
Figure 16 is 16 detailed figures of Fig. 1.(the 1st embodiment)
Label declaration
11A：Input shaft main part (transmission input shaft)；
11B：Input shaft upstream portion (driving source output shaft)；
12B：Output shaft downstream portion (transmission output shaft)；
26：Input gear (input element)；
27：Output gear (output element)；
28：Idler gear (intermediate elements)；
29：Auxiliary power transfer unit；
51a：Torsional spring (spring element)；
52：Dry clutch (clutch)；
53：Clutch input part；
54：Clutch output block；
55：Clutch workpiece；
56：Case of transmission；
57：Ball bearing (bearing)；
E：Engine (driving source)；
U：Variable-speed unit (gear)；
W：Driving wheel.
Specific implementation mode
Hereinafter, according to Fig. 1~Figure 16, embodiments of the present invention will be described.
1st embodiment
As shown in Figure 1, the driving force of engine E is transferred to by power transmission apparatus for vehicle via left and right axle 10,10
There is contiuously variable transmission T, the 1st power to transmit switching mechanism S1, the 2nd power biography for driving wheel W, W, the power transmission apparatus for vehicle
Pass switching mechanism S2 and differential mechanism D.1st power transmits switching mechanism S1 and allows hand over parking shift, reverse gear shift, neutral gear and preceding
Into gear.2nd power transmits switching mechanism S2 and allows hand over usually traveling and engine-braking condition, idle stop state and event
Barrier state.
Then, the structure of power transmission apparatus for vehicle is illustrated according to Fig. 1~Fig. 7.
As shown in Figure 1, input shaft 11 is transmitted by input shaft main part 11A and than input shaft main part 11A by driving force
The input shaft upstream portion 11B of direction upstream side (sides engine E) is constituted, and input shaft main part 11A is connect with contiuously variable transmission T,
Input shaft upstream portion 11B is connect with engine E.It is provided with damping between input shaft upstream portion 11B and input shaft main part 11A
Device 51 and dry clutch 52.Dry clutch 52 is maintained in engagement state when usual, and in aftermentioned input shaft body
Portion 11A is disengaged when blocking, by input shaft main part 11A and the 11B separation of input shaft upstream portion.
Also, the 1st output shaft 12 leans on driving force transmission side by output shaft main part 12A and than output shaft main part 12A
Downstream the output shaft downstream portion 12B of (sides driving wheel W, W) is constituted, and output shaft main part 12A is connect with contiuously variable transmission T,
Output shaft downstream portion 12B transmits switching mechanism S2 with the 2nd power and connect.Output shaft main part 12A and output shaft downstream portion 12B begin
It is integrated eventually.
As shown in Figures 2 and 3, the contiuously variable transmission T of present embodiment is that overlapping is more with same structure in the axial direction
Made of a (being in embodiments 4) variable-speed unit U ..., these variable-speed units U ... has the shared defeated of configured in parallel
Enter axis 11 and the 1st shared output shaft 12, the rotation of input shaft 11 be decelerated or speedup after be transferred to the 1st output shaft 12.
In the following, being illustrated to the structure of a variable-speed unit U as representing.The input for connecting and rotating with engine E
Axis 11 by relative rotation freely in a manner of the shifting actuator 14 as the electro-motor hollow rotary shaft 14a in
Portion.The rotor 14b of shifting actuator 14 is fixed on rotary shaft 14a, and stator 14c is fixed on shell.The rotation of shifting actuator 14
Axis 14a can be rotated with input shaft 11 with identical speed, further, it is possible to relative to the opposite rotation at different rates of input shaft 11
Turn.
It is fixed with the 1st pinion gear 15 on the input shaft 11 through the rotary shaft 14a of shifting actuator 14, is somebody's turn to do with crossing over
The planet carrier 16 of crank is connected to the rotary shaft 14a of shifting actuator 14 by the mode of the 1st pinion gear 15.Diameter and the 1st small tooth
Take turns 15 identical 2 the 2nd pinion gears 17,17 be supported on by means respectively of pinion pin 16a, 16a cooperate with the 1st pinion gear 15 and
Constitute equilateral triangle position on, gear ring 18a is eccentrically formed in the inside of the eccentric disc 18 of circular plate type, gear ring 18a and this
A little 1st pinion gears 15 and the engagement of the 2nd pinion gear 17,17.The ring portion 19b warps being set on one end of the bar portion 19a of connecting rod 19
By ball bearing 20 by relative rotation freely in a manner of be sleeved on the peripheral surface of eccentric disc 18.
The 1st one-way clutch 21 for being set to the periphery of the 1st output shaft 12 has：Cricoid exterior part 22, by means of
Pin 19c and be pivotally supported at the bar portion 19a of connecting rod 19；Inner part 23, is configured at the inside of exterior part 22, and is fixed on
1st output shaft 12；And roller 25 ... is configured in the flat of the periphery of the arc surface and inner part 23 of the inner circumferential of exterior part 22
It exerts a force in the wedge-shaped space formed between face, and by spring 24 ....
It could be aware that from Fig. 2,4 variable-speed unit U ... have the planet carrier 16 of shared crank-like, and small by means of the 2nd
The phase for the eccentric disc 18 that gear 17,17 is supported on planet carrier 16 differs 90 ° respectively according to each variable-speed unit U.For example,
In Fig. 2, the eccentric disc 18 of the variable-speed unit U of left end is displaced to top in figure relative to input shaft 11, from left to right the 3rd variable-speed unit
The eccentric disc 18 of U is displaced to lower section in figure relative to input shaft 11, from left to right the eccentric disc of the 2nd and the 4th variable-speed unit U, U
18,18 are located at upper and lower directions centre position.
It could be aware that from Fig. 1, contiuously variable transmission T is had and can be passed with the path different from above-mentioned 4 variable-speed unit U ...
Pass the complementary power transfer path of driving force.That is, being set to the input gear 26 in the downstream side of damper 51 and being set to
The output gear 27 of transmission axle 13 is connected via idler gear 28, the transmission axle 13 by relative rotation freely in a manner of be sleeved on
On the periphery of the output shaft downstream portion 12B in the downstream side of output shaft main part 12A, these input gears 26, output gear 27 with
And idler gear 28 constitutes auxiliary power transfer unit 29.
It could be aware that from Fig. 7, the 1st power transmits switching mechanism S1 in addition to being sleeved on axle 10 freely with relative rotation
1st output shaft 12 of the tubular on periphery is also sleeved on the 2nd defeated of the tubular on the periphery of axle 10 freely with relative rotation
Shaft 31 and relative rotation are sleeved on the 3rd output shaft 32 of the tubular on the periphery of the 2nd output shaft 31 freely.It is defeated the 1st
The right end of the output shaft downstream portion 12B of shaft 12 is formed with the 4th periphery spline 12a, and is formed in the left end of the 2nd output shaft 31
5 periphery spline 31a are formed with the 6th periphery spline 32a in the left end of the 3rd output shaft 32.
Form the 4th periphery spline 12a, the 5th periphery spline of the 1st engagement switching mechanism 33 being made of jaw clutch
31a and the 6th periphery spline 32a are axially aligned, and the outer diameter of the 5th periphery spline 31a and the 6th periphery spline 32a are equal to each other, and
And it is smaller than the outer diameter of the 4th periphery spline 12a.Also, the sleeve 34 of the 1st engagement switching mechanism 33 has in the outer diameter is larger the 2nd
Zhou Huajian 34a and outer diameter smaller the 3rd inner circumferential spline 34b, the 2nd inner circumferential spline 34a are engaged always with the 4th periphery spline 12a, and
3 inner circumferential spline 34b are engaged always with the 6th periphery spline 32a, the 3rd inner circumferential spline 34b it is only shown in Fig. 7 when being moved to the left with
5th periphery spline 31a is engaged.That is, when sleeve 34 by shift fork 34c from it is as shown in Figure 7 move to left state move right when,
3 inner circumferential spline 34b are released from the 5th engaging for periphery spline 31a.
Planetary gear mechanism 35 has：Sun gear 36 as the 1st element；Planet carrier 37 as the 3rd element；As
The gear ring 38 of 2 elements；And relative rotation is supported on multiple pinion gears 39 ... of planet carrier 37 freely, pinion gear 39 ... with too
Sun wheel 36 and gear ring 38 engage.Sun gear 36 is connect with the right end of the 3rd output shaft 32, the right end of gear ring 38 and the 2nd output shaft 31
Connection.
It is formed with the 1st inner circumferential spline on the sleeve 41 for the 2nd engagement switching mechanism 40 being made of jaw clutch
41a, the 1st inner circumferential spline 41a and be formed in planet carrier 37 peripheral part periphery spline 37a and be formed in the periphery of shell 42
Spline 42a engagements.Therefore, when sleeve 41 is moved to the left by shift fork 41b to position shown in Fig. 7, planet carrier 37 is from shell
42 separation, when sleeve 41 is moved right by shift fork 41b from position shown in Fig. 8, planet carrier 37 is combined with shell 42.
2nd power transmits switching mechanism S2 and is arranged between transmission axle 13 and output shaft downstream portion 12B, and the 2nd power transmits
Switching mechanism S2 has：It is set to the 1st periphery spline 13a of transmission axle 13；It is set to the 2nd periphery of output shaft downstream portion 12B
Spline 12b and the 3rd periphery spline 12c；Sleeve 43 with inner circumferential spline 43a；The shift fork 43b of drive sleeve 43；And configuration
The 2nd one-way clutch 45 between output shaft downstream portion 12B and the 2nd periphery spline 12b.
Sleeve 43 can take following position：Shift left what the 1st periphery spline 13a and the 2nd periphery spline 12b was combined
It sets；The middle position that 1st periphery spline 13a, the 2nd periphery spline 12b and the 3rd periphery spline 12c are combined；And it will be outside the 2nd
What Zhou Huajian 12b and the 3rd periphery spline 12c were combined moves to right position.Also, it is more than to transmit in the rotating speed of output shaft downstream portion 12B
When the rotating speed of axis 13, the 2nd one-way clutch 45 configured between output shaft downstream portion 12B and the 2nd periphery spline 12b is connect
It closes.
The differential carrier 47 for constituting the outer profile of differential mechanism D is connect with the right end of the 2nd output shaft 31.Differential mechanism D has：One
To pinion gear 49,49, they are rotatably freely supported on the pinion shaft 48 for being fixed on differential carrier 47；And side gear
50,50, they are fixedly installed on the end of axle 10,10 and are engaged with pinion gear 49,49.
As shown in figure 16, configuration has in the dry clutch 52 of the radially inner side of damper 51 from the sides variable-speed unit U ...
Clutch input part 53, clutch output block 54 and the clutch workpiece 55 stacked gradually towards the sides engine E.
The damper 51 being configured between input shaft upstream portion 11B and input shaft main part 11A is double quality dampings of known construction
Device will be made up of the input shaft upstream portion 11B and composition of an inferior quality the multiple torsional spring 51a ... that can be stretched in the circumferential
The clutch input part 53 of two inferior qualities connects.The input gear 26 of auxiliary power transfer unit 29 is integrally formed at work
On clutch input part 53 for two inferior qualities of damper 51, these clutch input parts 53 and input gear 26 pass through
Case of transmission 56 is supported on by rotary shaft by ball bearing 57.Clutch output block 54 is connect with input shaft main part 11A, from
Clutch workpiece 55 is connect by means of clutch working beam 58 with clutch actuator 59, and clutch working beam 58 is coaxially
Through the inside of hollow input shaft main part 11A.
By spring (not shown), the left side into figure exerts a force clutch working beam 58, by means of clutch working beam 58, clutch
Clutch output block 54 is pressed against clutch input part 53, clutch output block 54 and clutch by device workpiece 55
Input part 53 is integrally formed, as a result, the engagement of dry clutch 52 and by input shaft upstream portion 11B and input shaft main part 11A
It is combined as a whole.When using the driving clutch working beam 58 in right side into figure of clutch actuator 59, worked based on clutch
The pressing of component 55 is released from, and clutch output block 54 and clutch input part 53 detach, and the releasing of dry clutch 52 connects
It closes, to relieve the transmission of the driving force between input shaft upstream portion 11B and input shaft main part 11A.
Then, to having the function of that the embodiments of the present invention of above structure illustrate.
First, the effect of a variable-speed unit U of contiuously variable transmission T is illustrated.When the rotation for making shifting actuator 14
When shaft 14a is relative to 11 relative rotation of input shaft, axis L1 rotation of the planet carrier 16 around input shaft 11.At this point, planet carrier 16
Center O, i.e. the 1st pinion gear 15 and 2 the 2nd pinion gears 17,17 be formed by axis of the center around input shaft 11 of equilateral triangle
Line L1 rotations.
Fig. 3 and Fig. 5 shows that the center O of planet carrier 16 is located at the 1st output relative to the 1st pinion gear 15 (i.e. input shaft 11)
The state of the opposite side of axis 12, eccentric disc 18 is maximum relative to the eccentricity of input shaft 11 at this time, the gear ratio of contiuously variable transmission T
As OD (over drive, hypervelocity driving) state (hypervelocity driving condition).Fig. 4 and Fig. 6 shows the center O phases of planet carrier 16
It is located at the state of side identical with the 1st output shaft 12 for the 1st pinion gear 15 (i.e. input shaft 11), eccentric disc 18 is opposite at this time
It is zero in the eccentricity of input shaft 11, the gear ratio of contiuously variable transmission T becomes GN (gear neutral, Geared neutral) state
(Geared neutral state).
Under OD states shown in Fig. 5, when using engine E make input shaft 11 rotate and with identical as input shaft 11
Speed when making the rotary shaft 14a rotation of shifting actuator 14, input shaft 11, rotary shaft 14a, planet carrier 16, the 1st pinion gear
15,2 the 2nd pinion gears 17,17 and eccentric disc 18 are in the state of being integrally formed, centered on input shaft 11 counterclockwise
(reference arrow A) is eccentrically rotated.During (A) from Fig. 5 is rotated via (B) of Fig. 5 to the state of (C) of Fig. 5, by ring portion
19b makes to pivot by pin 19c via the connecting rod 19 that 20 relative rotation of ball bearing is supported on freely on the periphery of eccentric disc 18
It is supported on (reference arrow B) rotation counterclockwise of exterior part 22 of the end of bar portion 19a.(A) of Fig. 5 and (C) of Fig. 5
Show the both ends of rotation of the exterior part 22 along the directions the arrow B.
When exterior part 22 is rotated to the directions arrow B in this way, the exterior part 22 of engaging-in 1st one-way clutch 21 of roller 25 ...
In wedge-shaped space between inner part 23, the rotation of exterior part 22 is transferred to the 1st output shaft 12 via inner part 23, because
(reference arrow C) rotates this 1st output shaft 12 counterclockwise.
When input shaft 11 and the 1st pinion gear 15 further rotate, make gear ring 18a and the 1st pinion gear 15 and the 2nd pinion gear
17, (reference arrow A) is eccentrically rotated the eccentric disc 18 of 17 engagements counterclockwise.(C) from Fig. 5 via Fig. 5 (D) to
During the state rotation of (A) of Fig. 5, ring portion 19b is supported on eccentric disc 18 freely via 20 relative rotation of ball bearing
Connecting rod 19 on periphery makes the exterior part 22 by the ends for being pivotally supported at bar portion 19a pin 19c (join clockwise
According to arrow B ') rotation.(C) of Fig. 5 and (A) of Fig. 5 show the both ends of the rotation along the directions the arrow B ' of exterior part 22.
Byed from outside while roller 25 ... is on one side compressed spring 24 ... when exterior part 22 is rotated to the directions arrow B ' in this way
Wedge-shaped space between part 22 and inner part 23 squeezes out, and exterior part 22 skids relative to inner part 23 as a result, to which the 1st is defeated
Shaft 12 does not rotate.
As described above, in 22 reciprocating rotary of exterior part, due to only in the direction of rotation of exterior part 22 for counterclockwise
(reference arrow C) rotates the 1st output shaft 12 counterclockwise when (reference arrow B), and therefore, the 1st output shaft 12 intermittently revolves
Turn.
Effect when Fig. 6 shows to operate contiuously variable transmission T under GN states.At this point, due to input shaft 11 position with partially
The center of cartridge 18 is consistent, and therefore, eccentric disc 18 is zero relative to the eccentricity of input shaft 11.When in this state using starting
When machine E is made input shaft 11 rotate and is made the rotary shaft 14a rotations of shifting actuator 14 with speed identical with input shaft 11,
Input shaft 11, rotary shaft 14a, planet carrier 16,15,2 the 2nd pinion gears 17,17 of the 1st pinion gear and eccentric disc 18 are as one
In the state of body, (reference arrow A) is eccentrically rotated counterclockwise centered on input shaft 11.However, due to eccentric disc 18
Eccentricity be zero, therefore, the stroke of the reciprocating motion of connecting rod 19 also becomes zero, and the 1st output shaft 12 does not rotate.
Therefore, as long as driving shifting actuator 14 and the position of planet carrier 16 being set in the OD states of Fig. 3 and the GN of Fig. 4
Between state, it will be able to be operated with the arbitrary gear ratio between minimum gear ratio and maximum (infinity) gear ratio.
In contiuously variable transmission T, the phase of the eccentric disc 18 ... of the 4 variable-speed unit U ... configured side by side is wrong separately from each other
90 ° are opened, it is therefore, by alternately transmitting driving force by 4 variable-speed unit U ..., i.e. arbitrary in 4 the 1st one-way clutch 21 ...
One is necessarily in engagement state, and thereby, it is possible to make 12 continuous rotation of the 1st output shaft.
Then, to switching parking shift, reverse gear shift, neutral gear and forward gear the 1st power transmit the effect of switching mechanism S1 into
Row explanation.
As shown in Figure 8 and Figure 9, when making the sleeve 34 of the 1st engagement switching mechanism 33 be moved to the left, by the 1st output shaft 12
Output shaft downstream portion 12B, the 2nd output shaft 31 and the 3rd output shaft 32 are combined as a whole, also, make the 2nd engagement switching mechanism 40
Sleeve 41 when moving right and the planet carrier 37 of planetary gear mechanism 35 being made to be combined with shell 42, establish parking shift.
In parking shift, the gear ring 38 of planetary gear mechanism 35 is incorporated into the 2nd output shaft 31 of 47 one of differential carrier,
Also, the 2nd output shaft 31 via the 1st engagement switching mechanism 33 and the 3rd output shaft 32 and too with planetary gear mechanism 35
36 connection of sun wheel, in addition, the planet carrier 37 of planetary gear mechanism 35 is combined via the 2nd engagement switching mechanism 40 with shell 42.
As a result, planetary gear mechanism 35 becomes lock-out state, it is constrained to not via differential mechanism D driving wheel W, W connected to it
It can rotation.
As shown in figs, when making the sleeve 34 of the 1st engagement switching mechanism 33 move right, by output shaft downstream portion
12B and the 3rd output shaft 32 in conjunction with and detach the 2nd output shaft 31, also, the sleeve 41 of the 2nd engagement switching mechanism 40 is made to move right
When moving and being combined the planet carrier of planetary gear mechanism 35 37 with shell 42, reverse gear shift is established.
In reverse gear shift, be output to from contiuously variable transmission T the driving force of the output shaft downstream portion 12B of the 1st output shaft 12 with
The path of the 1st engagement 37 → gear ring of output shaft 32 → sun gear, 36 → planet carrier 38 of switching mechanism 33 → the 3rd is passed to differential
Device shell 47, while slowing down and inverting in planetary gear mechanism 35, thereby, it is possible to so that vehicle rollback is travelled.
As shown in Figure 8 and Figure 11, when making the sleeve 34 of the 1st engagement switching mechanism 33 move right, by output shaft downstream portion
12B and the 3rd output shaft 32 in conjunction with and detach the 2nd output shaft 31, and the sleeve 41 of the 2nd engagement switching mechanism 40 is made to be moved to the left
And when detaching the planet carrier 37 of planetary gear mechanism 35 from shell 42, establish neutral gear.
In neutral gear, since the planet carrier 37 of planetary gear mechanism 35 is detached from shell 42, gear ring 38 can be free
Rotation, also, since the 2nd output shaft 31 can rotate freely, differential carrier 47 can rotate freely and become driving wheel
W, the not confined states of W.In this state, the driving force of engine E from contiuously variable transmission T with output shaft downstream portion 12B →
The path of the 1st engagement output shaft 32 of switching mechanism 33 → the 3rd is passed to sun gear 36, and due to planet carrier 37 there is no limit,
Therefore planetary gear mechanism 35 dallies, and driving force will not be passed to differential mechanism D.
As shown in figs. 9 and 12, when making the sleeve 34 of the 1st engagement switching mechanism 33 be moved to the left, by output shaft downstream portion
12B, the 2nd output shaft 31 and the 3rd output shaft 32 are combined as a whole, and make the sleeve 41 of the 2nd engagement switching mechanism 40 to moving to left
When moving and detaching the planet carrier of planetary gear mechanism 35 37 from shell 42, forward gear is established.
In forward gear, since the gear ring 38 of planetary gear mechanism 35 engages switching mechanism 33 with sun gear 36 by the 1st
And combine, therefore, planetary gear mechanism 35 becomes the state that can be rotated integrally.As a result, being output to from contiuously variable transmission T
The driving force of output shaft downstream portion 12B is cut with the path of the 1st engagement output shaft 31 of switching mechanism 33 → the 2nd or with the 1st engagement
The path of the 37 → gear ring of output shaft 32 → sun gear, 36 → planet carrier 38 of converting mechanism 33 → the 3rd is passed to differential carrier 47, energy
Enough make vehicle advance to travel.
As described above, the 1st output shaft 12 of the contiuously variable transmission T about present embodiment, due to via the 1st one-way clutch
Device 21 ... transfers a driving force to the 1st output shaft 12, thus the travel direction rotation that can only march forward, and by that will have advance
The 1st power transmission switching mechanism S1 for retreating handoff functionality is configured in the downstream side of the 1st output shaft 12, can be after without setting
The electro-motor that regression is sailed in the case of realizing hybrid power, makes vehicle carry out retrogressing traveling.
Moreover, because the 1st power transmits switching mechanism S1 can also establish parking shift other than forward gear and reverse gear shift
And neutral gear, therefore, it is possible to further make power transmission itself miniaturization.
Then, switching mechanism is transmitted to the 2nd power of switching engine on-position, idle stop state and malfunction
The effect of S2 illustrates.
As shown in fig. 10 and fig. 12, it transmits switching mechanism S1 in the 1st power and is in above-mentioned parking shift, reverse gear shift, neutral gear
And under the usual state of any one in forward gear, the sleeve 41 that the 2nd power transmits switching mechanism S2 is moved to the left and connects
Meet the 2nd periphery spline 12b of the 1st periphery spline 13a and output shaft downstream portion 12B of transmission axle 13.Therefore, in forward gear or
In traveling when car bumper, the driving force of engine E is not only transferred to output shaft downstream portion from input shaft 11 via variable-speed unit U ...
12B, and transmitted from input shaft 11 by the auxiliary power being made of input gear 26, idler gear 28 and output gear 27
Unit 29 and be transferred to transmission axle 13, be transferred to outside the 2nd of output shaft downstream portion 12B from the 1st periphery spline 13a of transmission axle 13
Zhou Huajian 12b.
However, due to the gear ratio of variable-speed unit U ... be set to it is bigger than the gear ratio of auxiliary power transfer unit 29, because
This, the rotating speed (that is, rotating speed of the 2nd periphery spline 12b) of transmission axle 13 is bigger than the rotating speed of output shaft downstream portion 12B, the 2nd unidirectionally from
45 debonding of clutch and without via auxiliary power transfer unit 29 power transmission, vehicle is by means of via variable-speed unit
The power of U ... transmits and carries out advance traveling or retreat traveling.
When being transferred to deceleration regime in the advance traveling when vehicle is in forward gear, as shown in figure 13, engine speed drop
Low, the 1st one-way clutch 21 ... the debonding of variable-speed unit U ... as a result, the driving force from driving wheel W, W is via differential
Device D and the 1st power transmit switching mechanism S1 and are transferred to output shaft downstream portion 12B.At this point, the rotating speed of output shaft downstream portion 12B
Than the transmission axle 13 that is connect with input shaft 11 via auxiliary power transmission mechanism 29 rotating speed (that is, the 2nd periphery spline 12b
Rotating speed) greatly, the engagement of the 2nd one-way clutch 45, thus the driving force of output shaft downstream portion 12B can be via auxiliary power transmission machine
Structure 29 and input shaft 11 and it is inverse be transferred to engine E, engine brake can be made to work.
In the case that even vehicle is slowed down in the retrogressing traveling in reverse gear shift, due to output shaft downstream portion
12B is to identical direction rotates when driving with advance when forward gear, thus, it is also possible to similarly make engine brake work
Make.
When further slowing down in the advance traveling when vehicle is in forward gear, as shown in figure 14, the 2nd power is made to transmit switching
The sleeve 41 of mechanism S2 moves right and ties the 2nd periphery spline 12b of output shaft downstream portion 12B and the 3rd periphery spline 12c
It closes.As a result, by from the output shaft downstream portion 12B that the inverse driving force transmitted of driving wheel W, W rotates from transmission axle 13
(that is, from engine E) is detached, therefore, it is possible to realize the idle stop in Reduced Speed Now, so as to realize fuel consumption
It saves and reduces.
In the case where variable-speed unit U ... breaks down and vehicle cannot travel, as shown in figure 15, the 2nd power is made to transmit
The sleeve 41 of switching mechanism S2 is centrally located and by the 1st periphery spline 13a of transmission axle 13, output shaft downstream portion 12B
2nd periphery spline 12b and the 3rd periphery spline 12c is combined.As a result, transmission axle 13 and output shaft downstream portion 12B without
2nd one-way clutch 45 and be directly connected to, therefore, it is possible to which the driving force of engine E is passed from input shaft 11 via auxiliary power
It passs unit 29, transmission axle 13, output shaft downstream portion 12B, the 1st power transmission switching mechanism S1 and differential mechanism D and is transferred to driving wheel
W, W can make vehicle advance traveling or retreat to drive to repair shop.
Additionally, there are following situations：Because supporting the ball bearing (not shown) or support connection bar 19 of input shaft main part 11A
Ring portion 19b ball bearing 20 (with reference to Fig. 3) breakage, and generate input shaft main part 11A and block without revolvable failure.
In the case where generating the failure, if engine E is connect indissociably with input shaft main part 11A, engine E it is flame-out and
It can not operate, thus there are problems that vehicle cannot travel.
However, according to the present embodiment, by connecing the releasing of dry clutch 52 when input shaft main part 11A is blocked
It closes, therefore the mould of the malfunction illustrated by Figure 15 is switched to from input shaft main part 11A separation input shaft upstream portion 11B
Formula, thereby, it is possible to by auxiliary power transfer unit 29 by the driving force of engine E from input shaft upstream portion 11B without nothing
It is transferred to grade speed changer T output shaft downstream portion 12B, to make vehicle carry out keeping out of the way traveling.
During this keeps out of the way traveling, since engine E and driving wheel W, W are directly connected to, thus, it is also possible to make to start mechanism
Dynamic device work, still, there are the following problems：When the vehicle is stopped, the engine E being directly connected to driving wheel W, W is flame-out.So
And according to the present embodiment, when being moved to the left the sleeve 41 of the 2nd power transmission switching mechanism S2 when vehicle stops, connecting
When the 2nd periphery spline 12b of the 1st periphery spline 13a and output shaft downstream portion 12B of transmission axle 13, it is input to transmission axle 13
The driving force of engine E is transferred to output shaft downstream portion 12B because the 2nd one-way clutch 45 is slipping without, even if stopping in vehicle
Also idle running can be carried out in the state of only in the case where not making engine E flame-out.
In addition, in the case of the failure other than the blocking of input shaft main part 11A, due to input shaft main part 11A energy
Enough rotations, therefore the engagement of dry clutch 52 not have to be released, as long as and release dry clutch 52 engagement and from
Input shaft upstream portion 11B separation input shaft main parts 11A, it will be able to prevent the towing of contiuously variable transmission T from disappearing to save fuel
Consumption.
As described above, according to the present embodiment, the axial dimension enlargement of power transmission apparatus for vehicle need not be made
Electro-motor can make vehicle carry out advance traveling and retreat traveling, can be carried out when driving with retrogressing when driving advancing
Engine braking, and row when can realize idle stop and variable-speed unit U ... failure of the vehicle in Reduced Speed Now
It sails.Also, the axial dimension for 11 side of input shaft of power transmission apparatus for vehicle being connect with engine E is easy enlargement, but
It is that can inhibit the enlargement of the axial dimension of 11 side of input shaft in 12 side of the 1st output shaft by being arranged transmission axle 13, it can
The axial dimension of power transmission apparatus for vehicle is inhibited in minimum limit on the whole.
Also, it is as a result, between input shaft main part 11A and input shaft upstream portion 11B by the configuration of dry clutch 52
So that input shaft main part 11A is blocked failure also can make vehicle carry out keeping out of the way traveling.Also, it is small by using axial dimension
Dry clutch 52, the enlargement of the axial dimension of power transmission apparatus for vehicle can be avoided.Moreover, because by damper
51 configurations are between engine E and input shaft upstream portion 11B, therefore, damper 51 can be also played during keeping out of the way traveling
Shock-absorbing function and ensure riding comfort.
As shown in figure 16, it is input into the inferior quality as damper 51 when the rotation of the bent axle of engine E changes
When input shaft upstream portion 11B, the torsional spring 51a ... that is configured between two inferior qualities, that is, clutch input part 53 of side downstream
Flexible, the rotation variation as a result, is absorbed.At this point, since clutch input part 53 by ball bearing 57 is supported on speed change
Device shell 56, therefore, even if torsional spring 51a ... is flexible, 53 relative rotation of input shaft upstream portion 11B and clutch input part, from
Clutch input part 53 is also constant relative to the direction of rotation of case of transmission 56, therefore, the outer ring of ball bearing 57 and inner ring
Relative rotation direction is also constant.
Assuming that clutch input part 53 is supported on input shaft upstream portion 11B by ball bearing, then when torsional spring 51a ... stretches
When contracting, input shaft upstream portion 11B and clutch 53 relative rotation of input part, be configured at the ball bearing between them outer ring and
Inner ring is alternately towards opposite direction relative rotation, the problem of decline accordingly, there exist the durability of the ball bearing.But according to
Present embodiment, since clutch input part 53 is supported on case of transmission 56 by ball bearing 57, ball bearing 57
Outer ring is with inner ring always towards same direction relative rotation, it is ensured that its durability.
Further, since the clutch input part 53 of dry clutch 52 is used as to the 2nd mass of damper 51, therefore,
Special 2nd mass need not be set, can realize the miniaturization of damper 51.Moreover, auxiliary power transfer unit 29 is defeated
Enter gear 26 and be formed as cyclic annular, the inside in sky portion, clutch input part 53 are supported on speed changer by ball bearing 57 wherein
Shell 56, therefore, it is possible to efficiently use the hollow portion of input gear 26, to realize contiuously variable transmission T axial dimension it is small
Type.
More than, embodiments of the present invention are illustrated, still, the present invention can in the range of not departing from its main idea
To carry out various design alterations.
For example, the bearing of the present invention is not limited to the ball bearing 57 of embodiment, the roller bearing of construction can be arbitrary
Deng the bearing of other forms.
In addition, the clutch of the present invention is not limited to the dry clutch 52 of present embodiment, can also be wet clutch.
Claims (4)
1. a kind of power transmission apparatus for vehicle, has：
Transmission input shaft (11A), by clutch (52) with the driving source output shaft (11B) that is driven by driving source (E)
Connection；Transmission output shaft (12B) is connect with driving wheel (W)；The gear (U) of crank-type, can be by the speed change
The driving force speed change of device input shaft (11A) simultaneously passes to the transmission output shaft (12B)；And auxiliary power transfer unit
(29), it is configured side by side relative to the gear (U), it can be in the driving source output shaft (11B) and the speed changer
Driving force is transmitted between output shaft (12B), the auxiliary power transfer unit (29) consists of the following parts：Input element
(26), it is rotated integrally with the driving source output shaft (11B) by spring element (51a)；Element (27) is exported, with institute
State transmission output shaft (12B) connection；And intermediate elements (28), connect the input element (26) and the output element
(27), which is characterized in that,
The clutch (52) has：Clutch input part (53) is rotated integrally with the input element (26)；Clutch
Output block (54) is rotated integrally with the transmission input shaft (11A)；And clutch workpiece (55), make institute
It states clutch output block (54) to engage with the clutch input part (53), by the drive of the driving source output shaft (11B)
Power passes to the transmission input shaft (11A),
The driving source output shaft (11B) and the clutch input part (53) are connected by the spring element (51a), and
And the clutch input part (53) is supported on by case of transmission (56) by bearing (57),
Prevent the inner ring of the bearing from alternately being driven towards opposite direction with outer ring as a result,.
2. power transmission apparatus for vehicle according to claim 1, which is characterized in that
It regard the driving source output shaft (11B) as the 1st mass, regard the clutch input part (53) as the 2nd mass, lead to
Cross the 1st mass, the spring element (51a) and the 2nd mass make the driving source (E) rotation change decaying after
It is transferred to the transmission input shaft (11A).
3. power transmission apparatus for vehicle according to claim 1 or 2, which is characterized in that
The bearing (57) is ball bearing.
4. power transmission apparatus for vehicle according to claim 1, which is characterized in that
The hollow portion that the input element (26) has diameter bigger than the bearing (57), the input element (26) is in described
The inside in empty portion is supported on the case of transmission (56) by the bearing (57).
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2014/060267 WO2015155849A1 (en) | 2014-04-09 | 2014-04-09 | Vehicular power transmission device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106068405A CN106068405A (en) | 2016-11-02 |
| CN106068405B true CN106068405B (en) | 2018-08-07 |
Family
ID=54287451
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201480076966.1A Expired - Fee Related CN106068405B (en) | 2014-04-09 | 2014-04-09 | Power transmission apparatus for vehicle |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6120471B2 (en) |
| CN (1) | CN106068405B (en) |
| WO (1) | WO2015155849A1 (en) |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11190411A (en) * | 1997-12-12 | 1999-07-13 | Hyundai Motor Co Ltd | Vehicular continuously variable transmission |
| JP2009115184A (en) * | 2007-11-06 | 2009-05-28 | Toyota Motor Corp | Dual mass flywheel |
| JP2012255473A (en) * | 2011-06-08 | 2012-12-27 | Honda Motor Co Ltd | Power transmission device for vehicle |
| JP5825684B2 (en) * | 2012-08-09 | 2015-12-02 | 本田技研工業株式会社 | Power transmission device for vehicle |
-
2014
- 2014-04-09 WO PCT/JP2014/060267 patent/WO2015155849A1/en active Application Filing
- 2014-04-09 JP JP2016512525A patent/JP6120471B2/en not_active Expired - Fee Related
- 2014-04-09 CN CN201480076966.1A patent/CN106068405B/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CN106068405A (en) | 2016-11-02 |
| JP6120471B2 (en) | 2017-04-26 |
| WO2015155849A1 (en) | 2015-10-15 |
| JPWO2015155849A1 (en) | 2017-04-13 |
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Granted publication date: 20180807 |