CN106183783A - Stepless speed changing mechanism - Google Patents

Abstract

The present invention provides a kind of stepless speed changing mechanism, and it can suppress because the internal diameter size precision of the through hole through for crankpin caused by the opening of eccentric disc reduces.1st and the 2nd crankshaft journal (16p～16v, 17p～17v) is respectively arranged to: vertically the 1st and the 2nd crankshaft journal (16p～16v, 17p～17v) is projected obtained projection section (N1) and is positioned at the profile (N2) of the 1st and the 2nd crankpin (16p～16v, 17p～17v) being connected with the 1st and the 2nd crankshaft journal (16p～16v, 17p～17v).The axial width (L1) of eccentric disc (14) is less than the axial length (L2) of the 1st and the 2nd crankshaft journal.

Description

Stepless speed changing mechanism

Technical field

The present invention relates to the stepless speed changing mechanism of crank-type, its eccentric rotary of eccentric disc that will rotate together with power shaft The reciprocally swinging of the input block of one-way clutch is converted to via connecting member, and by the reciprocally swinging warp of input block Be converted to the unidirectional intermittent rotary of output shaft by one-way clutch, the present invention be more particularly directed to infinitely to change stepless The stepless speed changing mechanism of the offset of variator.

Background technology

Such buncher is being had: the rotation of the power shaft being connected with electromotor is turned by it described in patent documentation 1 It is changed to the reciprocating motion of connecting rod, and then the one-way clutch that reciprocates through of connecting rod is converted to the rotation of output shaft Transhipment is dynamic.

Patent documentation 1: No. 5142234 publications of Japanese Patent Publication No.

The stepless speed changing mechanism of the crank-type of patent documentation 1 possesses crankshaft component, and this crankshaft component has: multiple bent axles Axle journal, they have common central axis；With multiple crankpins, they with different phase places from crankshaft journal Heart eccentric axis, and the most chimeric on the plurality of crankpin have eccentric disc.Each crankpin is to difference Direction eccentric, therefore, it is impossible to assembled from axially penetrating through insertion crankshaft component by eccentric disc, each eccentric disc is The semicircle shape parts being radially divided into 2 are docked and carries out bolt fastening and constitute.If making bias like this Dish type becomes the docking structure of 2 semicircle shape parts, then when big torque or load act on stepless speed changing mechanism, On 2 semicircle shape parts, effect has the power in direction disconnected from each other and opening, consequently, it is possible to through to crankpin institute The internal diameter size precision of through hole have undesirable effect.Additionally, there are the increase of number of parts or the increasing of assembly work Manufacturing cost is waited greatly to raise such worry.

Summary of the invention

It is an object of the invention to provide a kind of stepless speed changing mechanism, it can make the most chimeric with crankpin Eccentric disc is one-body molded, and is axially assemblied in each crankpin from crankshaft component, it is possible to suppression is because of the opening of eccentric disc The internal diameter size precision of the caused through hole through for crankpin reduces.

In order to reach above-mentioned purpose, the invention described in technical scheme 1 is stepless speed changing mechanism (such as, enforcement described later Stepless speed changing mechanism BD in mode), described stepless speed changing mechanism possesses: power shaft (such as, enforcement described later Power shaft 151 in mode), this power shaft accept from power source produce rotary power and around input central axis (example As, the input central axis O1 in embodiment described later) rotate；(such as, the enforcement described later of multiple eccentric discs Eccentric disc 14 in mode), the plurality of eccentric disc has the 1st fulcrum (such as, reality described later at respective center Execute the 1st fulcrum O3 in mode), each 1st fulcrum being circumferentially about disposed at equal intervals at this input central axis, And each 1st fulcrum is relative to the offset of described input central axis (such as, the bias in embodiment described later Amount r) can be changed, and the plurality of eccentric disc is keeping while this offset around this input central axis with described Power shaft rotates together, and, the plurality of eccentric disc is respectively formed with and described input centerline axis parallel ground Extend the 1st through hole and the 2nd through hole (such as, the 1st through hole 14a in embodiment described later, the 2nd Through hole 14b)；1st crankshaft component (such as, the 1st crankshaft component 16 in embodiment described later), the 1st Crankshaft component has multiple 1st crankpin (such as, the 1st crankpin 16c～16h in embodiment described later) With multiple 1st crankshaft journals (such as, the 1st crankshaft journal 16p～16v in embodiment described later), described many The most through described 1st through hole formed on the plurality of eccentric disc of individual 1st crankpin, and each other Linking, the plurality of 1st crankshaft journal is respectively from central axis (such as, the reality described later of this each 1st crankpin Execute the central axis 16k in mode) position that offset by equidistance has central axis (such as, reality described later Execute the central axis 16b in mode)；2nd crankshaft component (such as, the 2nd crank portion in embodiment described later Part 17), the 2nd crankshaft component has multiple 2nd crankpin (such as, the 2nd bent axle in embodiment described later Pin 17c～17h) and multiple 2nd crankshaft journal (such as, the 2nd crankshaft journal 17p in embodiment described later～ 17v), the plurality of 2nd crankpin the most through formed on the plurality of eccentric disc described 2nd through Hole, and connected to each other, and the plurality of 2nd crankshaft journal is respectively in the central axis (example from this each 2nd crankpin Such as, the central axis 17k in embodiment described later) position that offset by equidistance has central axis (example As, the central axis 17b in embodiment described later)；One-way clutch is (such as, in embodiment described later One-way clutch OWC), this one-way clutch has around the output center axis (example deviateing described input central axis Such as, the output center axes O 2 in embodiment described later) output block (such as, the embodiment party described later that rotates Clutch inner part 121 in formula), by accepting the power of direction of rotation from outside and around described output center axis Swing input block (such as, the clutch Outside part 122 in embodiment described later) and make these input Parts and output block become mutually joint elements (such as, the embodiment described later of lock-out state or non-locking state In roller 123), when the rotating speed of the forward that the rotating speed of the forward of described input block exceedes described output block, should One-way clutch will enter into the rotary power of described input block and is transferred to described output block, thus by described input The oscillating motion of parts is converted to the rotary motion of described output block；(such as, the enforcement described later of multiple connecting members Connecting member 130 in mode), the respective one end of the plurality of connecting member is (such as, in embodiment described later Ring portion 131) centered by described 1st fulcrum, rotatably it is attached at the periphery of each described eccentric disc, the plurality of company The respective other end of knot part (such as, the end 132 in embodiment described later) is rotatably linked in institute State the 2nd fulcrum (example that the position deviateing described output center axis on the input block of one-way clutch is arranged As, the 2nd fulcrum O4 in embodiment described later), thus, described eccentric disc will be put on from described power shaft Rotary motion is transferred to this input block as the oscillating motion of the input block of described one-way clutch；And gear ratio Changeable mechanism (such as, the gear ratio changeable mechanism 112 in embodiment described later), this gear ratio changeable mechanism has Standby actuator (such as, the actuator 180 in embodiment described later), described actuator makes described 1st crankpin Synchronously rotate centered by described 1st and the 2nd crankshaft journal respectively with described 2nd crankpin, regulate described 1 fulcrum relative to the offset of described input central axis, thus change from described eccentric disc be transferred to described unidirectional from The pendulum angle of the oscillating motion of the input block of clutch, thus, described gear ratio changeable mechanism changes being input to The rotary power stating power shaft is transferred to described list via described eccentric disc and described connecting member as rotary power Gear ratio when the output block of clutch, and, owing to described offset can be set as zero such that it is able to Gear ratio is set as infinity, wherein, external diameter (such as, the embodiment described later of the plurality of 1st crankpin In outer diameter D 1) the most equal or become big from side towards opposite side in the axial direction, the plurality of 2nd crankpin External diameter (such as, the outer diameter D 3 in embodiment described later) the most equal or in the axial direction from side towards separately Side becomes big, and the plurality of 1st crankshaft journal is respectively arranged to: throw described 1st crankshaft journal vertically Projection section (such as, projection section N1 in embodiment described later) obtained by shadow is positioned at and the 1st bent axle In the profile (such as, the profile N2 in embodiment described later) of described 1st crankpin that axle journal connects, described Multiple 2nd crankshaft journals are respectively arranged to: vertically described 2nd crankshaft journal is projected obtained projection Described in partly (such as, projection section N1 in embodiment described later) is positioned at and is connected with the 2nd crankshaft journal In the profile (such as, the profile N2 in embodiment described later) of the 2nd crankpin, the axle of the plurality of eccentric disc To width (such as, the axial width L1 in embodiment described later) respectively than described 1st crankshaft journal and described The axial length (such as, the axial length L 2 in embodiment described later) of the 2nd crankshaft journal is little.

It addition, about the invention described in technical scheme 2, in the invention described in technical scheme 1, at described eccentric disc Described 1st through hole of upper formation does not connects with described 2nd through hole.

According to the invention described in technical scheme 1, the external diameter of multiple 1st crankpins is the most equal or in the axial direction from one Side becomes big towards opposite side, and multiple 1st crankshaft journals are respectively arranged to project the 1st crankshaft journal vertically Obtained projection section is positioned at the profile of the 1st crankpin being connected with the 1st crankshaft journal, and, Duo Ge The external diameter of 2 crankpins is the most equal or becomes big from side towards opposite side in the axial direction, and multiple 2nd crankshaft journals divide It is not configured to vertically the 2nd crankshaft journal be projected obtained projection section be positioned at and the 2nd crankshaft journal In the profile of the 2nd crankpin connected.Further, since the axial width of eccentric disc is than the 1st and the 2nd crankshaft journal Axial length is little, therefore, it is possible to will the most radially carry out splitting but integrated eccentric disc is from the 1st and the 2nd The side of crankshaft component is sequentially inserted into towards opposite side and assembles.Therefore, it is possible to prevent because the opening of eccentric disc is drawn The reduction of the internal diameter size precision of the through hole through for crankpin risen, it is possible to prevent the change of offset, thus can Enough suppress the impact that gear ratio is caused.Further, since eccentric disc is one-body molded, therefore, it is possible to cut down number of parts.

According to the invention described in technical scheme 2, the 1st and the 2nd through hole being formed on eccentric disc does not connects, therefore The rigidity of eccentric disc can be improved such that it is able to be more reliably prevented from the change of the offset of eccentric disc.

Accompanying drawing explanation

Fig. 1 is the sectional view of the stepless speed changing mechanism illustrating reference example.

Fig. 2 is the side view of the stepless speed changing mechanism shown in Fig. 1.

Fig. 3 is the axonometric chart of the major part illustrating stepless speed changing mechanism.

Fig. 4 is the side view of each crankshaft component in stepless speed changing mechanism.

Fig. 5 is the side view illustrating 2 kinds of eccentric discs in stepless speed changing mechanism.

Fig. 6 is the explanatory diagram illustrating the position relationship between each eccentric disc and each crankpin that constitute stepless speed changing mechanism.

Fig. 7 be every 60 ° of anglecs of rotation illustrate in stepless speed changing mechanism eccentric disc when offset is fixing The action diagram of the change when input central axis rotates.

Fig. 8 be every each crankshaft component 45 ° of anglecs of rotation the bias of the eccentric disc made in stepless speed changing mechanism is shown The explanatory diagram of quantitative change state more.

Fig. 9 shows the position relationship between each eccentric disc under each offset of stepless speed changing mechanism and each crankpin, Wherein (a) is the figure of the state illustrating that offset r is " zero ", and (b) is to illustrate the state that offset r is " medium " Figure, (c) is the figure of the state illustrating that offset r is " greatly ".

Figure 10 is the schematic diagram of the four joint linkages illustrating stepless speed changing mechanism.

Figure 11 is the one-way clutch external part in the case of the offset difference of the eccentric disc illustrating stepless speed changing mechanism The action diagram of change of oscillating quantity, wherein (a) is the figure of the state illustrating offset r bigger " greatly ", (b) Being the figure of the state illustrating that offset r is less than the situation of (a) " medium ", (c) is to illustrate that offset r is ratio (b) The figure of state of little " little " of situation.

Figure 12 is that the offset r being shown in stepless speed changing mechanism and making the eccentric disc of constant speed rotation together with power shaft (becomes Speed ratio i) is changed in the case of " greatly ", " medium ", " little ", anglec of rotation θ of power shaft and one-way clutch Input block angle of oscillation speed omega 2 between the figure of relation.

Figure 13 is for illustrating in stepless speed changing mechanism when utilizing multiple connecting member from input side (power shaft or inclined Cartridge) figure of derivation principle of output when outlet side (output block of one-way clutch) transmission power.

Figure 14 is the sectional view of the stepless speed changing mechanism illustrating the present invention.

Figure 15 is the three-dimensional cutaway view illustrating the state that eccentric disc is assemblied in crankshaft component.

Figure 16 is the axonometric chart illustrated eccentric disc relative to the assembling of crankshaft component.

Figure 17 is the top view of crankshaft component and eccentric disc.

(a) of Figure 18 is the right side view of Figure 17, and (b) is the section view of the XVIII XVIII line along Figure 17 Figure.

Figure 19 is crankshaft component and the axonometric chart of eccentric disc of the assembling when the offset of eccentric disc is zero.

Label declaration

14: eccentric disc；

14a: the 1 through hole；

14b: the 2 through hole；

16: the 1 crankshaft components；

The central axis of the 16b: the 1 crankshaft journal；

16c～16h: the 1 crankpin；

16k: the central axis of each 1st crankpin；

16p～16v: the 1 crankshaft journal；

17: the 2 crankshaft components；

The central axis of the 17b: the 2 crankshaft journal；

17c～17h: the 2 crankpin；

17k: the central axis of each 2nd crankpin；

17p～17v: the 2 crankshaft journal；

112: gear ratio changeable mechanism；

121: clutch inner part (output block)；

122: clutch Outside part (input block)；

123: roller (joint elements)；

130: connecting member；

131: ring portion (one end)；

132: end (other end)；

151: power shaft；

180: actuator；

BD ': stepless speed changing mechanism；

The external diameter of the D1: the 1 crankpin；

The external diameter of the D2: the 1 crankshaft journal；

The external diameter of the D3: the 2 crankpin；

The external diameter of the D4: the 2 crankshaft journal；

The aperture (diameter of the 1st through hole) of the D5: the 1 through hole；

The aperture (diameter of the 2nd through hole) of the D6: the 2 through hole；

The axial width of L1: eccentric disc；

L2: the 1 and the 2nd axial length of crankshaft journal；

N1: projection section；

N2: profile；

O1: input central axis；

O2: output center axis；

O3: the 1 fulcrum；

O4: the 2 fulcrum；

OWC: one-way clutch；

R: offset.

Detailed description of the invention

First, referring to figs. 1 through Figure 13, to the ginseng with the basic structure identical with the stepless speed changing mechanism of the present invention Examine example to illustrate.

The stepless speed changing mechanism of reference example be referred to as IVT (Infinity Variable Transmission=do not use from Make gear ratio infinitely great in the case of clutch it is thus possible to make output rotate to be the gear of mode of zero) variable-speed motor The one of structure, it is made up of following such stepless speed changing mechanism BD: this stepless speed changing mechanism BD can be infinitely Change gear ratio i, and the maximum of gear ratio can be set as infinity (∞).

As it is shown in figure 1, stepless speed changing mechanism BD possesses: power shaft 151, it drives the output in source with electromotor etc. Axle S links, and rotates around input central axis O1 by accepting the rotary power in driving source；Multiple (in this enforcement Mode is 6) eccentric disc 104 (following, also 6 eccentric discs to be called 104A～104F), they warps Rotated integrally with power shaft 151 by the 1st and the 2nd crankshaft component 106,107；Identical with the quantity of eccentric disc 104 Connecting member 130, they are for coupling together input side and outlet side；And one-way clutch OWC, its It is arranged on outlet side.

The most in the lump as shown in Fig. 2, Fig. 3 and Fig. 5, multiple eccentric discs 104 be respectively formed as with the 1st fulcrum O3 be Center round-shaped, each 1st fulcrum O3 is to be circumferentially, equally spaced positioned at the surrounding of input central axis O1 Mode configures.Further, multiple eccentric discs 104 are respectively when remain offset r, along with power shaft 151 Rotation and around input central axis O1 carry out eccentric rotary.It addition, multiple eccentric discs 104 are configured to change Each 1st fulcrum O3 is relative to the offset r of input central axis O1.And, on multiple eccentric discs 104 respectively It is formed and inputs 2 through holes 104a, 104b that central axis O1 extends parallel to.

As shown in Figure 1 to 4, the 1st crankshaft component 106 has: multiple 1st crankpin 106c～106h, they 2 through holes being formed on multiple eccentric disc 104 rotatably it are applied in respectively by sliding bearing 155 In a through hole 104a in 104a, 104b, and they are connected to each other；With multiple 1st crankshaft journal 106p, 106q, 106r, they are offseting the position of equidistance from the central axis 106k of each 1st crankpin 106c～106h The place of putting has central axis 106b.

2nd crankshaft component 107 has similarly: multiple 2nd crankpin 107c～107h, they respectively via Sliding bearing 155 is rotatably applied in another through hole 104b being formed on multiple eccentric disc 104, And they are connected to each other；With multiple 2nd crankshaft journal 107p, 107q, 107r, they are from each 2nd crankpin The position of the central axis 107b skew equidistance of 107c～107h has central axis 107k.

Thus, each 1st and the 2nd crankpin 106c～106h of these the 1st and the 2nd crankshaft components 106,107, Each central axis 106k, 107k of 107c～107h and each 1st and the 2nd crankshaft journal 106p, 106q, 106r, Central axis 106b, 107b of 107p, 107q, 107r are joined when being installed on stepless speed changing mechanism BD It is set to parallel with inputting central axis O1.

It addition, each 1st and the 2nd crankpin 106c～106h, the 107c of each 1st and the 2nd crankshaft component 106,107～ 107h so that they each central axis 106k, 107k with crankshaft journal 106p, 106q, 106r, 107p, 107q, The angle of regulation it is spaced in a circumferential direction (in the present embodiment centered by central axis 106b, 107b of 107r Be 60 °) mode respectively the most combined.

Further, in figure 3, eliminate the 1st, the 2nd crankshaft journal 106q, 107q illustrates.

It addition, as it is shown in figure 5, through each of each 1st and the 2nd crankpin 106c～106h, 107c～107h 2 through holes 104a, 104b of eccentric disc 104 are formed as: 2 through holes 104a, 104b arrange adjacent to each other Arrange, and the intermediate point M of through hole 104a, 104b offsets from the 1st fulcrum O3.It addition, each eccentric disc 104 2 through holes 104a, 104b be respectively formed as: the centre of through hole 104a, 104b of multiple eccentric discs 104 The angle (being 60 ° in the present embodiment) that some M specifies at circumferencial direction interval centered by the 1st fulcrum O3.

Specifically, in 6 eccentric discs 104 of present embodiment, for the 1st and the 2nd crankpin 106c, 107c Eccentric disc 104D through for through eccentric disc 104A and confession the 1st and the 2nd crankpin 106f, 107f is by following Such structure is constituted: the line of center 104e, 104f of connecting through hole 104a, 104b is positioned at by the 1st fulcrum On the line of O3.It addition, for the through eccentric disc 104B of the 1st and the 2nd crankpin 106d, 107d, for the 1st and Through for 2nd crankpin 106e, 107e eccentric disc 104C, through for the 1st and the 2nd crankpin 106g, 107g Eccentric disc 104E and for the through eccentric disc 104F of the 1st and the 2nd crankpin 106h, 107h by following this The structure of sample is constituted: connect the line of intermediate point M and the 1st fulcrum O3 with 60 ° be connected 2 through holes 104a, 104b Center 104e, 104f line intersect.

Therefore, if each eccentric disc 104A of being shown respectively under offset r centered by input central axis O1～ 104F, the most each eccentric disc 104A～104F have such position relationship shown in Fig. 6.That is, each bias is being become The 1st fulcrum O3 at the center of dish 104A～the 104F state identical for offset r relative to input central axis O1 Under, each 1st and the 2nd crankpin 106c～106h, 107c～107h are in central axis 106b, 107b being The heart have rotated the position of 60 ° the most successively, and each eccentric disc 104A～104F also becomes to input central axis O1 Centered by have rotated the position relationship of 60 ° the most successively.

Further, combine centered by central axis 106b, 107b each 1st and the 2nd crankpin 106c～106h, 107c～ The angle of 107h or each through hole 104a, 104b of being formed on each eccentric disc 104 and the 1st fulcrum O3 it Between relation (such as, connect the intermediate point M of each through hole 104a, 104b and the line of the 1st fulcrum O3 and even The angle that the line of center 104e, 104f of meeting 2 through holes 104a, 104b intersects) by eccentric disc 104 Number determines, i.e. become 360 degree divided by the value obtained by the quantity of eccentric disc 104.

Power shaft 151 is the one-body molded product being made up of following part: cylindrical portion 151d, itself and the end of output shaft S End spline combines；With axle journal support 151h, it has the 1st and the 2nd crankshaft component via sliding bearing 157 106, crankshaft journal 106p, 107p of 107 is supported to rotatable 2 through hole 151a, 151b.

It addition, the song of the 1st and the 2nd crankshaft component 106,107 between 2 eccentric discs 104C, 104D Shaft neck 106q, 107q by be formed at axle journal supporting parts 152 on 2 the 1st and the 2nd support holes 152a, 152b is supported to rotatable via sliding bearing 157.

And, crankshaft journal 106r, 107r of the 1st and the 2nd crankshaft component 106,107 is formed with passive tooth Wheel 106a, 107a, these driven gears 106a, 107a are in actuator 180 and and input central axis O1 together The little gear 180b engagement of rotary shaft 180a that axle ground is arranged, and also with the gear ring 115 of the surrounding being arranged on them Engagement.

Further, 2 the 1st and the 2nd crankshaft components 106,107 are supported to rotatable power shaft 151 and axle Neck support part 152 and gear ring 115 respectively via bearing 102,105,103 by the variator of not shown variator Housing 160 supports.

The number of teeth of driven gear 106a, 107a of 2 the 1st and the 2nd crankshaft components 106,107 is identical, little gear 180b rotates by means of actuator 180, and thus, 2 driven gears 106a, 107a rotate with identical rotating speed. Actuator 180 is made up of d.c. motor and reducing gear etc., time usual, makes little gear 180b and power shaft 151 Rotate and synchronously rotate.Therefore, as shown in (a)～(f) of Fig. 7, the 1st and the 2nd crankshaft component 106,107 Rotate integratedly centered by input central axis O1 with eccentric disc 104, as shown in (d) of Fig. 7, if will The diameter of eccentric disc 104 is set to D, then the peak swing W of eccentric disc 104 is W=D+2 r.Further, Fig. 7 (a)～(f) of Fig. 7 show the 1st and the 2nd crankshaft component 106,107 and the rotation of eccentric disc 104 Angle is set to α=0 °, 60 °, 120 °, 180 °, 240 °, the state of 300 °.

It addition, on the basis of the rotating speed that power shaft 151 and little gear 180b synchronize, little gear 180b is applied ratio defeated Enter the rotating speed that the rotating speed of axle 151 is big or little, thus make little gear 180b rotate against relative to power shaft 151.Base The rotating speed carried out in this actuator 180 controls to realize the most in the following manner: relative to the rotating speed of power shaft 151, Control the little tooth being multiplied by obtained by the rotating speed of actuator 180 by the speed reducing ratio of reducing gear (such as, planetary gear) The rotating speed of wheel 180b.Now, there is not rotational difference at little gear 180b and power shaft 151 and realize situation about synchronizing Under, offset r does not changes.

Therefore, by little gear 180b provides the rotating speed of the rotating speed more than or less than power shaft 151, it is passive to have 1st and the 2nd crankshaft journal 106r, 107r rotation of gear 106a, 107a, thus, the 1st crankpin 106c～ 106h and the 2nd crankpin 107c～107h respectively with the central axis 106b of the 1st and the 2nd crankshaft journal 106r, 107r, Synchronous rotary centered by 107b, regulates the 1st fulcrum O3 offset r relative to input central axis O1.

It addition, one-way clutch OWC has: as the clutch inner part 121 of output block, it is defeated around deviation The output center axes O 2 entering central axis O1 rotates；As the ring-type clutch Outside part 122 of input block, It swings around output center axes O 2 by accepting the power of direction of rotation from outside；Multiple as joint elements Roller 123, its in order to these clutch Outside parts 122 and clutch inner part 121 are set to mutually lock-out state or Non-locking state and be inserted between clutch Outside part 122 and clutch inner part 121；And force application part 126, Roller 123 is exerted a force, when the forward (arrow in Fig. 2 of clutch Outside part 122 by it towards the direction applying lock-out state Head direction shown in RD1) the rotating speed of the rotating speed forward that exceedes clutch inner part 121 time, one-way clutch OWC The rotary power being imported into clutch Outside part 122 is transferred to clutch inner part 121, thereby, it is possible to will be from The oscillating motion of clutch external part 122 is converted into the rotary motion of clutch inner part 121.

As it is shown in figure 1, the clutch inner part 121 of one-way clutch OWC is configured to continuous print the most integratedly Parts, but, clutch Outside part 122 is divided into multiple vertically, and with eccentric disc 104 and connecting member The quantity of 130 is accordingly arranged in and can axially separately swing.Further, roller 123 is corresponding to each clutch Device external part 122 inserts between clutch Outside part 122 and clutch inner part 121.

At of circumference on ring-type each clutch Outside part 122, position is provided with protuberance 124, at this protuberance The 2nd fulcrum O4 of deviation output center axes O 2 it is provided with on 124.Further, at each clutch Outside part 122 It is configured with pin 125 on 2nd fulcrum O4, utilizes this pin 125 by the end (the other end) 132 of connecting member 130 Clutch Outside part 122 it is linked in the way of rotatable.

End side at connecting member 130 has ring portion 131, the inner circumferential of the circular open 133 of this ring portion 131 by Bearing 140 is entrenched in the periphery of eccentric disc 104 in the way of rotatable.Therefore, connecting member 130 like this One end in the way of rotatable, be linked to the periphery of eccentric disc 104, and, the other end of connecting member 130 with The mode rotated freely is linked on the clutch Outside part 122 of one-way clutch OWC the 2nd fulcrum arranged O4, thus constitutes to input central axis O1, the 1st fulcrum O3, output center axes O the 2, the 2nd fulcrum O4 These 4 nodes are four joint linkages of run-on point, from power shaft 151 via 2 the 1st and the 2nd crankshaft components 106,107 it is provided to the rotary motion of eccentric disc 104 by the clutch Outside part as one-way clutch OWC The oscillating motion of 122 is passed to this clutch Outside part 122, and the oscillating motion of this clutch Outside part 122 is turned It is changed to the rotary motion of clutch inner part 121.

Now, utilize actuator 180, make by 2 the 1st and the 2nd crankshaft components 106,107, actuator 180 Deng the little gear 180b action of the gear ratio changeable mechanism 112 of composition, it is possible to change the bias of eccentric disc 104 Amount r.Further, by change offset r, it is possible to the pendulum of the clutch Outside part 122 of change one-way clutch OWC Dynamic angle, θ 2, thereby, it is possible to the ratio of the rotating speed and the rotating speed of power shaft 151 changing clutch inner part 121 (becomes Speed ratio i).Therefore, it is possible to change is being input to the rotary power of power shaft 151 via eccentric disc 104 and connecting member 130 gear ratio when being transferred to the clutch inner part 121 of one-way clutch OWC as rotary power, it addition, Owing to offset r can be set as zero, therefore, it is possible to gear ratio is set as infinity.

With reference to Fig. 8 and Fig. 9, the transmission principle of stepless speed changing mechanism BD described above is illustrated.

In (a)～(e) of Fig. 8, the figure in left side is to be shown in eccentric disc 104A to make little gear 180b relative The figure of the change of the offset under each rotational angle θ c of the 1st and the 2nd crankshaft component 106,107 during rotation, The figure on right side is that central axis 106b, 107b (black circle) of crankshaft journal 106r, 107r is bent with the 1st and the 2nd Position relationship between central axis 106k, 107k (white circle) of pivot pin 106c, 107c is extracted out from the figure in left side Figure.Further, for shape easy to understand, the 1st and the 2nd crankpin 106c, 107c is applied with shade, separately Outward, in (b)～(e) of Fig. 8, eliminate the little gear 180b shown in (a) of Fig. 8, with solid line Circle shows driven gear 106a, 107a.

As shown in (a) of Fig. 8, in eccentric disc 104A, turning at the 1st and the 2nd crankshaft component 106,107 During dynamic angle, θ c=0 °, central axis 106b, 107b of crankshaft journal 106r, 107r is respectively relative to the 1st and the Central axis 106k, 107k of 2 crankpin 106c, 107c are in the position offset upward, with little gear 180b Coaxial input central axis O1 and the 1st fulcrum O3 as the center of eccentric disc 104A overlaps.Therefore, partially The center (the 1st fulcrum O3) of cartridge 104 is zero relative to the offset r of input central axis O1, it is possible to will become Speed ratio i is set as " infinitely great (∞) ".

It follows that as shown in (b) of Fig. 8～(d) of Fig. 8, at the 1st and the 2nd crankshaft component 106,107 Rotational angle θ c=45 °, 90 °, 135 ° time, the central axis 106k of the 1st and the 2nd crankpin 106c, 107c, 107k central axis 106b, 107b relative to crankshaft journal 106r, 107r rotates to same direction, eccentric disc The center (the 1st fulcrum O3) of 104 is gradually left from input central axis O1, and offset r becomes larger.

Then, as shown in (e) of Fig. 8, the rotational angle at the 1st and the 2nd crankshaft component 106,107 is θ c=180 ° Time, central axis 106b, 107b of crankshaft journal 106r, 107r be respectively relative to the 1st and the 2nd crankpin 106c, Central axis 106k, 107k of 107c are in the position offset downwards, center (the 1st fulcrum of eccentric disc 104 O3) distance input central axis O1 is farthest, and offset r becomes maximum, it is possible to realize little gear ratio.

(a)～(c) of Fig. 9 is the figure observing 6 eccentric disc 104A～104F respectively from actuator 180 side, (a) of Fig. 9 show each 1st fulcrum O3 of eccentric disc 104A～104F consistent with input central axis O1, Offset r is set to the state of " zero ", i.e. gear ratio i is set as infinitely-great situation, and (b) of Fig. 9 sets The each 1st fulcrum O3 having determined eccentric disc 104A～104F is that central axis O1 leaves, by offset r from inputting It is set as the state of " medium ", i.e. gear ratio i is set as the situation of the gear ratio of centre, and (c) of Fig. 9 illustrates The each 1st fulcrum O3 distance input central axis O1 of eccentric disc 104A～104F farthest, by offset r It is set as the state of " greatly ", i.e. gear ratio i is set as the situation of less gear ratio.

The tune to offset r that such rotational angle θ c based on the 1st and the 2nd crankshaft component 106,107 realizes Whole is that the rotating speed of rotary shaft 180a by utilizing not shown control unit to control the actuator 180 shown in Fig. 1 comes Carry out.

As shown in Figure 10, in stepless speed changing mechanism BD, constitute to input central axis O1, the 1st fulcrum O3, output center axes O the 2, the 2nd these 4 nodes of fulcrum O4 are as four joint linkages of run-on point, from defeated Enter axle 151 apply to eccentric disc 104 rotary motion by as oscillating motion be transferred to one-way clutch OWC from Clutch external part 122, the oscillating motion of this clutch Outside part 122 is converted into the rotation of clutch inner part 121 Motion.

As shown in (a) of Figure 11, the offset r of eccentric disc 104 is being set as " greatly " and is making the 1st fulcrum O3 In the case of rotating in the direction of the arrow centered by input central axis O1, it is possible to increase one-way clutch OWC's The pendulum angle θ 2 of clutch Outside part 122, therefore, it is possible to realize less gear ratio i.

As shown in (b) of Figure 11, in the case of the offset r of eccentric disc 104 is set as " medium ", it is possible to In the case of the pendulum angle θ 2 making the clutch Outside part 122 of one-way clutch OWC is less than (a) of Figure 11 Pendulum angle θ 2 little, therefore, it is possible to realize gear ratio i bigger than the situation of (a) of Figure 11.

As shown in (c) of Figure 11, in the case of the offset r of eccentric disc 104 is set as " little ", it is possible to make In the case of the pendulum angle θ 2 of the clutch Outside part 122 of one-way clutch OWC is less than (b) of Figure 11 Pendulum angle θ 2 is little, therefore, it is possible to realize gear ratio i bigger than the situation of (b) of Figure 11.

Thus, the offset r of eccentric disc 104 is the least, then the pendulum angle θ 2 of clutch Outside part 122 is the least, And gear ratio i is the biggest, in the case of the offset r making eccentric disc 104 is " zero ", it is possible to make one-way clutch OWC The pendulum angle θ 2 of clutch Outside part 122 be " zero ", therefore, it is possible to gear ratio i to be set as " infinitely great (∞) ".

As shown in Figure 10, the clutch Outside part 122 of one-way clutch OWC accept via connecting member 130 from The power that eccentric disc 104 applies carries out oscillating motion.If the power shaft 151 making eccentric disc 104 rotate rotates 1 Circle, then clutch Outside part 122 reciprocally swinging of one-way clutch OWC 1 time.As shown in figure 12, with bias The value of the offset r of dish 104 is unrelated, and the hunting period of the clutch Outside part 122 of one-way clutch OWC is always Fixing.The angle of oscillation speed omega 2 of clutch Outside part 122 is by the anglec of rotation speed of eccentric disc 104 (power shaft 151) Degree ω 1 and offset r determines.

Connect the ring portion 131 of multiple connecting members 130 of power shaft 151 and one-way clutch OWC rotatably Be linked to around input multiple eccentric discs 104 of being disposed at equal intervals in the circumferential of central axis O1, therefore, because of each partially The rotary motion of cartridge 104 and make the oscillating motion such as figure that the clutch Outside part 122 of one-way clutch OWC produces So carry out successively with fixing phase place shown in 13.

Now, power (torque) from the clutch Outside part 122 of one-way clutch OWC towards clutch inner part The transmission of 121 only the rotating speed of the forward of clutch Outside part 122 (the arrow RD1 direction of Figure 10) exceeded from Just carry out under conditions of the rotating speed of the forward of clutch inner part 121.That is, in one-way clutch OWC, clutch is worked as When the rotating speed of device external part 122 becomes higher than the rotating speed of clutch inner part 121, just start via roller 123 occur from Clutch external part 122 engages (locking) with clutch inner part 121, and the power of clutch Outside part 122 is passed It is handed to clutch inner part 121 and produces driving force.

After the driving realized based on 1 connecting member 130 terminates, the rotating speed of clutch Outside part 122 is less than clutch The rotating speed of device inner part 121, and lock the driving force by means of other connecting members 130 based on what roller 123 realized It is released from and returns state (idling conditions) freely.Carry out above-mentioned the most successively with the quantity of connecting member 130 Action, is thus converted into the rotary motion in a direction by oscillating motion.Therefore, only clutch inner part is being exceeded The power of the clutch Outside part 122 in the moment of the rotating speed of 121 is passed to clutch inner part 121 successively, substantially Smoothly achieve average rotary power and be applied to clutch inner part 121.

It addition, as shown in (a)～(c) of Figure 11, in the stepless speed changing mechanism BD of four joint connecting-rod mechanism types, By changing the offset r of eccentric disc 104, it is possible to determine gear ratio (variable Rate).In this case, by inciting somebody to action Offset r is set as zero, it is possible to gear ratio i is set as infinity (∞), even if the output shaft S in the source of driving In rotary course, it is also possible to the pendulum angle θ 2 that will be transmitted to clutch Outside part 122 is set as zero.That is, even if The output shaft S (with reference to Fig. 1) in driving source rotates, it is also possible to by the clutch inner part 121 of one-way clutch OWC Speed setting be zero.

It follows that with reference to Figure 14～Figure 19, embodiments of the present invention are illustrated.Further, present embodiment The basic structure of stepless speed changing mechanism BD ' except the 1st and the 2nd crankshaft component and the structure of eccentric disc and axle journal Beyond the quantity difference of supporting parts 152, identical with the stepless speed changing mechanism BD of reference example.Therefore, below, also With reference to Fig. 4～Figure 13 of structure as a reference example, mainly to the portion different from the stepless speed changing mechanism BD of reference example Divide and illustrate.Therefore, for or the part of equivalent identical with the stepless speed changing mechanism BD of reference example, labelling is identical Label or suitable label, and simplify or omit the description.

As shown in Figure 14～Figure 17, the 1st crankshaft component 16 of present embodiment has joins with 60 ° of intervals in the circumferential Multiple (being 6 in the present embodiment) the 1st crankpin 16c～16h put.Each 1st crankpin 16c～16h By multiple (being 7 in the present embodiment) that are alternately arranged in the way of clipping the 1st crankpin 16c～16h 1st crankshaft journal 16p～16v links together.Multiple 1st crankshaft journal 16p～16v are from each 1st crankpin The position of 16c～16h respective central axis 16k deviation equidistance has central axis 16b.In other words, Multiple 1st crankpin 16c～16h centered by the central axis 16b of multiple 1st crankshaft journal 16p～16v in week The most equally spaced configure.The outer diameter D 1 of the 1st crankpin 16c～16h is the most equal, or in the axial direction from one Side becomes larger towards opposite side.

The 1st crankshaft journal 16p being positioned at actuator 180 side is formed with driven gear 16a, this driven gear 16a Be configured to and input the little gear 180b of rotary shaft 180a coaxial for central axis O1 engage, and also with set The gear ring 115 put around these parts engages.The 1st crankshaft journal 16v being positioned at output shaft S side is rotated from As be supported on power shaft 151 formed through hole 151a in.

Each 1st crankpin 16c～16h is being formed at correspondence via sliding bearing 155 is the most through respectively In a 1st through hole 14a in 2 the 1st and the 2nd through holes 14a, 14b on eccentric disc 14.Further, In Figure 14～Figure 19, eliminate sliding bearing 155.

Therefore, the 1st crankshaft component 16 of present embodiment is equivalent to the 1st bent axle of stepless speed changing mechanism of reference example Parts 106, driven gear 16a is equivalent to driven gear 106a, central axis 16b and is equivalent to central axis 106b, 1st crankpin 16c～16h is equivalent to the 1st crankpin 106c～106h, central axis 16k and is equivalent to central axis 106k, the 1st crankshaft journal 16p, 16s, 16v are equivalent to the 1st crankshaft journal 106r, 106q, 106p.This enforcement The 1st crankshaft journal 16q, 16r, 16t, 16u of mode is the 1st crankshaft component of the stepless speed changing mechanism of reference example 106 unexistent structures.

About multiple 1st crankshaft journal 16p～16v, obtained to the 1st crankshaft journal 16p～16v projection vertically Projection section N1 lay respectively at the wheel of the 1st crankpin 16c～16h being connected with the 1st crankshaft journal 16p～16v In wide (appearance profile) N2.More specifically illustrate, such as shown in (b) of Figure 18, vertically to 1 crankshaft journal 16q carries out projecting obtained projection section N1 and is positioned at the 1st be connected with the 1st crankshaft journal 16q In profile (appearance profile) N2 of crankpin 16c, 16d (not shown).This relation for the 1st crankshaft journal 16p, 16r～16v is also identical.Further, in the present embodiment, it is shown that the external diameter of the 1st crankpin 16c～16h The situation that D1 is the most equal.

2nd crankshaft component 17 is identical with the 1st crankshaft component 16, has and is spaced the multiple of configuration with 60 ° in the circumferential (being 6 in the present embodiment) the 1st crankpin 17c～17h.Each 2nd crankpin 17c～17h is by with folder Multiple (being 7 in the present embodiment) the 2nd bent axle that the mode of the 2nd crankpin 17c～17h is alternately arranged Axle journal 17p～17v links together.Multiple 2nd crankshaft journal 17p～17v are from each 2nd crankpin 17c～17h The position of respective central axis 17k deviation equidistance has central axis 17b.In other words, the multiple 2nd Crankpin 17c～17h centered by the central axis 17b of the 2nd crankshaft journal 17p～17v the most equally spaced Configuration.The outer diameter D 3 of the 2nd crankpin 17c～17h is the most equal, or in the axial direction from side towards opposite side Become larger.

The 2nd crankshaft journal 17p being positioned at actuator 180 side is formed with driven gear 17a, this driven gear 16a Be configured to and input the little gear 180b of rotary shaft 180a coaxial for central axis O1 engage, and also with set The gear ring 115 put around these parts engages.The 2nd crankshaft journal 17v being positioned at output shaft S side is rotated from As be supported on power shaft 151 formed through hole 151b in.

Each 2nd crankpin 17c～17h is being formed at correspondence via sliding bearing 155 is the most through respectively In another the 2nd through hole 14b in 2 the 1st and the 2nd through holes 14a, 14b on eccentric disc 14.Further, In Figure 14～Figure 19, eliminate sliding bearing 155.

Therefore, the 2nd crankshaft component 17 of present embodiment is equivalent to the 2nd bent axle of stepless speed changing mechanism of reference example Parts 107, driven gear 17a is equivalent to driven gear 107a, central axis 17b and is equivalent to central axis 107b, 2nd crankpin 17c～17h is equivalent to the 2nd crankpin 107c～107h, central axis 17k and is equivalent to central axis 107k, the 2nd crankshaft journal 17p, 17s, 17v are equivalent to the 2nd crankshaft journal 107r, 107q, 107p.This enforcement The 2nd crankshaft journal 17q, 17r, 17t, 17u of mode is the 2nd crankshaft component of the stepless speed changing mechanism of reference example 107 unexistent structures.

About multiple 2nd crankshaft journal 17p～17v, obtained to the 2nd crankshaft journal 17p～17v projection vertically Projection section N1 lay respectively at the wheel of the 2nd crankpin 17c～17h being connected with the 2nd crankshaft journal 17p～17v In wide (appearance profile) N2.More specifically illustrate, such as shown in (b) of Figure 18, vertically to 2 crankshaft journal 17q carry out projecting obtained projection section N1 and are positioned at the 2nd be connected with the 2nd crankshaft journal 17q Crankpin 17c, 17d are (not shown.) profile (appearance profile) N2 in.This relation is for the 2nd crankshaft journal 17p, 17r～17v are also identical.Further, in the present embodiment, it is shown that the 2nd crankpin 17c～17h The most equal situation of outer diameter D 3.

1st and the 2nd crankpin 16c～16h, the eccentric direction of 17c～17h and the offset of present embodiment and ginseng Examine the 1st and the 2nd crankpin 106c～106h, 107c～107h of the 1st and the 2nd crankshaft component 106,107 of example Identical.

As shown in figure 17, the 1st and the 2nd crankshaft journal 16p～16v, the axial length L 2 of 17p～17v are set For identical or longer than described axial width L1 with the axial width L1 of eccentric disc 14 described later.Thus, eccentric disc 14 Can opposite one another and between adjacent the 1st and the 2nd crankpin (such as, 16c and 16d, 17c and 17d) along footpath Mobile to (direction vertical with central axis 16b, 17b).

As shown in Figure 14 and Figure 15, in the axial direction, the of the 1st and the 2nd crankshaft component 16,17 that phase place is identical 1 and the 2nd crankshaft journal 16q～16u, 17q～17u are rotatably embedded in via sliding bearing 157 respectively On axle journal supporting parts 152 in the 1st and the 2nd support holes 152a of formation, 152b.Further, at Figure 14～Figure 19 In, eliminate sliding bearing 157.

Multiple axle journals supporting parts 152 are supported on the case of transmission 160 of variator respectively via bearing 105.

It addition, each eccentric disc 14 is embedded in the ring portion 131 of connecting member 130 via bearing 140.

As shown in (a) of Figure 18, in the same manner as the eccentric disc 104 of reference example, the 1st and the 2nd of eccentric disc 14 Through hole 14a, 14b are formed as parallel.But, the eccentric disc 14 of present embodiment has the most divided but shape It is integrally forming such feature.1st crankpin 106c～106h is the most rotatably embedded in multiple eccentric disc 14 The 1st through hole 14a in.It addition, the 2nd crankpin 107c～107h be the most rotatably embedded in multiple partially In 2nd through hole 14b of cartridge 14.

As shown in figure 18, about the 1st and the 2nd crankshaft component 16,17 of present embodiment, as it has been described above, from axle In time observing, each 1st crankshaft journal 16p～16v is configured in the profile N2 of the 1st crankpin 16c～16h, Each 2nd crankshaft journal 17p～17v is configured in the profile N2 of the 2nd crankpin 17c～17h.It addition, the 1st The outer diameter D 1 of the 1st crankpin 16c～16h of crankshaft component 16 is through with the 1st of each self-corresponding eccentric disc 14 the The aperture D5 of hole 14a is roughly the same, the outer diameter D of the 2nd crankpin 17c～17h of the 2nd crankshaft component 17 3 with The aperture D6 of the 2nd through hole 14b of each self-corresponding eccentric disc 14 is roughly the same.

Thereby, it is possible to respectively the 1st and the 2nd crankshaft component 16,17 to be inserted the 1st of eccentric disc 14 from end side And the 2nd assemble eccentric disc 14 in through hole 14a, 14b.

Specifically, as shown in Figure 16 and Figure 17, first, by the 1st of the 1st and the 2nd crankshaft component 16,17 And the 2nd crankpin 16h, 17h run through and be inserted into 1st and 2nd crankpin 16c, 17c the most inboard with direction of insertion In the 1st and the 2nd through hole 14a, 14b of the eccentric disc 14 of corresponding (being fitted together to), make eccentric disc 14 vertically Mobile to eccentric disc 14 will the side (being right flank in figure) of the 1st and the 2nd crankpin 16g, 17g with No. 2 Till abutting.Now, eccentric disc 14 is in the position corresponding with the 1st and the 2nd crankshaft journal 16u, 17u in the axial direction Put.

It follows that make eccentric disc 14 move radially, make the 1st and the 2nd through hole 14a, 14b and the 1st and the 2nd The axle center of crankpin 16g, 17g is consistent.Now, due to the axial length of the 1st and the 2nd crankshaft journal 16u, 17u L2 is longer than the axial width L1 of eccentric disc 14 for degree, and therefore, moving radially of eccentric disc 14 will not be hindered. Then, make the 1st and the 2nd crankpin 16g, 17g run through in insertion the 1st and the 2nd through hole 14a, 14b, and pass through Pass to till eccentric disc 14 will abut with the side of the 1st and the 2nd crankpin 16f, 17f of No. 3.

Hereinafter, similarly make eccentric disc 14 the most axially and radially, while through the 1st and the 2nd Crankpin 16f, 17f, 16e, 17e, 16d, 17d, make the 1st and the 2nd through hole 14a, 14b of this eccentric disc 14 1st and 2nd crankpin 16c, 17c the most inboard with direction of insertion is fitted together to.

It follows that while making and starting from the back side is that the 1st and the 2nd crankpin 16d, 17d of No. 2 is corresponding Eccentric disc 14 moves the most radially and axially, makes the 1st and the 2nd crankshaft component 16,17 Run through insertion the 1st and the 2nd through hole 14a, 14b, make the 1st and the 2nd through hole 14a, 14b of this eccentric disc 14 It is fitted together to the 1st and the 2nd crankpin 16d, 17d.

The most identical, make remaining 1st and the 2nd crankpin 16e～16h, 17e～17h and each self-corresponding bias The the 1st and the 2nd through hole 14a, 14b of dish 14 is fitted together to.Figure 19 shows a status that: at each eccentric disc 14 Offset r be zero state under, respectively eccentric disc 14 is assemblied in the of the 1st and the 2nd crankshaft component 16,17 1 and the 2nd crankpin 16c～16h, 17c～17h, so axle journal is supported parts 152 be assembled to eccentric disc 14 it Between.

In such manner, it is possible to the eccentric disc 14 not carrying out splitting but be made up of single part is assembled to the 1st and the 2nd Crankshaft component 16,17, therefore, it is possible to improve the supporting rigidity of eccentric disc 14 such that it is able to high accuracy supporting the 1 and the 2nd crankshaft component 16,17.Thus, the variation of the offset r of eccentric disc 104, i.e. gear ratio reduces, energy Enough realize stable speed change.

Further, in the assembling of eccentric disc 14, if outside the 1st and the 2nd crankpin 16c～16h, 17c～17h Footpath D1, D3 are formed as gradually becoming from side towards opposite side (from direction of insertion end side towards inboard) in the axial direction Greatly, then it is positioned at than 1st and 2nd crankpin 16c～16h, 17c～17h corresponding with eccentric disc 14 to be assembled Become than this near the 1st and the 2nd crankpin 16c～16h of position of front side, the outer diameter D 1 of 17c～17h, D3 Aperture D5, D6 of the 1st and the 2nd through hole 14a, 14b of eccentric disc 14 are little, so that eccentric disc 14 Insertion becomes easy, and efficiency of assembling improves.

As mentioned above, according to the stepless speed changing mechanism BD of present embodiment, multiple 1st crankpin 16c～16h Outer diameter D 1 the most equal or become big from side towards opposite side in the axial direction, multiple 1st crankshaft journal 16p～ 16v is respectively arranged to vertically the 1st crankshaft journal 16p～16v be projected obtained projection section N1 position In the profile N2 of the 1st crankpin 16c～16h being connected with the 1st crankshaft journal 16p～16v, and, many The outer diameter D 3 of individual 2nd crankpin 17c～17h is the most equal or becomes big from side towards opposite side in the axial direction, Multiple 2nd crankshaft journal 17p～17v are respectively arranged to project the 2nd crankshaft journal 17p～17v vertically Obtained projection section N1 is positioned at the 2nd crankpin 17c～17h being connected with the 2nd crankshaft journal 17p～17v Profile N2 in.Further, since the axial width L1 of multiple eccentric discs 14 respectively than the 1st crankshaft journal 16p～ The axial length L 2 of 16v and the 2nd crankshaft journal 17p～17v is little, therefore, it is possible to will the most radially split But integrated eccentric disc 14 is sequentially inserted into towards opposite side from the side of the 1st and the 2nd crankshaft component 16,17 Assemble.Therefore, it is possible to prevent because of caused by the opening of eccentric disc 14 for the 1st and the 2nd crankpin 16c～ The reduction of the internal diameter size precision of the 1st and the 2nd through hole 14a, 14b that 16h, 17c～17h are through, it is possible to anti- The only change of offset r, it is possible to the impact that gear ratio is caused by suppression.Further, since eccentric disc 14 one Molding, therefore, it is possible to cut down number of parts.

It addition, the 1st and the 2nd through hole 14a, the 14b being formed on eccentric disc 14 does not connects, therefore, it is possible to improve The rigidity of eccentric disc 14 such that it is able to be more reliably prevented from the change of the offset r of eccentric disc 14.

Further, the present invention is not limited to aforesaid embodiment, it is possible to carry out suitable deformation, improvement etc..Additionally, As long as the present invention of being capable of, the above-mentioned material of each structural element in each embodiment, shape, size, quantity, Configuration position etc. can be arbitrary, and it is fixed to be not limited.

Such as, in the eccentric disc 14 of above-mentioned embodiment, be formed as the 1st and the 2nd crankpin 16c～16h, The the 1st and the 2nd through for 17c～the 17h disconnected structure of through hole 14a, 14b, but it is also possible to be configured to: The the 1st and the 2nd through hole 14a, 14b connection is made to arrange for the 1st and the 2nd crankpin 16c～16h, 17c～17h The single elongated hole that both sides are through.

Claims (2)

1. a stepless speed changing mechanism, it has:

Power shaft, this power shaft accepts to rotate around input central axis from the rotary power of power source generation；

Multiple eccentric discs, the plurality of eccentric disc has the 1st fulcrum at respective center, and each 1st fulcrum is in this input Circumferentially about being disposed at equal intervals of central axis, and inclined relative to described input central axis of each 1st fulcrum Heart amount can be changed, and the plurality of eccentric disc is defeated with described around this input central axis while keeping this offset Enter axle to rotate together, and, the plurality of eccentric disc is respectively formed with described input centerline axis parallel prolong The 1st through hole stretched and the 2nd through hole；

1st crankshaft component, the 1st crankshaft component has multiple 1st crankpin and multiple 1st crankshaft journal, described The most through described 1st through hole formed on the plurality of eccentric disc of multiple 1st crankpins, and that This links, and the plurality of 1st crankshaft journal is offseting the position of equidistance from the central axis of this each 1st crankpin Place has central axis；

2nd crankshaft component, the 2nd crankshaft component has multiple 2nd crankpin and multiple 2nd crankshaft journal, described The most through described 2nd through hole formed on the plurality of eccentric disc of multiple 2nd crankpins, and that This links, and the plurality of 2nd crankshaft journal is offseting the position of equidistance from the central axis of this each 2nd crankpin Place has central axis；

One-way clutch, this one-way clutch has around the output center axis rotation deviateing described input central axis Output block, by accept the power of direction of rotation from outside and around described output center axis oscillating input block, And make these input blocks and output block become mutually lock-out state or the joint elements of non-locking state, when described During the rotating speed of the forward that the rotating speed of the forward of input block exceedes described output block, this one-way clutch will enter into institute The rotary power stating input block is transferred to described output block, thus the oscillating motion of described input block is converted to The rotary motion of described output block；

Multiple connecting members, the respective one end of the plurality of connecting member rotatably connects centered by described 1st fulcrum Knot is in the periphery of each described eccentric disc, and the respective other end of the plurality of connecting member is rotatably linked at described list The 2nd fulcrum that the position deviateing described output center axis on the input block of clutch is arranged, thus, will The rotary motion swing as the input block of described one-way clutch of described eccentric disc is put on from described power shaft Motion is transferred to this input block；And

Gear ratio changeable mechanism, this gear ratio changeable mechanism possesses actuator, and described actuator makes described 1st crankpin Synchronously rotate centered by described 1st crankshaft journal and the 2nd crankshaft journal respectively with described 2nd crankpin, adjust Save described 1st fulcrum offset relative to described input central axis, thus change and be transferred to institute from described eccentric disc Stating the pendulum angle of the oscillating motion of the input block of one-way clutch, thus, the change of described gear ratio changeable mechanism exists The rotary power being input to described power shaft is transmitted as rotary power via described eccentric disc and described connecting member To the gear ratio during output block of described one-way clutch, and, owing to described offset can be set as zero, It is thus possible to gear ratio is set as infinity, wherein,

The external diameter of the plurality of 1st crankpin is the most equal or becomes big from side towards opposite side in the axial direction,

The external diameter of the plurality of 2nd crankpin is the most equal or becomes big from side towards opposite side in the axial direction,

The plurality of 1st crankshaft journal is respectively arranged to: carry out described 1st crankshaft journal vertically projecting gained To projection section be positioned at the profile of described 1st crankpin being connected with the 1st crankshaft journal,

The plurality of 2nd crankshaft journal is respectively arranged to: carry out described 2nd crankshaft journal vertically projecting gained To projection section be positioned at the profile of described 2nd crankpin being connected with the 2nd crankshaft journal,

The axial width of the plurality of eccentric disc axial than described 1st crankshaft journal and described 2nd crankshaft journal respectively Length is little.

Stepless speed changing mechanism the most according to claim 1, wherein,

Described 1st through hole formed on described eccentric disc does not connects with described 2nd through hole.