CN105365547A - Continuously variable transmission mechanism - Google Patents
Continuously variable transmission mechanism Download PDFInfo
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- CN105365547A CN105365547A CN201510479446.1A CN201510479446A CN105365547A CN 105365547 A CN105365547 A CN 105365547A CN 201510479446 A CN201510479446 A CN 201510479446A CN 105365547 A CN105365547 A CN 105365547A
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Abstract
The invention provides a continuously variable transmission mechanism. The provided continuously variable transmission mechanism can at least prevent the increasing of eccentric amount when an actuator, which is used to drive a crankshaft part to rotate and control the eccentric amount of an eccentric disc, is at fault. The gear ratio variable mechanism (112) comprises the center (A) of a first crankshaft journal (106p, 106q, 106r), the center (B) of a second crankshaft journal (107p, 107q, 107r), the center (C) of a first crankshaft pin (106c-106h), and the center (D) of a second crankshaft pin (107c-107h). The gravity centers (GP) of each eccentric disc (104) are arranged in one area (U1) (including the imaginary line) of two areas (U1,U2), which are formed by an imaginary line (175). The eccentric quantities (r) of AC connecting rod (173) and BD connecting rod (174) decrease in the rotation direction; and when the maximal eccentric quantity is reached, the input shaft rotates at a maximal rotation speed, the imaginary line goes through the rotation center (O1) of the input shaft and is parallel to the AC connecting rod and the BD connecting rod.
Description
Technical field
The present invention relates to the stepless speed changing mechanism of crank-type, the eccentric rotary of the eccentric disk be arranged on input shaft is converted to the reciprocally swinging of the input block of free-wheel clutch by it via connecting member, and converts the reciprocally swinging of input block the unidirectional intermittent rotary of output shaft to via free-wheel clutch.
Background technology
As the toric transmission of crank-type, the structure described in known patent document 1.As shown in figure 20, the stepless speed changing mechanism of the toric transmission described in patent documentation 1 possesses: a pair crankshaft component 201,201, and they have crankshaft neck 202 and Crankpin 203; With input shaft (not shown), each crankshaft neck 202 is supported to rotatable by respectively.Input shaft rotates centered by the central O1 (following, to be also called input central axis or centre of gration) connecting the line segment of center A, B of a pair crankshaft neck 202,202, and thus, a pair crankshaft component 201,201 revolves round the sun around centre of gration O1.
The Crankpin 203 of a pair crankshaft component 201,201 is rotatably embedded in a pair through hole 205,206 be located on eccentric disk 204.Thus, by making a pair crankshaft component 201,201 synchronously rotate around each crankshaft neck 202, the offset r of eccentric disk 204 relative to the centre of gration O1 of input shaft can be changed.Namely, as shown in figure 21, a pair crankshaft component 201,201 constitutes following four joints connecting rod mechanism (parallel linkage) 210 like this: it has the center D of center A, the center B of another crankshaft neck 202 of a crankshaft neck 202, the center C of a Crankpin 203 and another Crankpin 203, center A and center B is stationary nodes, and center C and center D is movable node.Eccentric disk 204 changes along with the movement of the CD connecting rod as movable link relative to the offset r of the centre of gration O1 of input shaft.Further, when eccentric disk 204 rotates together with input shaft, all not shown pipe link corresponds to the offset r of eccentric disk 204 and swings, and exports output shaft via free-wheel clutch to as rotary motion.
Patent documentation 1: Japanese Patent No. 5142234 publication
As shown in figure 21, when eccentric disk 204 rotates, at the center of gravity GP place of eccentric disk 204, produce centnifugal force F along from the centre of gration O1 of input shaft towards the direction of the center of gravity GP of eccentric disk 204.If be not intended to especially, the center of gravity GP of the eccentric disk 204 and external diameter center O3 of eccentric disk 204 is (following, be called the 1st fulcrum) roughly consistent, therefore, the centnifugal force F putting on eccentric disk 204 works as making a pair Crankpin 203,203 become towards the offset r of eccentric disk 204 the torque T that large direction rotates centered by respective crankshaft neck 202,202.This torque T is driven a pair crankshaft component 201 actuator (not shown) that synchronously flexing shaft neck 202 rotates to support, and stops the rotation of a pair Crankpin 203,203.
On the other hand, as shown in figure 22, the permission rotating speed of input shaft corresponds to the offset r of eccentric disk 204 and decides.In other words, if the offset r of eccentric disk 204 is comparatively large, then the amount of exercise of pipe link or free-wheel clutch etc. also becomes large, therefore, according to the relation of the mechanical strength of each part etc., sets the rotating speed of permission.
Usually, the torque T produced on crankshaft component 201 because of the centnifugal force F of eccentric disk 204 works as the load of actuator, and the rotation of crankshaft component 201 is stoped by actuator, and the offset r of eccentric disk 204 is maintained.; if just in case actuator is not because fault etc. work; then exist and to make because of the centnifugal force F of eccentric disk 204 crankshaft component 201 become towards the offset r of eccentric disk 204 possibility that large direction rotates, in this case, the control allowed band shown in Figure 22 may be departed from.
Summary of the invention
The object of the present invention is to provide a kind of stepless speed changing mechanism, even if rotate at driving a pair crankshaft component and when there occurs fault to the actuator that the offset of eccentric disk controls, eccentric quantitative change also at least can be stoped large.
In order to reach above-mentioned purpose, invention described in technical scheme 1 be stepless speed changing mechanism (such as, stepless speed changing mechanism BD in embodiment described later), described stepless speed changing mechanism possesses: input shaft (such as, axle journal support unit 151 in embodiment described later), it rotates around input central axis (the input central axis O1 such as, in embodiment described later) by accepting rotary power from drive source, multiple eccentric disk (such as, eccentric disk 104 in embodiment described later), described multiple eccentric disk has the 1st fulcrum (such as at respective center, the 1st fulcrum O3 in embodiment described later), each 1st fulcrum is circumferentially disposed at equal intervals around this input central axis, and each 1st fulcrum relative to described input central axis offset (such as, offset r in embodiment described later) can be changed, described multiple eccentric disk rotates together with described input shaft around this input central axis while this offset of maintenance, and, described multiple eccentric disk is formed respectively with described input centerline axis parallel the through hole that extends (such as, through hole 104a in embodiment described later, 104b), 1st crankshaft component (such as, the 1st crankshaft component 106 in embodiment described later), 1st crankshaft component has multiple 1st Crankpin (such as, the 1st Crankpin 106c ~ 106h in embodiment described later) and multiple 1st crankshaft neck is (such as, the 1st crankshaft neck 106p in embodiment described later, 106q, 106r), described multiple 1st Crankpin rotatably through described through hole formed on described multiple eccentric disk, and it is connected to each other, described multiple 1st crankshaft neck respectively at the central axis from this each 1st Crankpin (such as, central axis 106k in embodiment described later) position that offset by equidistance has central axis (such as, central axis 106b in embodiment described later), 2nd crankshaft component (such as, the 2nd crankshaft component 107 in embodiment described later), 2nd crankshaft component has multiple 2nd Crankpin (such as, the 2nd Crankpin 107c ~ 107h in embodiment described later) and multiple 2nd crankshaft neck is (such as, the 2nd crankshaft neck 107p in embodiment described later, 107q, 107r), described multiple 2nd Crankpin rotatably through described through hole formed on described multiple eccentric disk, and it is connected to each other, described multiple 2nd crankshaft neck respectively at the central axis from this each 2nd Crankpin (such as, central axis 107k in embodiment described later) position that offset by equidistance has central axis (such as, central axis 107b in embodiment described later), free-wheel clutch (such as, free-wheel clutch OWC in embodiment described later), this free-wheel clutch has around departing from the output center axis of described input central axis (such as, output center axes O 2 in embodiment described later) output block that rotates is (such as, power-transfer clutch inner component 121 in embodiment described later), by accept from outside hand of rotation power and around described output center axis oscillating input block (such as, clutch Outside part 122 in embodiment described later), and make these input blocks and output block become mutually the attachment of lock-out state or unlock state (such as, roller 123 in embodiment described later), when the rotating speed of the forward of described input block exceedes the rotating speed of the forward of described output block, the rotary power being input to described input block is passed to described output block by this free-wheel clutch, thus the hunting motion of described input block is converted to the rotary motion of described output block, multiple connecting member (such as, connecting member 130 in embodiment described later), the plurality of connecting member one end separately (such as, ring portion 131 in embodiment described later) centered by described 1st fulcrum, be rotatably attached at the periphery of each described eccentric disk, the plurality of connecting member other end separately (such as, end 132 in embodiment described later) be rotatably linked on the input block of described free-wheel clutch depart from described output center axis position arrange the 2nd fulcrum (such as, the 2nd fulcrum O4 in embodiment described later), thus, the rotary motion putting on described eccentric disk from described input shaft is passed to this input block as the hunting motion of the input block of described free-wheel clutch, and converter speed ratio changeable mechanism (such as, converter speed ratio changeable mechanism 112 in embodiment described later), this converter speed ratio changeable mechanism possesses actuator (such as, actuator 180 in embodiment described later), described actuator makes described 1st Crankpin and described 2nd Crankpin synchronously rotate centered by the described 1st and the 2nd crankshaft neck respectively, regulate described 1st fulcrum relative to the offset of described input central axis, change the pendulum angle of the hunting motion being passed to the input block of described free-wheel clutch from described eccentric disk thus, described converter speed ratio changeable mechanism utilizes this actuator to change the converter speed ratio when the rotary power being input to described input shaft is passed to the output block of described free-wheel clutch via described eccentric disk and described connecting member as rotary power, and, owing to described offset can be set as zero, thus converter speed ratio can be set as infinity, wherein, described converter speed ratio changeable mechanism comprises four joint connecting rod mechanisms (such as, parallel linkage 170 in embodiment described later), this four joints connecting rod mechanism is having from during end on observation: the center A of described 1st crankshaft neck of regulation, the center B of described 2nd crankshaft neck identical with described 1st crankshaft neck phase place, the center C of described 1st Crankpin be connected with described 1st crankshaft neck of described regulation, and the center D of described 2nd Crankpin identical with described 1st Crankpin phase place, in this four joints connecting rod mechanism, when described offset change, described center A and described center B is stationary nodes, described center C and described center D is movable node, the center of gravity of each described eccentric disk (such as, center of gravity GP in embodiment described later) be arranged on by following straight line (such as, imaginary line 175 in embodiment described later) 2 regions being partitioned into are (such as, region U1 in embodiment described later, U2), comprise and described straight line makes the AC connecting rod of connection described center A and described center C (such as, AC connecting rod 173 in embodiment described later) be connected the BD connecting rod of described center B and described center D (such as, BD connecting rod 174 in embodiment described later) side that rotates towards the direction that described offset reduces, when described offset is the maximum eccentricity amount in the offset that described input shaft can be made to rotate with maximum speed, the centre of gration of input shaft described in described straight-line pass, and it is parallel with described BD connecting rod with described AC connecting rod.
In addition, about the invention described in technical scheme 2, in the invention described in technical scheme 1, when described offset is zero, the center of gravity of each described eccentric disk is arranged on the described straight line that described straight line and the intersection point (the intersection point XP such as, in embodiment described later) of CD connecting rod and the AB connecting rod side from this intersection point eliminated.
In addition, about the invention described in technical scheme 3, in the invention described in technical scheme 1, the center of gravity of each described eccentric disk is arranged on the point of intersection of described straight line and CD connecting rod.
Invention according to technical scheme 1, the center of gravity of eccentric disk is arranged on the region that the centnifugal force acting on eccentric disk makes eccentric disk rotate towards reduction eccentric disk relative to the direction of the offset of crankshaft component, therefore, even if when the actuator et out of order that contingency driving crank parts rotate, also the action under the state having departed from running allowed band can be prevented, thereby, it is possible to prevent the part forming stepless speed changing mechanism from damaging.
Invention according to technical scheme 2, on the basis of the effect of technical scheme 1, when actuator there occurs fault, can make the offset of eccentric disk naturally converge to zero.Thereby, it is possible to make the vehicle safety being equipped with stepless speed changing mechanism stop.
Invention according to technical scheme 3, has nothing to do with the size of the offset of eccentric disk, and the centnifugal force acting on eccentric disk can not produce the torque in the direction that crankshaft component is rotated.Thus, the load caused by the centnifugal force of eccentric disk can not act on actuator, and the load of actuator reduces.
Accompanying drawing explanation
Fig. 1 is the cutaway view of the stepless speed changing mechanism that the 1st embodiment of the present invention is shown.
Fig. 2 is the lateral plan of the stepless speed changing mechanism shown in Fig. 1.
Fig. 3 is the block diagram of the main portion that stepless speed changing mechanism is shown.
Fig. 4 is the lateral plan of each crankshaft component in stepless speed changing mechanism.
Fig. 5 is the lateral plan of the 2 kinds of eccentric disks illustrated in stepless speed changing mechanism.
Fig. 6 is the instruction diagram that the position relationship between each eccentric disk and each Crankpin forming stepless speed changing mechanism is shown.
Fig. 7 be every 60 ° of anglecs of rotation illustrate that eccentric disk in stepless speed changing mechanism rotates around input central axis under the state that offset is fixed time the action diagram of change.
Fig. 8 be every each crankshaft component 45 ° of anglecs of rotation the instruction diagram of state that the offset of the eccentric disk made in stepless speed changing mechanism changes is shown.
Fig. 9 shows the position relationship between each eccentric disk under each offset of stepless speed changing mechanism and each Crankpin, wherein (a) illustrates that offset r is the figure of the state of " zero ", b () illustrates that offset r is the figure of the state of " medium ", (c) illustrates that offset r is the figure of the state of " greatly ".
Figure 10 is the schematic diagram of the four joint connecting rod mechanisms that stepless speed changing mechanism is shown.
Figure 11 be the offset of the eccentric disk that stepless speed changing mechanism is shown different when the action diagram of change of oscillating quantity of free-wheel clutch exterior part, wherein (a) is the figure of the state that offset r larger " greatly " is shown, b () illustrates that offset r is the figure of the state of less than the situation of (a) " medium ", (c) illustrates that offset r is the figure of the state of less than the situation of (b) " little ".
Figure 12 is the figure that when making the offset r of the eccentric disk of constant speed rotation together with input shaft (converter speed ratio i) be changed to " greatly ", " medium ", " little " in stepless speed changing mechanism, between the anglec of rotation θ of input shaft and the pivot angle speed omega 2 of the input block of free-wheel clutch relation is shown.
Figure 13 is the figure of the derivation principle for illustration of the output in stepless speed changing mechanism when utilizing multiple connecting member from input side (input shaft or eccentric disk) to outgoing side (output block of free-wheel clutch) transferring power.
Figure 14 is the lateral plan that the relation between parallel linkage and the center of gravity of eccentric disk formed by the 1st and the 2nd crankshaft component in the 1st embodiment is described.
Figure 15 is the line chart of the state that Figure 14 is shown.
Figure 16 is the lateral plan of the relation between the parallel linkage formed by the 1st and the 2nd crankshaft component of the stepless speed changing mechanism that the 2nd embodiment of the present invention is described and the center of gravity of eccentric disk.
Figure 17 is the line chart of the state that Figure 16 is shown, wherein (a) is the line chart that the state that parallel linkage rotates to the direction making offset reduce is shown, (b) is offset is zero line chart achieving the state of convergence.
Figure 18 is the stepless speed changing mechanism of the 3rd embodiment of the present invention, and wherein (a) is the lateral plan of parallel linkage when illustrating that offset is less and the relation between the center of gravity of eccentric disk, and (b) is the line chart of (a).
(a) of Figure 19 is the lateral plan of parallel linkage when illustrating that offset is larger and the relation between the center of gravity of eccentric disk, and (b) is the line chart of (a).
Figure 20 is the lateral plan of the relation between the parallel linkage formed by the 1st and the 2nd crankshaft component of the stepless speed changing mechanism illustrated in the past and the center of gravity of eccentric disk.
Figure 21 is the line chart of the state that Figure 20 is shown.
Figure 22 illustrates that the offset of eccentric disk and input shaft allow the figure of the relation between rotating speed.
Label declaration
104,104A-104F: eccentric disk;
104a, 104b: through hole;
106: the 1 crankshaft components;
The central axis of the 106b: the 1 crankshaft neck;
106c-106h: the 1 Crankpin;
The central axis of the 106k: the 1 Crankpin;
106p-106r: the 1 crankshaft neck;
107: the 2 crankshaft components;
The central axis of the 107b: the 2 crankshaft neck;
107c-107h: the 2 Crankpin;
107p-107r: the 2 crankshaft neck;
The central axis of the 107k: the 2 Crankpin;
112: converter speed ratio changeable mechanism;
121: power-transfer clutch inner component (output block);
122: clutch Outside part (input block);
123: roller (attachment);
130: connecting member;
131: ring portion (one end);
132: end (other end);
151: axle journal support unit (input shaft);
170: parallel linkage (four joint connecting rod mechanisms);
171:AB connecting rod;
172:CD connecting rod;
173:AC connecting rod;
174:BD connecting rod;
175: imaginary line (straight line);
180: actuator;
BD: stepless speed changing mechanism;
The center of the A: the 1 crankshaft neck;
The center of the B: the 2 crankshaft neck;
The center of the C: the 1 Crankpin;
The center of the D: the 2 Crankpin;
GP: the center of gravity of eccentric disk;
O1: input central axis, centre of gration;
O2: output center axis;
O3: the 1 fulcrum;
O4: the 2 fulcrum;
OWC: free-wheel clutch;
R: the offset of eccentric disk;
U1, U2: region;
XP: the intersection point of straight line and CD connecting rod.
Detailed description of the invention
Below, with reference to accompanying drawing, embodiments of the present invention are described.
(the 1st embodiment)
The stepless speed changing mechanism of the 1st embodiment is the one of the speed-changing mechanism being referred to as IVT (InfinityVariableTransmission=makes when not using power-transfer clutch converter speed ratio infinitely great thus output can be made to rotate to be the speed-changing mechanism of the mode of zero), it is made up of following such stepless speed changing mechanism BD: this stepless speed changing mechanism BD can infinitely change converter speed ratio i, and the maxim of converter speed ratio can be set as infinity (∞).
As shown in Figure 1, stepless speed changing mechanism BD possesses: as the axle journal support unit 151 of input shaft, and the output shaft S of the drive sources such as itself and driving engine links, and rotates around input central axis O1 by accepting the rotary power of drive source; Multiple (being 6 in the present embodiment) eccentric disk 104 (following, also 6 eccentric disks to be called 104A ~ 104F), they rotate integrally via the 1st and the 2nd crankshaft component 106,107 and axle journal support unit 151; The connecting member 130 identical with the quantity of eccentric disk 104, they are for coupling together input side and outgoing side; And free-wheel clutch OWC, it is arranged on outgoing side.
Also in the lump as shown in Fig. 2, Fig. 3 and Fig. 5, it is round-shaped that multiple eccentric disk 104 is formed as respectively centered by the 1st fulcrum O3, and each 1st fulcrum O3 configures in the mode of the surrounding being circumferentially equally spaced positioned at input central axis O1.Further, multiple eccentric disk 104, respectively under the state that remain offset r, carries out eccentric rotary along with the rotation of axle journal support unit 151 around input central axis O1.In addition, multiple eccentric disk 104 is configured to change the offset r of each 1st fulcrum O3 relative to input central axis O1.And, multiple eccentric disk 104 is formed 2 through holes 104a, 104b respectively that extend abreast with input central axis O1.
As shown in Figure 1 to 4,1st crankshaft component 106 has: multiple 1st Crankpin 106c ~ 106h, they are rotatably applied in by plain bearing 155 in a through hole 104a in 2 through holes 104a, the 104b be formed on multiple eccentric disk 104 respectively, and they are connected to each other; With multiple 1st crankshaft neck 106p, 106q, 106r, they are offseting equidistance position from the central axis 106k of each 1st Crankpin 106c ~ 106h has central axis 106b.
2nd crankshaft component 107 has similarly: multiple 2nd Crankpin 107c ~ 107h, and they are rotatably applied in by plain bearing 155 in another through hole 104b of being formed on multiple eccentric disk 104 respectively, and they are connected to each other; With multiple 2nd crankshaft neck 107p, 107q, 107r, they are offseting equidistance position from the central axis 107b of each 2nd Crankpin 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 central axis 106b, 107b of each 1st and the 2nd crankshaft neck 106p, 106q, 106r, 107p, 107q, 107r are configured to parallel with input central axis O1 under the state being installed on stepless speed changing mechanism BD.
In addition, centered by central axis 106b, 107b of the 1st and the 2nd crankshaft neck 106p, 106q, 106r, 107p, 107q, 107r, the mode of angle (being 60 ° in the present embodiment) that specifies of interval is combined respectively in a circumferential direction to make their each central axis 106k, 107k for each 1st and the 2nd Crankpin 106c ~ 106h, the 107c ~ 107h of each 1st and the 2nd crankshaft component 106,107.
Further, in figure 3, eliminate the 1st and the 2nd crankshaft neck 106q, 107q to illustrate.
In addition, as shown in Figure 5,2 through holes 104a, 104b of each eccentric disk 104 that each 1st and the 2nd Crankpin 106c ~ 106h, 107c ~ 107h are through are formed as: 2 through holes 104a, 104b arrange adjacent to each other, and the intermediate point M of through hole 104a, 104b offsets from the 1st fulcrum O3.In addition, 2 through holes 104a, 104b of each eccentric disk 104 are formed as respectively: the angle (being 60 ° in the present embodiment) that the intermediate point M of through hole 104a, 104b of multiple eccentric disk 104 specifies at circumferencial direction interval centered by the 1st fulcrum O3.Specifically, in 6 eccentric disks 104 of present embodiment, for the through eccentric disk 104A of the 1st and the 2nd Crankpin 106c, 107c with for the through eccentric disk 104D of the 1st and the 2nd Crankpin 106f, 107f by following such Structure composing: the line being connected center 104e, 104f of through hole 104a, 104b is positioned on the line by the 1st fulcrum O3.In addition, for the through eccentric disk 104B of the 1st and the 2nd Crankpin 106d, 107d, for the through eccentric disk 104C of the 1st and the 2nd Crankpin 106e, 107e, for the through eccentric disk 104E of the 1st and the 2nd Crankpin 106g, 107g and for the through eccentric disk 104F of the 1st and the 2nd Crankpin 106h, 107h by following such Structure composing: the line connecting intermediate point M and the 1st fulcrum O3 intersects with 60 ° of lines with center 104e, 104f of being connected 2 through holes 104a, 104b.
Therefore, if to input each eccentric disk 104A ~ 104F illustrated respectively centered by central axis O1 under offset r, then each eccentric disk 104A ~ 104F has position relationship such shown in Fig. 6.Namely, under the state making the 1st fulcrum O3 at the center becoming each eccentric disk 104A ~ 104F identical relative to the offset r of input central axis O1, each 1st and the 2nd Crankpin 106c ~ 106h, 107c ~ 107h are in the position that to have rotated 60 ° centered by central axis 106b, 107b clockwise successively, and each eccentric disk 104A ~ 104F also becomes to input the position relationship that to have rotated 60 ° centered by central axis O1 clockwise successively.
And, centered by central axis 106b, 107b in conjunction with the angle of each 1st and the 2nd Crankpin 106c ~ 106h, 107c ~ 107h or the relation between each through hole 104a, 104b of being formed on each eccentric disk 104 and the 1st fulcrum O3 (such as, the angle connecting the line of intermediate point M with the 1st fulcrum O3 of each through hole 104a, 104b, intersect with the line of center 104e, 104f of being connected 2 through holes 104a, 104b) determined by the number of eccentric disk 104, that is, 360 degree of values obtained divided by the quantity of eccentric disk 104 are become.
Axle journal support unit 151 is the one-body molded product be made up of following part: cylindrical portion 151d, and it is combined with the end spline of output shaft S; With axle journal support 151h, it has, via plain bearing 157, the 1st and the 2nd crankshaft neck 106p, 107p of the 1st and the 2nd crankshaft component 106,107 is supported to rotatable 2 through holes 151a, 151b.
In addition, the 1st and the 2nd crankshaft neck 106q, 107q of the between 2 eccentric disks 104C, 104D the 1st and the 2nd crankshaft component 106,107 is supported to rotatable by 2 through holes 152a, the 152b be formed on axle journal support unit 152 via plain bearing 157.
And, the the 1st and the 2nd crankshaft neck 106r, 107r of 1st and the 2nd crankshaft component 106,107 is formed with ring gear 106a, 107a, these ring gears 106a, 107a in actuator 180 with and the miniature gears 180b that inputs the S. A. 180a that central axis O1 is arranged coaxially engage, and to engage with the gear ring 115 of the surrounding being arranged on them.
Further, 2 the 1st and the 2nd crankshaft component 106,107 are supported to rotatable axle journal support unit 151,152 and gear ring 115 is supported by the case of transmission 160 of not shown change-speed box via bearing 102,105,103 respectively.
The number of teeth of ring gear 106a, 107a of 2 the 1st and the 2nd crankshaft component 106,107 is identical, and miniature gears 180b rotates by means of actuator 180, and thus, 2 ring gears 106a, 107a rotate with identical rotating speed.Actuator 180 is made up of Direct Current Motor and speed reduction gearing etc., time usual, the rotation of miniature gears 180b and axle journal support unit 151 is synchronously rotated.Therefore, as shown in (a) ~ (f) of Fig. 7,1st and the 2nd crankshaft component 106,107 and eccentric disk 104 rotate integratedly to input centered by central axis O1, as shown in (d) of Fig. 7, if the diameter of eccentric disk 104 is set to D, then the peak swing W of eccentric disk 104 is W=D+2r.Further, (f) of (a) ~ Fig. 7 of Fig. 7 shows and the anglec of rotation of the 1st and the 2nd crankshaft component 106,107 and eccentric disk 104 is set to respectively α=0 °, the state of 60 °, 120 °, 180 °, 240 °, 300 °.
In addition, to make axle journal support unit 151 and the synchronous rotating speed of miniature gears 180b for benchmark, the rotating speed being greater than or less than the rotating speed of axle journal support unit 151 is applied to miniature gears 180b, makes miniature gears 180b relatively rotate relative to axle journal support unit 151 thus.The rotating speed carried out based on this actuator 180 controls such as to realize in the following manner: relative to the rotating speed of axle journal support unit 151, the rotating speed of the miniature gears 180b that the rotating speed controlling to be multiplied by actuator 180 by the reduction ratio of speed reduction gearing (such as, planetary wheel) obtains.Now, when miniature gears 180b and axle journal support unit 151 do not exist rotation difference and realize synchronous, offset r does not change.
Therefore, by providing the rotating speed of the rotating speed being greater than or less than axle journal support unit 151 to miniature gears 180b, there is the 1st and the 2nd crankshaft neck 106r, 107r rotation of ring gear 106a, 107a, thus, 1st Crankpin 106c ~ 106h and the 2nd Crankpin 107c ~ 107h is synchronous rotary centered by central axis 106b, 107b of the 1st and the 2nd crankshaft neck 106r, 107r respectively, regulates the 1st fulcrum O3 relative to the offset r of input central axis O1.
In addition, free-wheel clutch OWC has: as the power-transfer clutch inner component 121 of output block, and it rotates around the output center axes O 2 departing from input central axis O1; As the clutch Outside part 122 of the ring-type of input block, it swings around output center axes O 2 by accepting the power of hand of rotation from outside; As multiple rollers 123 of attachment, it is in order to be set to mutually lock-out state or unlock state and be inserted between clutch Outside part 122 and power-transfer clutch inner component 121 by these clutch Outside parts 122 and power-transfer clutch inner component 121; And force application part 126, its pair roller 123 is towards the direction force applying lock-out state, when the rotating speed of the forward (direction shown in the arrow RD1 in Fig. 2) of clutch Outside part 122 exceedes the rotating speed of the forward of power-transfer clutch inner component 121, the rotary power being imported into clutch Outside part 122 is passed to power-transfer clutch inner component 121 by free-wheel clutch OWC, thereby, it is possible to the hunting motion of clutch Outside part 122 to be converted to the rotary motion of power-transfer clutch inner component 121.
As shown in Figure 1, the power-transfer clutch inner component 121 of free-wheel clutch OWC is configured to vertically continuous print parts integratedly, but, clutch Outside part 122 is split into multiple vertically, and is correspondingly arranged in can axially separately swinging with the quantity of eccentric disk 104 and connecting member 130.Further, roller 123 corresponds to each clutch Outside part 122 and inserts between clutch Outside part 122 and power-transfer clutch inner component 121.
One position, place of the circumference on each clutch Outside part 122 of ring-type is provided with protrusion 124, and this protrusion 124 is provided with the 2nd fulcrum O4 departing from output center axes O 2.Further, the 2nd fulcrum O4 of each clutch Outside part 122 is configured with pin 125, utilizes this pin 125 that the end (the other end) 132 of connecting member 130 is linked to clutch Outside part 122 in rotatable mode.
Have ring portion 131 in the end side of connecting member 130, the inner circumferential of the circular open 133 of this ring portion 131 is entrenched in the periphery of eccentric disk 104 in rotatable mode by bearing 140.Therefore, one end of connecting member 130 is linked to the periphery of eccentric disk 104 in rotatable mode like this, and, the other end of connecting member 130 is linked to the 2nd fulcrum O4 arranged on the clutch Outside part 122 of free-wheel clutch OWC in a rotatable manner, thus constitute to input central axis O1, 1st fulcrum O3, output center axes O 2, these 4 nodes of 2nd fulcrum O4 are four joint connecting rod mechanisms of run-on point, from the axle journal support unit 151 as input shaft via 2 the 1st and the 2nd crankshaft component 106, 107 rotary motions being provided to eccentric disk 104 are passed to this clutch Outside part 122 by the hunting motion of the clutch Outside part 122 as free-wheel clutch OWC, the hunting motion of this clutch Outside part 122 is converted into the rotary motion of power-transfer clutch inner component 121.
Now, utilize actuator 180, make by 2 the 1st and the 2nd crankshaft component 106,107, the miniature gears 180b action of converter speed ratio changeable mechanism 112 that forms such as actuator 180, the offset r of eccentric disk 104 can be changed thus.And, by changing offset r, the pendulum angle θ 2 of the clutch Outside part 122 of free-wheel clutch OWC can be changed, thereby, it is possible to change the rotating speed of power-transfer clutch inner component 121 and the ratio (converter speed ratio i) of the rotating speed of the axle journal support unit 151 as input shaft.Therefore, the converter speed ratio when the rotary power being input to axle journal support unit 151 is passed to the power-transfer clutch inner component 121 of free-wheel clutch OWC via eccentric disk 104 and connecting member 130 as rotary power can be changed, in addition, owing to offset r can be set as zero, therefore, it is possible to converter speed ratio is set as infinity.
With reference to Fig. 8 and Fig. 9, the transmission principle of the above stepless speed changing mechanism BD described is described.
In (a) ~ (e) of Fig. 8, the figure in left side is the figure of the change of the offset under each rotational angle θ c of the 1st and the 2nd crankshaft component 106,107 illustrated when miniature gears 180b being rotated relatively in eccentric disk 104A, and the figure on right side is figure central axis 106b, 107b (black circle) of the 1st and the 2nd crankshaft neck 106r, 107r and the position relationship between central axis 106k, 107k (enclosing in vain) of the 1st and the 2nd Crankpin 106c, 107c extracted out from the figure in left side.Further, in order to easy understand shape, shade is applied with to the 1st and the 2nd Crankpin 106c, 107c, in addition, in (b) ~ (e) of Fig. 8, eliminate the miniature gears 180b shown in (a) of Fig. 8, show ring gear 106a, 107a with solid line circle.
As shown in (a) of Fig. 8, in eccentric disk 104A, when the rotational angle θ c=0 ° of the 1st and the 2nd crankshaft component 106,107, central axis 106b, 107b of 1st and the 2nd crankshaft neck 106r, 107r respectively relative to the 1st and central axis 106k, 107k of the 2nd Crankpin 106c, 107c be in the position offset upward, the input central axis O1 coaxial with miniature gears 180b and the 1st fulcrum O3 as the center of eccentric disk 104A overlaps.Therefore, the center (the 1st fulcrum O3) of eccentric disk 104 is zero relative to the offset r of input central axis O1, converter speed ratio i can be set as " infinitely great (∞) ".
Next, as shown in (d) of (b) ~ Fig. 8 of Fig. 8, the the 1st and the 2nd crankshaft component 106,107 rotational angle θ c=45 °, 90 °, 135 ° time, central axis 106k, 107k of 1st and the 2nd Crankpin 106c, 107c relative to the 1st and central axis 106b, 107b of the 2nd crankshaft neck 106r, 107r rotate to same direction, the center (the 1st fulcrum O3) of eccentric disk 104 is left gradually from input central axis O1, and offset r becomes large gradually.
Then, as shown in (e) of Fig. 8, when the rotational angle of the 1st and the 2nd crankshaft component 106,107 is θ c=180 °, central axis 106b, 107b of 1st and the 2nd crankshaft neck 106r, 107r respectively relative to the 1st and central axis 106k, 107k of the 2nd Crankpin 106c, 107c be in the position offset downwards, distance input central axis O1 farthest at the center (the 1st fulcrum O3) of eccentric disk 104, offset r becomes maximum, can realize little converter speed ratio.
(a) ~ (c) of Fig. 9 is the figure observing 6 eccentric disk 104A ~ 104F respectively from actuator 180 side, each 1st fulcrum O3 that (a) of Fig. 9 shows eccentric disk 104A ~ 104F is consistent with input central axis O1, offset r is set to the state of " zero ", namely, converter speed ratio i is set as infinitely-great situation, (b) of Fig. 9 sets that each 1st fulcrum O3 of eccentric disk 104A ~ 104F leaves from input central axis O1, offset r is set as the state of " medium ", namely, converter speed ratio i is set as the situation of middle converter speed ratio, each 1st fulcrum O3 distance input central axis O1 that (c) of Fig. 9 shows eccentric disk 104A ~ 104F farthest, offset r is set as the state of " greatly ", namely, converter speed ratio i is set as the situation of less converter speed ratio.
What the such rotational angle θ c based on the 1st and the 2nd crankshaft component 106,107 realized carries out the rotating speed that the adjustment of offset r is S. A. 180a by utilizing the actuator 180 shown in not shown control unit control chart 1.
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 2, these 4 nodes of the 2nd fulcrum O4 as four joint connecting rod mechanisms of run-on point, the rotary motion being applied to eccentric disk 104 from axle journal support unit 151 is passed to the clutch Outside part 122 of free-wheel clutch OWC as hunting motion, the hunting motion of this clutch Outside part 122 is converted into the rotary motion of power-transfer clutch inner component 121.
As shown in (a) of Figure 11, when the offset r of eccentric disk 104 being set as " greatly " and making the 1st fulcrum O3 rotate in the direction of the arrow centered by central axis O1 to input, the pendulum angle θ 2 of the clutch Outside part 122 of free-wheel clutch OWC can be increased, therefore, it is possible to realize less converter speed ratio i.
As shown in (b) of Figure 11, when the offset r of eccentric disk 104 is set as " medium ", pendulum angle θ 2 when the pendulum angle θ 2 of the clutch Outside part 122 of free-wheel clutch OWC can be made to be less than (a) of Figure 11 is little, therefore, it is possible to realize the converter speed ratio i larger than the situation of (a) of Figure 11.
As shown in (c) of Figure 11, when the offset r of eccentric disk 104 is set as " little ", pendulum angle θ 2 when the pendulum angle θ 2 of the clutch Outside part 122 of free-wheel clutch OWC can be made to be less than (b) of Figure 11 is little, therefore, it is possible to realize the converter speed ratio i larger than the situation of (b) of Figure 11.
Thus, the offset r of eccentric disk 104 is less, then the pendulum angle θ 2 of clutch Outside part 122 is less, and converter speed ratio i is larger, when making the offset r of eccentric disk 104 for " zero ", the pendulum angle θ 2 that can make the clutch Outside part 122 of free-wheel clutch OWC is " zero ", therefore, it is possible to be set as by converter speed ratio i " infinitely great (∞) ".
As shown in Figure 10, the power that the clutch Outside part 122 of free-wheel clutch OWC accepts to apply from eccentric disk 104 via connecting member 130 carries out hunting motion.If the axle journal support unit 151 making eccentric disk 104 rotate rotates 1 circle, then clutch Outside part 122 reciprocally swinging 1 time of free-wheel clutch OWC.As shown in figure 12, have nothing to do with the value of the offset r of eccentric disk 104, the oscillation period of the clutch Outside part 122 of free-wheel clutch OWC is always fixed.The pivot angle speed omega 2 of clutch Outside part 122 is determined by the spin velocity ω 1 of eccentric disk 104 (axle journal support unit 151) and offset r.
The ring portion 131 of multiple connecting members 130 of adapter shaft neck support part 151 and free-wheel clutch OWC is rotatably linked to the multiple eccentric disks 104 be disposed at equal intervals in the circumferential around input central axis O1, therefore, the hunting motion because of the rotary motion of each eccentric disk 104, the clutch Outside part 122 of free-wheel clutch OWC being produced is carried out with fixing phase place as shown in figure 13 so successively.
Now, power (torque) only just carries out from the clutch Outside part 122 of free-wheel clutch OWC towards the transmission of power-transfer clutch inner component 121 the rotating speed of the forward of clutch Outside part 122 (the arrow RD1 direction of Figure 10) has exceeded the condition of the rotating speed of the forward of power-transfer clutch inner component 121.Namely, in free-wheel clutch OWC, when the rotating speed of clutch Outside part 122 becomes the rotating speed height than power-transfer clutch inner component 121, just start, via roller 123, engaging (locking) of clutch Outside part 122 and power-transfer clutch inner component 121 occurs, the power of clutch Outside part 122 is passed to power-transfer clutch inner component 121 and produces propulsive effort.
After the driving realized based on 1 connecting member 130 terminates, the rotating speed of clutch Outside part 122 is lower than the rotating speed of power-transfer clutch inner component 121, and the locking realized based on roller 123 is returned state (idling conditions) freely by means of the propulsive effort of other connecting members 130 by removing.Correspondingly carry out above-mentioned action successively with the quantity of connecting member 130, thus hunting motion is converted to the rotary motion in a direction.Therefore, be only passed to power-transfer clutch inner component 121 successively at the power of clutch Outside part 122 in moment of the rotating speed exceeding power-transfer clutch inner component 121, achieve average rotary power roughly smoothly and be applied to power-transfer clutch inner component 121.
In 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 disk 104, converter speed ratio (variable Rate) can be determined.In this case, by offset r is set as zero, converter speed ratio i can be set as infinity (∞), even if in the rotary course of the output shaft S of drive source, also the pendulum angle θ 2 being passed to clutch Outside part 122 can be set as zero.That is, even if the output shaft S (with reference to Fig. 1) of drive source rotates, and can be also zero by the speed setting of the power-transfer clutch inner component 121 of free-wheel clutch OWC.
As mentioned above, make that there is the 1st and the 2nd crankshaft neck 106p ~ 106r respectively, 107p ~ 107r and the 1st and the 2nd Crankpin 106c ~ 106h, 1st and the 2nd crankshaft component 106 of 107c ~ 107h, 107 synchronous rotaries and change in the converter speed ratio changeable mechanism 112 of 2 crank-types of the offset r of eccentric disk 104, if be conceived to 1 group the 1st and the 2nd Crankpin (such as, 1st and the 2nd Crankpin 106c, 107c) and be embedded in eccentric disk on the 1st and the 2nd Crankpin (such as, 104A), then as shown in Figure 14 and Figure 15, by the center A of the 1st crankshaft neck 106p ~ 106r, the center B of the 2nd crankshaft neck 107p ~ 107r, the center C of the 1st Crankpin (106c), and the 2nd the center D of Crankpin (107c) constitute parallel linkage 170.
In this parallel linkage 170, center A and center B becomes stationary nodes, and the AB connecting rod 171 connecting center A and center B becomes stationary links.In addition, center C and center D becomes movable node, and the BD connecting rod 174 connecting the CD connecting rod 172 of center C and center D, be connected the AC connecting rod 173 of center A and center C and be connected center B and center D becomes movable link.
If (the some P0 of Figure 22) is by as the centre of gration O1 of the axle journal support unit 151 of input shaft and the imaginary line 175 parallel with BD connecting rod 174 with AC connecting rod 173 when utilizing the permission maximum eccentricity amount r0 at allowed maximum speed N0 and under this rotating speed, eccentric disk 104 is divided into 2 regions U1, U2, then the center of gravity GP of eccentric disk 104 is set at region, i.e. the region U1 of the side that AC connecting rod 173 and BD connecting rod 174 are rotated towards the direction that offset r reduces.Further, region U1 comprises the point on imaginary line 175.
When the 1st and the 2nd crankshaft component 106,107 and eccentric disk 104 rotate centered by centre of gration O1 by means of the power from input shaft, on eccentric disk 104, there is centnifugal force F along from centre of gration O1 towards the direction effect of the center of gravity GP of eccentric disk 104.The component of this centnifugal force F on the direction vertical with BD connecting rod 174 with AC connecting rod 173 works as the torque T making AC connecting rod 173 and BD connecting rod 174 direction that in fig .15 counterclockwise, namely offset r reduces rotate.
Usually, the AC connecting rod 173 caused by centnifugal force F and the torque T of BD connecting rod 174 become the load of actuator 180, and the rotation of the 1st and the 2nd crankshaft component 106,107 is stoped by actuator 180.Now, even if actuator 180 is failure to actuate for a certain reason, the direction that the 1st and the 2nd crankshaft component 106,107 also automatically can reduce to offset r by the centnifugal force F of eccentric disk 104 rotates.Further, when rotating to the position that imaginary line 175 is consistent with the center of gravity GP of eccentric disk 104, torque T disappears, and the rotation of the 1st and the 2nd crankshaft component 106,107 stops.
Therefore, such as, in fig. 22, even if actuator 180 is failure to actuate in the process operated with the condition of the offset r1 of eccentric disk 104, rotating speed N1 (some P1), 1st and the 2nd crankshaft component 106,107 also can by means of centnifugal force F automatic rotation, thus make offset r reduce.Thus, operating condition moves along dotted line towards arrow X-direction in fig. 22, ensure that safety.
Further, in the above description, the phase place for the 1st under the state of offset r=0 and the 2nd Crankpin describes relative to the situation (with reference to Figure 16) that AB connecting rod 171 is 90 °, but this angle is arbitrary.Also identical about following embodiment.
As mentioned above, stepless speed changing mechanism BD according to the present embodiment, converter speed ratio changeable mechanism 112 comprises parallel linkage 170, and this parallel linkage 170 is having from during end on observation: the center A of the 1st crankshaft neck 106p, 106q, 106r of regulation; The center B of 2nd crankshaft neck 107p, 107q, 107r identical with the 1st crankshaft neck 106p, 106q, 106r phase place; The center C of the 1st Crankpin 106c ~ 106h be connected with the 1st crankshaft neck 106p, 106q, 106r of regulation; And the center D of the 2nd Crankpin 107c ~ 107h identical with the 1st Crankpin 106c ~ 106h phase place.About this parallel linkage 170, when offset r changes, center A and center B is stationary nodes, and center C and center D is movable node.The center of gravity GP of each eccentric disk 104 be arranged on be supposed in 2 regions U1, U2 that straight line 175 is partitioned into, comprise the side that the AC connecting rod 173 making connection center A and center C on imaginary line 175 and the BD connecting rod 174 that is connected center B and center D rotate towards the direction that offset r reduces, when offset r is the maximum eccentricity amount r in the offset that input shaft can be made to rotate with maximum speed, described imaginary line 175 is parallel with BD connecting rod 174 with AC connecting rod 173 by the centre of gration O1 of input shaft.Therefore, even if when actuator 180 et out of order that contingency drives the 1st and the 2nd crankshaft component 106,107 to rotate, also the action under the state departing from running allowed band can be prevented, thereby, it is possible to prevent the part forming stepless speed changing mechanism BD from damaging.
(the 2nd embodiment)
Figure 16 is the lateral plan be described the relation between the parallel linkage of the stepless speed changing mechanism of the 2nd embodiment of the present invention and the center of gravity of eccentric disk, and (a), (b) of Figure 17 is its line chart.The difference of the stepless speed changing mechanism of the 2nd embodiment and the stepless speed changing mechanism of the 1st embodiment is, the center-of-gravity position of eccentric disk is different.Identical with the 1st embodiment except this point, in (a), (b) of Figure 16 and Figure 17, identical label is marked for the inscape identical with the 1st embodiment.
Therefore, for the part identical or equivalent with the stepless speed changing mechanism of the 1st embodiment, mark identical label or suitable label, and simplify or omit the description.
As shown in Figure 16 and Figure 17, in the stepless speed changing mechanism BD of present embodiment, when offset r is zero, the center of gravity GP of each eccentric disk 104 is arranged on the imaginary line 175 except imaginary line 175 and the intersection point XP of CD connecting rod 172 and AB connecting rod 171 side from this intersection point XP.
About the centnifugal force F that the eccentric disk 104 center of gravity GP being set in above-mentioned position acts on, as offset r > 0, the component of centnifugal force F on the direction vertical with BD connecting rod 174 with AC connecting rod 173 works ((a) with reference to Figure 17) as making AC connecting rod 173 and the BD connecting rod 174 torque T rotated to offset r=0, and the state ((b) with reference to Figure 17) of the centre of gration O1 finally the converging on input shaft offset r=0 consistent with the 1st fulcrum O3.
Therefore, such as, in fig. 22, even if actuator 180 is failure to actuate in the process operated with the condition of the offset r1 of eccentric disk 104, rotating speed N1 (some P1), the 1st and the 2nd crankshaft component 106,107 also can be automatically rotated to offset r=0 by means of the effect of centnifugal force F.Thus, operating condition moves towards arrow X-direction along dotted line in fig. 22 and becomes the state of the some P2 of offset r=0, exports and independently stops with the rotation of input shaft, ensure that safety.
As mentioned above, stepless speed changing mechanism BD according to the present embodiment, when offset r is zero, the center of gravity GP of eccentric disk 104 is arranged on the imaginary line 175 that eliminated in imaginary line 175 and the intersection point XP of CD connecting rod 172 and AB connecting rod 171 side from this intersection point XP, therefore, when actuator 180 there occurs fault, the offset r of eccentric disk 104 can be made naturally to converge to zero.Thus, when stepless speed changing mechanism BD is equipped on vehicle, vehicle parking can be made safely.And, from imaginary line 175 remove imaginary line 175 with the intersection point XP of CD connecting rod 172 be because: when the center of gravity GP of eccentric disk 104 is in intersection point XP, do not produce torque T, the state of offset r=0 can not be converged, by than this intersection point XP by AB connecting rod 171 side part removing be because: when the center of gravity GP of eccentric disk 104 is in this part, torque T can become large direction to offset r and work.
(the 3rd embodiment)
(a), (b) of Figure 18 be the offset of the stepless speed changing mechanism of the 3rd embodiment of the present invention less time lateral plan and line chart, (a), (b) of Figure 19 be offset larger time lateral plan and line chart.The difference of the stepless speed changing mechanism of the 3rd embodiment and the stepless speed changing mechanism of the 1st embodiment is, the center-of-gravity position of eccentric disk is different.Identical with the 1st embodiment except this point, in Figure 18 and Figure 19, identical label is marked for the inscape identical with the 1st embodiment.
Therefore, for the part identical or equivalent with the stepless speed changing mechanism of the 1st embodiment, mark identical label or suitable label, and simplify or omit the description.
In the stepless speed changing mechanism BD of present embodiment, as shown in (a), (b) of Figure 18 and (a), (b) of Figure 19, the center of gravity GP of eccentric disk 104 is arranged on the intersection point XP place of imaginary line 175 and CD connecting rod 172.That is, the center of gravity GP of eccentric disk 104 is consistent with the intersection point XP of CD connecting rod 172 with imaginary line 175.
Direction center of gravity GP being set in the centnifugal force F of eccentric disk 104 effect of above-mentioned position is parallel with BD connecting rod 174 with AC connecting rod 173, and has nothing to do with the size of offset r.Thus, torque T does not act on the 1st and the 2nd crankshaft component 106,107.Therefore, even if actuator 180 is failure to actuate, the 1st and the 2nd crankshaft component 106,107 also can not rotate, but maintains its position.In addition, even if when actuator 180 regular event, the 1st and the 2nd crankshaft component 106,107 also can not act on the torque T caused by centnifugal force F, therefore, the load acting on actuator 180 reduces.
As mentioned above, stepless speed changing mechanism BD according to the present embodiment, the center of gravity GP of eccentric disk 104 is arranged on the intersection point XP place of imaginary line 175 and CD connecting rod 172, therefore, the centnifugal force F acting on eccentric disk 104 becomes the power parallel with BD connecting rod 174 with AC connecting rod 173, and have nothing to do with the size of the offset r of eccentric disk 104, thus the torque T that the 1st and the 2nd crankshaft component 106,107 is rotated can not be produced.Thus, the load caused by the centnifugal force F of eccentric disk 104 can not act on actuator 180, and the load of actuator 180 reduces.
Further, the present invention is not limited to aforesaid each embodiment, can suitably carry out being out of shape, improvement etc.In addition, as long as can realize the present invention, the material, shape, size, quantity, configuration position etc. of each structural element in above-mentioned each embodiment can be arbitrary, not circumscribed.
Such as, in the above-described embodiment, be formed as such structure: be provided with on each eccentric disk 104 for through 2 through holes 104a, the 104b of the 1st and the 2nd Crankpin, but also can be such structure: be provided with on each eccentric disk 104 for the through single through hole be made up of elongated hole of the 1st and the 2nd Crankpin 106c ~ 106h, 107c ~ 107h both sides.
Claims (3)
1. a stepless speed changing mechanism, it has:
Input shaft, this input shaft rotates around input central axis by accepting rotary power from drive source;
Multiple eccentric disk, described multiple eccentric disk has the 1st fulcrum at respective center, each 1st fulcrum is circumferentially disposed at equal intervals around this input central axis, and each 1st fulcrum can be changed relative to the offset of described input central axis, described multiple eccentric disk rotates together with described input shaft around this input central axis while this offset of maintenance, further, described multiple eccentric disk is formed respectively and the through hole that extends of described input centerline axis parallel ground;
1st crankshaft component, 1st crankshaft component has multiple 1st Crankpin and multiple 1st crankshaft neck, described multiple 1st Crankpin rotatably through described through hole formed on described multiple eccentric disk, and connected to each other, described multiple 1st crankshaft neck has central axis in the position of the central axis skew equidistance from this each 1st Crankpin;
2nd crankshaft component, 2nd crankshaft component has multiple 2nd Crankpin and multiple 2nd crankshaft neck, described multiple 2nd Crankpin rotatably through described through hole formed on described multiple eccentric disk, and connected to each other, described multiple 2nd crankshaft neck has central axis in the position of the central axis skew equidistance from this each 2nd Crankpin;
Free-wheel clutch, this free-wheel clutch has the output block rotated around the output center axis departing from described input central axis, by accept from outside hand of rotation power and around the input block of described output center axis oscillating, and make these input blocks and output block become mutually the attachment of lock-out state or unlock state, when the rotating speed of the forward of described input block exceedes the rotating speed of the forward of described output block, the rotary power being input to described input block is passed to described output block by this free-wheel clutch, thus the hunting motion of described input block is converted to the rotary motion of described output block,
Multiple connecting member, the plurality of connecting member one end separately is rotatably attached at the periphery of each described eccentric disk centered by described 1st fulcrum, the plurality of connecting member other end separately is rotatably linked to the 2nd fulcrum that the position of departing from described output center axis on the input block of described free-wheel clutch is arranged, thus, the rotary motion putting on described eccentric disk from described input shaft is passed to this input block as the hunting motion of the input block of described free-wheel clutch; And
Converter speed ratio changeable mechanism, this converter speed ratio changeable mechanism possesses actuator, described actuator makes described 1st Crankpin and described 2nd Crankpin synchronously rotate centered by described 1st crankshaft neck and the 2nd crankshaft neck respectively, regulate described 1st fulcrum relative to the offset of described input central axis, change the pendulum angle of the hunting motion being passed to the input block of described free-wheel clutch from described eccentric disk thus, described converter speed ratio changeable mechanism utilizes this actuator to change the converter speed ratio when the rotary power being input to described input shaft is passed to the output block of described free-wheel clutch via described eccentric disk and described connecting member as rotary power, and, owing to described offset can be set as zero, thus converter speed ratio can be set as infinity, wherein,
Described converter speed ratio changeable mechanism comprises four joint connecting rod mechanisms, and this four joints connecting rod mechanism is having from during end on observation:
The center A of described 1st crankshaft neck of regulation;
The center B of described 2nd crankshaft neck identical with described 1st crankshaft neck phase place;
The center C of described 1st Crankpin be connected with described 1st crankshaft neck of described regulation; And
The center D of described 2nd Crankpin identical with described 1st Crankpin phase place,
In this four joints connecting rod mechanism, when described offset change, described center A and described center B is stationary nodes, and described center C and described center D is movable node,
The center of gravity of each described eccentric disk be arranged in 2 regions gone out by following line segmentation, comprise the side that the AC connecting rod making connection described center A and described center C on described straight line and the BD connecting rod that is connected described center B and described center D rotate towards the direction that described offset reduces: when described offset is the maximum eccentricity amount in the offset that described input shaft can be made to rotate with maximum speed, the centre of gration of input shaft described in described straight-line pass, and parallel with described BD connecting rod with described AC connecting rod.
2. stepless speed changing mechanism according to claim 1, wherein,
When described offset is zero, the center of gravity of each described eccentric disk is arranged on the described straight line that described straight line and the intersection point of CD connecting rod and the AB connecting rod side from this intersection point eliminated.
3. stepless speed changing mechanism according to claim 1, wherein,
The center of gravity of each described eccentric disk is arranged on the point of intersection of described straight line and CD connecting rod.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-170657 | 2014-08-25 | ||
| JP2014170657A JP2016044772A (en) | 2014-08-25 | 2014-08-25 | Continuously variable transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105365547A true CN105365547A (en) | 2016-03-02 |
Family
ID=55368378
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510479446.1A Pending CN105365547A (en) | 2014-08-25 | 2015-08-03 | Continuously variable transmission mechanism |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2016044772A (en) |
| CN (1) | CN105365547A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108731862A (en) * | 2017-04-17 | 2018-11-02 | 青岛鼎通新能源科技有限公司 | A method of realizing that permanent torque exports using centrifugal force |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1124829A (en) * | 1995-04-09 | 1996-06-19 | 李卫东 | Eccentric angle speed-change variable drive |
| JP2005256883A (en) * | 2004-03-10 | 2005-09-22 | Toyota Motor Corp | Controller for drive unit for vehicle |
| CN101140025A (en) * | 2006-09-06 | 2008-03-12 | 朱健 | Unidirectional clutch type stepless speed changer |
| JP2012149769A (en) * | 2012-02-27 | 2012-08-09 | Kubota Corp | Variable speed transmission |
-
2014
- 2014-08-25 JP JP2014170657A patent/JP2016044772A/en not_active Withdrawn
-
2015
- 2015-08-03 CN CN201510479446.1A patent/CN105365547A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1124829A (en) * | 1995-04-09 | 1996-06-19 | 李卫东 | Eccentric angle speed-change variable drive |
| JP2005256883A (en) * | 2004-03-10 | 2005-09-22 | Toyota Motor Corp | Controller for drive unit for vehicle |
| CN101140025A (en) * | 2006-09-06 | 2008-03-12 | 朱健 | Unidirectional clutch type stepless speed changer |
| JP2012149769A (en) * | 2012-02-27 | 2012-08-09 | Kubota Corp | Variable speed transmission |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108731862A (en) * | 2017-04-17 | 2018-11-02 | 青岛鼎通新能源科技有限公司 | A method of realizing that permanent torque exports using centrifugal force |
| CN108731862B (en) * | 2017-04-17 | 2021-10-26 | 青岛鼎通新能源科技有限公司 | Method for realizing constant torque output by utilizing centrifugal force |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2016044772A (en) | 2016-04-04 |
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