CN105370829A - Stepless speed changer - Google Patents
Stepless speed changer Download PDFInfo
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- CN105370829A CN105370829A CN201510441661.2A CN201510441661A CN105370829A CN 105370829 A CN105370829 A CN 105370829A CN 201510441661 A CN201510441661 A CN 201510441661A CN 105370829 A CN105370829 A CN 105370829A
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- China
- Prior art keywords
- eccentric disc
- pin portion
- crankshaft component
- axis
- support unit
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H21/00—Gearings comprising primarily only links or levers, with or without slides
- F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
- F16H21/12—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for conveying rotary motion
- F16H21/14—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for conveying rotary motion by means of cranks, eccentrics, or like members fixed to one rotary member and guided along tracks on the other
Abstract
The invention provides a stepless speed changer. The eccentric disc of the stepless speed changer is configured to inhibit the flexure of the first and second crankshafts which can adjust the eccentric amount. The stepless speed changer comprises a plurality of shaft neck bearing parts (22), which can support the first shaft net part (17a-17f) of the first crankshaft part (17) and the second shaft net part (18a-18f) of the second crankshaft part (18). The plurality of shaft neck bearing parts (22) is abut on the axial end surface of multiple eccentric discs (21), which are arranged on the first shaft net part (17a-17f) of the first crankshaft part (17) and the second shaft net part (18a-18f) of the second crankshaft part (18), and is capable of freely rotating relative to the axial end surface. So when a driving counter-force, which is transmitted from the connection rod (27) to the eccentric discs (21), is going to bend the first crankshaft part (17) and the second crankshaft part (18), the central shaft neck bearing part (22) inhibits the inclination of the eccentric discs (21), and thus the flexure of the first crankshaft part (17) and the second crankshaft part (18) is indirectly inhibited.
Description
Technical field
The present invention relates to stepless speed variator, it is by being connected and reciprocating connecting rod with the multiple eccentric discs carrying out eccentric rotary by input shaft, make multiple swing member reciprocally swinging, the reciprocally swinging of swing member is converted to the continuous rotation of output shaft via overrunning clutch, and, make the offset of multiple eccentric disc change thus the reciprocally swinging angle of swing member is changed, infinitely increase and decrease gear ratio thus.
Background technique
According to an example of following patent documentation 1 this stepless speed variator known.This stepless speed variator possesses configuration in parallel to each other and the 1st crankshaft component rotated integratedly with input shaft and the 2nd crankshaft component, the 1st pin portion embedding hole be arranged on eccentric disc and the 2nd pin portion embedding hole are supported on the 1st pin portion and the 2nd pin portion that arrange on the 1st crankshaft component and the 2nd crankshaft component respectively, make that the 1st crankshaft component is relative relative to input shaft with the 2nd crankshaft component to be rotated, make eccentric disc relative to the offset change of input axis thus.
Patent documentation 1: Japanese Patent No. 5142234 publication
; in above-mentioned stepless speed variator in the past; when the connecting rod be connected with eccentric disc moves to a direction and drives swing member; overrunning clutch engages and transfers a driving force to output shaft; but; the counter-force of the driving force that connecting rod transmits but puts on the 1st, the 2nd crankshaft component via eccentric disc, therefore, the 1st, the 2nd crankshaft component may be made to bend.If 1st, the 2nd crankshaft component bends, then the 1st, the 2nd pin portion tilts, therefore, there is such problem: 1st, the slide part of the 1st, the 2nd pin portion embedding hole of the 2nd pin portion and eccentric disc frictional loss or the frictional loss of the bearing of link supporting on eccentric disc is increased.
Summary of the invention
The present invention completes in view of aforesaid situation, its object is to the flexure suppressing the eccentric disc of stepless speed variator to be supported to the 1st, the 2nd crankshaft component that can adjust offset.
In order to reach above-mentioned purpose, according to the invention described in technological scheme 1, propose a kind of stepless speed variator, this stepless speed variator possesses: input shaft, and it is configured on input axis, and is transfused to the driving force of driving source, output shaft, it is configured in and exports on axis, and the driving force of described input shaft is passed to this output shaft after by speed change, 1st crankshaft component, itself and described input shaft rotate integratedly, 2nd crankshaft component, itself and described input shaft rotate integratedly, multiple eccentric disc, they are supported in described 1st, the 2nd crankshaft component, and described multiple eccentric disc is relative to the eccentricity variable of described input axis, multiple swing member, they are rotatably supported on the periphery of described output shaft, multiple overrunning clutch, they are configured between described output shaft and described multiple swing member, and multiple connecting rod, they connect described multiple eccentric disc and described multiple swing member, and described 1st crankshaft component possesses: multiple 1st collar, and they are configured on the 1st axis relative to described input eccentric axis, with multiple 1st pin portion, they are eccentric relative to described multiple 1st collar, and described 2nd crankshaft component possesses: multiple 2nd collar, and they are configured on the 2nd axis relative to described input eccentric axis, with multiple 2nd pin portion, they are eccentric relative to described multiple 2nd collar, and described multiple eccentric disc possesses: the 1st pin portion embedding hole, and it is rotatably fitted together to for described 1st pin portion, with the 2nd pin portion embedding hole, it is rotatably fitted together to for described 2nd pin portion, by making the described 1st, 2nd crankshaft component rotates relatively relative to described input shaft, change between the value making the offset of described multiple eccentric disc specify at zero-sum thus, the feature of described stepless speed variator is, described stepless speed variator possesses multiple axle journal support unit, described multiple axle journal support unit supporting described 1st collar of described 1st crankshaft component and described 2nd collar of described 2nd crankshaft component, the axial end of described multiple eccentric disc and the described multiple 1st, at least one party in the axial end in the 2nd pin portion abuts in relative rotatable mode with described multiple axle journal support unit.
In addition, according to the invention described in technological scheme 2, propose a kind of stepless speed variator, it is characterized in that, on the basis of the structure of technological scheme 1, described multiple axle journal support unit is made up of the intermediate journal support unit being positioned at the 1st end axis neck support part at axial two end part of described input axis and the 2nd end axis neck support part and the axial intermediate portion that is positioned at described input axis, described 1st, the 2nd end axis neck support part is supported in case of transmission, and described intermediate journal support unit is not supported in described case of transmission.
In addition, according to the invention described in technological scheme 3, propose a kind of stepless speed variator, it is characterized in that, on the basis of the structure of technological scheme 2, the axial thickness of described multiple eccentric disc is larger than the axial thickness in described 1st, the 2nd pin portion, and described multiple axle journal support unit abuts in relative rotatable mode with the axial end of described multiple eccentric disc.
In addition, invention according to technological scheme 4, proposes a kind of speed changer, it is characterized in that, on the basis of the structure of any one in technological scheme 1 ~ technological scheme 3, the external diameter of described multiple eccentric disc is roughly consistent with the external diameter of described multiple axle journal support unit.
In addition, 1st end axis neck support part the 12, the 2nd end axis neck support part 13 and the intermediate journal support unit 22 of mode of execution correspond to axle journal support unit of the present invention, 1st end axis neck support part 12 of mode of execution corresponds to input shaft of the present invention, and the motor E of mode of execution corresponds to driving source of the present invention.
According to the structure of technological scheme 1, when the 1st, the 2nd crankshaft component rotates integratedly with the input shaft being connected to driving source, by multiple eccentric discs of the 1st, the 2nd crankshaft component supporting around input axis eccentric rotary, connecting rod moves back and forth, make swing member reciprocally swinging, thus, multiple overrunning clutch engages off and on and makes output shaft continuous rotation.When the offset change making eccentric disc relative to input axis, the stroke of the reciprocating stroke of connecting rod and the reciprocally swinging of swing member changes, and the change of intermittent rotary angle each time of output shaft, gear ratio infinitely increases and decreases thus.
1st crankshaft component possesses: multiple 1st collar, and they are configured on the 1st axis relative to input eccentric axis; With multiple 1st pin portion, they are eccentric relative to multiple 1st collar, and the 2nd crankshaft component possesses: multiple 2nd collar, and they are configured on the 2nd axis relative to input eccentric axis; With multiple 2nd pin portion, they are eccentric relative to multiple 2nd collar, and multiple eccentric disc possesses: the 1st pin portion embedding hole, and it is rotatably fitted together to for the 1st pin portion; With the 2nd pin portion embedding hole, it is rotatably fitted together to for the 2nd pin portion, therefore, by making the 1st, the 2nd crankshaft component relatively rotate relative to input shaft, infinitely changes between the value that the offset of multiple eccentric disc can be made to specify at zero-sum.
Owing to possessing the multiple axle journal support units supported the 1st collar of the 1st crankshaft component and the 2nd collar of the 2nd crankshaft component, and the axial end of multiple eccentric disc and the 1st, the multiple 1st of 2nd crankshaft component, at least one party in the axial end in the 2nd pin portion abuts in relative rotatable mode with multiple axle journal support unit, therefore, the 1st, when 2nd crankshaft component will bend due to the driving counter-force from connecting rod transmission, axle journal support unit prevents the 1st, the inclination in the 2nd pin portion, thus, 1st, the flexure of the 2nd crankshaft component is inhibited directly, or, axle journal support unit suppresses the inclination of eccentric disc, thus, 1st, the flexure of the 2nd crankshaft component is suppressed indirectly.
In addition, according to the structure of technological scheme 2, multiple axle journal support unit is by the 1st end axis neck support part and the 2nd end axis neck support part that are positioned at the axial two end part inputting axis, form with the intermediate journal support unit of the axial intermediate portion being positioned at input axis, 1st, 2nd end axis neck support part is supported in case of transmission, intermediate journal support unit is not supported in case of transmission, therefore, can by the 1st, 2nd end axis neck support part is by the 1st, 2nd crankshaft component is stably supported on case of transmission, there is no need for the bearing be supported on by intermediate journal support unit on case of transmission simultaneously, the reduction of weight Xiao Minus and frictional loss can be realized.
In addition, according to the structure of technological scheme 3, the axial thickness of multiple eccentric disc than the 1st, the axial thickness in the 2nd pin portion is large, multiple axle journal support unit abuts in relative rotatable mode with the axial end of multiple eccentric disc, therefore, the area of abutting part can be suppressed for minimum limit thus reduce frictional loss, simultaneously, by making eccentric disc abut with axle journal support unit away from the position of the 1st axis and the 2nd axis as far as possible, the effect preventing the 1st, the 2nd crankshaft component flexure effectively can be played thus.
In addition, according to the structure of technological scheme 4, the external diameter of multiple eccentric disc is roughly consistent with the external diameter of multiple axle journal support unit, therefore, the effect preventing the 1st, the 2nd crankshaft component flexure can be played fully, the external diameter of axle journal support unit can be suppressed for minimum limit thus cut down weight simultaneously.
Accompanying drawing explanation
Fig. 1 is the longitudinal section of crank-type stepless speed variator.
Fig. 2 is the sectional view along the 2-2 line in Fig. 1.
Fig. 3 is the stereogram that state eccentric disc being supported on the 1st, the 2nd crankshaft component is shown.
Fig. 4 is the figure of the shape that 2 kinds of eccentric discs are shown.
Fig. 5 illustrates the phase place in pin portion of the 1st, the 2nd crankshaft component and the figure of the phase place of each eccentric disc.
Fig. 6 is the figure of the 6 direction arrows observations along Fig. 1.
Fig. 7 is the figure of the change of the offset that eccentric disc is shown.
Fig. 8 is the figure of the relation illustrated between the offset of eccentric disc and the angle of oscillation of swing member.
Fig. 9 is 9 enlarged views of Fig. 1.
Label declaration
11: case of transmission;
12: the 1 end axis neck support parts (input shaft, axle journal support unit);
13: the 2 end axis neck support parts (axle journal support unit);
17: the 1 crankshaft components;
17a ~ 17f: the 1 collar;
17h ~ 17m: the 1 pin portion;
18: the 2 crankshaft components;
18a ~ 18f: the 2 collar;
18h ~ 18m: the 2 pin portion;
21: eccentric disc;
21a: the 1 pin portion embedding hole;
21b: the 2 pin portion embedding hole;
22: intermediate journal support unit (axle journal support unit);
23: output shaft;
24: overrunning clutch;
25: swing member;
27: connecting rod;
E: motor (driving source);
L1: input axis;
L2: export axis;
L3: the 1 axis;
L4: the 2 axis;
W1: the axial thickness of eccentric disc;
The axial thickness in the W2: the 1, the 2nd pin portion;
ε: the offset of eccentric disc.
Embodiment
Below, based on Fig. 1 ~ Fig. 9, embodiments of the present invention are described.
As shown in Fig. 1 ~ Fig. 3 and Fig. 9, the 1st end axis neck support part the 12 and the 2nd end axis neck support part 13 be configured on input axis L1 is rotatably freely supported on the 1st sidewall 11a and the 2nd sidewall 11b of the case of transmission 11 of crank-type stepless speed variator T respectively via ball bearing 14,15.1st end axis neck support part 12 possesses: discoideus dish portion 12a, and it is supported on the 1st sidewall 11a via ball bearing 14; With the joint part 12b of cylindrical shape, it is given prominence to from an end face of dish portion 12a along input axis L1, and the bent axle 16 of motor E is connected with joint part 12b.1st axle journal bearing hole 12c and the 2nd axle journal bearing hole 12d is formed at the dish portion 12a of the 1st end axis neck support part 12 in the mode clipping input axis L1.On the other hand, be supported on via ball bearing 15 the 2nd sidewall 11b cylindrical shape the 2nd end axis neck support part 13 inner peripheral surface on, be formed with gear ring 13a.To be connected with the bent axle 16 of motor E and around the input shaft inputting the 1st end axis neck support part 12 that axis L1 rotates and constitute crank-type stepless speed variator T.
The two end part of the 1st crankshaft component 17 and the 2nd crankshaft component 18 are supported in the 1st end axis neck support part the 12 and the 2nd end axis neck support part 13.1st crankshaft component 17 possesses 6 the 1st collar 17a ~ 17f and 1 the 1st driven pinion 17g be configured on its 1st axis L3, and possesses 6 the 1st pin portion 17h ~ 17m that the mode be clipped between the 1st collar 17a ~ 17f and the 1st driven pinion 17g configures.The center of 6 the 1st pin portion 17h ~ 17m is eccentric with fixing distance relative to the 1st axis L3, and eccentric direction staggers mutually 60 °.The 2nd crankshaft component 18 be configured on the 2nd axis L4 is the parts with the 1st crankshaft component 17 same shape, and possesses 6 the 2nd collar 18a ~ 18f, 1 the 2nd driven pinion 18g and 6 the 2nd pin portion 18h ~ 18m.
The the 1st, the 2nd collar 17a, 18a of the end side of the 1st crankshaft component 17 and the 2nd crankshaft component 18 is rotatably embedded in the 1st axle journal bearing hole 12c and the 2nd axle journal bearing hole 12d of the 1st end axis neck support part 12 respectively.In addition, the the 1st, the 2nd driven pinion 17g, 18g of another side of the 1st crankshaft component 17 and the 2nd crankshaft component 18 engages with the gear ring 13a of driving pinion 20 and the 2nd end axis neck support part 13 simultaneously, and this driving pinion 20 is arranged on the output shaft of the shifting actuator 19 be made up of electric motor be supported on the 2nd sidewall 11b of case of transmission 11.Therefore, when driving shifting actuator 19, the 1st crankshaft component 17 and the 2nd crankshaft component 18 rotate in the same direction identical angle via driving pinion 20 and the 1st, the 2nd driven pinion 17g, 18g.
1st crankshaft component 17 and the 2nd crankshaft component 18 are supported with 6 eccentric discs 21.Further, when needs difference 6 eccentric discs 21 are described, there is such situation: from the eccentric disc of motor E side, be called eccentric disc 21A ~ 21F successively towards the eccentric disc of shifting actuator 19 side.
5 intermediate journal support units 22 are configured with between 6 eccentric disc 21A ~ 21F.Intermediate journal support unit 22 is the discoideus parts being formed with the 1st circular axle journal bearing hole 22a and the 2nd circular axle journal bearing hole 22b, and the 1st, the 2nd collar 17b ~ 17f of the 1st, the 2nd crankshaft component 17,18,18b ~ 18f are rotatably embedded in the 1st, the 2nd axle journal bearing hole 22a, 22b respectively.In order to can relative to the 1st, the 2nd crankshaft component 17,18 assembles, intermediate journal support unit 22 is divided into two-part by the parting plane by the 1st axle journal bearing hole 22a and the 2nd axle journal bearing hole 22b, and integral by not shown bolton.The diameter of intermediate journal support unit 22 is roughly consistent with the diameter of eccentric disc 21A ~ 21F.
As shown in Figure 4, eccentric disc 21 is the discoideus parts with center O1, has respectively and is formed as contacting with each other at intermediate point M from the 1st, the 2nd pin portion embedding hole 21a, 21b of the circle of the center O2 of center O1 bias and center O3.The shape of 6 eccentric disc 21A ~ 21F has 2 kinds, about 2 eccentric discs 21A, 21D, connects the center O2 of the 1st, the 2nd pin portion embedding hole 21a, 21b and overlaps mutually with the straight line of the straight line of center O3 with the center O1 and intermediate point M that are connected eccentric disc 21A, 21D.On the other hand, about remaining 4 eccentric discs 21B, 21C, 21E, 21F, foregoing 2 straight lines are mutually with the angular cross of 60 ゜.
As shown in Figure 5, 1st, 2nd crankshaft component 17, 18 the 1st, 2nd pin portion 17h, 18h is embedded in the 1st of eccentric disc 21A the respectively, 2nd pin portion embedding hole 21a, 21b, 1st, 2nd crankshaft component 17, 18 the 1st, 2nd pin portion 17i, 18i is embedded in the 1st of eccentric disc 21B the respectively, 2nd pin portion embedding hole 21a, 21b, 1st, 2nd crankshaft component 17, 18 the 1st, 2nd pin portion 17j, 18j is embedded in the 1st of eccentric disc 21C the respectively, 2nd pin portion embedding hole 21a, 21b, 1st, 2nd crankshaft component 17, 18 the 1st, 2nd pin portion 17k, 18k is embedded in the 1st of eccentric disc 21D the respectively, 2nd pin portion embedding hole 21a, 21b, 1st, 2nd crankshaft component 17, 18 the 1st, 2nd pin portion 17l, 18l is embedded in the 1st of eccentric disc 21E the respectively, 2nd pin portion embedding hole 21a, 21b, 1st, 2nd crankshaft component 17, 18 the 1st, 2nd pin portion 17m, 18m is embedded in the 1st of eccentric disc 21F the respectively, 2nd pin portion embedding hole 21a, 21b.
As shown in Figure 6, when being loaded on 6 eccentric disc 21A ~ 21F on the 1st crankshaft component 17 and the 2nd crankshaft component 18 along input axis L1 direction observation group, the center O1 of these eccentric discs 21A ~ 21F is eccentric with fixing offset ε relative to input axis L1, further, its eccentric direction staggers mutually 60 °.
In FIG, when making the output shaft of shifting actuator 19 rotate with the speed that the bent axle 16 with motor E is identical, the driving pinion 20 connected with shifting actuator 19 rotates with identical speed with the gear ring 13a be arranged on the 2nd end axis neck support part 13, therefore, the the 1st, the 2nd driven pinion 17g, 18g non rotating simultaneously engaged with driving pinion 20 and gear ring 13a, therefore, the 1st crankshaft component 17 and the 2nd crankshaft component 18 rotate integratedly with the 1st end axis neck support part the 12 and the 2nd end axis neck support part 13 under the state keeping the phase place of fixing.In this case, 1st pin portion 17h ~ 17m of the 1st crankshaft component 17 and the 2nd pin portion 18h ~ 18m of the 2nd crankshaft component 18 is maintained fixing relative to the position relationship of input axis L1, therefore, 6 eccentric disc 21A ~ 21F rotate integratedly with the 1st crankshaft component 17 and the 2nd crankshaft component 18 under the state that maintain fixing offset ε.
When making the output shaft of shifting actuator 19 rotate with the speed that the bent axle 16 from motor E is different, with driving pinion that shifting actuator 19 connects 20 be arranged on that gear ring 13a on the 2nd end axis neck support part 13 is relative to be rotated, therefore, the the 1st, the 2nd driven pinion 17g, the 18g simultaneously engaged with driving pinion 20 and gear ring 13a rotates in the same direction the angle of regulation, therefore, the 1st crankshaft component 17 rotates to same direction is relative with the 2nd end axis neck support part 13 relative to the 1st end axis neck support part 12 with the 2nd crankshaft component 18.
Fig. 7 shows the phase place and the 1st of the 1st, the 2nd pin portion 17h, 18h of the 1st, the 2nd crankshaft component 17,18, the 2nd pin portion embedding hole 21a, 21b is supported in relation between the offset ε of the eccentric disc 21A on the 1st, the 2nd pin portion 17h, 18h.
As shown in (A) of Fig. 7, when the rotation angle θ of the 1st, the 2nd crankshaft component 17,18 is θ=0 °, 1st, the 2nd pin portion 17h, 18h relative to the 1st, the 1st, the 2nd axis L3, L4 of the 2nd crankshaft component 17,18 be to Figure below bias, in this condition, eccentric disc 21A relative to the offset ε of input axis L1 be as minimum value zero.
As shown in (B) of Fig. 7, when the rotation angle θ of the 1st, the 2nd crankshaft component 17,18 is θ=45 °, 1st, the 2nd pin portion 17h, 18h relative to the 1st, the 1st, the 2nd axis L3, L4 of the 2nd crankshaft component 17,18 be to lower right bias in figure, in this condition, eccentric disc 21A becomes ε 1 relative to the offset ε of input axis L1.
As shown in (C) of Fig. 7, when the rotation angle θ of the 1st, the 2nd crankshaft component 17,18 is θ=90 °, 1st, the 2nd pin portion 17h, 18h relative to the 1st, the 1st, the 2nd axis L3, L4 of the 2nd crankshaft component 17,18 right side bias in figure, in this condition, eccentric disc 21A becomes the ε 2 larger than ε 1 relative to the offset ε of input axis L1.
As shown in (D) of Fig. 7, when the rotation angle θ of the 1st, the 2nd crankshaft component 17,18 is θ=135 °, 1st, the 2nd pin portion 17h, 18h relative to the 1st, the 1st, the 2nd axis L3, L4 of the 2nd crankshaft component 17,18 be to upper right bias in figure, in this condition, eccentric disc 21A becomes the ε 3 larger than ε 2 relative to the offset ε of input axis L1.
As shown in (E) of Fig. 7, when the rotation angle θ of the 1st, the 2nd crankshaft component 17,18 is θ=180 °, 1st, the 2nd pin portion 17h, 18h relative to the 1st, the 1st, the 2nd axis L3, L4 of the 2nd crankshaft component 17,18 top bias in figure, in this condition, eccentric disc 21A is ε 4 as maximum value relative to the offset ε of input axis L1.
As mentioned above, by making the output shaft of shifting actuator 19 rotate with the speed that the bent axle 16 from motor E is different, the offset ε of eccentric disc 21A can be made infinitely to change between zero as minimum value and the ε 4 as maximum value.The offset ε of remaining 5 eccentric disc 21B ~ 21F also maintains the size identical with the offset ε of above-mentioned eccentric disc 21A infinitely to be changed between zero as minimum value and the ε 4 as maximum value.
As depicted in figs. 1 and 2, output shaft 23 is configured on the output axis L2 parallel with inputting axis L1, and 6 swing members 25 are rotatably bearing on output shaft 23 via 6 overrunning clutchs 24.The large end 27a of connecting rod 27 is supported on the periphery of each eccentric disc 21 via needle bearing 26, the small end 27b of connecting rod 27 is connected with swing member 25 via pin 28.
Overrunning clutch 24 possesses: multiple roller 29, and they are configured between the inner piece 23a be made up of the outer circumferential face of the output shaft 23 and exterior part 25a be made up of the inner peripheral surface of swing member 25; With multiple engage spring 30, they are to the side force of these rollers 29 to circumferencial direction.
When eccentric disc 21 is relative to input axis L1 eccentric rotary, the connecting rod 27 that large end 27a is connected with eccentric disc 21 moves back and forth, and the swing member 25 be connected with the small end 27b of connecting rod 27 is around output shaft 23 reciprocally swinging.When swing member 25 swings to the counter clockwise direction of Fig. 2, between the roller 29 engaging-in inner piece 23a and exterior part 25a that engaged spring 30 exerts a force, overrunning clutch 24 is engaged, output shaft 23 rotates the angle of regulation.When swing member 25 swings to the clockwise direction of Fig. 2, the elastic force that roller 29 overcomes engage spring 30 is extruded by between inner piece 23a and exterior part 25a, and the joint of overrunning clutch 24 is removed, and the rotation of output shaft 23 stops.
As mentioned above, when connecting rod 27 to-and-fro motion, overrunning clutch 24 engages off and on and output shaft 23 is rotated off and on, but 6 connecting rods 27, with different phase alternations ground transmission of drive force, make output shaft 23 rotate continuously thus.
As shown in (A) of Fig. 8, when the offset ε of eccentric disc 21 is larger, the reciprocating stroke of connecting rod 27 becomes large, and therefore the angle of oscillation δ of swing member 25 becomes large, and the intermittent rotary angle of the output shaft 23 when eccentric disc 21 often rotates 1 circle becomes greatly.Therefore, the offset ε of eccentric disc 21 is larger, and input shaft rotating speed diminishes relative to the ratio of output shaft rotating speed and gear ratio.
As shown in (B) of Fig. 8, when the offset ε of eccentric disc 21 reduces, the reciprocating stroke of connecting rod 27 diminishes, and the angle of oscillation δ of swing member 25 diminishes, and eccentric disc 21 often rotates the 1 intermittent rotary angle of output shaft 23 when enclosing and diminishes.Therefore, along with the offset ε of eccentric disc 21 diminishes, gear ratio becomes large.As shown in (C) of Fig. 8, when the offset ε of eccentric disc 21 is zero, connecting rod 27 stops to-and-fro motion, and swing member 25 stops reciprocally swinging, and therefore output shaft 23 stops the rotation, and gear ratio becomes infinitely great.
As mentioned above, by making the offset ε of eccentric disc 21 change between maximum eccentricity amount and zero, the gear ratio of crank-type stepless speed variator T can be made infinitely to change between minimum OD state (overdrive) and infinitely-great GN state (neutral state).
As shown in Figure 9, the axial thickness W1 of eccentric disc 21 is set than the 1st, the axial thickness W2 of the 1st, the 2nd pin portion 17h ~ 17m of the 2nd crankshaft component 17,18,18h ~ 18m is large.The axial end of the axial end and eccentric disc 21 that are clipped in 5 intermediate journal support units 22 between 6 eccentric discs 21 abuts in the mode slid freely, and has small gap α between the axial end of the axial end and the 1st of these 5 intermediate journal support units 22, the 2nd pin portion 17h ~ 17m, 18h ~ 18m.In addition, the axial end of eccentric disc 21A, 21F that the axial end of the 1st end axis neck support part the 12 and the 2nd end axis neck support part 13 is also opposed with them abuts in the mode slid freely, and has small gap α between the axial end of the axial end and the 1st of the 1st end axis neck support part the 12 and the 2nd end axis neck support part 13, the 2nd pin portion 17h, 18h, 17m, 18m.
Next, based on Fig. 9, the effect of the 1st end axis neck support part the 12, the 2nd end axis neck support part 13 and intermediate journal support unit 22 is described.
As shown in Figure 2, in the crank-type stepless speed variator T of present embodiment, when connecting rod 27 moves to arrow A 1 direction and makes swing member 25 swing to arrow A 2 direction, namely when tension load acts on connecting rod 27, overrunning clutch 24 engages and transmission of drive force.
In fig .9, when tension load acts on 6 connecting rods 27, be connected with connecting rod 27 via eccentric disc 21A ~ 21F the 1st, the 2nd crankshaft component 17,18 is stretched towards output shaft 23 to Figure below for fulcrum with the 1st end axis neck support part the 12 and the 2nd end axis neck support part 13 at axial two ends, thus for bending to the arcuation shown in thick dot and dash line.Like this, when the 1st, 2nd crankshaft component 17, 18 bending time, 1st, 2nd pin portion 17h ~ 17m, 18h ~ 18m tilts, therefore, the 1st is made in order to make gear ratio change, 2nd crankshaft component 17, during 18 rotation, not only the 1st, 2nd pin portion 17h ~ 17m, the outer circumferential face of 18h ~ 18m and the 1st of each eccentric disc 21 the, 2nd pin portion embedding hole 21a, the frictional loss of the slide part of the inner peripheral surface of 21b increases, eccentric disc 21 also can by the 1st, 2nd pin portion 17h ~ 17m, 18h ~ 18m tractive and tilting, therefore, also may increase the frictional loss of the needle bearing 26 that the large end 27a of connecting rod 27 supports.
; according to the present embodiment; the 1st end axis neck support part the 12, the 2nd end axis neck support part 13 configured in the mode clipping eccentric disc 21 abuts in relative rotatable mode with the axial end of eccentric disc 21 with intermediate journal support unit 22; therefore; inhibit the flexure of the 1st, the 2nd crankshaft component 17,18 by the face pressure produced at abutting part, the increase of the frictional loss that the flexure because of the 1st, the 2nd crankshaft component 17,18 causes is suppressed to minimum limit.
Now, 1st end axis neck support part the 12 and the 2nd end axis neck support part 13 is via ball bearing 14, 15 are supported in case of transmission 11, therefore, stably the 1st can be supported by the 1st end axis neck support part the 12 and the 2nd end axis neck support part 13, 2nd crankshaft component 17, 18, and, 5 intermediate journal support units 22 are not supported in case of transmission 11 but are in state of suspension, therefore, there is no need for the bearing be supported on by intermediate journal support unit 22 on case of transmission 11, the reduction of weight and the further reduction of frictional loss can be realized.
In addition, owing to making the axial thickness W1 of eccentric disc 21 than the 1st, the axial thickness W2 of the 2nd pin portion 17h ~ 17m, 18h ~ 18m is large, and the axial end of the 1st, the 2nd pin portion 17h ~ 17m, 18h ~ 18m does not abut with the axial end of the 1st end axis neck support part the 12, the 2nd end axis neck support part 13 and intermediate journal support unit 22, therefore, when gear ratio changes, the area of abutting part can be suppressed for minimum limit, thus can frictional loss be reduced.
And, the abutting part that 1st end axis neck support part the 12, the 2nd end axis neck support part 13 and intermediate journal support unit 22 abut with eccentric disc 21 leaves significantly from the 1st axis L3 of the 1st, the 2nd crankshaft component 17,18 and the 2nd axis L4, therefore, it is possible to effectively play the effect preventing the 1st, the 2nd crankshaft component 17,18 from bending.
And then, because the external diameter of eccentric disc 21 is roughly consistent with the external diameter of the 1st end axis neck support part the 12, the 2nd end axis neck support part 13 and intermediate journal support unit 22, therefore, can prevent the 1st, the 2nd crankshaft component 17,18 from bending while this effect giving full play to, the external diameter of the 1st end axis neck support part the 12, the 2nd end axis neck support part 13 and intermediate journal support unit 22 is suppressed for minimum limit thus cuts down weight.
Above, embodiments of the present invention are illustrated, but the present invention can carry out various design alteration in the scope not departing from its main points.
Such as, in embodiments, 1st end axis neck support part the 12, the 2nd end axis neck support part 13 and intermediate journal support unit 22 only abut with the axial end of eccentric disc 21, but, them also can be made only to abut with the 1st, the 2nd pin portion 17h ~ 17m of the 1st, the 2nd crankshaft component 17,18, the axial end of 18h ~ 18m.
Like this, can the inclination of the 1st, the 2nd pin portion 17h ~ 17m, 18h ~ 18m be suppressed by the 1st end axis neck support part the 12, the 2nd end axis neck support part 13 and intermediate journal support unit 22 thus suppress the flexure of the 1st, the 2nd crankshaft component 17,18, and then, the inclination of eccentric disc 21 can be suppressed.
Certainly, also can make the axial end and the 1st of the 1st end axis neck support part the 12, the 2nd end axis neck support part 13 and intermediate journal support unit 22 and eccentric disc 21, the 1st, the 2nd pin portion 17h ~ 17m of the 2nd crankshaft component 17,18, the axial end both sides of 18h ~ 18m abut.
In addition, in embodiments, connecting rod 27, but also can by compressive load transmission of drive force by tension load transmission of drive force.
In addition, driving source of the present invention is not limited to the motor E of mode of execution, also can be the driving source of such other kind of electric motor.
In addition, in embodiments, crank-type stepless speed variator T possesses 6 eccentric disc 21A ~ 21F, but the quantity of eccentric disc is not limited to 6.
Claims (5)
1. a stepless speed variator, it possesses: input shaft (12), and it is configured in input axis (L1), and is transfused to the driving force of driving source (E); Output shaft (23), it is configured in and exports on axis (L2), and the driving force of described input shaft (12) is passed to this output shaft after by speed change; 1st crankshaft component (17), itself and described input shaft (12) rotate integratedly; 2nd crankshaft component (18), itself and described input shaft (12) rotate integratedly; Multiple eccentric disc (21), they are supported in described 1st crankshaft component (17) and the 2nd crankshaft component (18), and described multiple eccentric disc (21) is variable relative to the offset (ε) of described input axis (L1); Multiple swing member (25), they are rotatably supported on the periphery of described output shaft (23); Multiple overrunning clutch (24), they are configured between described output shaft (23) and described multiple swing member (25); And multiple connecting rod (27), they connect described multiple eccentric disc (21) and described multiple swing member (25),
Described 1st crankshaft component (17) possesses: multiple 1st collar (17a ~ 17f), and they are configured on the 1st axis (L3) eccentric relative to described input axis (L1); With multiple 1st pin portion (17h ~ 17m), they are eccentric relative to described multiple 1st collar (17a ~ 17f),
Described 2nd crankshaft component (18) possesses: multiple 2nd collar (18a ~ 18f), and they are configured on the 2nd axis (L4) eccentric relative to described input axis (L1); With multiple 2nd pin portion (18h ~ 18m), they are eccentric relative to described multiple 2nd collar (18a ~ 18f),
Described multiple eccentric disc (21) possesses: the 1st pin portion embedding hole (21a), and it is rotatably fitted together to for described 1st pin portion (17h ~ 17m); With the 2nd pin portion embedding hole (21b), it is rotatably fitted together to for described 2nd pin portion (18h ~ 18m),
By making, described 1st crankshaft component (17) is relative relative to described input shaft (12) with the 2nd crankshaft component (18) to be rotated, change between the value making the offset (ε) of described multiple eccentric disc (21) specify at zero-sum thus, the feature of described stepless speed variator is
Described stepless speed variator possesses multiple axle journal support unit (12, 13, 22), described multiple axle journal support unit (12, 13, 22) described 1st collar (17a ~ 17f) of described 1st crankshaft component (17) and described 2nd collar (18a ~ 18f) of described 2nd crankshaft component (18) is supported, the axial end of described multiple eccentric disc (21) and described multiple 1st pin portion (17h ~ 17m), at least one party in the axial end in the 2nd pin portion (18h ~ 18m) and described multiple axle journal support unit (12, 13, 22) abut in relatively rotatable mode.
2. stepless speed variator according to claim 1, is characterized in that,
Described multiple axle journal support unit (12, 13, 22) by the 1st end axis neck support part (12) at axial two end part and the 2nd end axis neck support part (13) that are positioned at described input axis (L1), form with the intermediate journal support unit (22) of the axial intermediate portion being positioned at described input axis (L1), described 1st end axis neck support part (12) and the 2nd end axis neck support part (13) are supported in case of transmission (11), described intermediate journal support unit (22) is not supported in described case of transmission (11).
3., according to stepless speed variator according to claim 1 or claim 2, it is characterized in that,
The axial thickness (W1) of described multiple eccentric disc (21) is larger than the axial thickness (W2) in described 1st pin portion (17h ~ 17m) and the 2nd pin portion (18h ~ 18m), and described multiple axle journal support unit (12,13,22) abuts in relative rotatable mode with the axial end of described multiple eccentric disc (21).
4., according to stepless speed variator according to claim 1 or claim 2, it is characterized in that,
The external diameter of described multiple eccentric disc (21) is roughly consistent with the external diameter of described multiple axle journal support unit (12,13,22).
5. stepless speed variator according to claim 3, is characterized in that,
The external diameter of described multiple eccentric disc (21) is roughly consistent with the external diameter of described multiple axle journal support unit (12,13,22).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-162098 | 2014-08-08 | ||
| JP2014162098A JP6157425B2 (en) | 2014-08-08 | 2014-08-08 | Continuously variable transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105370829A true CN105370829A (en) | 2016-03-02 |
Family
ID=55373306
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510441661.2A Pending CN105370829A (en) | 2014-08-08 | 2015-07-24 | Stepless speed changer |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6157425B2 (en) |
| CN (1) | CN105370829A (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5543318Y2 (en) * | 1975-12-25 | 1980-10-11 | ||
| CN2416279Y (en) * | 2000-04-12 | 2001-01-24 | 万永立 | Mechanical stepless speed changer |
| GB2434847A (en) * | 2006-01-30 | 2007-08-08 | Clifford Orval Daniels | Self-regulating continuously variable transmission |
| RU2426021C1 (en) * | 2010-03-25 | 2011-08-10 | Валерий Михайлович Боровских | Device for torque transfer from driving shaft to driven one |
| JP5142234B2 (en) * | 2011-01-06 | 2013-02-13 | 本田技研工業株式会社 | Continuously variable transmission mechanism and automobile drive system |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1945702A (en) * | 1930-02-10 | 1934-02-06 | Pitter Trnst | Variable speed transmission |
| CN103534516B (en) * | 2011-06-30 | 2016-03-09 | 本田技研工业株式会社 | Four joint chain-type stepless speed variators |
| JP5822594B2 (en) * | 2011-08-08 | 2015-11-24 | 本田技研工業株式会社 | Four-bar linkage type continuously variable transmission |
-
2014
- 2014-08-08 JP JP2014162098A patent/JP6157425B2/en not_active Expired - Fee Related
-
2015
- 2015-07-24 CN CN201510441661.2A patent/CN105370829A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5543318Y2 (en) * | 1975-12-25 | 1980-10-11 | ||
| CN2416279Y (en) * | 2000-04-12 | 2001-01-24 | 万永立 | Mechanical stepless speed changer |
| GB2434847A (en) * | 2006-01-30 | 2007-08-08 | Clifford Orval Daniels | Self-regulating continuously variable transmission |
| RU2426021C1 (en) * | 2010-03-25 | 2011-08-10 | Валерий Михайлович Боровских | Device for torque transfer from driving shaft to driven one |
| JP5142234B2 (en) * | 2011-01-06 | 2013-02-13 | 本田技研工業株式会社 | Continuously variable transmission mechanism and automobile drive system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2016038035A (en) | 2016-03-22 |
| JP6157425B2 (en) | 2017-07-05 |
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