CN104565256A - Stepless transmission - Google Patents

Stepless transmission Download PDF

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Publication number
CN104565256A
CN104565256A CN201410577986.9A CN201410577986A CN104565256A CN 104565256 A CN104565256 A CN 104565256A CN 201410577986 A CN201410577986 A CN 201410577986A CN 104565256 A CN104565256 A CN 104565256A
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CN
China
Prior art keywords
bearing
transmission
case
output shaft
input shaft
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Granted
Application number
CN201410577986.9A
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Chinese (zh)
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CN104565256B (en
Inventor
西村优史
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Honda Motor Co Ltd
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Honda Motor Co Ltd
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Publication of CN104565256A publication Critical patent/CN104565256A/en
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Publication of CN104565256B publication Critical patent/CN104565256B/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
    • F16H29/02—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts
    • F16H29/04—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts in which the transmission ratio is changed by adjustment of a crank, an eccentric, a wobble-plate, or a cam, on one of the shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/0006—Vibration-damping or noise reducing means specially adapted for gearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
    • B60K6/54—Transmission for changing ratio
    • B60K6/543—Transmission for changing ratio the transmission being a continuously variable transmission
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/02—Shafts; Axles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/12—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types
    • F16H37/124—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types for interconverting rotary motion and reciprocating motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings

Abstract

The invention provides a stepless transmission, which can inhibit the generation of vibration and noise. No matter the temperature state, the change in the internal gap of a bearing is very small. The bearing (22,24) of a stepless transmission (1A) is inserted into a gearbox shell (21) in a way that under any temperature state, not a gap will generated between the bearing (22,24) and the gearbox shell (21). The contact part between the external ring (22a, 24a)/internal ring (22b, 24b) and a rolling body (22c, 24c) is inclined relative to the central axis (P1) of the bearing, so that the intersection point of the force line from the external ring (22a, 24a)/internal ring (22b, 24b) to the rolling body (22c, 24c) and the bearing central axis (P1) is closer to the external surface of the gearbox shell (21) than the center of the bearing (22, 24).

Description

Stepless speed variator
Technical field
The present invention relates to the stepless speed variator of the four joint linkage mechanism types using crankrocker mechanism.
Background technique
In the past, the stepless speed variator of known four joint linkage mechanism types like this, it possesses: the input shaft being passed the hollow of the driving force from driving sources such as motors; With the output shaft that configures of the rotating center axis being parallel of input shaft ground; With multiple crankrocker mechanism (for example, referring to patent documentation 1).
In the stepless speed variator described in patent documentation 1, crankrocker mechanism is made up of following part: turning radius controlling mechanism, and it is arranged on the rotating center axis of input shaft; Swing link, it is supported on output shaft by rotatably axle; And connecting rod, one end thereof is rotatably outer is embedded in turning radius controlling mechanism, and its another end is linked to the swing end swinging link.
Turning radius controlling mechanism is made up of following part: discoid cam part, and it rotates integratedly with input shaft under the state relative to input shaft bias; Rotary part, it is rotatable under the state relative to this cam part bias, and is rotatably embedded with connecting rod outward thereon; Pinion shaft, it possesses multiple small gear vertically; And secondary driving source, it makes pinion shaft rotate.
Further, except the structure shown in patent documentation 1, turning radius controlling mechanism can also be made up of following part: discoid rotary part, and it has from center bias and runs through the penetration hole of setting; Internal-gear, it is installed in the inner peripheral surface of the penetration hole of rotary part; 1st small gear, it is fixed in input shaft, and engages with internal-gear; Planet carrier, it is passed the driving force of self-regulation driving source; And 2 the 2nd small gears, they are supported to by planet carrier shaft respectively can freely rotation and revolution, and they engage with internal-gear respectively.
The overrunning clutch stoping mechanism as single direction rotation is provided with between swing link and output shaft, when swing link for centered by output shaft to a sideway swivel time, described overrunning clutch swing fixing relative to output shaft link, when swinging link for rotating to opposite side centered by output shaft, described overrunning clutch makes swing link dally relative to output shaft.
Be formed with penetration hole in cam part, this penetration hole runs through along the rotating center axis direction of input shaft, and runs through the position of the center bias be arranged on relative to cam part.In addition, in cam part, in the region of the rotating center axis the clipping input shaft side contrary with the center of cam part, be formed with the cut hole that the outer circumferential face of cam part is communicated with the inner peripheral surface of penetration hole.Further, adjacent cam part is fixed each other by bolt and forms cam part union body.
Cam part union body axially one end and input part links, and constitutes camshaft (input shaft) by cam part union body and input part.Further, for camshaft, except the structure shown in patent documentation 1, cam part or cam part union body can also be configured to be installed on the outer surface of the shaft-like input part of hollow by spline combination etc.
Cam part union body becomes hollow due to the penetration hole connection of each cam part, is inserted with pinion shaft in the inside of this cam part union body.Further, the pinion shaft inserted in cam part union body exposes from the cut hole of each cam part.
The reception hole of storage camshaft is provided with at rotary part.Internal tooth is formed at the inner peripheral surface of this reception hole.The pinion shaft that this internal tooth exposes with the otch (penetration hole) from each cam part engages.
When camshaft is identical with the rotating speed of pinion shaft, rotary part rotatable under the state relative to cam part bias does not rotate relatively relative to cam part, and therefore, the radius of the center of rotary part, the i.e. rotary motion of input side fulcrum is maintained.On the other hand, when camshaft is different from the rotating speed of pinion shaft, rotary part rotates relatively relative to cam part, and the radius of the rotary motion of input side fulcrum is changed, and gear ratio changes.
In this stepless speed variator, when making rotary part rotate together with cam part by making camshaft rotate, an end fitted in the connecting rod on rotary part is rotated, and the swing link linked with another end of connecting rod swings.Further, be supported on output shaft owing to swinging link through overrunning clutch axle, therefore, only to during a sideway swivel, rotary driving force (moment of torsion) be passed to output shaft at swing link.
In addition, it is different that cam part is configured to phase place, forms a circle in the circumference of the rotating center axis of input shaft with multiple cam part.Therefore, by being embedded in the connecting rod of the rotary part arranged in each cam part outward, each link that swings transfers a torque to output shaft successively, thus output shaft can be made to rotate swimmingly.
Further, input shaft and output shaft, via the bearing installed on the case of transmission of storage crankrocker mechanism and overrunning clutch, are supported to freely to rotate.
Patent documentation 1: Japanese Unexamined Patent Application Publication 2005-502543 publication
In the stepless speed variator possessing such crankrocker mechanism, the direction putting on the load of input shaft or output shaft significantly changes during axle rotates a circle.Therefore, in order to the impact suppressing this variation to cause, input shaft or output shaft are supported to rotatable bearing and are pressed in the mounting hole that case of transmission is formed, thus be firmly fixed at case of transmission.
, in general, for bearing, in order to ensure durability, main use iron and steel etc. are as material, and for case of transmission, in order to weight reduction, main aluminium or the resin etc. of using is as material.
Therefore, when stepless speed variator makes the state of temperature of case of transmission change due to heat from traveling driving source etc., due to the difference of the rates of thermal expansion of the material of bearing and case of transmission, therefore gap can be formed between case of transmission and bearing, thus case of transmission may be caused to wear and tear, bearing's looseness, produces vibration or noise.
In order to prevent such loosening, even if the mode so that the gap caused by the difference of rates of thermal expansion also can not be produced at high operating temperatures between case of transmission and bearing can be considered, that is, be pressed in the mode how all becoming interference fit regardless of state of temperature.
; when carrying out such press-in; according to state of temperature; the internal void of bearing may change; namely there is following worry like this: the gap between outer ring and inner ring becomes large and produces vibration or noise from the inside of bearing; or contrary, the gap smaller between outer ring and inner ring and hinder the action of the rolling element of bearing.
Summary of the invention
The present invention completes in view of above problem, and its object is to provides a kind of stepless speed variator, can suppress to vibrate or the generation of noise, and no matter state of temperature how, and the change of the internal void of bearing is all very little.
In order to realize above-mentioned problem, stepless speed variator of the present invention possesses: input shaft, and input shaft is passed the driving force of traveling driving source, output shaft, output shaft is configured to the rotating center axis being parallel with input shaft, crankrocker mechanism, crankrocker mechanism has turning radius controlling mechanism and swings link, turning radius controlling mechanism has the rotary part that can rotate centered by the rotating center axis of input shaft, and freely can regulate the turning radius of this rotary part, swing link and be supported on output shaft by axle, the rotary motion of input shaft is converted to the oscillating motion swinging link by crankrocker mechanism, single direction rotation stops mechanism, when swing link is for during to a sideway swivel, single direction rotation stops mechanism to be fixed relative to output shaft by swing link, and when swinging link for rotating to opposite side, single direction rotation stops mechanism that swing link is dallied relative to output shaft, case of transmission, case of transmission has an end wall of the end side being positioned at input shaft and output shaft and is positioned at the other end wall portion of another side of input shaft and output shaft, and case of transmission storage crankrocker mechanism and single direction rotation stop mechanism, and multiple bearing, multiple bearing is installed in an end wall and the other end wall portion of case of transmission, by outer ring, inner ring, and the multiple rolling elements be configured between this outer ring and this inner ring are formed, the end side of input shaft or output shaft or the other end side bearing are become can freely rotate, the feature of stepless speed variator is, at least 1 bearing in multiple bearing and case of transmission are installed into by press-in: no matter the state of temperature of this case of transmission how, all can not produce gap between this bearing and this case of transmission, the part contacted with rolling element of the internal surface of the outer ring of bearing or the outer surface of inner ring tilts relative to the bearing central axis of this bearing, the point that the bearing central axis of the line of action and this bearing being passed to the power of rolling element from the internal surface of the outer ring of this bearing or the outer surface of inner ring is intersected in the bearing central axis direction of this bearing than the central authorities of this bearing near the outer surface side of case of transmission.
Like this, in stepless speed variator of the present invention, by press-in, bearing and case of transmission are mounted to: no matter the state of temperature of case of transmission how, it is no matter such as the state of the condition of high temperature or the degree being heated to the state of not reaching a high temperature, all can not produce the gap caused because of the difference of rates of thermal expansion between case of transmission and bearing, namely no matter how state of temperature all becomes interference fit.
Therefore, even if stepless speed variator becomes the condition of high temperature due to heat from traveling driving source etc., gap can not also be produced between case of transmission and bearing, therefore, there is not following such situation: case of transmission weares and teares, bearing's looseness, thus produce vibration or noise.
In addition, such as, even if when being pressed in case of transmission by bearing in the mode also becoming interference fit at high operating temperatures, when case of transmission becomes the condition of high temperature and expands, the expansion direction of outer ring due to its recuperability to case of transmission of bearing is expanding.That is, to follow the mode of the expansion direction of case of transmission, heart axial direction and the side vertical with bearing central axis direction move up the internal surface of outer ring within the bearing.
Consequently, when using wrapping angle to be the deep groove ball bearing of 0 degree, there is such worry: the internal void of bearing, the gap namely between outer ring and inner ring significantly change, produce vibration or noise from the inside of bearing, the action of the rolling element of bearing is hindered.Further, wrapping angle refers to, is passed to from the internal surface of the outer ring of bearing or the outer surface of inner ring the angle that the line of action of the power of rolling element and the line vertical with the bearing central axis of this bearing form.
Therefore, in stepless speed variator of the present invention, the part contacted with rolling element of the internal surface of the outer ring of bearing or the outer surface of inner ring is tilted relative to the bearing central axis of this bearing, the point that the bearing central axis of the line of action and this bearing being passed to the power of rolling element from the internal surface of the outer ring of this bearing or the outer surface of inner ring is intersected in the bearing central axis direction of this bearing than the central authorities of this bearing near the outer surface side of case of transmission.That is, the wrapping angle of bearing is set as the value more than 0 degree.
In other words, about the bearing of stepless speed variator of the present invention, compared with the deep groove ball bearing being 0 degree with wrapping angle, the expansion direction (tilting relative to the central axis of bearing and the direction intersected with this central axis in the inner surface side of case of transmission) of the line of action being passed to the power of rolling element and the case of transmission at the region place that is provided with this bearing is with subvertical angular cross.
Further in other words, about the bearing of stepless speed variator of the present invention, compared with deep groove ball bearing, the shape of the part contacted with rolling element of the internal surface of outer ring or the outer surface of inner ring is relative to being provided with the expansion direction of case of transmission at region place of this bearing close to parallel.
Therefore, when becoming the condition of high temperature, case of transmission expands due to this heat, and the pressure acting on bearing from case of transmission reduces, and the outer ring of bearing is expanding due to recuperability, move relative to inner ring simultaneously, nonetheless, but due to its movement direction be connect subparallel direction with the inclination of the internal surface of outer ring or the outer surface of inner ring, therefore, compared with deep groove ball bearing, the bearing of stepless speed variator of the present invention can reduce the change of internal void.
In addition, in stepless speed variator of the present invention, preferably, traveling driving source is motor, when at one end wall portion is fixed in traveling driving source, the wrapping angle that the bearing of axle supporting is carried out in another side of the end side of input shaft being carried out to this input shaft of wrapping angle comparison of the bearing of axle supporting is large.
Traveling driving source is motor, and when at one end wall portion is fixed in this motor, expand than the other end wall portion side significantly due to the heat of motor in the end wall side be fixed on motor of case of transmission.
Therefore, as long as set by the wrapping angle of the bearing being pressed into the end wall side that this significantly expands larger than the wrapping angle of bearing of the other end wall portion being pressed into the side contrary with an end wall, the change of internal void can just be reduced further.
In addition, preferably, in stepless speed variator of the present invention, the wrapping angle of at least one bearing in multiple bearing meets following condition expression.
Wherein, be wrapping angle, D is the diameter of the surface of contact of bearing and case of transmission, and L is the distance from an end wall to the other end wall portion.
At high operating temperatures, case of transmission, swell increment on the central axis direction of bearing changes according to from an end wall to the distance L of the other end wall portion.In addition, the swell increment in the radial direction of bearing is according to the diameter D of the surface of contact of this bearing and case of transmission, the internal diameter of opening portion be namely pressed into for bearing or be pressed into the external diameter of the parts in bearing and change.
Therefore, as long as based on the wrapping angle carrying out regulation bearing from an end wall to the distance L of the other end wall portion and diameter D in the mode meeting above-mentioned condition expression just can reduce the change of internal void further.
In addition, stepless speed variator of the present invention also can be configured to, and bearing is pressed in case of transmission, and input shaft or output shaft are pressed in bearing.
If formed like this, then easily bearing is installed on case of transmission, therefore, it is possible to boost productivity.
In addition, stepless speed variator of the present invention can be configured to, and input shaft or output shaft have: extension, and it extends radially out to this input shaft or output shaft; With the 1st lip part, it extends from the peripheral end portion of extension along the central axis direction of bearing, and case of transmission has: opening portion, and it runs through insertion for input shaft or output shaft; With the 2nd lip part, it extends from the peripheral portion of opening portion along the bearing central axis direction of bearing, and bearing is pressed in the 1st lip part, and the 2nd lip part of case of transmission is pressed in bearing.
If formed like this, at high operating temperatures, the 2nd lip part of case of transmission expands in the mode making bearing expand from inner side, i.e. heart axial direction and the side vertical with bearing central axis direction move up within the bearing for the inner ring of bearing.
, identical with bearing being pressed into situation about being pressed in bearing in case of transmission and by input shaft or output shaft, even if become the condition of high temperature, internal void is also difficult to significantly change.
In addition, if formed like this, then at high operating temperatures, from a part, i.e. the 2nd lip part of the case of transmission that the material higher than bearing with rates of thermal expansion is formed, the inner ring of bearing is applied with and makes it expand such power.
Therefore, and the outer ring of bearing is pressed into compared with the situation in case of transmission, is not easy to produce gap between bearing and case of transmission, and then vibration or noise can be made to be difficult to produce.
Accompanying drawing explanation
Fig. 1 is the partial sectional view of the 1st mode of execution that stepless speed variator of the present invention is shown.
Fig. 2 is the side view from axially illustrating the crankrocker mechanism of the stepless speed variator of Fig. 1.
Fig. 3 is the explanatory drawing of the change of the turning radius of the input side fulcrum of the crankrocker mechanism of the stepless speed variator that Fig. 1 is shown, it is maximum situation that the A of Fig. 3 shows turning radius, the B of Fig. 3 show turning radius be in situation, it is little situation that the C of Fig. 3 shows turning radius, and the D of Fig. 3 shows the situation that turning radius is " 0 ".
Fig. 4 is the explanatory drawing of the relation between the change of the turning radius of the input side fulcrum of the crankrocker mechanism of the stepless speed variator that Fig. 1 is shown and the hunting range of outlet side fulcrum, it is maximum situation that the A of Fig. 4 shows hunting range, the B of Fig. 4 show hunting range be in situation, it is little situation that the C of Fig. 4 shows hunting range, and the D of Fig. 4 shows the situation that hunting range is " 0 ".
Fig. 5 is the sectional view of the axial structure of input of the stepless speed variator that Fig. 1 is shown.
Fig. 6 is the sectional view of the axial structure of output of the stepless speed variator that Fig. 1 is shown.
Fig. 7 is the partial sectional view of the 2nd mode of execution that stepless speed variator of the present invention is shown.
Fig. 8 is the sectional view of the axial structure of input of the stepless speed variator that Fig. 7 is shown.
Fig. 9 is the sectional view of the axial structure of output of the stepless speed variator that Fig. 7 is shown.
Label declaration
1A, 1B: stepless speed variator; 2: input part; 3: output shaft; 3a, 3c: extension; 3b, 3d: lip part (the 1st lip part); 4: turning radius controlling mechanism; 5: cam disk (cam part); 5a: penetration hole; 5b: cut hole; 5c, 5e: extension; 5d, 5f: lip part (the 1st lip part); 6: rotating disc (rotary part); 6a: reception hole; 6b: internal tooth; 7: pinion shaft; 7a: small gear; 7b: pinion bearing; 8: differential attachment; 14a: running shaft; 9: sun gear; 10: the 1 gear rings; 11: the 2 gear rings; 12: band ladder small gear; 12a: large-diameter portion; 12b: minor diameter part; 13: planet carrier; 14: actuator (adjustment driving source (secondary driving source)); 15: connecting rod; 15a: input side annulus; 15b: outlet side annulus; 16: connecting rod bearing; 17: overrunning clutch (single direction rotation stops mechanism); 18: swing link; 18a: swing end; 18b: tab; 18c: patchhole; 19: connection pin; 20: crankrocker mechanism; 21: case of transmission; 21a: one end wall; 21b: the other end wall portion; 21c: surrounding wall portion; 21d, 21e, 21f, 21g: opening portion; 22,23,24,25: bearing (bearing); 22a, 23a, 24a, 25a: outer ring; 22b, 23b, 24b, 25b: inner ring; 22c, 23c, 24c, 25c: ball (rolling element); 26: case of transmission; 26a: one end wall; 26b: the other end wall portion; 26c: surrounding wall portion; 26d, 26e, 26f, 26g: opening portion; 26h, 26i, 26j, 26k: lip part (the 2nd lip part); 27,28,29,30: bearing; 27a, 28a, 29a, 30a: outer ring; 27b, 28b, 29b, 30b: inner ring; 27c, 28c, 29c, 30c: ball (rolling element); 50: run through patchhole; ENG: motor (traveling driving source (main driving source)); H: gear ratio; P1: the rotating center axis of input part 2; P2: the center of cam disk 5; P3: the center (input side fulcrum) of rotating disc 6; P4: the center (outlet side fulcrum) of connection pin 19; P5: the rotating center axis of output shaft 3; Distance between Rx:P1 and P2; Distance between Ry:P2 and P3; Distance (turning radius of the center P3 (input side fulcrum) of offset, rotating disc 6) between R1:P1 and P3; Distance (swinging the length of link 18) between R2:P4 and P5; θ 1: the phase place of turning radius controlling mechanism 4; θ 2: the hunting range swinging link 18; wrapping angle.
Embodiment
Below, be described with reference to the mode of execution of accompanying drawing to stepless speed variator of the present invention.The stepless speed variator of present embodiment is the stepless speed variator of four joint linkage mechanism types, and is gear ratio h (rotating speed of the rotating speed/output shaft of h=input shaft) can be made to be infinitely great (∞) thus make the rotating speed of output shaft be the one of speed changer, the i.e. so-called IVT (Infinity Variable Transmission: Limitless speed variator) of " 0 ".
[the 1st mode of execution]
With reference to Fig. 1 ~ Fig. 6, the stepless speed variator 1A of present embodiment is described.
First, see figures.1.and.2 and the structure of the stepless speed variator 1A of present embodiment is described.
As shown in Figure 1, the stepless speed variator 1A of present embodiment possesses: input part 2; The output shaft 3 configured abreast with the rotating center axis P1 of input part 2; And the turning radius controlling mechanism 4 of 6 be located on the rotating center axis P1 of input part 2.
Input part 2 rotates centered by rotating center axis P1 by being passed the driving force of autonomous driving source, i.e. motor ENG (traveling driving source).Further, as main driving source, except internal-combustion engine, motor etc. can also be used.
Rotating power to be passed to the driving wheel (omitting diagram) of vehicle by output shaft 3 via eliminating illustrated differential mechanism.Further, transmission shaft also can be set to replace differential mechanism.
Turning radius controlling mechanism 4 has: be located at the cam disk 5 (cam part) on the rotating center axis P1 of input part 2; The rotatably outer rotating disc 6 (rotary part) being embedded in cam disk 5.
Cam disk 5 is discoid, under the state of the rotating center axis P1 bias relative to input part 2, is 1 group arranges in the mode that can rotate integratedly with input part 2 with 2.Each group of cam disk 5 is set to and makes phase place offset one from another 60 °, and is configured to form a circle with the circumference of 6 groups of cam disks 5 around the rotating center axis P1 of input part 2.
Cam disk 5 is formed penetration hole 5a, and this penetration hole 5a runs through along the rotating center axis P1 direction of input part 2, and runs through the position of the center P2 bias be arranged on relative to cam disk 5.In addition, on cam disk 5, in the region of the rotating center axis P1 clipping input part 2 side contrary with the center P2 of cam disk 5, be formed with the cut hole 5b that the outer circumferential face of cam disk 5 is communicated with the inner peripheral surface of penetration hole 5a.
2 is that the cam disk 5 of 1 group is fixing each other by bolt (omit diagram).In addition, that the side in 2 cam disks 5 that are 1 group and adjacent turning radius controlling mechanism 4 have, other 2 is that the opposing party in the cam disk 5 of 1 group forms as one, and constitutes one-piece type cam part.In addition, the cam disk 5 be in closest to the position of motor ENG in cam disk 5 forms as one with input part 2.Like this, input part 2 and multiple cam disk 5 constitute input shaft.
Further, 2 is that the cam disk 5 of 1 group also can be fixed each other by other means, instead of bolt.In addition, one-piece type cam part can by one-body molded and formed, also can by being welded together by 2 cam disks 5 and realizing integration.In addition, as making to be in the method formed as one closest to cam disk 5 and the input part 2 of the position of motor ENG, can by one-body molded and formed, also can by cam disk 5 and input part 2 be welded together and realize integration.
As shown in Figure 2, the position of rotating disc 6 Shi Congqi center P3 bias is provided with the discoid of reception hole 6a, and it is arranged to rotate relative to the rotating center axis P1 of input part 2.Every 1 group of cam disk 5 rotatably embeds in this reception hole 6a.In addition, in the reception hole 6a of rotating disc 6, as shown in Figure 1, the position between 1 group of cam disk 5 is provided with internal tooth 6b.
In addition, the reception hole 6a of rotating disc 6 relative to cam disk 5 bias is: identical to the distance Ry of the center P3 of rotating disc 6 with the center P2 from cam disk 5 to the distance Rx of the center P2 (center of reception hole 6a) of cam disk 5 from the rotating center axis P1 of input part 2.
The input shaft be made up of with multiple cam disk 5 input part 2 possess be connected by the penetration hole 5a of cam disk 5 and form run through patchhole 50.Thus, input shaft becomes such hollow shaft shape: the one end open of the side contrary with motor ENG, and the other end is closed.
Pinion shaft 7 is with concentric with rotating center axis P1 and relative rotatable mode is configured at and runs through patchhole 50 with input shaft.
Pinion shaft 7 has small gear 7a in the position that the internal tooth 6b with rotating disc 6 is corresponding.In addition, pinion shaft 7 is provided with pinion bearing 7b, this pinion bearing 7b on the rotating center axis P1 direction of input part 2 between adjacent small gear 7a.Pinion shaft 7 supports input shaft via this pinion bearing 7b.
The axle portion of small gear 7a and pinion shaft 7 forms as one.Small gear 7a engages with the internal tooth 6b of rotating disc 6 via the cut hole 5b of cam disk 5.Further, small gear 7a also can with pinion shaft 7 split form, and combined by spline and link with pinion shaft 7.In the present embodiment, during simply referred to as small gear 7a, be defined as and comprise pinion shaft 7.
In addition, the differential attachment 8 that pinion shaft 7 is formed with by planetary gears etc. is connected.
As shown in Figure 1, differential attachment 8 is such as configured to planetary gears, and has: sun gear 9; 1st gear ring 10, it links with the input shaft be made up of input part 2 and multiple cam disk 5; 2nd gear ring 11, itself and pinion shaft 7 link; And planet carrier 13, band ladder small gear 12 axle is supported to by it can freely rotation and revolution, and described band ladder small gear 12 is made up of the large-diameter portion 12a engaged with sun gear 9 and the 1st gear ring 10 and the minor diameter part 12b that engages with the 2nd gear ring 11.
Sun gear 9 is passed the driving force from the secondary driving source of pinion shaft 7, i.e. actuator 14 (adjustment driving source).Therefore, the driving force of actuator 14 is also passed to small gear 7a via differential attachment 8.
When making the rotating speed of pinion shaft 7 identical with the rotating speed of input part 2, sun gear 9 and the 1st gear ring 10 rotate with same speed.Consequently, sun gear 9, the 1st gear ring 10, these 4 components of the 2nd gear ring 11 and planet carrier 13 become the lock state that can not relatively rotate, and the pinion shaft 7 linked with the 2nd gear ring 11 rotates with the speed identical with input part 2.
When the rotating speed of the rotating ratio input part 2 making pinion shaft 7 is slow, if set the rotating speed of sun gear 9 as Ns, if the rotating speed of the 1st gear ring 10 is NR1, if the velocity ratio of sun gear 9 and the 1st gear ring 10 (number of teeth of the number of teeth/sun gear 9 of the 1st gear ring 10) is j, then the rotating speed of planet carrier 13 is (jNR1+Ns)/(j+1).In addition, if set the velocity ratio of sun gear 9 and the 2nd gear ring 11 ((number of teeth of the number of teeth/sun gear 9 of the 2nd gear ring 11) × (being with the number of teeth of the number of teeth/minor diameter part 12b of the large-diameter portion 12a of ladder small gear 12)) as k, then the rotating speed of the 2nd gear ring 11 is { j (k+1) NR1+ (k-j) Ns}/{ k (j+1) }.
Namely, when existing poor between the rotating speed and the rotating speed of pinion shaft 7 of input part 2, by transmit via the internal tooth 6b of the rotating disc 6 engaged with the small gear 7a of pinion shaft 7, from the driving force of actuator 14, rotating disc 6 rotates at the periphery of cam disk 5 centered by the center P2 of cam disk 5.
In addition, as shown in Figure 2, rotating disc 6 relative to cam disk 5 bias is: identical to the distance Ry of the center P3 of rotating disc 6 with the center P2 from cam disk 5 from the distance Rx of rotating center axis P1 to the center P2 of cam disk 5 of input part 2.
Therefore, the rotating center axis P1 of the center P3 of rotating disc 6 and input part 2 can also be made to be located along the same line, thus to make distance (turning radius of turning radius controlling mechanism 4), i.e. offset R1 between the rotating center axis P1 of the input part 2 and center P3 of rotating disc 6 be " 0 ".
Connecting rod 15 is the outer periphery being embedded in rotating disc 6 rotatably, connecting rod 15 has the input side annulus 15a in large footpath (input part 2 side) end, has the outlet side annulus 15b less than the diameter of input side annulus 15a in another (output shaft 3) end.
The input side annulus 15a of connecting rod 15 is embedded in rotating disc 6 via connecting rod bearing 16 is rotatably outer, connecting rod bearing 16 by arrange by twos vertically, 2 be that the ball bearing of 1 group is formed.
On output shaft 3, be supported with 6 swing link 18 via overrunning clutch 17 (single direction rotation the stops mechanism) earth's axis corresponding to connecting rod 15.
Overrunning clutch 17 is arranged on and swings between link 18 and output shaft 3, when swinging link 18 for relatively rotating to side relative to output shaft 3 centered by the rotating center axis P5 of output shaft 3, overrunning clutch 17 will swing link 18 relative to output shaft 3 fixing (stationary state), when swinging link 18 for relatively rotating to opposite side, overrunning clutch 17 makes swing link 18 dally (idling conditions) relative to output shaft 3.
Swing link 18 and be formed as ring-type, be thereunder provided with the swing end 18a linked with the outlet side annulus 15b of connecting rod 15.Swing end 18a is provided with a pair tab 18b, and described a pair tab 18b is to give prominence to the mode that outlet side annulus 15b sandwiches vertically.A pair tab 18b runs through and is provided with the patchhole 18c corresponding with the internal diameter of outlet side annulus 15b.
By the connection pin 19 as swing axis is inserted in patchhole 18c and outlet side annulus 15b, thus connecting rod 15 and swing link 18 are linked up.
In the stepless speed variator 1A of present embodiment, turning radius controlling mechanism 4, swing link 18 and the connecting rod 15 with above-mentioned such structure is utilized to constitute crankrocker mechanism 20.
Crankrocker mechanism 20 and overrunning clutch 17 are incorporated in case of transmission 21.In the below of this case of transmission 21, lubricant oil forms oil sump.
Further, swing link 18 to be configured to make it swing end 18a and to be submerged in the oil sump of the lubricant oil of the below being stored in housing 21.
Therefore, when driving crank slotted link mechanism 20, lubricate with oil sump and swing end 18a, and, by the oscillating motion swinging link 18, the lubricant oil in oil sump is kicked up, can lubricate the miscellaneous part of stepless speed variator 1A.
Further, in the present embodiment, the structure possessing 6 crankrocker mechanism 20 is illustrated.
But the quantity of the crankrocker mechanism in stepless speed variator of the present invention is not limited to this quantity, such as, the crankrocker mechanism of less than 5 can be possessed, also can possess the crankrocker mechanism of more than 7.
In addition, in the present embodiment, be illustrated following structure: form input shaft by input part 2 and multiple cam disk 5, input shaft possesses and runs through patchhole 50, and this runs through patchhole 50 and is connected by the penetration hole 5a of cam disk 5 and forms.
; input shaft in stepless speed variator of the present invention is not limited to form like this; also can be such as: make input part be configured to have the hollow shaft-like running through patchhole in the mode of one end open; discoid cam disk is formed the penetration hole larger than the penetration hole of present embodiment; to enable input part run through insertion, and cam disk spline is made to be incorporated into the outer circumferential face of the input part being configured to hollow shaft-like.
In this case, by the input part that quill shaft is formed, with the cut hole of cam disk, cut hole is set accordingly.Further, the small gear inserted in input part engages with the internal tooth of rotating disc through the cut hole of input part and the cut hole of cam disk.
In addition, in the present embodiment, to using overrunning clutch 17 to stop the situation of mechanism to be illustrated as single direction rotation.
; single direction rotation in stepless speed variator of the present invention stops mechanism to be not limited to overrunning clutch; such as can adopt following such twin-direction clutch: this twin-direction clutch is configured to, can freely switch can by moment of torsion from swing link be passed to output shaft, swing link relative to the sense of rotation of output shaft.
Next, be described with reference to the crankrocker mechanism 20 of Fig. 1 ~ Fig. 4 to the stepless speed variator of present embodiment.
As shown in Figure 1, the stepless speed variator 1A of present embodiment possesses 6 crankrocker mechanism 20 (four joint linkage mechanisms) altogether.As shown in Figure 2, crankrocker mechanism 20 is made up of following part: connecting rod 15; Swing link 18; And turning radius controlling mechanism 4, it has rotating disc 6, and can freely regulate its turning radius.This crankrocker mechanism 20 is utilized the rotary motion of input shaft to be converted to the oscillating motion swinging link 18.
In this crankrocker mechanism 20, if the turning radius (offset R1) of the center P3 of the rotating disc 6 at turning radius controlling mechanism 4 (input side fulcrum) does not make input part 2 and pinion shaft 7 rotate with identical speed for " 0 ", then each connecting rod 15 is alternately repeatedly pressed to output shaft 3 thruster or is swung end 18a to input part 2 side tractive while change phase place between input part 2 and output shaft 3, thus swing link 18 is swung.
And, owing to being provided with overrunning clutch 17 between swing link 18 and output shaft 3, therefore, if swing link 18 to be swung by connecting rod 15 push-and-pull, then when swinging any one party of link 18 to press direction side or direction of draw side and rotating, swing link 18 be fixed relative to output shaft 3 and output shaft 3 is rotated, when swinging link 18 and rotating to the opposing party, swing link 18 and dally relative to output shaft 3.
In the stepless speed variator 1A of present embodiment, the turning radius controlling mechanism 4 of 6 crankrocker mechanism 20 changes phase place with being configured to every 60 degree, and therefore, output shaft 3 is rotated by 6 crankrocker mechanism 20 successively.
Fig. 3 is the figure that under the state that changes in the turning radius (offset R1) of the center P3 (input side fulcrum) of the rotating disc 6 making turning radius controlling mechanism 4, pinion shaft 7 and the position relationship of rotating disc 6 are shown.
The A of Fig. 3 shows and makes offset R1 be the state of " maximum ", and pinion shaft 7 and rotating disc 6 are positioned at the position making the rotating center axis P1 of input part 2, the center P2 of cam disk 5 and the center P3 of rotating disc 6 be arranged in straight line.In this case gear ratio h becomes minimum.
The B of Fig. 3 show make offset R1 be less than the A of Fig. 3 " in " state, the C of Fig. 3 shows and makes offset R1 be the state of " little " less than the B of Fig. 3.In the B of Fig. 3, gear ratio h be larger than the gear ratio h of the A of Fig. 3 " in ", in the C of Fig. 3, gear ratio h is " greatly " larger than the gear ratio h of the B of Fig. 3.
The D of Fig. 3 shows and makes offset R1 be the state of " 0 ", and the rotating center axis P1 of the input part 2 and center P3 of rotating disc 6 is positioned at concentric position.In this case gear ratio h becomes infinity (∞).
In addition, Fig. 4 is the figure of the relation between the hunting range θ 2 of the turning radius (offset R1) of the center P3 (input side fulcrum) of the rotating disc 6 that turning radius controlling mechanism 4 is shown and the oscillating motion of swing link 18.
The A of Fig. 4 shows the situation (gear ratio h is minimum situation) that offset R1 is " maximum " of the A of Fig. 3, the B of Fig. 4 show offset R1 be the B of Fig. 3 " in " situation (gear ratio h be in situation), the C of Fig. 4 shows the situation (gear ratio h is large situation) that offset R1 is " little " of the C of Fig. 3, and the D of Fig. 4 shows the situation (gear ratio h is the situation of infinitely great (∞)) that offset R1 is " 0 " of the D of Fig. 3.
At this, R2 is the length swinging link 18.More particularly, R2 is the distance from the rotating center axis P5 of output shaft 3 to connecting rod 15 with the swing tie point of end 18a and the center P4 of connection pin 19.In addition, θ 1 is the phase place of the rotating disc 6 of turning radius controlling mechanism 4.
Clearly known according to this Fig. 4, along with offset R1 diminishes, the hunting range θ 2 swinging link 18 narrows, and when offset R1 becomes " 0 ", swings link 18 and does not swing.
Next, with reference to Fig. 1, the case of transmission 21 of the stepless speed variator 1A of present embodiment is described in detail.
Case of transmission 21 is parts of aluminum.As shown in Figure 1, this case of transmission 21 possesses: an end wall 21a, and it is fixed in motor ENG; The other end wall portion 21b, it is configured to opposed with an end wall 21a; And surrounding wall portion 21c, it covers crankrocker mechanism 20 and overrunning clutch 17 at spaced intervals, and links the outer rim of an end wall 21a and the outer rim of the other end wall portion 21b.
At one end wall portion 21a is formed for the opening portion 21d of axle supporting input shaft and the opening portion 21e for axle supporting output shaft 3.
The other end wall portion 21b is formed for the opening portion 21f of axle supporting input shaft and the opening portion 21g for axle supporting output shaft 3.
Bearing 22,23,24,25 (bearing) is embedded with respectively in these opening portions 21d, 21e, 21f, 21g.Input shaft and output shaft 3 are rotatably freely supported on case of transmission 21 via these bearings 22,23,24,25.
Next, with reference to Fig. 5 and Fig. 6, the bearing 22,23,24,25 being installed on case of transmission 21 is described in detail.
As shown in Figure 5 and Figure 6, bearing 22,23,24,25 is the ball bearings (angular contact ball bearing) be made up of following part: outer ring 22a, 23a, 24a, 25a; Inner ring 22b, 23b, 24b, 25b; And be configured in this outer ring 22a, 23a, 24a, 25a and multiple ball 22c, 23c, 24c, 25c (rolling element) between inner ring 22b, 23b, 24b, 25b.
In addition, bearing 22,23,24,25 uses rates of thermal expansion than being formed as material, i.e. ferrous materials that the aluminium of the material of case of transmission 21 is little.
And input shaft is pressed into the inner side of inner ring 22b, 24b of the bearing 22,24 in bearing 22,23,24,25.In addition, output shaft 3 is pressed into the inner side of inner ring 23b, 25b of bearing 23,25.
And, outer ring 22a, 23a, 24a, 25a of bearing 22,23,24,25 are pressed in opening portion 21d, 21e, 21f, 21g of case of transmission 21 in the following manner: even if when stepless speed variator 1A becomes the condition of high temperature due to heat from motor ENG etc., also can not bearing 22,23, produce the gap caused because of the difference of rates of thermal expansion between 24,25 and case of transmission 21, namely no matter how state of temperature all becomes interference fit.
Therefore, in the stepless speed variator 1A of present embodiment, on opening portion 21d, 21e, 21f, 21g of case of transmission 21 and the surface of contact of bearing 22,23,24,25, fretting wear or creep wearing and tearing can not be there are.Consequently, in the stepless speed variator 1A of present embodiment, bearing 22,23,24,25 can not loosen, thus can not produce vibration or noise.
In addition, when bearing 22,23,24,25 being pressed in case of transmission 21 in the mode how all becoming interference fit regardless of state of temperature, when causing case of transmission 21 to expand when becoming the condition of high temperature, outer ring 22a, 23a, 24a, 25a expansion direction (direction shown in the arrow in Fig. 5, Fig. 6) due to its recuperability to case of transmission 21 of bearing 22,23,24,25 is expanding.
Now, to follow the mode of the expansion of case of transmission 21, heart axial direction and the side vertical with bearing central axis direction move up the internal surface of outer ring 22a, 23a, 24a, 25a within the bearing.
Consequently, at employing wrapping angle be 0 degree deep groove ball bearing as bearing 22,23,24,25 when, the internal void of bearing, the gap namely between outer ring and inner ring significantly change, may produce vibration or noise.Further, wrapping angle refer to, be passed to from the internal surface of the outer ring of bearing or the outer surface of inner ring the angle that the line of action of the power of ball and the line vertical with the bearing central axis of this bearing form.
In addition, in the stepless speed variator 1A of present embodiment, make bearing 22, 23, 24, the outer ring 22a of 25, 23a, 24a, the internal surface of 25a or inner ring 22b, 23b, 24b, the outer surface of 25b with ball 22c, 23c, 24c, the part of 25c contact is relative to this bearing 22, 23, 24, the bearing central axis of 25 tilts, make from outer ring 22a, 23a, 24a, the internal surface of 25a or inner ring 22b, 23b, 24b, the outer surface of 25b is passed to ball 22c, 23c, 24c, the line of action of the power of 25c and bearing central axis are (namely, the rotating center axis P1 of the input part 2 or rotating center axis P5 of output shaft 3) point that intersects is at bearing 22, 23, 24, than bearing 22 on the bearing central axis direction of 25, 23, 24, the outer surface side of case of transmission 21 is leaned on by the central authorities of 25.That is, by the wrapping angle of bearing 22,23,24,25 be set as the value more than 0 degree.
In other words, about the bearing 22,23,24,25 of the stepless speed variator 1A of present embodiment, with wrapping angle be that the deep groove ball bearing of 0 degree is compared, the expansion direction (tilting relative to the central axis of bearing and the direction intersected with this central axis in the inner surface side of case of transmission 21) of the line of action being passed to the power of ball 22c, 23c, 24c, 25c and the case of transmission 21 at the region place being provided with this bearing 22,23,24,25 is with subvertical angular cross.
Further in other words, about the bearing 22,23,24,25 of the stepless speed variator 1A of present embodiment, compared with deep groove ball bearing, the shape of the part contacted with ball 22c, 23c, 24c, 25c of the internal surface of outer ring 22a, 23a, 24a, 25a or the outer surface of inner ring 22b, 23b, 24b, 25b is relative to being provided with the expansion direction of case of transmission 21 at region place of this bearing 22,23,24,25 close to parallel.
Therefore, when becoming the condition of high temperature, case of transmission 21 expands, bearing 22 is acted on from case of transmission 21, 23, 24, the pressure of 25 reduces, outer ring 22a, 23a, 24a, 25a is expanding due to recuperability, simultaneously relative to inner ring 22b, 23b, 24b, 25b moves, nonetheless, but because its movement direction is and outer ring 22a, 23a, 24a, the internal surface of 25a or inner ring 22b, 23b, 24b, the inclination of the outer surface of 25b connects subparallel direction, therefore, compared with deep groove ball bearing, the bearing 22 of the stepless speed variator 1A of present embodiment, 23, 24, the change of the internal void of 25 is less.
In addition, in the stepless speed variator 1A of present embodiment, traveling driving source is motor ENG, and an end wall 21a is fixed in motor ENG, and therefore, the bearing 22 end side of input shaft being carried out to axle supporting is configured to, its wrapping angle carry out the wrapping angle of the bearing 24 of axle supporting in another side of comparison input shaft greatly.
Because traveling driving source is motor ENG, an end wall 21a is fixed in this motor, and therefore, expand than the other end wall portion 21b side significantly due to the heat of motor ENG in the end wall 21a side be fixed on motor ENG of case of transmission 21.
Therefore, in the stepless speed variator 1A of present embodiment, make the wrapping angle of the bearing 22 be pressed in this end wall 21a side of expanding significantly be greater than the wrapping angle of the bearing 24 be pressed in the other end wall portion 21b of the side contrary with an end wall the change of further reduction internal void.
Specifically, such as, the outer diameter D 1 of bearing 22 is formed larger than the outer diameter D 3 of bearing 24, and, consider the heat being passed to case of transmission 21 from motor ENG, by the wrapping angle of bearing 22 be set as the value just over following condition expression (1).
Wherein, be the wrapping angle of bearing 22, D1 is the diameter of the surface of contact of bearing 22 and case of transmission 21, and L is the distance from an end wall 21a to the other end wall portion 21b.
In addition, in the stepless speed variator 1A of present embodiment, be configured to, the wrapping angle of the bearing 23,24,25 beyond the bearing 22 that the end side of input shaft is supported meet following condition expression (2), (3), (4).
Wherein, be the wrapping angle of bearing 23,24,25, D2, D3, D4 are the diameters of the surface of contact of bearing 23,24,25 and case of transmission 21, and L is the distance from an end wall 21a to the other end wall portion 21b.
At high operating temperatures, case of transmission 21, swell increment on the central axis direction of bearing 22,23,24,25 changes according to from an end wall 21a to the distance L of the other end wall portion 21b.In addition, diameter D1, the D2 of the surface of contact that the swell increment in the radial direction of bearing 22,23,24,25 contacts with case of transmission according to bearing 22,23,24,25, D3, D4, the internal diameter of opening portion 21d, 21e, 21f, 21g that is namely pressed into for bearing 22,23,24,25 and changing.
Therefore, in the stepless speed variator 1A of present embodiment, bearing 23,24,25 except the bearing 22 of the king-sized position of impact of causing about the heat except being installed in motor ENG, based on from an end wall 21a to the distance L of the other end wall portion 21b and respective diameter D2, D3, D4, to meet the mode regulation wrapping angle of above-mentioned condition expression the change of further reduction internal void.
[the 2nd mode of execution]
With reference to Fig. 7 ~ Fig. 9, the stepless speed variator 1B of present embodiment is described.But, for the structure identical with the stepless speed variator 1A of the 1st mode of execution in the structure of the stepless speed variator 1B of present embodiment, mark identical label, and the description thereof will be omitted.
First, with reference to Fig. 7 ~ Fig. 9, the case of transmission 26 of the stepless speed variator of present embodiment is described in detail.
Case of transmission 26 is parts of aluminum.As shown in Figure 7, this case of transmission 26 possesses: an end wall 26a, and it is fixed in motor ENG; The other end wall portion 26b, it is configured to opposed with an end wall 26a; And surrounding wall portion 26c, it covers crankrocker mechanism 20 and overrunning clutch 17 at spaced intervals, and links the outer rim of an end wall 26a and the outer rim of the other end wall portion 26b.
At one end wall portion 26a is formed with the opening portion 26d (with reference to Fig. 8) for running through insertion input shaft and the opening portion 26e (with reference to Fig. 9) for running through insertion output shaft 3.In addition, at the peripheral portion leaned on inside case of transmission 26 of opening portion 26d, 26e, be formed with lip part 26h, 26i (the 2nd lip part) of extending along the rotating center axis P1 direction of input part 2 or the rotating center axis P5 direction of output shaft 3.
The other end wall portion 26b is formed the opening portion 26f (with reference to Fig. 8) for axle supporting input shaft and the opening portion 26g (with reference to Fig. 9) for axle supporting output shaft 3.In addition, at the peripheral portion leaned on inside case of transmission 26 of opening portion 26f, 26g, be formed with lip part 26j, 26k (the 2nd lip part) of extending along the rotating center axis P1 direction of input part 2 or the rotating center axis P5 direction of output shaft 3.
In addition, as mentioned above, the stepless speed variator 1B of present embodiment possesses: the input shaft be made up of input part 2 and multiple cam disk 5; With output shaft 3.
As shown in Figure 8, in the part being positioned at the inner side of case of transmission 26 of input part 2, be formed with the radially-protruding discoideus extension 5c to input part 2.Lip part 5d (the 1st lip part) extends from the peripheral end portion of this extension 5c along the rotating center axis P1 direction of input part 2.
This lip part 5d (the 1st lip part) is opposed with the lip part 26h (the 2nd lip part) of case of transmission 26, is configured with the bearing 27 (bearing) of the end side of supporting input shaft between which.
In multiple cam disk 5, be on the cam disk 5 of position of the other end wall portion 26b closest to case of transmission 26, as shown in Figure 8, becoming the part of inner side of case of transmission 26, be formed with the radially-protruding discoideus extension 5e to input part 2.Lip part 5f (the 1st lip part) extends from the peripheral end portion of this extension 5e along the rotating center axis P1 direction of input part 2.
This lip part 5f (the 1st lip part) is opposed with the lip part 26j (the 2nd lip part) of case of transmission 26.Be configured with the bearing 29 (bearing) of another side of supporting input shaft between which.
In addition, as shown in Figure 9, for the output shaft 3 of the stepless speed variator 1B of present embodiment, between an end wall 26a and the crankrocker mechanism 20 being in closest to the position of this end wall 26a of case of transmission 26, be formed with the radially-protruding discoideus extension 3a to output shaft 3.Lip part 3b (the 1st lip part) extends from the peripheral end portion of this extension 3a along the rotating center axis P5 direction of output shaft 3.
This lip part 3b (the 1st lip part) is opposed with the lip part 26i (the 2nd lip part) of case of transmission 26.Be configured with the bearing 28 (bearing) of the end side of supporting output shaft 3 between which.
In addition, as shown in Figure 9, for output shaft 3, between the other end wall portion 26b and the crankrocker mechanism 20 being in closest to the position of this other end wall portion 26b of case of transmission 26, the radially-protruding discoideus extension 3c to output shaft 3 is formed with.Lip part 3d (the 1st lip part) extends from the peripheral end portion of this extension 3c along the rotating center axis P5 direction of output shaft 3.
This lip part 3d (the 1st lip part) is opposed with the lip part 26k (the 2nd lip part) of case of transmission 26.Be configured with the bearing 30 (bearing) of another side of supporting output shaft 3 between which.
Next, with reference to Fig. 8 and Fig. 9, the bearing 27,28,29,30 being installed on case of transmission 26 is described in detail.
As shown in Figure 8 and Figure 9, bearing 27,28,29,30 is the ball bearings (angular contact ball bearing) be made up of following part: outer ring 27a, 28a, 29a, 30a; Inner ring 27b, 28b, 29b, 30b; And be configured in this outer ring 27a, 28a, 29a, 30a and multiple ball 27c, 28c, 29c, 30c (rolling element) between inner ring 27b, 28b, 29b, 30b.
In addition, bearing 27,28,29,30 uses rates of thermal expansion than being formed as material, i.e. ferrous materials that the aluminium of the material of case of transmission 26 is little.
And for the bearing 27,29 in bearing 27,28,29,30, its outer ring 27a, 29a are pressed in lip part 5d, 5f (the 1st lip part) of input shaft, and its bearing central axis is consistent with the rotating center axis P1 of input part 2.In addition, for bearing 28,30, its outer ring 28a, 30a are pressed in lip part 3b, 3d (the 1st lip part) of output shaft 3, and its bearing central axis is consistent with the rotating center axis P5 of output shaft 3.
And, the lip part 26h of case of transmission 26, 26i, 26j, 26k (the 2nd lip part) is pressed into bearing 27 in the following manner, 28, 29, the inner ring 27b of 30, 28b, 29b, in 30b: no matter be when stepless speed variator 1B becomes the condition of high temperature due to heat from motor ENG etc., or when becoming the state of the degree being heated to the state of not reaching a high temperature, all can not at bearing 27, 28, 29, the gap caused because of the difference of rates of thermal expansion is produced between 30 and case of transmission 26, namely no matter how state of temperature all becomes interference fit.
Therefore, for the stepless speed variator 1B of present embodiment, on lip part 26h, 26i, 26j, 26k (the 2nd lip part) of case of transmission 26 and the surface of contact of bearing 27,28,29,30, fretting wear or creep wearing and tearing can not be there are.Consequently, in the stepless speed variator 1B of present embodiment, bearing 27,28,29,30 can not loosen, thus can not produce vibration or noise.
In addition, with be at high operating temperatures or the mode all becoming interference fit under the state of degree being heated to the state of not reaching a high temperature is pressed in bearing 27,28,29,30 by case of transmission 26 when, when case of transmission 26 becomes the condition of high temperature and expands, inner ring 27b, 28b, 29b, 30b of bearing 27,28,29,30 are expanded by case of transmission 26, thus expanding to the expansion direction (direction shown in the arrow in Fig. 8, Fig. 9) of case of transmission 26.
Now, to follow the mode of the expansion of case of transmission 26, heart axial direction and the side vertical with bearing central axis direction move up the outer surface of inner ring 27b, 28b, 29b, 30b within the bearing.
Consequently, at employing wrapping angle be 0 degree deep groove ball bearing as bearing 27,28,29,30 when, the internal void of bearing, the gap namely between outer ring and inner ring significantly change, and the action of ball 27c, 28c, 29c, 30c of bearing may be hindered.Further, wrapping angle refer to, be passed to from the internal surface of the outer ring of bearing or the outer surface of inner ring the angle that the line of action of the power of ball and the line vertical with the bearing central axis of this bearing form.
Therefore, in the stepless speed variator 1B of present embodiment, make bearing 27, 28, 29, the outer ring 27a of 30, 28a, 29a, the internal surface of 30a or inner ring 27b, 28b, 29b, the outer surface of 30b with ball 27c, 28c, 29c, the part of 30c contact is relative to this bearing 27, 28, 29, the bearing central axis of 30 tilts, make from outer ring 27a, 28a, 29a, the internal surface of 30a or inner ring 27b, 28b, 29b, the outer surface of 30b is passed to ball 27c, 28c, 29c, the line of action of the power of 30c and bearing central axis are (namely, the rotating center axis P1 of the input part 2 or rotating center axis P5 of output shaft 3) point that intersects is at bearing 27, 28, 29, than bearing 27 on the bearing central axis direction of 30, 28, 29, the outer surface side of case of transmission 26 is leaned on by the central authorities of 30.That is, by the wrapping angle of bearing 27,28,29,30 be set as the value more than 0 degree.
In other words, about the bearing 27,28,29,30 of the stepless speed variator 1B of present embodiment, with wrapping angle be that the deep groove ball bearing of 0 degree is compared, make the line of action of the power being passed to ball 27c, 28c, 29c, 30c and the expansion direction (tilting relative to the central axis of bearing and the direction intersected with this central axis in the inner surface side of case of transmission) of case of transmission 26 at region place of this bearing 27,28,29,30 be installed with subvertical angular cross.
Further in other words, about the bearing 27,28,29,30 of the stepless speed variator 1B of present embodiment, compared with deep groove ball bearing, the shape of the part contacted with ball 27c, 28c, 29c, 30c of the internal surface of outer ring 27a, 28a, 29a, 30a or the outer surface of inner ring 27b, 28b, 29b, 30b is relative to being provided with the expansion direction of case of transmission 26 at region place of this bearing 27,28,29,30 close to parallel.
Therefore, when becoming the condition of high temperature, case of transmission 26 expands, bearing 27 is acted on from case of transmission 26, 28, 29, the pressure of 30 increases, inner ring 27b, 28b, 29b, 30b while expanding relative to outer ring 27a, 28a, 29a, 30a moves, nonetheless, but because its movement direction is and outer ring 27a, 28a, 29a, the internal surface of 30a or inner ring 27b, 28b, 29b, the inclination of the outer surface of 30b connects subparallel direction, therefore, compared with deep groove ball bearing, the bearing 27 of the stepless speed variator 1B of present embodiment, 28, 29, the change of the internal void of 30 is less, the ball 27c of bearing, 28c, 29c, the action of 30c is not easy to be hindered.
In addition, in the stepless speed variator 1B of present embodiment, traveling driving source is motor ENG, and an end wall 26a is fixed in motor ENG, and therefore, the bearing 27 end side of input shaft being carried out to axle supporting is configured to, its wrapping angle carry out the wrapping angle of the bearing 29 of axle supporting in another side of comparison input shaft greatly.
Because traveling driving source is motor ENG, an end wall 26a is fixed in this motor, and therefore, expand than the other end wall portion 26b side significantly due to the heat of motor ENG in the end wall 26a side be fixed on motor ENG of case of transmission 26.
Therefore, in the stepless speed variator 1B of present embodiment, make the wrapping angle of the bearing 27 be pressed in this end wall 26a side of expanding significantly be greater than the wrapping angle of the bearing 29 be pressed in the other end wall portion 26b of the side contrary with an end wall the change of further reduction internal void.
Specifically, such as, the outer diameter D 1 of bearing 27 is formed larger than the outer diameter D 3 of bearing 29, and, consider the heat being passed to case of transmission 26 from motor ENG, by the wrapping angle of bearing 27 be set as the value just over following condition expression (1).
Wherein, be the wrapping angle of bearing 27, D1 is the diameter of the surface of contact of bearing 27 and case of transmission 26, and L is the distance from an end wall 26a to the other end wall portion 26b.
In addition, in the stepless speed variator 1B of present embodiment, be configured to, the wrapping angle of the bearing 28,29,30 beyond the bearing 27 that the end side of input shaft is supported meet following condition expression (2), (3), (4).
Wherein, be the wrapping angle of bearing 28,29,30, D2, D3, D4 are the diameters of the surface of contact of bearing 28,29,30 and case of transmission 26, and L is the distance from an end wall 26a to the other end wall portion 26b.
At high operating temperatures, case of transmission 26, swell increment on the central axis direction of bearing 27,28,29,30 changes according to from an end wall 26a to the distance L of the other end wall portion 26b.In addition, diameter D1, the D2 of the surface of contact that the swell increment in the radial direction of bearing 27,28,29,30 contacts with case of transmission according to bearing 27,28,29,30, D3, D4, the external diameter of lip part 26h, 26i, 26j, 26k that is namely pressed into for bearing 27,28,29,30 and changing.
Therefore, in the stepless speed variator 1B of present embodiment, bearing 28,29,30 except the bearing 27 of the king-sized position of impact of causing about the heat except being installed in motor ENG, based on from an end wall 26a to the distance L of the other end wall portion 26b and respective diameter D2, D3, D4, to meet the mode regulation wrapping angle of above-mentioned condition expression the change of further reduction internal void.
In addition, in the stepless speed variator 1B of present embodiment, be formed with extension 3a, the 3c not available for stepless speed variator 1A of the 1st mode of execution, 5c, 5e, lip part 3b, 3d, 5d, 5f and lip part 26h, 26i, 26j, 26k.
Therefore, compared with the stepless speed variator 1B of present embodiment, the bearing 22,23,24,25 of the stepless speed variator 1A of the 1st mode of execution is easier to relative to the installation ratio of case of transmission 21, and productivity is higher.
; in the stepless speed variator 1B of present embodiment; at high operating temperatures; from with rates of thermal expansion than bearing 27,28,29,30 high materials a part, i.e. lip part 26h, 26i, 26j, 26k of case of transmission 26 of being formed, inner ring 27b, 28b, 29b, 30b of bearing 27,28,29,30 are applied with and make it expand such power.
Therefore, compared with the stepless speed variator 1A of the 1st mode of execution, the stepless speed variator 1B of present embodiment bearing 27,28, be not easy between 29,30 and case of transmission 26 to produce gap, and then be not easy to produce vibration or noise.
Above, illustrated mode of execution is illustrated, but the present invention is not limited to such mode.
Such as, in the above-described embodiment, use aluminium to form case of transmission 21,26, use steel to form bearing 22 ~ 25,27 ~ 30., also can use other materials to be formed.
In addition, in above-mentioned 2nd mode of execution, for the inner side keeping lip part 26h, 26i, 26j, 26k of the case of transmission 26 of bearing 27,28,29,30 (the 2nd lip part), lip part 5d, 5f (the 1st lip part) of input shaft and lip part 3b, 3d (the 1st lip part) of output shaft 3 to be formed at case of transmission 26., these lip parts also can be formed at the outside of case of transmission.
In addition, in the above-described embodiment, use ball bearing (angular contact ball bearing) as bearing., as long as wrapping angle can be designed to the bearing of arbitrary value, the bearing of other kinds, such as tapered roller bearing etc. also can be used to replace ball bearing.
Such as, in the above-described embodiment, for wrapping angle except being in the position close to motor ENG outward, these wrapping angles are defined by the condition expression (2) of service range L and diameter D2, D3, D4, (3), (4)., these condition expressions (1), (2), (3), (4) are the condition expression specifying preferred wrapping angle, as long as the wrapping angle in the present invention more than 0 degree and less than 90 degree, this condition expression (1), (2), (3), (4) also can not be met.In addition, on the contrary, also all wrapping angles can be specified based on condition expression (1), (2), (3), (4).

Claims (7)

1. a stepless speed variator, it possesses:
Input shaft, described input shaft is passed the driving force of traveling driving source;
Output shaft, described output shaft is configured to the rotating center axis being parallel with described input shaft;
Crankrocker mechanism, described crankrocker mechanism has turning radius controlling mechanism and swings link, described turning radius controlling mechanism comprises the rotary part that can rotate centered by the rotating center axis of described input shaft, and freely can regulate the turning radius of this rotary part, described swing link is supported on described output shaft by axle, and the rotary motion of described input shaft is converted to the oscillating motion of described swing link by described crankrocker mechanism;
Single direction rotation stops mechanism, when described swing link is for during to a sideway swivel, described single direction rotation stops mechanism to be fixed relative to described output shaft by described swing link, when described swing link is for rotating to opposite side, described single direction rotation stops mechanism that described swing link is dallied relative to described output shaft;
Case of transmission, described case of transmission has an end wall of the end side being positioned at described input shaft and described output shaft and is positioned at the other end wall portion of another side of described input shaft and described output shaft, and described case of transmission receives described crankrocker mechanism and described single direction rotation stops mechanism; And
Multiple bearing, described multiple bearing is installed in a described end wall of described case of transmission and described the other end wall portion, be made up of outer ring, inner ring and the multiple rolling elements be configured between this outer ring and this inner ring, the described end side of described input shaft or described output shaft or described the other end side bearing are become can freely rotate
The feature of described stepless speed variator is,
At least 1 described bearing in described multiple bearing and described case of transmission are installed into by press-in: no matter the state of temperature of this case of transmission how, all can not produce gap between this bearing and this case of transmission,
The part contacted with described rolling element of the internal surface of the described outer ring of described bearing or the outer surface of described inner ring tilts relative to the bearing central axis of this bearing, the point that the bearing central axis of the line of action and this bearing being passed to the power of described rolling element from the internal surface of the outer ring of this bearing or the outer surface of described inner ring is intersected in the bearing central axis direction of this bearing than the central authorities of this bearing near the outer surface side of described case of transmission.
2. stepless speed variator according to claim 1, is characterized in that,
Described traveling driving source is motor,
A described end wall is fixed in described traveling driving source,
The wrapping angle that the bearing of axle supporting is carried out in another side described in this input shaft of the wrapping angle comparison described end side of described input shaft being carried out to the bearing of axle supporting is large.
3., according to stepless speed variator according to claim 1 or claim 2, it is characterized in that,
The wrapping angle of at least 1 described bearing in described multiple bearing meets following condition expression:
Wherein, be described wrapping angle, D is the diameter of the surface of contact of described bearing and described case of transmission, and L is the distance from a described end wall to described the other end wall portion.
4., according to stepless speed variator according to claim 1 or claim 2, it is characterized in that,
Described bearing is pressed in described case of transmission,
Described input shaft or described output shaft are pressed in described bearing.
5. stepless speed variator according to claim 3, is characterized in that,
Described bearing is pressed in described case of transmission,
Described input shaft or described output shaft are pressed in described bearing.
6., according to stepless speed variator according to claim 1 or claim 2, it is characterized in that,
Described input shaft or described output shaft have: extension, and it extends radially out to this input shaft or output shaft; With the 1st lip part, it extends from the peripheral end portion of described extension along the central axis direction of described bearing,
Described case of transmission has: opening portion, and it runs through insertion for described input shaft or described output shaft; With the 2nd lip part, it extends from the peripheral portion of described opening portion along the bearing central axis direction of described bearing,
Described bearing is pressed in described 1st lip part,
Described 2nd lip part of described case of transmission is pressed in described bearing.
7. stepless speed variator according to claim 3, is characterized in that,
Described input shaft or described output shaft have: extension, and it extends radially out to this input shaft or output shaft; With the 1st lip part, it extends from the peripheral end portion of described extension along the central axis direction of described bearing,
Described case of transmission has: opening portion, and it runs through insertion for described input shaft or described output shaft; With the 2nd lip part, it extends from the peripheral portion of described opening portion along the bearing central axis direction of described bearing,
Described bearing is pressed in described 1st lip part,
Described 2nd lip part of described case of transmission is pressed in described bearing.
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DE6810425U (en) * 1967-12-07 1971-04-22 Skf Svenska Kullagerfab Ab DEVICE FOR MAINTAINING THE AXIAL BEARING CLEARANCE IN ROLLER BEARING INSTALLATIONS.
DE4326177A1 (en) * 1992-08-10 1994-02-17 Volkswagen Ag Light-alloy housing for outer race of roller bearing - incorporates steel reinforcing ring shrunk onto ring-shaped extension of solid housing body to reduce thermal expansion
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