CN104648118A - Power transmission device - Google Patents
Power transmission device Download PDFInfo
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- CN104648118A CN104648118A CN201410584524.XA CN201410584524A CN104648118A CN 104648118 A CN104648118 A CN 104648118A CN 201410584524 A CN201410584524 A CN 201410584524A CN 104648118 A CN104648118 A CN 104648118A
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Abstract
The present invention provides a power transmission device which can restrain the flexure of a shaft further. The power transmission device (1) comprises an input shaft (2) rotating in a shell; an output shaft parallel with a rotating central axis of the input shaft (2); a one-way clutch; and a plurality of crank rocker mechanisms (1-6) for transforming the rotation movement of the input shaft (2) into the swing movement of a swinging rod. The input shaft comprises two end part shaft necks of which the two end parts are supported by bearings (90) respectively, and an intermediate shaft neck utilizing a bearing (91) to support the intermediate part of the input shaft (2). The first to sixth crank rocker mechanisms transmit the driving forces orderly from the input shaft (2) to the output shaft according to the rotation phases of the input shaft (2), after one of the crank rocker mechanisms (1-6) transmits the driving force, the other crank rocker mechanisms for transmitting the driving forces are configured to span the intermediate shaft neck.
Description
Technical field
The present invention relates to and be located at radius of rotation regulating mechanism on the centre of gration axis of input shaft regulate radius of rotation and can the torque transfer of four joint connecting rod mechanism types of free speed change by utilizing.
Background technology
In the past, the torque transfer of known following four joint connecting rod mechanism types, it possesses: the input shaft of hollow, and it is rotated in housing by the propulsive effort be passed from main drive sources such as the driving engines being located at vehicle; Output shaft, itself and input shaft configure abreast; Multiple radius of rotation regulating mechanism, they are located on the centre of gration axis of input shaft; Multiple swing arm, their axles are supported on output shaft; And connecting rod, it has the rotatably outer input side annulus being embedded in radius of rotation regulating mechanism an end, the swing end of its another end and swing arm links (for example, referring to patent documentation 1).
The input shaft of patent documentation 1, output shaft, radius of rotation regulating mechanism, swing arm and connecting rod constitute quadric linkage.The free-wheel clutch stoping mechanism as single direction rotation is provided with between swing arm and output shaft, swing arm is fixed on output shaft when relatively rotating to side relative to output shaft by it, when relatively rotating to opposite side, swing arm is dallied relative to output shaft.
Radius of rotation regulating mechanism is made up of such as lower part: discoid rotating part, and it has the through hole running through setting with center deviation heart; Gear ring, it is located at the inner peripheral surface of through hole; 1st miniature gears, it is fixed on input shaft and engages with gear ring; Planetary wheel carrier, it is passed the propulsive effort of self-regulation drive source; And 2 the 2nd miniature gearss, they can the mode of free rotation and revolution be supported by planetary wheel carrier axle, engage with gear ring respectively simultaneously respectively.1st miniature gears and 2 the 2nd miniature gearss are configured to their the central axis triangle that is summit for equilateral triangle.
And, when the input shaft rotated by main drive source is identical with the rotative speed of the planetary wheel carrier rotated by adjustment drive source, maintain the offset of center-point relative to the input central axis of input shaft of rotating part, thus the radius of the rotational trajectory of radius of rotation regulating mechanism is also maintained constant.When the input shaft rotated by main drive source is different with the rotative speed of the planetary wheel carrier rotated by adjustment drive source, the center-point of rotating part changes relative to the offset of the centre of gration axis of input shaft, thus the radius of the rotary motion of radius of rotation regulating mechanism also changes.
And due to the change in radius of the rotary motion of radius of rotation regulating mechanism, the amplitude of the swing end of swing arm also changes, thus switches converter speed ratio, controls the rotative speed of output shaft relative to input shaft.
In such torque transfer, by the distance between the center-point of the distance between the center-point of the equilateral triangle being summit with the central axis of 3 miniature gearss and the input central axis of input shaft and this equilateral triangle and the center-point of rotating part is set as equal, the centre of gration axis of input shaft and the point coincides of rotating part can be made, thus make offset be 0.When offset is 0, even if be also 0 at the amplitude of the swing end of the situation bottom lever of input shaft rotation, become the non-rotary state of output shaft.
Patent documentation 1: Japanese Unexamined Patent Publication 2012-1048 publication
The flexure of axle is there is in the torque transfer possessing input and output between centers transmission mechanism.In order to suppress this flexure as much as possible, consider to arrange the tween drive shaft neck utilizing the centre portion of bearing to axle to support.
Summary of the invention
The object of this invention is to provide the torque transfer that can suppress the flexure of axle further.
In order to reach above-mentioned purpose, the present invention is a kind of torque transfer, and it possesses: input shaft, its transmission by the propulsive effort of main drive source and rotating in housing; Output shaft, the centre of gration axis being parallel ground configuration of itself and this input shaft; Single direction rotation stops mechanism, it has outer ring, when described outer ring will rotate to a side relatively relative to described output shaft, described output shaft is fixed in described outer ring, when described outer ring will rotate to the opposing party relatively relative to described output shaft, is dallied relative to described output shaft in described outer ring; And multiple input and output between centers transmission mechanism, the rotary motion of described input shaft is transformed into the hunting motion of described outer ring by them, the feature of described torque transfer is, an axle in described input shaft and described output shaft possesses: 2 end axis necks, and they utilize bearing to support the both ends of a described axle respectively; With tween drive shaft neck, it utilizes bearing to support the pars intermedia of a described axle, described input and output between centers transmission mechanism according to the rotatable phase of described input shaft successively from described input shaft to described output shaft transmission of drive force, after 1 described input and output between centers transmission mechanism in multiple described input and output between centers transmission mechanism delivers propulsive effort, the described input and output between centers transmission mechanism of following transmission of drive force is configured to stride across described tween drive shaft neck.
When arranging tween drive shaft neck, when supposing the input and output between centers transmission mechanism transmission of drive force between an end axis neck and tween drive shaft neck, between this end axis neck and tween drive shaft neck, produce the flexure of axle.Now, clipping the opposition side of tween drive shaft neck, producing rightabout flexure.
According to the present invention, when switching in the input and output between centers transmission mechanism of transmission of drive force between input shaft and output shaft, the input and output between centers transmission mechanism of following transferring power strides across tween drive shaft neck, and therefore the rightabout flexure of axle is suppressed.Thus result can suppress the flexure of axle entirety.
Further, in the present invention, preferably the diameter of the bearing used at tween drive shaft neck place is configured to larger than the diameter of the bearing used at end axis neck place.When the input and output between centers transmission mechanism being configured to carry out transmission of power strides across tween drive shaft neck to suppress the flexure of axle, the known load applied tween drive shaft neck is large.Therefore, if the diameter of the bearing used at tween drive shaft neck is configured to larger than the diameter of the bearing used at end axis neck, also can support securely even if be then applied with large load.
Further, in the present invention, preferably, input and output between centers transmission mechanism possesses: cam part, and it is arranged prejudicially relative to the centre of gration axis of input shaft, and rotates integrally with input shaft; And rotating part, it is rotatably located in cam part with the state of bias, the interior interpolating unit in bearing is inserted in tween drive shaft neck possesses, interior interpolating unit possesses the recess caved in towards the axis direction of an axle, and a part for the cam part of the input and output between centers transmission mechanism adjacent with tween drive shaft neck is positioned at recess.
When arranging tween drive shaft neck, correspondingly, the length of the axis of torque transfer.In this case, if interpolating unit arranges recess in tween drive shaft neck, and a part for cam part is configured in this recess, then can suppresses the length of the axis of torque transfer.
And, in the present invention, 6 input and output between centers transmission mechanisms can be set, and the interval of the phase place of input and output between centers transmission mechanism is set as 120 °, 120 ° ,-60 °, 120 °, 120 ° from a side of the centre of gration axis of the input shaft as an axle, tween drive shaft neck is configured between from a number formulary of centre of gration axis the 3rd and the 4th input and output between centers transmission mechanism.
And, the present invention also can be applied to following structure: input and output between centers transmission mechanism possesses can the radius of rotation regulating mechanism of free adjustment radius of rotation, by regulating the radius of rotation of radius of rotation regulating mechanism, the rotative speed speed change of input shaft can be made, and to output shaft transmission.
Accompanying drawing explanation
Fig. 1 is the instruction diagram that the mode cut open with a part illustrates the embodiment of torque transfer of the present invention.
Fig. 2 is the instruction diagram of the quadric linkage that present embodiment is shown.
Fig. 3 is the instruction diagram of the change of the radius of rotation that present embodiment is shown.The A of Fig. 3 illustrates that radius of rotation is maximum state, the B of Fig. 3 illustrate radius of rotation be in state, the C of Fig. 3 illustrates that radius of rotation is little state, and the D of Fig. 3 illustrates that radius of rotation is the state of 0.
Fig. 4 is the instruction diagram of the change of the hunting range of the outer ring relative with the change of radius of rotation that present embodiment is shown.The A of Fig. 4 illustrates that radius of rotation is the hunting range of maximum state, the B of Fig. 4 illustrate radius of rotation be in the hunting range of state, the C of Fig. 4 illustrates that radius of rotation is the hunting range of little state.
Fig. 5 amplifies the cutaway view that the part of the input shaft of present embodiment is shown.
Fig. 6 is the instruction diagram of the configuration of the phase place of the cam part that present embodiment is schematically shown.
Fig. 7 is the instruction diagram that the transmission of power of present embodiment and the flexure of axle are schematically shown.
Fig. 8 is the instruction diagram of the flexure that transmission of power in the past and axle are schematically shown.
Label declaration
1: torque transfer;
2: input shaft;
2a: input shaft end;
2b: input shaft bearing;
3: output shaft;
3a: output shaft bearing;
4: radius of rotation regulating mechanism;
5: face cam (cam part);
5a: through hole;
5b: cut hole;
5c: one-piece type cam part;
6: rotating disc (rotating part);
6a: reception hole (inner peripheral portion);
6b: internal tooth;
8: modified roll mechanism (sun and planet gear);
14: regulate with drive source (electrical motor);
15: connecting rod;
15a: input side annulus;
15b: outgoing side annulus;
16: connecting rod bearing;
17: free-wheel clutch;
18: swing arm (outer ring);
18a: swing end;
18b: tab;
18c: patchhole;
19: connecting pin;
20: quadric linkage (four joint connecting rod mechanisms);
60: run through patchhole;
70: miniature gears;
72: pinion shaft;
74: pinion bearing;
80: housing;
80a: dividing wall;
90: the bearing of end axis neck;
91: the bearing of tween drive shaft neck;
100: interior interpolating unit;
101: recess;
P1: centre of gration axis;
P2: the center-point of face cam;
P3: the center-point of rotating disc;
The distance of Ra:P1 and P2;
The distance of Rb:P2 and P3;
R1: offset (distance of P1 and P3).
Detailed description of the invention
Referring to figs. 1 through Fig. 7, the embodiment of torque transfer of the present invention is described.The torque transfer of present embodiment can make converter speed ratio h (rotative speed of the rotative speed/output shaft of h=input shaft) infinitely great (∞) and make the rotative speed of output shaft be the one of change-speed box, the i.e. so-called IVT (Infinity VariableTransmission: Limitless speed variator) of " 0 ".
With reference to Fig. 1, the torque transfer 1 of four joint connecting rod mechanism types possesses: input shaft end 2a, and it is rotated centered by centre of gration axis P1 by the propulsive effort be passed from the main drive source ENG of driving engine or the electrical motors etc. such as combustion engine; Output shaft 3, itself and centre of gration axis P1 configure abreast, via omitting the drive wheel of graphic differential gear to vehicle (omitting diagram) transmitting rotary power; With 6 radius of rotation regulating mechanisms 4, they are located on centre of gration axis P1.In addition, transmission shaft also can be set to replace differential gear.
See figures.1.and.2, each radius of rotation regulating mechanism 4 possesses the face cam 5 as cam part and the rotating disc 6 as rotating part.Face cam 5 is discoid, eccentric from centre of gration axis P1, and is located at each radius of rotation regulating mechanism 4 relative to 1 radius of rotation regulating mechanism 4 in the mode that 2 is 1 group.Further, face cam 5 is provided with along the through through hole 5a in the direction of centre of gration axis P1.Further, face cam 5 is provided with cut hole 5b, its to the side's opening in the opposite direction relative to centre of gration axis P1 bias, thus the inner peripheral surface of the outer peripheral face of face cam 5 and formation through hole 5a is communicated with.
Each group of face cam 5 is configured to, and makes phase with one another differ 60 degree, thus by the circumference one week of 6 groups of face cams 5 around centre of gration axis P1.
Face cam 5 is integrally formed with the face cam 5 of adjacent radius of rotation regulating mechanism 4 and is integrally formed type cam part 5c.This one-piece type cam part 5c can be formed by one-body molded, or also can weld 2 cam part and make its integration.The face cam 5 of 21 group of each radius of rotation regulating mechanism 4 is fixing each other by bolt (omitting diagram).The face cam 5 centre of gration axis P1 being close to main driving source is most integrally formed with input shaft end 2a.Like this, the input shaft 2 possessing face cam 5 is constituted by input shaft end 2a and multiple face cam 5.
Input shaft 2 possesses by connecting the through hole 5a of face cam 5 and form run through patchhole 60.Thus, input shaft 2 is configured to the one end open of the side contrary with main drive source ENG and the hollow shaft shape closed of the other end.The face cam 5 being positioned at the other end of main driving source is integrally formed with input shaft end 2a.As the method that this face cam 5 and input shaft end 2a are integrally formed, can use one-body molded, or, also can weld face cam 5 and input shaft end 2a and make its integration.
Further, the discoid rotating disc 6 possessing the reception hole 6a of storage face cam 5 is embedded on each group of face cam 5 so that the state of bias is rotatably outer.
As shown in Figure 2, if the center-point of face cam 5 is P2, if the center-point of rotating disc 6 is P3, rotating disc 6 is eccentric relative to face cam 5 in the mode that the distance Ra between centre of gration axis P1 and center point P 2 is equal with the distance Rb between center point P 2 and center point P 3.
Be provided with internal tooth 6b at the reception hole 6a of rotating disc 6, and make internal tooth 6b between 1 group of face cam 5.
Be configured with miniature gears 70 in running through in patchhole 60 of camshaft 51 in rotatable mode relative to the input shaft 2 with face cam 5, and make miniature gears 70 concentric with centre of gration axis P1, and be positioned at the position corresponding with the internal tooth 6b of rotating disc 6.Miniature gears 70 and pinion shaft 72 are integrally formed.In addition, miniature gears 70 and pinion shaft 72 split also can be made to form, be combined by spline and miniature gears 70 and pinion shaft 72 are linked.In the present embodiment, when only mentioning miniature gears 70, be defined as the structure comprising pinion shaft 72.
Miniature gears 70 engages with the internal tooth 6b of rotating disc 6 via the cut hole 5b of face cam 5.Pinion shaft 72 is provided with pinion bearing 74, and makes pinion bearing 74 between adjacent miniature gears 70.Pinion shaft 72 supports input shaft 2 via this pinion bearing 74.Pinion shaft 72 is connected with the modified roll mechanism 8 be made up of sun and planet gear etc.The propulsive effort of adjustment drive source 14 is passed to miniature gears 70 via modified roll mechanism 8.
Because rotating disc 6 is eccentric in the mode that distance Ra and distance Rb is equal relative to face cam 5, therefore the distance between centre of gration axis P1 and center point P 3, i.e. offset R1 can also be made for " 0 ", the center point P 3 of rotating disc 6 is positioned on the axis identical with centre of gration axis P1.
The input side annulus 15a of connecting rod 15 is by the connecting rod bearing 16 rotatably outer periphery being embedded in rotating disc 6, described connecting rod 15 possesses large diameter input side annulus 15a in the end of a side (input shaft 2 side), the diameter outgoing side annulus 15b less than the diameter of input side annulus 15a is possessed in the end of the opposing party (output shaft 3 side), described connecting rod bearing 16 is made up of the ball bearing of main shaft of 2 group, and these 2 ball bearing of main shafts arrange vertically.Output shaft 3 is provided with 6 swing arms 18 via free-wheel clutch 17 in the mode corresponding with connecting rod 15.In the present embodiment, swing arm 18 has the standby function as the outer ring of free-wheel clutch 17 concurrently.
Free-wheel clutch 17 is located between swing arm 18 and output shaft 3, when swing arm 18 relatively will rotate to side relative to output shaft 3, swing arm 18 is fixed on output shaft 3 (stationary state), makes when relatively rotating to opposite side swing arm 18 dally (idling conditions) relative to output shaft 3.
Swing arm 18 is formed as ring-type, and is thereunder provided with the swing end 18a linked with the outgoing side annulus 15b of connecting rod 15.Be provided with to sandwich in the axial direction a pair outstanding tab 18b of the mode of outgoing side annulus 15b swinging end 18a.A pair tab 18b runs through and is provided with the patchhole 18c corresponding with the internal diameter of outgoing side annulus 15b.The connecting pin 19 as oscillating axle is inserted with in patchhole 18c and outgoing side annulus 15b.Thus, connecting rod 15 and swing arm 18 are linked up.
In the present embodiment, the swing end 18a of swing arm 18 is with the below making the 18a mode be immersed in the oil groove of the lubricating oil of the below of housing 80 storage in swing end be configured in output shaft 3.Thereby, it is possible to lubricate swing end 18a in oil groove, utilize the hunting motion of swing arm 18 simultaneously, take up the lubricating oil in oil groove, thus the miscellaneous part of torque transfer 1 can be made to be lubricated.
In addition, in description of the present embodiment, converter speed ratio is defined as the rotative speed of the rotative speed/output shaft of input shaft.
Fig. 3 shows the position relationship of the pinion shaft 72 chord rotating disk 6 under the state that the offset R1 (radius of rotation) of radius of rotation regulating mechanism 4 is changed.The A of Fig. 3 shows and makes offset R1 be the state of " maximum ", and pinion shaft 72 chord rotating disk 6 is positioned at the position that the center point P 2 of centre of gration axis P1, face cam 5 and the center point P 3 of rotating disc 6 are arranged in a line.Converter speed ratio h is now 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.Converter speed ratio h in the B of Fig. 3 be larger than the converter speed ratio h of the A of Fig. 3 " in ", be " greatly " larger than the converter speed ratio h of the B of Fig. 3 in the C of Fig. 3.The D of Fig. 3 shows and makes offset R1 be the state of " 0 ", and the center point P 3 of centre of gration axis P1 and rotating disc 6 is positioned at concentric position.Converter speed ratio h is now infinitely great (∞).The torque transfer 1 of present embodiment changes offset R1 by utilizing radius of rotation regulating mechanism 4, carrys out the radius of rotation of free adjustment radius of rotation regulating mechanism 4.
Fig. 4 shows the change of the hunting range of the swing arm 18 when the offset R1 of radius of rotation regulating mechanism 4 is changed.The A of Fig. 4 shows the hunting range of the swing arm 18 when offset R1 is maximum, and the B of Fig. 4 shows the hunting range of the swing arm 18 when offset R1 is middle, and the C of Fig. 4 shows the hunting range of the swing arm 18 that offset R1 is hour.According to Fig. 4, along with offset R1 diminishes and hunting range stenosis is narrow.And when offset R1 is " 0 ", swing arm 18 does not swing.
In the present embodiment, quadric linkage 20 (four joint connecting rod mechanisms) is formed by radius of rotation regulating mechanism 4, connecting rod 15, swing arm 18.And, utilize quadric linkage 20, the rotary motion of input shaft 2 is transformed into the hunting motion of swing arm 18.The torque transfer 1 of present embodiment possesses total 6 quadric linkages 20.When offset R1 is not " 0 ", if make input shaft 2 rotate, make pinion shaft 72 rotate with the speed equal with input shaft 2 simultaneously, then the every 60 degree of ground of each connecting rod 15 change phase place, between input shaft 2 and output shaft 3, alternately repeat swing end 18a to push output shaft 3 side to and pull to the action of input shaft 2 side according to offset R1, thus swing arm 18 swings simultaneously.
The outgoing side annulus 15b of connecting rod 15 links with the swing arm 18 being located at output shaft 3 via free-wheel clutch 17, therefore when swing arm 18 is swung by connecting rod 15 push-and-pull, only have when swing arm 18 rotates to press direction side or the one party pulled in side, direction, output shaft 3 just rotates, when swing arm 18 rotates to the opposing party, the power of the hunting motion of swing arm 18 is not passed to output shaft 3, thus swing arm 18 dallies.Each radius of rotation regulating mechanism 4 configures in the mode every 60 degree changing phase place, and therefore output shaft 3 is rotated successively by each radius of rotation regulating mechanism 4.
Further, the torque transfer of present embodiment possesses the control part (omitting diagram) exchanged and save drive source 14 and carry out controlling.Control part is the electronic unit be made up of CPU, memory device etc., by performing the control program that is held in memory device in CPU, exchanging and saving drive source 14 and control, playing the function regulated the offset R1 of radius of rotation regulating mechanism 4.
The torque transfer 1 of present embodiment possesses the housing 80 of rotatable earth's axis supporting input shaft 2.As shown in Figure 5, housing 80 is provided with dividing wall 80a, and makes this dividing wall 80a be positioned at the middle body of input shaft 2.Input shaft 2 is supported by bearing 90 axle at its both ends.The both ends of being supported by this bearing 90 are equivalent to the end axis neck of input shaft of the present invention.In addition, in FIG, the bearing 91 of dividing wall 80a and tween drive shaft neck is eliminated.
Further, input shaft 2 divides in the central portion and is supported on dividing wall 80a via bearing 91.Be equivalent to the tween drive shaft neck of input shaft of the present invention via the part that bearing 91 and dividing wall 80a are supported on housing 80 at the middle body of this input shaft 2.
Fig. 6 schematically illustrates the configuration of the quadric linkage 20 as input and output between centers transmission mechanism of present embodiment.From adjustment with drive source 14 side successively using the quadric linkage 20 of present embodiment as the 1st quadric linkage #1, the 2nd quadric linkage #2, the 3rd quadric linkage #3, the 4th quadric linkage #4, the 5th quadric linkage #5, the 6th quadric linkage #6.
As shown in Figure 6, about the phase difference of the face cam 5 of the quadric linkage 20 as input and output between centers transmission mechanism, according to from the 1st quadric linkage #1 to the order of the 6th quadric linkage #6, the phase difference of the face cam 5 of the 1st quadric linkage #1 and the 2nd quadric linkage #2 is set as 120 °, the phase difference of the face cam 5 of the 2nd quadric linkage #2 and the 3rd quadric linkage #3 is set as 120 °.
And, the phase difference of the face cam 5 of the 3rd quadric linkage #3 and the 4th quadric linkage #4 is set as-60 °, the phase difference of the face cam 5 of the 4th quadric linkage #4 and the 5th quadric linkage #5 is set as 120 °, the phase difference of the face cam 5 of the 5th quadric linkage #5 and the 6th quadric linkage #6 is set as 120 °.
By setting the phase difference of each face cam 5 in this wise, quadric linkage 20 as the input and output between centers transmission mechanism carrying out transmission of power switches the quadric linkage 20 carrying out transmission of power all the time in the mode striding across tween drive shaft neck, such as, after the 1st quadric linkage #1, stride across tween drive shaft neck and switch to the 6th quadric linkage #6, after the 6th quadric linkage #6, stride across tween drive shaft neck and switch to the 2nd quadric linkage #2, after the 2nd quadric linkage #2, stride across tween drive shaft neck and switch to the 4th quadric linkage #4, after the 4th quadric linkage #4, stride across tween drive shaft neck and switch to the 3rd quadric linkage #3, after the 3rd quadric linkage #3, stride across tween drive shaft neck and switch to the 5th quadric linkage #5, after the 5th quadric linkage #5, stride across tween drive shaft neck and switch to the 1st quadric linkage #1.
Thus, such as, when producing the flexure of input shaft 2 with the tween drive shaft neck of Fig. 7 downwards in left side for boundary, stride across tween drive shaft neck and produce flexure on the right side of Fig. 7 to contrary upper side, but this flexure can be suppressed by the quadric linkage 20 next carrying out transmission of power.
Thus torque transfer 1 according to the present embodiment, can suppress the flexure of input shaft 2.
Further, in the figure 7, as shown in the arrow above accompanying drawing, when switching in the mode striding across tween drive shaft neck the quadric linkage 20 carrying out transmission of power, at tween drive shaft neck, the load that bearing 91 applies is become large.Therefore, in the torque transfer 1 of present embodiment, bearing 90 diameter be configured to by bearing 91 than being located at end axis neck is large.Thereby, it is possible to utilize the bearing 91 suitably bearing load of tween drive shaft neck.
Further, and arrange tween drive shaft neck accordingly, input shaft 2 is elongated vertically.Therefore, in the present embodiment, at tween drive shaft neck place, in the interior input shaft 2 inserting in bearing 91, interpolating unit 100 is provided with a pair recess 101 of the axial depression to input shaft 2.And a part for face cam 5 is positioned at this recess 101.Thereby, it is possible to the increase of the axial length of input shaft 2 that restraint measure tween drive shaft neck causes.
Fig. 8 illustrates in torque transfer in the past, the flexure of the input shaft 2 not striding across tween drive shaft neck and switch carry out transmission of power quadric linkage 20 from the 1st quadric linkage #1 to the 6th quadric linkage #6 successively.The bending deformation of known input shaft 2 is large.
In addition, in the present embodiment, as the axle being provided with tween drive shaft neck, input shaft 2 is illustrated, but also can is output shaft 3.
Further, in present embodiment, only have the situation of 1 to be illustrated to tween drive shaft neck, but tween drive shaft neck also can have multiple.
Further, in the present embodiment, the situation all striding across tween drive shaft neck when switching and carrying out the quadric linkage 20 of transmission of power is illustrated.But, even if be configured to switching part when carrying out the quadric linkage 20 of transmission of power (specifically, do not stride across tween drive shaft neck and the quantity of continuous print quadric linkage 20 is more than 2 times of the quantity of tween drive shaft neck, within 1 cycle, tween drive shaft neck is striden across with the quantity of 2 times that exceed the quantity of tween drive shaft neck) stride across tween drive shaft neck, although be inferior to present embodiment, the flexure of axle still can be suppressed compared with torque transfer in the past.
Further, in the present embodiment, form input shaft 2 to by input shaft end 2a and multiple face cam 5, and the situation running through patchhole 60 that input shaft 2 possesses the through hole 5a by connecting face cam 5 and forms is illustrated.
But, input shaft of the present invention is not limited thereto, such as, also can arrange and there is one end open and the component parts of input shaft core as input shaft running through the hollow of patchhole of shape closed of the other end, discoid face cam forms the through hole larger than the through hole of present embodiment so that insertion can be run through for input shaft core, each face cam is combined with the outer peripheral face spline of input shaft core, forms the input shaft possessing multiple face cam.
In this case, be provided with cut hole at the input shaft core of hollow, and make this cut hole corresponding with the cut hole of face cam.And the miniature gears be inserted in input shaft core engages with the internal tooth of rotating disc via the cut hole of input shaft core and the cut hole of face cam.
And, in the present embodiment, mechanism is stoped as single direction rotation, employ free-wheel clutch 17, but single direction rotation of the present invention stops mechanism to be not limited thereto, can be also such as bidirectional clutch, consist of to can from as outer ring swing arm to output shaft transmitting torque, swing arm carries out free switching relative to the hand of rotation of output shaft.
Claims (9)
1. a torque transfer, it possesses:
Input shaft, its transmission by the propulsive effort of main drive source and rotating in housing;
Output shaft, the centre of gration axis being parallel ground configuration of itself and this input shaft;
Single direction rotation stops mechanism, it has outer ring, when described outer ring will rotate to a side relatively relative to described output shaft, described output shaft is fixed in described outer ring, when described outer ring will rotate to the opposing party relatively relative to described output shaft, is dallied relative to described output shaft in described outer ring; And
Multiple input and output between centers transmission mechanism, the rotary motion of described input shaft is transformed into the hunting motion of described outer ring by them,
The feature of described torque transfer is,
An axle in described input shaft and described output shaft possesses: 2 end axis necks, and they utilize bearing to support the both ends of a described axle respectively; With tween drive shaft neck, it utilizes bearing to support the pars intermedia of a described axle,
Described input and output between centers transmission mechanism according to the rotatable phase of described input shaft successively from described input shaft to described output shaft transmission of drive force,
After 1 described input and output between centers transmission mechanism in multiple described input and output between centers transmission mechanism delivers propulsive effort, the described input and output between centers transmission mechanism of following transmission of drive force is configured to stride across described tween drive shaft neck.
2. torque transfer according to claim 1, is characterized in that,
The diameter of the bearing used at described tween drive shaft neck place is larger than the diameter of the bearing used at described end axis neck place.
3. torque transfer according to claim 1 and 2, is characterized in that,
Described input and output between centers transmission mechanism possesses: cam part, and it is arranged prejudicially relative to the centre of gration axis of described input shaft, and rotates integrally with described input shaft; And rotating part, it is rotatably located in this cam part with the state of bias,
The interior interpolating unit in described bearing is inserted in described tween drive shaft neck possesses,
This interior interpolating unit possesses the recess caved in towards the axis direction of a described axle,
A part for the cam part of the described input and output between centers transmission mechanism adjacent with described tween drive shaft neck is positioned at described recess.
4. torque transfer according to claim 1 and 2, is characterized in that,
Described input and output between centers transmission mechanism is provided with 6,
The interval of the phase place of described input and output between centers transmission mechanism is set to 120 °, 120 ° ,-60 °, 120 °, 120 ° from a side of the centre of gration axis of the described input shaft as a described axle,
Described tween drive shaft neck is configured between from a number formulary of described centre of gration axis the 3rd and the 4th described input and output between centers transmission mechanism.
5. torque transfer according to claim 3, is characterized in that,
Described input and output between centers transmission mechanism is provided with 6,
The interval of the phase place of described input and output between centers transmission mechanism is set to 120 °, 120 ° ,-60 °, 120 °, 120 ° from a side of the centre of gration axis of the described input shaft as a described axle,
Described tween drive shaft neck is configured between from a number formulary of described centre of gration axis the 3rd and the 4th described input and output between centers transmission mechanism.
6. torque transfer according to claim 1 and 2, is characterized in that,
Described input and output between centers transmission mechanism possesses can the radius of rotation regulating mechanism of free adjustment radius of rotation,
By regulating the radius of rotation of described radius of rotation regulating mechanism, making the rotative speed speed change of described input shaft, and transmitting to described output shaft.
7. torque transfer according to claim 3, is characterized in that,
Described input and output between centers transmission mechanism possesses can the radius of rotation regulating mechanism of free adjustment radius of rotation,
By regulating the radius of rotation of described radius of rotation regulating mechanism, making the rotative speed speed change of described input shaft, and transmitting to described output shaft.
8. torque transfer according to claim 4, is characterized in that,
Described input and output between centers transmission mechanism possesses can the radius of rotation regulating mechanism of free adjustment radius of rotation,
By regulating the radius of rotation of described radius of rotation regulating mechanism, making the rotative speed speed change of described input shaft, and transmitting to described output shaft.
9. torque transfer according to claim 5, is characterized in that,
Described input and output between centers transmission mechanism possesses can the radius of rotation regulating mechanism of free adjustment radius of rotation,
By regulating the radius of rotation of described radius of rotation regulating mechanism, making the rotative speed speed change of described input shaft, and transmitting to described output shaft.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013243254A JP6132751B2 (en) | 2013-11-25 | 2013-11-25 | Power transmission device |
| JP2013-243254 | 2013-11-25 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104648118A true CN104648118A (en) | 2015-05-27 |
| CN104648118B CN104648118B (en) | 2017-04-12 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410584524.XA Active CN104648118B (en) | 2013-11-25 | 2014-10-27 | Power transmission device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6132751B2 (en) |
| CN (1) | CN104648118B (en) |
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| CN1166579A (en) * | 1996-04-10 | 1997-12-03 | 易通公司 | Two-piece housing for compound transmission |
| CN2730903Y (en) * | 2004-04-28 | 2005-10-05 | 曹正芳 | Bevel gear driving box for double needle bed wrap knitting machine |
| JP2011518290A (en) * | 2008-04-15 | 2011-06-23 | シェフラー テクノロジーズ ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフト | Device for adjusting the amount of eccentricity for a crank CVT transmission |
| CN202510679U (en) * | 2012-03-23 | 2012-10-31 | 陕西法士特齿轮有限责任公司 | Intermediate shaft support structure of speed changer |
| WO2013001859A1 (en) * | 2011-06-30 | 2013-01-03 | 本田技研工業株式会社 | Four-joint link type continuously variable transmission |
| CN202914642U (en) * | 2012-10-29 | 2013-05-01 | 陕西法士特齿轮有限责任公司 | Speed changer with double counter shafts |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4909322B2 (en) * | 2008-07-24 | 2012-04-04 | 本田技研工業株式会社 | transmission |
| JP5372842B2 (en) * | 2010-06-15 | 2013-12-18 | 本田技研工業株式会社 | Vehicle engine starting device |
| JP5703143B2 (en) * | 2011-06-27 | 2015-04-15 | 本田技研工業株式会社 | Power transmission device for vehicle |
| JP5747081B2 (en) * | 2011-07-14 | 2015-07-08 | 本田技研工業株式会社 | Car drive system |
-
2013
- 2013-11-25 JP JP2013243254A patent/JP6132751B2/en not_active Expired - Fee Related
-
2014
- 2014-10-27 CN CN201410584524.XA patent/CN104648118B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1166579A (en) * | 1996-04-10 | 1997-12-03 | 易通公司 | Two-piece housing for compound transmission |
| CN2730903Y (en) * | 2004-04-28 | 2005-10-05 | 曹正芳 | Bevel gear driving box for double needle bed wrap knitting machine |
| JP2011518290A (en) * | 2008-04-15 | 2011-06-23 | シェフラー テクノロジーズ ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフト | Device for adjusting the amount of eccentricity for a crank CVT transmission |
| WO2013001859A1 (en) * | 2011-06-30 | 2013-01-03 | 本田技研工業株式会社 | Four-joint link type continuously variable transmission |
| CN202510679U (en) * | 2012-03-23 | 2012-10-31 | 陕西法士特齿轮有限责任公司 | Intermediate shaft support structure of speed changer |
| CN202914642U (en) * | 2012-10-29 | 2013-05-01 | 陕西法士特齿轮有限责任公司 | Speed changer with double counter shafts |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6132751B2 (en) | 2017-05-24 |
| JP2015102173A (en) | 2015-06-04 |
| CN104648118B (en) | 2017-04-12 |
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