CN105247253A - Power transmission device - Google Patents
Power transmission device Download PDFInfo
- Publication number
- CN105247253A CN105247253A CN201480024109.7A CN201480024109A CN105247253A CN 105247253 A CN105247253 A CN 105247253A CN 201480024109 A CN201480024109 A CN 201480024109A CN 105247253 A CN105247253 A CN 105247253A
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- China
- Prior art keywords
- turning radius
- output shaft
- swing arm
- offset
- power
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
- F16H29/22—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action with automatic speed change
Abstract
[Problem] To provide a power transmission device capable of, when changing gears, reaching a target point more rapidly than conventionally possible. [Solution] A power transmission device comprising a main drive source, a continuously variable transmission, and a control unit. The continuously variable transmission comprises: a lever crank mechanism that converts rotary motion of an input unit to pivoting motion of a pivot link; and an output shaft. A one-way clutch is provided on the output shaft. The output shafts rotates in one direction only, as result of the pivoting motion of the pivot link. The control unit increases (STEP 25) the drive force of the main drive source if a determination has been made (YES in STEP 23) that a force has been applied to a rotation radius adjustment mechanism, said force being in the reduced radius direction in which the rotation radius is reduced by the reduced radius force determination unit.
Description
Technical field
The present invention relates to the power transmitting deice of the stepless speed variator with four pole mechanism types, this stepless speed variator regulates turning radius and speed change freely by being arranged on turning radius controlling mechanism on the rotating center axis of input part.
Background technique
Conventionally, there is known the stepless speed variator of following four pole mechanism types, it has: input part, and it is passed the driving force from main driving sources such as the motors arranged in vehicle; Output shaft, the rotating center axis being parallel ground of itself and input part configures; Multiple turning radius controlling mechanism, they are arranged on rotating center axis; Multiple swing arm, their axles are supported on output shaft; And connecting rod, it has the input side annulus being rotatably embedded in turning radius controlling mechanism an end outward, the swing end connection (for example, referring to patent documentation 1) of another end and swing arm.
In patent documentation 1, each turning radius controlling mechanism is made up of cam part, rotary part and pinion shaft, and wherein, cam part is arranged prejudicially on rotating center axis, and rotary part is set to rotatable prejudicially relative to cam part.In addition, between swing arm and output shaft, the overrunning clutch stoping mechanism as single direction rotation is provided with.In overrunning clutch, when swing arm is for relatively rotating towards side relative to output shaft, making swing arm be fixed on output shaft, when for relatively rotating towards opposite side, swing arm being dallied relative to output shaft.
Each cam part has: at the axially through through hole of rotating center axis; And clearance opening, it is configured to be positioned at on the direction contrary relative to the eccentric direction of rotating center axis, and the outer circumferential face of cam part is communicated with through hole.In addition, in cam part, the mode clipping clearance opening is vertically provided with a pair extension.Adjacent cam part is bolted each other, forms cam part union body thus.Axial one end of cam part union body and input part connect, and constitute camshaft by cam part union body and input part.
Cam part union body is connected with the through hole of each cam part, becomes hollow thus, and pinion shaft is inserted into its inside.The pinion shaft inserted exposes from the clearance opening of each cam part.On rotary part, be provided with the receiving orifice accepting camshaft.At the inner peripheral surface of the rotary part of this receiving orifice of formation, be formed with internal tooth.
The pinion shaft that internal tooth exposes with the clearance opening from camshaft engages.When making camshaft rotate with identical speed with pinion shaft, maintain the turning radius of turning radius controlling mechanism.When making camshaft different from the rotational speed of pinion shaft, the turning radius of turning radius controlling mechanism is changed, and the gear ratio of stepless speed variator changes.
When making turning radius controlling mechanism rotate by making input part rotate, the input part side of connecting rod is rotated, and swings with the swing end of the swing arm of another end connection of connecting rod.That is, connecting rod is constituted by turning radius controlling mechanism, connecting rod and swing arm.Because swing arm is arranged on output shaft via overrunning clutch, therefore, only when towards a sideway swivel, rotary driving force (moment of torsion) is transmitted to output shaft.
The eccentric direction of the cam disk of each turning radius controlling mechanism is set in the different mode of respective phase place around input shaft one week.Therefore, by the connecting rod being embedded in each turning radius controlling mechanism outward, swing arm transfers torque to output shaft successively, therefore, it is possible to make output shaft rotate reposefully.
In addition, in patent documentation 1, when require faster car speed and larger driving force, in order to promptly complete speed change, the turning radius of turning radius controlling mechanism and the driving force of main driving source are controlled, make to be in as in lower area (hereinafter referred to as idle rotation area): not to output shaft transmission of drive force, swing arm dallies relative to output shaft.In this idle rotation area, control as the impact point close to the based target speed of a motor vehicle and the setting of target output drive strength.
Prior art document
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Publication 2013-47492 publication
Summary of the invention
The problem that invention will solve
The object of the present invention is to provide the power transmitting deice of the stepless speed variator with four pole mechanism types, this power transmitting deice promptly can arrive impact point than ever when carrying out speed change.
For the means of dealing with problems
In order to reach above-mentioned purpose, the present invention is following power transmitting deice, and this power transmitting deice has: input part, and its transmission by the rotary driving force of main driving source rotates, output shaft, the rotating center axis being parallel ground configuration of itself and this input part, connecting rod, it has the swing arm that axle is supported on this output shaft, the rotary motion of described input part is transformed to the oscillating motion of described swing arm, and single direction rotation stops mechanism, it can switch to the free position in stationary state and idling conditions, wherein, described stationary state is: when described swing arm is for relatively rotating towards a direction relative to described output shaft, described swing arm is made to be fixed on described output shaft, described idling conditions is: when described swing arm is for relatively rotating to another way relative to described output shaft, described swing arm is dallied relative to described output shaft, described connecting rod has the turning radius controlling mechanism regulating turning radius freely, the feature of described power transmitting deice is, described power transmitting deice has the control device controlling described turning radius controlling mechanism and described main driving source, this control device has: regional determination portion, it is according to turning radius and driving force, obtaining described single direction rotation stops mechanism to be the fixed area of stationary state and the idle rotation area for idling conditions, radius of target configuration part, it is based on the information of vehicles of regulation, target setting turning radius, target drive force configuration part, it is based on the information of vehicles of regulation, target setting driving force, undergauge power detection unit, its judge the power that applies to described turning radius controlling mechanism be whether necking square that turning radius is reduced to power, method for changing speed determination section, the point set based on current turning radius driving force is defined as current point, point based on described target turning radius and the setting of described target drive force is defined as impact point, described target turning radius be less than current turning radius and from described current point speed change to described impact point time, this method for changing speed determination section performs in described idle rotation area to carry out the idle rotation area internal speed-changing of speed change close to the mode of described impact point, when be judged to be by described undergauge power detection unit to described turning radius controlling mechanism be applied with necking square that turning radius is reduced to power, described control device makes the driving force of described main driving source increase.
According to the present invention, when be judged to be by undergauge power detection unit to turning radius controlling mechanism be applied with necking square that turning radius is reduced to power, control device makes the driving force of main driving source increase.Therefore, it is possible to by necking square to the power of masterpiece needed for speed change and efficient, flexible uses, more promptly can complete speed change than ever.
Accompanying drawing explanation
Fig. 1 is the explanatory drawing of the mode of execution that power transmitting deice of the present invention is shown by partial cross section.
Fig. 2 is the explanatory drawing of the connecting rod that present embodiment is shown.
Fig. 3 is the explanatory drawing of the turning radius change that present embodiment is shown.A illustrates that turning radius is maximum state, B illustrate turning radius be in state, C illustrates that turning radius is little state, and D illustrates that turning radius is the state of 0.
Fig. 4 is that the hunting range of the swing arm that present embodiment is shown is relative to the change of turning radius and the explanatory drawing changed.A illustrates that turning radius is the hunting range of maximum state, B illustrate turning radius be in the hunting range of state, C illustrates that turning radius is the hunting range of little state.
Fig. 5 is the block diagram of the power transmitting deice schematically showing present embodiment.
Fig. 6 illustrates the fixed area speed change of present embodiment and the plotted curve of idle rotation area speed change.
Fig. 7 is the plotted curve of the change that the fixed area of present embodiment and the boundary line of idle rotation area are shown.
Fig. 8 is the flow chart of the fixed area speed change of the control device that present embodiment is shown and the alternative condition of idle rotation area speed change.
The flow chart of the work of control device when Fig. 9 is the idle rotation area speed change that present embodiment is shown.
Embodiment
With reference to accompanying drawing, the mode of execution of power transmitting deice of the stepless speed variator with four pole mechanism types of the present invention is described.The stepless speed variator of present embodiment is the one that gear ratio h (rotational speed of the rotational speed/output shaft of h=input part) can be made to be infinitely great (∞), make the rotational speed of output shaft be the so-called IVT (InfinityVariableTransmission: unlimited speed changing type mechanical stepless transmission) in the speed changer of " 0 ".
With reference to Fig. 1, the stepless speed variator 1 of four pole mechanism types has: input part 2, and it rotates centered by rotating center axis P1 by accepting from the rotary driving force as the main driving source 50 (with reference to Fig. 5) such as the motor of internal-combustion engine or motor; Output shaft 3, itself and rotating center axis P1 configure abreast, via the illustrated differential mechanism of omission, to driving wheel 65 (with reference to Fig. 5) transmitting rotary power of vehicle; And 6 turning radius controlling mechanisms 4, they are arranged on rotating center axis P1.In addition, transmission shaft also can be set and carry out alternative differential mechanism.
See figures.1.and.2, each turning radius controlling mechanism 4 has: the cam disk 5 as cam part and the rotating disc 6 as rotary part.Cam disk 5 is discoid, eccentric from rotating center axis P1, and, be arranged in each turning radius controlling mechanism 4 in the mode 2 cam disks 5 being set to by 1 turning radius controlling mechanism 4 to 1 group.In addition, on cam disk 5, through hole 5a through on the direction of rotating center axis P1 is provided with.In addition, cam disk 5 is provided with clearance opening 5b, this clearance opening 5b court and the side's opening in the opposite direction relative to rotating center axis P1 bias, make the outer circumferential face of cam disk 5 be communicated with the inner peripheral surface forming through hole 5a.
Each group of cam disk 5 is configured to: make phase place differ 60 degree each other, with the circumference one week of 6 groups of cam disks 5 around rotating center axis P1.
Cam disk 5 forms as one with the cam disk 5 of adjacent turning radius controlling mechanism 4, constitutes one-piece type cam part 5c.This one-piece type cam part 5c also can be formed by one-body molded, or welds integrated to two cam part.The cam disk 5 of 21 group of each turning radius controlling mechanism 4 is fixing each other by bolt (omitting diagram).The cam disk 5 of the side of main driving source 50 that leans on most be positioned on rotating center axis P1 forms as one with input part 2.Like this, camshaft 51 is formed by input part 2 and cam disk 5.
Camshaft 51 have form by being connected with the through hole 5a of cam disk 5 run through patchhole 60.Thus, camshaft 51 forms the one end open towards the side contrary with main driving source 50 and hollow shaft shape that the other end is closed.The cam disk 5 being positioned at the other end of main driving source 50 side forms as one with input part 2.As the method making this cam disk 5 form with input part 2, also can use one-body molded, in addition, also cam disk 5 and input part 2 can be welded integrated.
In addition, the discoid rotating disc 6 with the receiving orifice 6a accepting cam disk 5 with the state of bias rotatably fitted on the cam disk 5 of each 1 group.
As shown in Figure 2, rotating disc 6 is eccentric relative to cam disk 5 as follows: set the central point of cam disk 5 as the central point of P2, rotating disc 6 be P3, the distance Ra between rotating center axis P1 and center point P 2 is identical with the distance Rb between center point P 2 and center point P 3.
On the receiving orifice 6a of rotating disc 6, the mode between the cam disk 5 of 1 group is provided with internal tooth 6b.
Be configured with small gear 70 in running through in patchhole 60 of camshaft 51, this small gear 70 is with concentric with rotating center axis P1 and be positioned at the mode at the position corresponding with the internal tooth 6b of rotating disc 6, rotatable relative to camshaft 51.Small gear 70 and pinion shaft 72 form.In addition, small gear 70 also can with pinion shaft 72 split form, by spline coupling, small gear 70 and pinion shaft 72 are connect.In the present embodiment, when being simply called small gear 70, being defined as and comprising pinion shaft 72.
Small gear 70, via the clearance opening 5b of cam disk 5, engages with the internal tooth 6b of rotating disc 6.On pinion shaft 72, the mode between adjacent small gear 70 is provided with bearing 74.Via this bearing 74, pinion shaft 72 bearer cams axle 51.Pinion shaft 72 is connected with differential attachment 8.The driving force of adjustment driving source 14 is delivered to small gear 70 via differential attachment 8.
Rotating disc 6 is relative to cam disk 5, eccentric in the mode that distance Ra is identical with distance Rb, therefore, it is possible to make the center point P 3 of rotating disc 6 be positioned on the axis identical with rotating center axis P1, make the distance between rotating center axis P1 and center point P 3, i.e. offset R1 for " 0 ".
The large footpath annulus 15a of connecting rod 15 is via the connecting rod bearing 16 be made up of roller bearing, rotatably fitted in the periphery of rotating disc 6, connecting rod 15 has the larger large footpath annulus 15a of diameter an end, have the path annulus 15b that diameter is less than the diameter of large footpath annulus 15a in another end.In addition, connecting rod bearing 16 also can be formed in the mode that 2 ball bearings are a group by arranging 2 ball bearings vertically.On output shaft 3, via overrunning clutch 17, be provided with 6 swing arms 18 accordingly with connecting rod 15.
Overrunning clutch 17 is arranged between swing arm 18 and output shaft 3, when swing arm 18 is for relatively rotating towards side relative to output shaft 3, swing arm 18 is made to be fixed on output shaft 3 (stationary state), when for relatively rotating towards opposite side, swing arm 18 is made to dally (idling conditions) relative to output shaft 3.
Swing arm 18 is formed as ring-type, above it, is provided with the swing end 18a connect with the path annulus 15b of connecting rod 15.Swing end 18a is provided with a pair tab 18b, and this pair tab 18b gives prominence in the mode clamping path annulus 15b vertically.On a pair tab 18b, be equipped with the patchhole 18c corresponding with the internal diameter of path annulus 15b.Coupling pin 19 as swing axis is inserted in patchhole 18c and path annulus 15b.Thus, connecting rod 15 and swing arm 18 connect.In the present embodiment, the hole marked off by the inner peripheral surface of path annulus 15b is equivalent to of the present inventionly run through patchhole.
In the present embodiment, be immersed in the mode in the oil sump of the lubricant oil of the below of accumulating in housing 80 with the swing end 18a of swing arm 18, swing end 18a be configured in the below of output shaft 3.Thereby, it is possible to utilize oil sump to lubricate swing end 18a, and the lubricant oil of oil sump of can kicking up by the oscillating motion of swing arm 18, lubricates other parts of stepless speed variator 1.
In addition, in the explanation of mode of execution, gear ratio is defined as the rotational speed of the rotational speed/output shaft of input part.
Fig. 3 illustrates the pinion shaft 72 of the state that the offset R1 of turning radius controlling mechanism 4 is changed and the position relationship of rotating disc 6.Fig. 3 A shows state offset R1 being set to " maximum ", and pinion shaft 72 chord rotating disk 6 is oriented to: the center point P 2 of rotating center axis P1, cam disk 5 is arranged in straight line with the center point P 3 of rotating disc 6.Gear ratio h is now minimum.
Fig. 3 B show make offset R1 be less than Fig. 3 A " in " state, Fig. 3 C shows the state of " little " making offset R1 less than Fig. 3 B.Gear ratio h in Fig. 3 B be larger than the gear ratio h of Fig. 3 A " in ", the gear ratio h in Fig. 3 C is " greatly " larger than the gear ratio h of Fig. 3 B.Fig. 3 D shows and makes offset R1 be the state of " 0 ", and the center point P 3 of rotating center axis P1 and rotating disc 6 is in one heart.Gear ratio h is now infinitely great (∞).The stepless speed variator 1 of mode of execution changes offset R1 by turning radius controlling mechanism 4, regulates the turning radius of turning radius controlling mechanism 4 thus freely.
Fig. 4 shows the change of the hunting range of the swing arm 18 when the offset R1 of turning radius controlling mechanism 4 is changed.Fig. 4 A show offset R1 maximum time the hunting range of swing arm 18, Fig. 4 B shows the hunting range of the swing arm 18 when offset R1 is middle, and Fig. 4 C shows the hunting range of the swing arm 18 that offset R1 is hour.As can be seen from Figure 4, along with offset R1 diminishes, hunting range narrows.And when offset R1 is " 0 ", swing arm 18 does not swing.
In the present embodiment, connecting rod 20 (four pole mechanisms) is constituted by turning radius controlling mechanism 4, connecting rod 15 and swing arm 18.And, by connecting rod 20, the rotary motion of input part 2 is converted to the oscillating motion of swing arm 18.The stepless speed variator 1 of present embodiment has total 6 connecting rods 20.When offset R1 is not " 0 ", when rotating when making input part 2 and pinion shaft 72 rotated with the speed identical with input part 2, each connecting rod 15 changes phase place one by one by 60 degree, and based on offset R1, between input part 2 and output shaft 3, with towards output shaft 3 side promote or towards input part 2 side stretching mode alternate repetition swing.
The path annulus 15b of connecting rod 15 connects with the swing arm 18 be arranged on output shaft 3 via overrunning clutch 17, therefore, when swing arm 18 is swung by connecting rod 15 push-and-pull, only when swing arm 18 is towards any one party rotary oscillation bar 18 in pushing direction side or draw direction side, output shaft 3 rotates, when swing arm 18 rotates towards the opposing party, the power of the oscillating motion of swing arm 18 is not delivered to output shaft 3, and swing arm 18 dallies.Each turning radius controlling mechanism 4 is configured to every 60 degree and changes phase place, and therefore, output shaft 3 is rotated successively by each turning radius controlling mechanism 4.
In addition, as is schematically illustrated in figure 5, the power transmitting deice of present embodiment has the control device 40 of regulating and controlling driving source 14.Control device 40 is the electronic units be made up of CPU or storage etc., the control program kept by CPU execute store, plays regulating and controlling driving source 14 thus, regulates the function of the offset R1 of turning radius controlling mechanism 4.
In addition, the control device 40 of present embodiment has regional determination portion 100, radius of target configuration part 110, target drive force configuration part 120, undergauge power detection unit 130, method for changing speed determination section 140, turning radius difference detection unit 150 and current driving force detection unit 160.The information of vehicles target setting turning radius of the regulation that radius of target configuration part 110 receives based on control device 40.Target drive force configuration part 120 is based on the information of vehicles target setting driving force of the regulation such as depression amount of gas pedal.
In addition, control device 40 receives the information of the rotational speed of main driving source 50 from input side rotational speed detection unit 41.In addition, control device 40 receives the information of the rotational speed of output shaft 3 or driving wheel 65 from outlet side rotational speed detection unit 42.In addition, control device 40 receives the opening information from throttle opening detection unit 43, and this throttle opening detection unit 43, according to the depression amount of gas pedal, detects the aperture of carrying out the closure of opening and closing.In addition, control device 40 receives the speed information in the Bus-Speed Monitoring portion (omitting diagram) from the travelling speed detecting vehicle.In addition, control device 40 receives the information of the turning radius (offset) from turning radius detection unit (omitting diagram).
Control device 40, when being in state (the so-called pressure downshift) needing increase gear ratio, increase driving force because stepping on the throttle pedal, performs the process shown in flow chart of Fig. 8.In addition, as shown in Figure 6 and Figure 7, in the system of coordinates being coordinate axes with turning radius and driving force, point based on current turning radius and driving force setting is defined as current point Ps1, Ps2, the point of based target offset (target turning radius) and target drive force setting is defined as impact point Pt.
With reference to Fig. 8, control device 40 receives opening information, speed information, the turning radius information (offset information) of gas pedal first in step 1, determines target offset (target turning radius).
Then, enter step 2, control device 40, as shown in the system of coordinates being coordinate axes with the turning radius of Fig. 6 and driving force, determines that overrunning clutch 17 is the fixed area of stationary state and the idle rotation area for idling conditions, and determines the boundary line L of fixed area and idle rotation area.Fig. 7 is the plotted curve of the boundary line that fixed area and idle rotation area are shown, transverse axis is offset, and the longitudinal axis is the rotational speed of main driving source 50.Known, the travelling speed of vehicle is larger, then boundary line is more moved towards the upper right of Fig. 7, and idle rotation area expands.Control device 40 has memory section (omit diagram), in advance by experiment or emulation etc., makes memory section (omitting diagram) in the mode speed of a motor vehicle, offset, rotational speed associated, stores fixed area and idle rotation area.And then control device 40, based on the speed information received, determines fixed area and idle rotation area.
And then, enter step 3, judge that whether the current point set based on current offset and current input queued switches power is as in fixed area.When fixed area, current point is the position of the Ps1 of Fig. 6, enters step 4, and control device 40 determines whether the state (secondary status) being in the power applying the direction that offset is reduced to turning radius controlling mechanism 4.
When not applying the power in the direction making offset reduce to turning radius controlling mechanism 4 in step 4, entering step 5, judging that whether the difference of current offset and target offset is as more than the value specified.More than the value for regulation, enter step 6, judge that whether current driving force is as below the value specified.
Below the value that current driving force is regulation, enter step 7, perform the process of idle rotation area internal speed-changing: make offset drop to the offset of regulation from current point Ps1, proceed in idle rotation area, then increase rotational speed, arrive impact point Pt.Thereby, it is possible to not by the idle rotation area of driving wheel or the inertial force of vehicle or the impact of running resistance, make offset be reduced near impact point Pt reposefully.
When being applied with the power in the direction making offset reduce in step 4 to turning radius controlling mechanism 4, in step 8 separately, perform the process of fixed area internal speed-changing: from current point Ps1, reduce offset, improve rotational speed, and carry out in fixed area until the speed change of impact point Pt.Thus, efficient, flexible uses the power in the direction that offset is reduced applied to turning radius controlling mechanism 4, offset can be made efficiently to drop to impact point Pt, even if do not proceed in idle rotation area, also can carry out stable speed change.
When the difference of offset current in steps of 5 and target offset is less than the value of regulation, in step 8 separately, the process of fixed area internal speed-changing is performed.The value of the regulation of step 5 refers to and to be worth faster when imagining and not proceeding in idle rotation area directly at fixed area internal speed-changing, is the value obtained by experiment etc. in advance.
When driving force current in step 6 exceedes the value of regulation, separate in step 8, perform the process of fixed area internal speed-changing.The driving force that the value of the regulation of step 6 is set to may to produce because proceeding to idle rotation area loses the value bringing discomfort to driver, and the value of this regulation is also obtained by experiment etc. in advance.
When be not fixed area in step 3 but idle rotation area when, in figure 6, current point is positioned at Ps2.And then in step 9 separately, control device 40 determines whether the power being applied with the direction making offset reduce to turning radius controlling mechanism 4.When left-hand tools radius controlling mechanism 4 is applied with the power in the direction that offset is reduced, enter step 10, increase the rotational speed of main driving source 50, move to fixed area from the current point Ps2 being positioned at idle rotation area.
And then, after confirming to proceed to fixed area in a step 11, enter step 8, perform the process of following fixed area internal speed-changing: reduce offset R1, improve the rotational speed of main driving source 50, and carry out in fixed area until the speed change of impact point Pt.Thereby, it is possible to efficient, flexible uses the power in the direction making offset reduce applied to turning radius controlling mechanism 4, offset can be made efficiently to drop to impact point Pt, even if do not proceed in idle rotation area, also can carry out stable speed change.
In step 9, when not applying the power in the direction making offset R1 reduce to turning radius controlling mechanism 4, perform the process of following idle rotation area internal speed-changing: from step 7 branch, proceed in idle rotation area from current point Ps2, until offset R1 becomes the offset of identical with target offset or close with target offset regulation, then rotational speed is made to increase, until arrive impact point Pt.
The step 3 of Fig. 8 of present embodiment is the process in regional determination portion 100, and step 1 is the process of radius of target configuration part 110 and target drive force configuration part 120, and step 4 and step 9 correspond to undergauge power detection unit 130.In addition, the flow chart of Fig. 8 corresponds to method for changing speed determination section 140.
It is the orthogonal coordinate system of coordinate axes that Fig. 6 shows with the offset R1 of the rotational speed of the main driving source 50 in the power transmitting deice of present embodiment (rotating speed, unit is such as [rpm]) and turning radius controlling mechanism 4 (turning radius unit is such as [mm]).The curve of solid line represents the boundary line L of idle rotation area and fixed area.In figure 6, with boundary line L for boundary, lower left is idle rotation area, and accompanying drawing upper right is fixed area.In addition, as shown in Figure 7, boundary line L is larger with the travelling speed of vehicle, and the mode that idle rotation area is more amplified is changed to La, Lb, Lc.
In addition, in the orthogonal coordinate system shown in Fig. 6, the point obtained is defined as current point, the point obtained according to target rotational speed and target offset R1 is defined as impact point according to rotational speed and the current offset R1 of current main driving source 50.And, in figure 6, some Ps1 represents that current point is in fixed area, in explanation, the point of this Ps1 is defined as fixing in current point.In addition, some when Ps2 represents that current point is in idle rotation area, is defined as current point in idle running in explanation by the point of this Ps2.Pt is impact point.
And in figure 6, C1 is following controllability path: from current point Ps1 in fixing, not by idle rotation area, and at fixed area internal speed-changing to impact point Pt.In addition, controllability path when C1 ' is the rotational speed controlling offset R1 and main driving source 50 as follows: from current point Ps1 in fixing, offset R1 is controlled for by until near target offset, then reaching impact point in idle rotation area.
In addition, in figure 6, controllability path when C2 is the rotational speed controlling offset R1 and main driving source 50 as follows: from current point Ps2 in idle running, maintain turning radius, improve the rotational speed of main driving source 50, proceed in fixed area, then, in fixed area, impact point is arrived.In addition, controllability path when C2 ' is the rotational speed controlling offset R1 and main driving source 50 as follows: from current point Ps2 in idle running, in idle rotation area, offset R1 is controlled near target offset, then arrive impact point.
Next, with reference to Fig. 9, the process of the control device 40 in the internal speed-changing of idle rotation area is described.First, in step 21, detect current offset R1.Then, enter step 22, the information stored based on memory section and the information that receives, judge that whether the power that applies to turning radius controlling mechanism 4 be the power in the direction that offset is reduced.
Then, enter step 23, judge that whether the power applied to turning radius controlling mechanism 4 be the power in the direction that offset is reduced.When the power that left-hand tools radius controlling mechanism 4 applies is the power in the direction that offset is reduced (secondary status), enter step 24, perform the process that offset R1 is reduced.Then, enter step 25, perform the process that the driving force (moment of torsion) of main driving source 50 is increased.
Then, enter step 26, judge whether current offset R1 becomes target offset.When becoming target offset, directly terminate this process.When not becoming target offset, turning back to step 24, performing the process that offset R1 is reduced.
In step 23, the power that left-hand tools radius controlling mechanism 4 applies is not when being the power in the direction that offset is reduced, in other words, when the power in the direction increased when making offset (brake status), enter step 26, perform the process that offset R1 is reduced.Then, enter step 27, judge current point whether as idle rotation area.When entering step 24 for when idle rotation area, continue to perform the process that offset R1 is reduced.
In step 27, when current point is not idle rotation area, in step 28 branch, perform the process reduced for proceeding to driving force (moment of torsion) in idle rotation area, that make main driving source 50.And then, turn back to step 23, judge that whether the power applied to turning radius controlling mechanism 4 be the power in the direction that offset is reduced.
Driving force transfer unit according to the present embodiment, control device 40 when be judged to be by undergauge power detection unit 130 to turning radius controlling mechanism 4 be applied with necking square that turning radius is reduced to power (step 23 of Fig. 9: yes), make the driving force of main driving source 50 increase (step 25).Therefore, it is possible to by necking square to the power of masterpiece needed for speed change and efficient, flexible uses, more promptly can complete speed change than ever.
In addition, in the present embodiment, describe following situation: form camshaft 51 by input part 2 and cam disk 5, camshaft 51 by have be connected with the through hole 5a of cam disk 5 and form run through patchhole 60.But, camshaft of the present invention is not limited thereto, input part such as also can be made to be configured to have one end open and the hollow shaft-like running through patchhole of the shape that the other end is closed, input part can be run through is inserted in discoid cam disk, make through hole be formed as larger than the 1st mode of execution, make cam disk carry out spline coupling with 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, clearance opening is provided with accordingly with the clearance opening of cam disk.And then, be inserted into the small gear in input part and engage with the internal tooth of rotating disc via the clearance opening of input part and the clearance opening of cam disk.
In addition, in the present embodiment, overrunning clutch 17 is used to stop mechanism as single direction rotation, but single direction rotation of the present invention stops mechanism to be not limited thereto, and also can be made up of following twin-direction clutch: this twin-direction clutch is configured to switch freely can from swing arm 18 to the sense of rotation of the swing arm 18 of output shaft 3 transmitting torque relative to output shaft 3.
Label declaration
1 stepless speed variator
2 input parts
3 output shafts
4 turning radius controlling mechanisms
5 cam disks (cam part)
5a through hole
5b clearance opening
The one-piece type cam part of 5c
6 rotating discs (rotary part)
6a receiving orifice (inner peripheral portion)
6b internal tooth
8 differential attachments (planetary gears)
12 segmentation small gears
14 regulate with driving source (motor)
15 connecting rods
15a large footpath annulus
15b path annulus
16 connecting rod bearing
17 overrunning clutchs
18 swing arms
18a swings end
18b tab
18c patchhole
19 coupling pins
20 connecting rods (four pole mechanisms)
40 control devices
41 input side rotational speed detection units
42 outlet side rotational speed detection units
43 throttle opening detection units
51 camshafts
60 run through patchhole
65 driving wheels
70 small gears
72 pinion shafts
74 bearings
80 housings
100 regional determination portions
110 radius of target configuration parts
120 target drive force configuration parts
130 undergauge power detection units
140 method for changing speed determination sections
150 turning radius difference detection units
160 existing driving force detection units
P1 rotating center axis
The central point of P2 cam disk
The central point of P3 rotating disc
The distance of RaP1 and P2
The distance of RbP2 and P3
R1 offset (distance of P1 and P3)
Claims (1)
1. a power transmitting deice, this power transmitting deice has:
Input part, its transmission by the rotary driving force of main driving source rotates;
Output shaft, the rotating center axis being parallel ground configuration of itself and this input part;
Connecting rod, it has the swing arm that axle is supported on this output shaft, the rotary motion of described input part is transformed to the oscillating motion of described swing arm; And
Single direction rotation stops mechanism, it can switch to the free position in stationary state and idling conditions, wherein, described stationary state is: when described swing arm is for relatively rotating towards a direction relative to described output shaft, described swing arm is made to be fixed on described output shaft, described idling conditions is: when described swing arm is for relatively rotating to another way relative to described output shaft, and described swing arm is dallied relative to described output shaft
Described connecting rod has the turning radius controlling mechanism regulating turning radius freely,
The feature of described power transmitting deice is,
Described power transmitting deice has the control device controlling described turning radius controlling mechanism and described main driving source,
This control device has:
Regional determination portion, it is according to turning radius and driving force, obtains described single direction rotation and stops mechanism to be the fixed area of stationary state and the idle rotation area for idling conditions;
Radius of target configuration part, it is based on the information of vehicles of regulation, target setting turning radius;
Target drive force configuration part, it is based on the information of vehicles of regulation, target setting driving force;
Undergauge power detection unit, its judge the power that applies to described turning radius controlling mechanism be whether necking square that turning radius is reduced to power; And
Method for changing speed determination section, point based on current turning radius and driving force setting is defined as current point, point based on described target turning radius and the setting of described target drive force is defined as impact point, described target turning radius be less than current turning radius and from described current point speed change to described impact point time, this method for changing speed determination section performs in described idle rotation area to carry out the idle rotation area internal speed-changing of speed change close to the mode of described impact point
When be judged to be by described undergauge power detection unit to described turning radius controlling mechanism be applied with necking square that turning radius is reduced to power, described control device makes the driving force of described main driving source increase.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013138469 | 2013-07-01 | ||
| JP2013-138469 | 2013-07-01 | ||
| PCT/JP2014/063213 WO2015001857A1 (en) | 2013-07-01 | 2014-05-19 | Power transmission device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105247253A true CN105247253A (en) | 2016-01-13 |
| CN105247253B CN105247253B (en) | 2017-02-22 |
Family
ID=52143450
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201480024109.7A Active CN105247253B (en) | 2013-07-01 | 2014-05-19 | Power transmission device |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP5973075B2 (en) |
| CN (1) | CN105247253B (en) |
| WO (1) | WO2015001857A1 (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1818575A2 (en) * | 2006-02-08 | 2007-08-15 | JATCO Ltd | Control device for a continuously variable transmission and control method thereof |
| JP2007292245A (en) * | 2006-04-26 | 2007-11-08 | Mazda Motor Corp | Holding pressure controller for belt type cvt |
| JP2007315520A (en) * | 2006-05-26 | 2007-12-06 | Toyota Motor Corp | Speed changing controller for continuously variable transmission |
| JP4747059B2 (en) * | 2006-09-20 | 2011-08-10 | ジヤトコ株式会社 | Vehicle control device |
| CN102959267A (en) * | 2010-07-09 | 2013-03-06 | 本田技研工业株式会社 | Automotive drive system and method for controlling same |
| JP2013047492A (en) * | 2011-08-29 | 2013-03-07 | Honda Motor Co Ltd | Drive control device and drive control method |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5543318Y2 (en) * | 1975-12-25 | 1980-10-11 | ||
| EP1475555A1 (en) * | 2002-02-07 | 2004-11-10 | Katsuya Kawakita | Continuously driving transmission, and equipment having continuously driving transmission |
| JP5382882B2 (en) * | 2011-07-25 | 2014-01-08 | 本田技研工業株式会社 | Continuously variable transmission mechanism and automobile drive system |
-
2014
- 2014-05-19 CN CN201480024109.7A patent/CN105247253B/en active Active
- 2014-05-19 WO PCT/JP2014/063213 patent/WO2015001857A1/en active Application Filing
- 2014-05-19 JP JP2015525088A patent/JP5973075B2/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1818575A2 (en) * | 2006-02-08 | 2007-08-15 | JATCO Ltd | Control device for a continuously variable transmission and control method thereof |
| EP1818575A3 (en) * | 2006-02-08 | 2010-04-28 | JATCO Ltd | Control device for a continuously variable transmission and control method thereof |
| JP2007292245A (en) * | 2006-04-26 | 2007-11-08 | Mazda Motor Corp | Holding pressure controller for belt type cvt |
| JP2007315520A (en) * | 2006-05-26 | 2007-12-06 | Toyota Motor Corp | Speed changing controller for continuously variable transmission |
| JP4747059B2 (en) * | 2006-09-20 | 2011-08-10 | ジヤトコ株式会社 | Vehicle control device |
| CN102959267A (en) * | 2010-07-09 | 2013-03-06 | 本田技研工业株式会社 | Automotive drive system and method for controlling same |
| JP2013047492A (en) * | 2011-08-29 | 2013-03-07 | Honda Motor Co Ltd | Drive control device and drive control method |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105247253B (en) | 2017-02-22 |
| JP5973075B2 (en) | 2016-08-23 |
| JPWO2015001857A1 (en) | 2017-02-23 |
| WO2015001857A1 (en) | 2015-01-08 |
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