CN105283696B - Toroidal continuously variable transmission - Google Patents
Toroidal continuously variable transmission Download PDFInfo
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- CN105283696B CN105283696B CN201480033466.XA CN201480033466A CN105283696B CN 105283696 B CN105283696 B CN 105283696B CN 201480033466 A CN201480033466 A CN 201480033466A CN 105283696 B CN105283696 B CN 105283696B
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- Prior art keywords
- hydraulic pressure
- input disc
- grease chamber
- piston
- state
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/664—Friction gearings
- F16H61/6649—Friction gearings characterised by the means for controlling the torque transmitting capability of the gearing
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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
- F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
- F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
- F16H15/04—Gearings providing a continuous range of gear ratios
- F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
- F16H15/32—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line
- F16H15/36—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface
- F16H15/38—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Friction Gearing (AREA)
- Control Of Transmission Device (AREA)
Abstract
In this toroidal continuously variable transmission, an input disk (15) is easily deformed as a result of the first piston (25) of a hydraulic loader (23) locally applying pressure to the second cylinder housing (15a) of the radial outer end section of the input disk (15), but deformation of the input disk (15) is reduced because the hydraulic pressure of a second oil chamber (28) evenly applies pressure to the entire back surface of the input disk (15). By switching between a first control state in which hydraulic pressure is supplied only to the second oil chamber (28) and a second control state in which hydraulic pressure is provided to both a first oil chamber (27) and the second oil chamber (28), pressure is preferentially applied to the input disk (15) by the hydraulic pressure of the second oil chamber (28), and hydraulic pressure is supplied to the first oil chamber (27) and the first piston (25) is used to apply pressure to the input disk (15) in an auxiliary manner when the hydraulic pressure of the second oil chamber (28) alone is not sufficient. As a result, it is possible to minimize the slipping of a power roller (19) while keeping deformation of the input disk (15) to a minimum.
Description
Technical field
The present invention relates to the use of press load suppression produced by hydraulic pressure loading device to be clipped between input disc and output panel
The anchor ring formula buncher of the skidding of power roller.
Background technology
Such technology according to known in following patent documentations 1：By making the power roller being clipped between input disc and output panel
Rolling and make the anchor ring formula buncher that gear ratio infinitely changes hydraulic pressure loading device have the 1st grease chamber and the 1st piston and
2nd grease chamber and the 2nd piston, by supplying identical hydraulic pressure to the 1st grease chamber and the 2nd grease chamber, thus press input disc, suppression vertically
The skidding of brake force roller.
Prior art literature
Patent documentation
Patent documentation 1：No. 4696537 publications of Japanese Patent Publication No.
Content of the invention
Invention problem to be solved
But, when input disc is pressed vertically by hydraulic pressure loading device, if input disc deformation, gear ratio can occur
Control accuracy the various problems such as reduce, therefore, it is intended that suppress power roller while skidding by the Deformation control of input disc
In Min..Particularly, possesses the partly piston of the ad-hoc location at the back side of pressing input disc and all in hydraulic pressure loading device
In the case of the grease chamber of the broad area pressing the back side of input disc, without being suitably used separately this two pressings evenly
Component, then may lead to the deflection of input disc to increase.
The present invention completes in view of the foregoing, it is intended that in the hydraulic pressure using anchor ring formula buncher
While the load that loader produces suppresses the skidding of power roller, by the Deformation control of the input disc being caused by described load
Little limit.
Means for solving the problems
In order to reach above-mentioned purpose, according to the present invention it is proposed that a kind of anchor ring formula buncher, it has：Rotary shaft, its
It is connected with driving source；Input disc, it is supported on described rotary shaft in the way of can not rotating against；Output panel, it rotates against
It is supported on described rotary shaft freely；Power roller, its rolling is supported on lug freely, and is clamped in described input disc and institute
State between output panel；And hydraulic pressure loading device, it is to described input disc to close to the direction of described output panel force, described hydraulic pressure
Loader has：1st cylinder body shell, it is fixed on described rotary shaft；1st piston, it slides axially and is embedded in the 1st freely
The inner peripheral surface of cylinder body shell, and abut with the axial end portion of the 2nd cylinder body shell at the projecting back side in described input disc；The
2 pistons, it is fixed on described rotary shaft, and slides axially and be embedded in the inner peripheral surface of described 2nd cylinder body shell freely；1st
Grease chamber, it is limited between the side wall of described 1st cylinder body shell and described 1st piston；2nd grease chamber, it is limited at described
Between the back side of input disc and described 2nd piston；And control unit, it controls to described 1st grease chamber and described 2nd grease chamber confession
The hydraulic pressure given, it the 1st is characterised by, described control unit based on the gear ratio between described input disc and described output panel, with
And at least one party from the input torque that described driving source inputs to described input disc, in the 1st controlled state and the 2nd control shape
Switch between state, described 1st controlled state is the state that only described 2nd grease chamber is supplied with hydraulic pressure, described 2nd controlled state
It is the state that described 1st grease chamber and described 2nd grease chamber both sides are supplied with hydraulic pressure.
In addition, according to the present invention, on the basis of described 1st feature, proposing a kind of anchor ring formula buncher, it the 2nd
It is characterised by, the outer peripheral face of the described input disc spline freely that slides axially is embedded in the inner circumferential of described 1st cylinder body shell
Face.
In addition, according to the present invention, on the basis of described 1st or the 2nd feature, proposing a kind of anchor ring formula buncher,
It the 3rd is characterised by, switches described 1st controlled state and described 2nd controlled state based on gear ratio and input torque, selects
The input torque of described 1st controlled state is set bigger than during in middle gear ratio in transmission ratio or low gear ratio.
In addition, according to the present invention, on the basis of any one feature in the described 1st～the 3rd, proposing a kind of anchor ring formula
Buncher, it the 4th is characterised by, switches the threshold value of the input torque of described 1st controlled state and described 2nd controlled state
When the output torque of described driving source sharply increases to the change of reduction direction.
And, the input shaft 13 of embodiment corresponds to the rotary shaft of the present invention, the electromotor E of embodiment corresponds to this
The driving source of invention, the electronic control unit U of embodiment corresponds to the control unit of the present invention.
The effect of invention
According to the 1st feature of the present invention, anchor ring formula buncher has：Rotary shaft, it is connected with driving source；Input
Disk, it is supported on rotary shaft in the way of can not rotating against；Output panel, it rotates against and is supported on rotary shaft freely；Dynamic
Power roller, its rolling is supported on lug freely, and is clamped between input disc and output panel；And hydraulic pressure loading device, it is right
To close to the direction of output panel force, hydraulic pressure loading device has input disc：1st cylinder body shell, it is fixed on rotary shaft；1st lives
Plug, it slides axially and is embedded in the inner peripheral surface of the 1st cylinder body shell freely, and the with the projecting back side in input disc
The axial end portion of 2 cylinder body shells abuts；2nd piston, it is fixed on rotary shaft, and slides axially and be embedded in the 2nd cylinder freely
The inner peripheral surface of body case；1st grease chamber, it is limited between the side wall of the 1st cylinder body shell and the 1st piston；2nd grease chamber, its quilt
It is limited between the back side of input disc and the 2nd piston；And control unit, it controls the liquid to the 1st grease chamber and the supply of the 2nd grease chamber
Pressure, therefore, using supplying the 1st piston abutting to the hydraulic-driven of the 1st grease chamber with the 2nd cylinder body shell, pressing input vertically
Disk, and, the hydraulic pressure using supply to the 2nd grease chamber being limited by the 2nd piston, press the back side of input disc vertically, thus, it is possible to
Enough power roller is clamped between input disc and output panel, prevent to skid.
Because the 1st piston partly presses its radially outer end (i.e. the 2nd cylinder body shell) of input disc, therefore, it is easily caused
Input disc deforms, but the hydraulic pressure of the 2nd grease chamber equably presses the whole region at the back side of input disc, the therefore deformation of input disc
Diminish.Thus, by control unit, based on the gear ratio between input disc and output panel and defeated to input disc from driving source
At least one party in the input torque entering, in the 1st controlled state that only the 2nd grease chamber is supplied with hydraulic pressure with to the 1st grease chamber and the 2nd oil
Switch between 2nd controlled state of room both sides supply hydraulic pressure, therefore, input disc preferentially pressed by the hydraulic pressure of the 2nd grease chamber,
Only by the hydraulic pressure of the 2nd grease chamber not enough in the case of, input disc is secondarily pressed by the 1st piston, thereby, it is possible to
Suppression power roller skid while by the Deformation control of input disc be Min., obtain following such effects：Improve and become
The precision of Transmission Ratio Control, improves power transmission efficiency, prevents the fretting wear of the annular surface of input disc and output panel, prevents the
1 piston and the 2nd piston contact etc..
In addition, according to the 2nd feature of the present invention, the outer peripheral face of the input disc spline freely that slides axially is embedded in
The inner peripheral surface of 1 cylinder body shell, therefore, can not only be by input disc can not rotate against and can prop up in the way of sliding axially
Hold in rotary shaft, and, it is fitted together to by the spline of the 1st cylinder body shell and input disc, following situations can be suppressed：Input disc
Its radially outer end is intended to axially external extension because of the counter-force load being subject to from power roller.
In addition, according to the 3rd feature of the present invention, the 1st controlled state and the 2nd control are switched based on gear ratio and input torque
State processed, selects the input torque of the 1st controlled state to be set than in middle gear ratio in transmission ratio or low gear ratio
Shi great, therefore, hydraulic pressure loading device press load to power roller skid suppression effectively work transmission ratio when or
During low gear ratio, as far as possible using the 2nd grease chamber and the 2nd piston and suppress the use of the 1st grease chamber and the 1st piston, thus, it is possible to more have
Prevent to effect the deformation of input disc.
In addition, according to the 4th feature of the present invention, switching the threshold value of the input torque of the 1st controlled state and the 2nd controlled state
When the output torque of driving source sharply increases to reduce direction change, therefore, driving source output torque due to force subtract
Shelves operation etc. and when sharply increasing, Pre-handoff is the 2nd controlled state, and by the 1st piston press in input disc radially
Located at the 2nd cylinder body shell in outside, its radially outer end thereby, it is possible to prevent input disc becomes in the way of to axially external extension
Shape, and can more reliably suppress the skidding of power roller.
Brief description
Fig. 1 is the skeleton drawing of anchor ring formula buncher.(the 1st embodiment)
Fig. 2 is the enlarged view of the main part of Fig. 1.(the 1st embodiment)
Fig. 3 is the sectional view of the 3-3 line along Fig. 2.(the 1st embodiment)
Fig. 4 is the necessary explanatory diagram producing load of hydraulic pressure loading device.(the 1st embodiment)
Fig. 5 is the curve chart of the relation loading between pressure and gear ratio illustrating hydraulic pressure loading device.(the 1st embodiment)
Fig. 6 is the mapping of the control area retrieving hydraulic pressure loading device according to gear ratio and input torque.(the 1st embodiment)
Fig. 7 is the flow chart of the hydraulic control of hydraulic pressure loading device.(the 1st embodiment)
Label declaration
13：Input shaft (rotary shaft)；
15：Input disc；
15a：2nd cylinder body shell；
16：Output panel；
17：Lug；
19：Power roller；
20：Spline is fitted together to；
23：Hydraulic pressure loading device；
24：1st cylinder body shell；
24b：Side wall；
25：1st piston；
26：2nd piston；
27：1st grease chamber；
28：2nd grease chamber；
E：Electromotor (driving source)；
U：Electronic control unit (control unit).
Specific embodiment
Below, based on Fig. 1～Fig. 7, embodiments of the present invention are illustrated.
1st embodiment
As shown in FIG. 1 to 3, the anchor ring formula buncher T of automobile-use possess via amortisseur 12 with electromotor E
Bent axle 11 connect input shaft 13, input shaft 13 is supported with and is essentially mutually isostructural 1st stepless speed changing mechanism 14F
With the 2nd stepless speed changing mechanism 14R.1st stepless speed changing mechanism 14F possesses：Substantially cone shape input disc 15, it is fixed on input
Axle 13；Substantially cone shape output panel 16, it is to rotate against freely and to be supported on input shaft in the way of sliding axially freely
13；A pair of lug 17,17, they are configured in the way of clipping input shaft 13；The pivot 18,18 of a pair of bent axle shape, their one
End is supported on lug 17 in the way of rotating freely；And a pair of power roller 19,19, they are supported in the way of rotating freely
The other end of pivot 18,18, and can abut with input disc 15 and output panel 16.
The opposed faces of input disc 15 and output panel 16 are made up of annular surface, when a pair of lug 17,17 along trunion shaft 21,
21 when moving in the opposite directions to each other, and a pair of power roller 19,19 is rolled around trunion shaft 21,21, and power roller 19,19 is with respect to defeated
Enter the abutment change of disk 15 and output panel 16.
2nd stepless speed changing mechanism 14R becomes face substantially to clip driving gear 22 with described 1st stepless speed changing mechanism 14F
Symmetrical mode configures, and the 1st, the output panel 16,16 of the 2nd stepless speed changing mechanism 14F, 14R and driving gear 22 form as one.
But, the input disc 15 of the 1st stepless speed changing mechanism 14F is fixedly installed in input shaft 13, on the other hand, the 2nd stepless speed changing mechanism
The input disc 15 of 14R is supported to be axially moveable with respect to input shaft 13, and is exerted a force vertically by hydraulic pressure loading device 23.
Input disc 15 with regard to the 1st stepless speed changing mechanism 14F and the output panel of the 1st, the 2nd stepless speed changing mechanism 14F, 14R
16th, 16, because their radial inside portion wall thickness in the axial direction is big, therefore it is being subject to axial load when ratio from power roller 19
Relatively it is difficult to deform, but, with regard to the input disc 15 of the 2nd stepless speed changing mechanism 14R, because its wall thickness in the axial direction is inside from footpath
Side be radially oriented outside approximately fixed, therefore from power roller 19,19 be subject to axial load when be easier deform.
Hydraulic pressure loading device 23 possesses：1st cylinder body shell 24, it is fixed on input shaft 13；1st piston 25, its periphery and interior
Week is sliding freely supported on the inner peripheral surface of perisporium 24a of the 1st cylinder body shell 24 and the outer peripheral face of input shaft 13 respectively；2nd cylinder
Body case 15a, it is axially protruded from input disc 15 and is abutted with the 1st piston 25；2nd piston 26, its outer peripheral face slides freely
Be supported on the inner peripheral surface of the 2nd cylinder body shell 15a, and inner circumferential surface is fixed on input shaft 13；1st grease chamber 27, it is defined
Between the side wall 24b and the 1st piston 25 of the 1st cylinder body shell 24；And the 2nd grease chamber 28, it is limited at the back of the body of input disc 15
Between face and the 2nd piston 26.
The peripheral part of the input disc 15 of the 2nd stepless speed changing mechanism 14R is can not rotate against and can slide axially
Mode spline is fitted together to 20 in the inner peripheral surface of the 1st cylinder body shell 24, and thus, input disc 15 is with can be with respect to input shaft 13 along axle
Integratedly rotate to the state slided with input shaft 13.When by hydraulic pressure loading device 23 towards power roller 19,19 press input disc
When 15, it is fitted together to 20 by the spline of the 1st cylinder body shell 24 and input disc 15 and can suppress following situations：The radial direction of input disc 15
Outer end is intended to axially external extension due to the counter-force load being subject to from power roller 19,19.
When the hydraulic pressure supplying to the 1st grease chamber 27 drives the 1st piston 25 with respect to the 1st cylinder body shell 24 in figure right direction
When, the 1st piston 25 presses the left end of the 2nd cylinder body shell 15a, thus to the right the input disc 15 of the 2nd stepless speed changing mechanism 14R is applied
Power, and to the 2nd grease chamber 28 supply hydraulic pressure with respect to the 2nd piston 26 input disc 15 to the 2nd stepless speed changing mechanism 14R to the right
Force.Its result is that power roller 19,19 is crimped between input disc 15 and the output panel 16 of the 2nd stepless speed changing mechanism 14R,
And power roller 19,19 is crimped between input disc 15 and the output panel 16 of the 1st stepless speed changing mechanism 14F, can produce suppression
The clamping force of the skidding between input disc 15,15 processed and output panel 16,16 and power roller 19.
Now, by the hydraulic pressure of the 1st grease chamber 27 the 1st piston 25 of action only by the radial outer end being pressed on input disc 15
The left part of the 2nd cylinder body shell 15a of side, on the other hand, the whole back side of the hydraulic unit input disc 15 of the 2nd grease chamber 28.
1st stepless speed changing mechanism 14F (or the 2nd stepless speed changing mechanism 14R) possesses on hydraulic control block 31,32 one
To hydraulic actuator 33,33.Each hydraulic actuator 33 is made up of following part：Piston rod 34, it is integrally formed in lug 17
Bottom, and rotate freely and slide up and down via roller bearing 30,30 and be supported on bottom support casting 29 freely；Cylinder body 35,
It is formed at hydraulic control block 31；Piston 36, it is integrally formed in piston rod 34 and is sliding freely embedded in cylinder body 35；Increase
Speed grease chamber 37, it is limited at the side up and down of piston 36；Slow down and use grease chamber 38, it is limited at the another up and down of piston 36
Side.
The upper end of total 4 lugs 17 is supported on a pivot on the corner of upper support plate 40 via each sphere connector 39,
And when 2 lugs 17,17 move up and other 2 lugs 17,17 move down, its action is synchronous.
The hydraulic pressure that oil pump 41 produces is conditioned in hydraulic control circuit 42, and is supplied to hydraulic actuator 33.When right
Speedup grease chamber 37 supplies high pressure and during to deceleration grease chamber 38 supply low pressure, piston 36 and piston rod 34 vertically in
One side move, on the contrary, when to deceleration with grease chamber 38 supply high pressure and to speedup grease chamber 37 supply low pressure when, piston 36 and live
Stopper rod 34 vertically in the opposing party move.
For example, when driving the one of the 1st stepless speed changing mechanism 14F in the opposite directions to each other using hydraulic actuator 33,33
During to lug 17,17, to the arrow a direction rolling of Fig. 1, the contact point contacting with input disc 15 is with respect to defeated for power roller 19,19
Enter axle 13 to side shifting outside radial direction, the contact point simultaneously contacting with output panel 16 is with respect to input shaft 13 into radial direction
The rotation speedup of side shifting, therefore input disc 15 is simultaneously transferred to output panel 16, and the gear ratio of anchor ring formula buncher T is continuously
Reduce.On the other hand, when power roller 19,19 is rolled to the arrow b direction of Fig. 1, the contact point contacting with input disc 15 is relatively
In input shaft 13 to radial direction medial movement, the contact point simultaneously contacting with output panel 16 is with respect to input shaft 13 to radius side
Outwards side shifting, the therefore rotational delay of input disc 15 are simultaneously transferred to output panel 16, and the gear ratio of anchor ring formula buncher T is even
Increase continuously.
The effect of the 2nd stepless speed changing mechanism 14R is identical with the effect of above-mentioned 1st stepless speed changing mechanism 14F, and the 1st, the 2nd no
Level gear 14F, 14R synchronously carry out chronotropic action.Therefore, the drive inputting to input shaft 13 from the bent axle 11 of electromotor E
Power is with the arbitrary gear ratio infinitely speed change in the variator ratio range of anchor ring formula gear T and defeated from driving gear 22
Go out.
Hydraulic pressure after adjusting in hydraulic control circuit 42 is also supplied to hydraulic pressure loading device 23, for beating of power roller 19
Sliding suppression controls.That is, hydraulic control circuit 42 possesses the 1st linear solenoid valve 43 and the 2nd linear solenoid valve 44, and oil pump 41 produces
Hydraulic pressure is supplied to the 1st grease chamber 27 of hydraulic pressure loading device 23 by the 1st linear solenoid valve 43 after adjusting, and, passes through the 2nd line
Property electromagnetic valve 44 adjust after be supplied to the 2nd grease chamber 28 of hydraulic pressure loading device 23.
The gear ratio based on anchor ring formula buncher T for the electronic control unit U and input torque control the 1st linear electromagnetic
The hydraulic pressure that valve 43 and the 2nd linear solenoid valve 44 are exported.The gear ratio of anchor ring formula buncher T can be according to can be by for example
The input speed that existing sensor detects and output speed calculate, the input torque energy of anchor ring formula buncher T
Enough obtained by the communication between fuel injection control ECU, therefore need not add special sensor.
Next, the effect to the embodiments of the present invention possessing said structure illustrates.
Fig. 4 is that the moment of torsion that can transmit and power roller 19 between in input disc 15 (or output panel 16) is illustrated
Figure, (A) of Fig. 4 corresponds to the state that gear ratio is low (or high), the state that (B) of Fig. 4 is 1 corresponding to gear ratio.
If the distance between axis by abutment P of input disc 15 and power roller 19 and input shaft 13 is set to R, and will
The load of the normal direction of described abutment P is set to Fc, then the moment of torsion that can transmit between input disc 15 and power roller 19 with
Fc × R × coefficient of friction represents.Here, coefficient of friction can be regarded fixed value.
In order to obtain necessary transmitting torque while avoiding the skidding between input disc 15 and output panel 16, Fig. 4's
(A) in the state of the gear ratio shown in is low, the gear ratio shown in (B) of Fig. 4 is compared with 1 state, described becomes apart from R
Slightly smaller, accordingly, it would be desirable to make normal direction load Fc slightly larger.But, in gear ratio in the state of low, the direction phase of load Fc
Axis angulation for input shaft 13 becomes big, in order to obtain this load Fc, the axial direction that hydraulic pressure loading device 23 should produce
On component F a significantly diminish, therefore in gear ratio in the state of low, even if reducing produced by hydraulic pressure loading device 23 axially
On component F a it is also possible to obtain necessary transmitting torque.
On the other hand, in the state of the gear ratio shown at (B) of Fig. 4 is 1, it is low with the gear ratio shown in (A) of Fig. 4
State compare, described somewhat become big apart from R, therefore, it is possible to somewhat reduce load Fc in normal direction.But, in gear ratio
In the state of 1, the direction of load Fc diminishes with respect to the axis angulation of input shaft 13, in order to obtain this load Fc,
The big amplitude variation of component F a in axial direction that hydraulic pressure loading device 23 should produce is big, therefore in the state of gear ratio is 1, if do not increased
Load Fa in axial direction produced by big hydraulic pressure loading device 23, then cannot obtain necessary transmitting torque.
As described above, in the state of gear ratio is low state or gear ratio is height, the state phase being 1 with gear ratio
Ratio can reduce axial load Fa produced by hydraulic pressure loading device 23.Fig. 5 shows the gear ratio of anchor ring formula buncher T
Relation and axial load Fa that hydraulic pressure loading device 23 should produce (loading pressure) between it is known that：It is 1.0～1.5 in gear ratio
Zone line, it is big to load buckling, in the gear ratio region bigger than above range and the region less than above range, loads buckling
Little.
In addition, the hydraulic pressure loading device 23 of present embodiment can produce the loading realized by the 1st grease chamber 27 and the 1st piston 25
Pressure and the loading pressure realized by the 2nd grease chamber 28 and the 2nd piston 26, but, by adding that the 1st grease chamber 27 and the 1st piston 25 are realized
Carrying pressure is to be produced by the 2nd cylinder body shell 15a of the radial outer end being pressed on input disc 15 by the 1st piston 25, therefore, defeated
Enter disk 15 and bear loading pressure in the radial outer end concentration being provided with the 2nd cylinder body shell 15a, the caused input disc 15 of this loading pressure
Deformation may become big.
On the other hand, the loading pressure with regard to being realized by the 2nd grease chamber 28 and the 2nd piston 26, the hydraulic pressure due to the 2nd grease chamber 28 exists
The whole region of radial direction equably presses the back side of input disc 15, therefore, the deformation quilt of the caused input disc 15 of this loading pressure
Suppress smaller.
Therefore, in the present embodiment, preferentially produce necessary loading using the 2nd grease chamber 28 and the 2nd piston 26 to press, logical
Cross this loading pressure not enough in the case of, produce the loading pressure suitable with the amount of deficiency using the 1st grease chamber 27 and the 1st piston 25,
Thus by the Deformation control of input disc 15 in Min..
In the mapping of Fig. 6, transverse axis is the gear ratio of anchor ring formula buncher T, and the longitudinal axis is anchor ring formula buncher T
Input torque, the 1st control area A on the downside of threshold line S is only to pass through the 2nd grease chamber 28 and the 2nd piston 26 and produce to load pressure
Region, the 2nd control area B on the upside of threshold line S is to pass through the 1st grease chamber 27 He on the basis of the 2nd grease chamber 28 and the 2nd piston 26
1st piston 25 produces the region loading pressure.Threshold line S uprises and is because in transmission ratio side and low gear ratio side：As it was previously stated,
In transmission ratio side and low gear ratio side, can be by the less skidding loading and constraining brake force roller 19, therefore, even if input
Moment of torsion becomes big it is also possible to only suppress to skid by the 2nd grease chamber 28 and the produced pressure that loads of the 2nd piston 26.
Next, the flow chart based on Fig. 7 illustrates to the hydraulic control of the 1st grease chamber 27 and the 2nd grease chamber 28.
First, in step sl, electronic control unit U is made to read in gear ratio and the input torsion of anchor ring formula buncher T
Square.In following step S2, gear ratio and input torque are applied in the mapping of Fig. 6, if this gear ratio and input
Moment of torsion is in the 1st control area A, is in the downside of threshold line S, then calculated according to gear ratio and input torque in step s3
Go out for the 2nd hydraulic pressure of the 2nd grease chamber 28 required for suppressing power roller 19 to skid.Then, in step s 4, control hydraulic control
2nd linear solenoid valve 44 in loop 42, exports the 2nd hydraulic pressure.Now, the 1st linear solenoid valve 43 is full-shut position, does not export liquid
Pressure.
If gear ratio and input torque are in the 2nd control area B, are in the upper of threshold line S in described step S2
Side, then make the 2nd linear solenoid valve 44 become full-gear in step s 5, export upper limit hydraulic pressure, and calculate in step s 6
Go out the 1st hydraulic pressure of the 1st required grease chamber 27 that skids in order to suppress power roller 19.Then, in the step s 7, control hydraulic pressure control
1st linear solenoid valve 43 in loop 42 processed, exports the 1st hydraulic pressure, and thus the hydraulic pressure by the 1st grease chamber and the 2nd grease chamber both sides suppresses
The skidding of power roller 19.
As described above, when controlling the hydraulic pressure of the 1st grease chamber 27 of hydraulic pressure loading device 23 and the 2nd grease chamber 28, defeated to being difficult to make
The 2nd grease chamber 28 entering disk 15 deformation preferentially supplies hydraulic pressure, only cannot suppress beating of power roller 19 by the hydraulic pressure of the 2nd grease chamber 28
In the case of cunning, secondarily hydraulic pressure is supplied to the 1st grease chamber 27, therefore, it is possible to incite somebody to action while suppressing the skidding of power roller 19
The Deformation control of input disc 15 is Min., obtains following such effects：Improve the precision that gear ratio controls, improve power
Transmission efficiency, prevents the fretting wear of the annular surface of input disc 15 and output panel 16, prevents the 1st piston 25 and the 2nd piston 26
Contact etc..
Drastically stepped on the throttle during the traveling of vehicle pedal pressure downshift operation under such circumstances, exist
The input torque of anchor ring formula buncher T sharply increase and lead to power roller 19 skid worry, but as shown in fig. 6,
In the case of carrying out forcing downshift operation, threshold line S is made to move downwards.As a result, the hydraulic pressure of the 1st grease chamber 27 than usual when
Rise in advance, the 1st piston 25 than usual when press input disc 15 in advance.
1st piston 25 only presses the 2nd cylinder body shell 15a of the radial outer end of input disc 15, therefore, the pressing of the 1st piston 25
Compressive load can effectively stop the radial outer end of input disc 15 from deforming in the way of to axially external extension, though input torque by
Sharply increase it is also possible to reliably stop the skidding of power roller 19 in forcing downshift operation.
More than, embodiments of the present invention are illustrated, but the present invention can be in the range of without departing from its main points
Carry out various design alterations.
For example although the anchor ring formula buncher T of embodiment is dual cavity type but it is also possible to be single chamber profile.
In addition, in embodiments, using gear ratio and this two parameter decision the 1st control area A and the 2nd of input torque
Control area B is but it is also possible to be judged using any one parameter therein.
In addition, the driving source of the present invention is not limited to electromotor E or electro-motor of embodiment etc. arbitrarily
Driving source.
Claims (5)
1. a kind of anchor ring formula buncher, it possesses：Rotary shaft (13), it is connected with driving source (E)；Input disc (15), its
It is supported on described rotary shaft (13) in the way of can not rotating against；Output panel (16), it rotates against and is supported on institute freely
State rotary shaft (13)；Power roller (19), its rolling is supported on lug (17) freely, and be clamped in described input disc (15) and
Between described output panel (16)；And hydraulic pressure loading device (23), it is to described input disc (15) to close to described output panel (16)
Direction force,
Described hydraulic pressure loading device (23) has：1st cylinder body shell (24), it is fixed on described rotary shaft (13)；1st piston
(25), it slides axially and is embedded in the inner peripheral surface of the 1st cylinder body shell (24) freely, and with projecting in described input disc
(15) axial end portion of the 2nd cylinder body shell (15a) at the back side abuts；2nd piston (26), it is fixed on described rotary shaft
, and slide axially and be embedded in the inner peripheral surface of described 2nd cylinder body shell (15a) freely (13)；1st grease chamber (27), it is limited
It is scheduled between side wall (24b) and described 1st piston (25) of described 1st cylinder body shell (24)；2nd grease chamber (28), it is defined
Between the back side of described input disc (15) and described 2nd piston (26)；And control unit (U), it controls to the described 1st oil
The hydraulic pressure that room (27) and described 2nd grease chamber (28) supply,
It is characterized in that,
Described control unit (U) is based on the gear ratio between described input disc (15) and described output panel (16) and from described
At least one party in the input torque that driving source (E) inputs to described input disc (15), in the 1st controlled state and the 2nd control shape
Switch between state, described 1st controlled state is the state that only described 2nd grease chamber (28) is supplied with hydraulic pressure, described 2nd control
State is the state that described 1st grease chamber (27) and described 2nd grease chamber (28) both sides are supplied with hydraulic pressure.
2. anchor ring formula buncher according to claim 1 it is characterised in that
The outer peripheral face of described input disc (15) slide axially freely spline be fitted together to (20) in described 1st cylinder body shell (24)
Inner peripheral surface.
3. the anchor ring formula buncher according to claim 1 or claim 2 it is characterised in that
Described 1st controlled state and described 2nd controlled state are switched based on gear ratio and input torque, selects described 1st control
The input torque of state processed is set bigger than during in middle gear ratio in transmission ratio or low gear ratio.
4. the anchor ring formula buncher according to claim 1 or claim 2 it is characterised in that
Switch described 1st controlled state and described 2nd controlled state input torque threshold value described driving source (E) output
To the change of reduction direction when moment of torsion sharply increases.
5. anchor ring formula buncher according to claim 3 it is characterised in that
Switch described 1st controlled state and described 2nd controlled state input torque threshold value described driving source (E) output
To the change of reduction direction when moment of torsion sharply increases.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013-130426 | 2013-06-21 | ||
| JP2013130426 | 2013-06-21 | ||
| PCT/JP2014/066123 WO2014203921A1 (en) | 2013-06-21 | 2014-06-18 | Toroidal continuously variable transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105283696A CN105283696A (en) | 2016-01-27 |
| CN105283696B true CN105283696B (en) | 2017-02-22 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201480033466.XA Active CN105283696B (en) | 2013-06-21 | 2014-06-18 | Toroidal continuously variable transmission |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6157618B2 (en) |
| CN (1) | CN105283696B (en) |
| WO (1) | WO2014203921A1 (en) |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1368610A (en) * | 1996-04-19 | 2002-09-11 | 托罗特拉克(开发)有限公司 | Control system of speed variator |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0672652B2 (en) * | 1986-05-01 | 1994-09-14 | 日産自動車株式会社 | Toroidal type continuously variable transmission |
| JP4529442B2 (en) * | 2003-02-28 | 2010-08-25 | 日本精工株式会社 | Toroidal continuously variable transmission |
| JP2005127490A (en) * | 2003-10-27 | 2005-05-19 | Nsk Ltd | Toroidal continuously variable transmission |
| JP4605495B2 (en) * | 2004-08-17 | 2011-01-05 | 日本精工株式会社 | Toroidal continuously variable transmission |
-
2014
- 2014-06-18 CN CN201480033466.XA patent/CN105283696B/en active Active
- 2014-06-18 JP JP2015522952A patent/JP6157618B2/en active Active
- 2014-06-18 WO PCT/JP2014/066123 patent/WO2014203921A1/en active Application Filing
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1368610A (en) * | 1996-04-19 | 2002-09-11 | 托罗特拉克(开发)有限公司 | Control system of speed variator |
Also Published As
| Publication number | Publication date |
|---|---|
| JPWO2014203921A1 (en) | 2017-02-23 |
| JP6157618B2 (en) | 2017-07-05 |
| WO2014203921A1 (en) | 2014-12-24 |
| CN105283696A (en) | 2016-01-27 |
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