WO2014192753A1 - 無段変速機 - Google Patents
無段変速機 Download PDFInfo
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- WO2014192753A1 WO2014192753A1 PCT/JP2014/063990 JP2014063990W WO2014192753A1 WO 2014192753 A1 WO2014192753 A1 WO 2014192753A1 JP 2014063990 W JP2014063990 W JP 2014063990W WO 2014192753 A1 WO2014192753 A1 WO 2014192753A1
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction 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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
- F16H2037/025—CVT's in which the ratio coverage is used more than once to produce the overall transmission ratio coverage, e.g. by shift to end of range, then change ratio in sub-transmission and shift CVT through range once again
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
- F16H2037/026—CVT layouts with particular features of reversing gear, e.g. to achieve compact arrangement
Definitions
- the present invention relates to a continuously variable transmission in which a speed reduction mechanism and a speed increasing mechanism are combined with a belt type continuously variable transmission mechanism.
- a continuously variable transmission that increases the overall gear ratio by combining a mode in which driving force is transmitted from one pulley to a second pulley and a mode in which driving force is transmitted from the second pulley to the first pulley is as follows. This is known from US Pat.
- a first clutch and a second clutch are disposed at both ends of the input shaft connected to the engine, and the driving force of the input shaft is increased by the engagement of the first clutch.
- This application establishes the LOW mode by transmitting to the first pulley, and establishing the HI mode by transmitting the driving force of the input shaft to the second pulley of the belt-type continuously variable transmission mechanism by engaging the second clutch.
- PCT / JP2012 / 063029 International Publication No. WO2013 / 175568
- the embodiment shown in FIG. 20 has the driving force of the engine E when the first clutch is engaged and the LOW mode is established. It is transmitted from the input shaft through the path of the first clutch ⁇ the first pulley ⁇ the endless belt ⁇ the second pulley ⁇ the dog clutch (output switching mechanism) supported on the input shaft ⁇ the differential gear. Since the torque transmitted in the LOW mode is larger than that in the HI mode, the dog clutch needs to be firmly supported so that it can withstand the large torque. However, since the dog clutch is not directly supported by the transmission case but supported via the input shaft, it is necessary to thicken the input shaft that does not transmit a large torque in order to firmly support the dog clutch, which increases the weight. There is a problem.
- the present invention has been made in view of the above circumstances, and an object thereof is to directly support an output switching mechanism that is supported on the outer periphery of an input shaft and transmits a large torque in a LOW mode by a transmission case to increase support rigidity. .
- an input shaft to which a driving force from a driving source is input a belt-type continuously variable transmission mechanism including a first pulley, a second pulley, and an endless belt
- An output shaft that outputs the driving force shifted by the belt-type continuously variable transmission mechanism, a first input path that transmits the driving force from the driving source to the first pulley, and the driving force from the driving source.
- a first input switching mechanism that switches to the first input path side, a speed reduction mechanism that is disposed in the first input path and decelerates an input to the first pulley, and a driving force from the driving source is applied to the second pulley.
- a continuously variable transmission comprising: an output switching mechanism; and a second output switching mechanism that is disposed in the second output path and switches the driving force from the first pulley to the output shaft side.
- the second pulley is a second fixed pulley and a second movable pulley
- the first fixed pulley and the second fixed pulley are arranged at diagonal positions with respect to each other
- the first movable pulley and the second movable pulley are arranged diagonally to each other
- the first input switching mechanism is arranged on the input shaft or on the rotating shaft on the back surface of the first movable pulley of the first pulley
- Second input switching The structure is disposed on the rotation shaft on the back surface of the second fixed pulley of the second pulley or on the input shaft, and the first output switching mechanism rotates relative to the outer periphery of the input shaft on the first output path.
- the first feature is that the second output switching mechanism and the output shaft are disposed on a rotating shaft on the back surface of the first fixed pulley of the first pulley.
- a continuously variable transmission is proposed.
- the first output switching mechanism selectively selects the first drive gear and the second drive gear, which are rotatably supported by the sub shaft, as the sub shaft.
- the first drive gear is connected to a driven gear provided on the output shaft
- the second drive gear is connected to a driven gear provided on the output shaft via an idle shaft.
- the first output switching mechanism is disposed at a position partially overlapping with the second output switching mechanism when viewed in the radial direction.
- a continuously variable transmission having the third characteristic is proposed.
- the gear ratio of the speed reduction mechanism is i red
- the gear ratio of the speed increasing mechanism is i ind
- the main input shaft 13 of the embodiment corresponds to the input shaft of the present invention
- the LOW friction clutch 24A of the embodiment corresponds to the first input switching mechanism of the present invention
- the HI friction clutch 24B of the embodiment corresponds to the second input switching mechanism of the present invention
- the first reduction gear 25 and the second reduction gear 26 of the embodiment correspond to the reduction mechanism of the present invention
- the first induction gear 27 and the second induction gear of the embodiment corresponds to the driven gear of the present invention.
- the reverse drive gear 34 of the embodiment corresponds to the second drive gear of the present invention
- the third reduction gear 39, the fourth reduction gear 40 of the embodiment, 5 reduction gear 29 and the sixth reduction gear 30 corresponds to a reduction gear of the present invention
- the engine E of the embodiment corresponds to the drive source of the present invention.
- the driving force from the driving source is calculated as follows: input shaft ⁇ first input switching mechanism and deceleration mechanism (or deceleration mechanism and first input switching mechanism) ⁇ first pulley ⁇ endless belt ⁇ first. 2 pulley ⁇ first output switching mechanism arranged in the first output path ⁇ transmitted through the path of the output shaft to establish the LOW mode, and the driving force from the drive source is input shaft ⁇ speed increasing mechanism and second input
- the HI mode is established by transmission through a switching mechanism (or second input switching mechanism and speed increasing mechanism) ⁇ second pulley ⁇ endless belt ⁇ first pulley ⁇ second output switching mechanism ⁇ output shaft path.
- the secondary shaft is disposed on the outer periphery of the input shaft so as to be relatively rotatable, and the first output switching mechanism is disposed on the secondary shaft.
- the input shaft and the countershaft have a double pipe structure, and the subshaft that transmits large torque is placed on the outer periphery of the double pipe and directly supported by the transmission case, so that the first output can be achieved without any special reinforcement.
- the switching mechanism can be supported with high rigidity.
- the first input switching mechanism is disposed on the input shaft or the rotating shaft on the back surface of the first movable pulley of the first pulley
- the second input switching mechanism is the rotating shaft on the back surface of the second fixed pulley of the second pulley.
- the first output switching mechanism is disposed on the auxiliary shaft that is relatively rotatably fitted to the outer periphery of the input shaft on the first output path
- the second output switching mechanism and the output shaft are disposed on the input shaft. Is arranged on the rotating shaft on the back surface of the first fixed pulley of the first pulley, so that the second input switching mechanism, the second By arranging the two-output switching mechanism and the output shaft, the continuously variable transmission can be reduced in size.
- the first output switching mechanism is a dog clutch that can selectively couple the first drive gear and the second drive gear, which are rotatably supported on the sub shaft, to the sub shaft. Since the first drive gear is connected to the driven gear provided on the output shaft and the second drive gear is connected to the driven gear provided on the output shaft via the idle shaft, the LOW mode and An RVS mode can be selectively established.
- the first output switching mechanism is disposed at a position where the first output switching mechanism partially overlaps the second output switching mechanism as viewed in the radial direction.
- the continuously variable transmission can be reduced in size by arranging the output switching mechanism in a compact manner.
- the gear ratio of the speed reduction mechanism is i red
- the gear ratio of the speed increasing mechanism is i ind
- the minimum ratio between the first pulley and the second pulley is i min
- the gear ratio of the reduction gear arranged in one output path is i sec
- the relationship i red ⁇ i min i ind
- FIG. 1 is a skeleton diagram of a continuously variable transmission.
- FIG. 2 is a torque flow diagram in the LOW mode.
- FIG. 3 is a torque flow diagram in the transition mode 1.
- FIG. 4 is a torque flow diagram in the transition mode 2.
- FIG. 5 is a torque flow diagram in the HI mode.
- FIG. 6 is a torque flow diagram in the reverse mode.
- FIG. 7 is a torque flow diagram in the direct connection LOW mode.
- FIG. 8 is a torque flow diagram in the direct connection HI mode.
- FIG. 9 is an explanatory diagram of transition between the LOW mode and the HI mode.
- FIG. 10 is a diagram showing the relationship between the gear ratio of the belt type continuously variable transmission mechanism and the overall gear ratio.
- FIG. 11 is an explanatory diagram of the difference in overall transmission ratio between the present invention and the comparative example.
- a continuously variable transmission T mounted on a vehicle is arranged in parallel to a main input shaft 13 connected to a crankshaft 11 of an engine E via a torque converter 12 and to the main input shaft 13.
- the first auxiliary input shaft 13A, the second auxiliary input shaft 13B, the auxiliary shaft 14, the output shaft 15 and the idle shaft 16 are provided.
- the cylindrical auxiliary shaft 14 is fitted on the outer periphery of the main input shaft 13 so as to be relatively rotatable.
- the cylindrical output shaft 15 is fitted to the outer periphery of the first auxiliary input shaft 13A so as to be relatively rotatable.
- the countershaft 14 is supported by the transmission case via bearings 17 and 17.
- the belt-type continuously variable transmission mechanism 20 disposed between the first sub input shaft 13A and the second sub input shaft 13B includes a first pulley 21 provided on the first sub input shaft 13A and a second sub input shaft 13B.
- a provided second pulley 22 and an endless belt 23 wound around the first and second pulleys 21 and 22 are provided.
- the groove widths of the first and second pulleys 21 and 22 are increased or decreased in opposite directions by hydraulic pressure, and the gear ratio between the first auxiliary input shaft 13A and the second auxiliary input shaft 13B can be continuously changed.
- the first pulley 21 includes a first fixed pulley 21A fixed to the first auxiliary input shaft 13A and a first movable pulley 21B that can approach and leave the first fixed pulley 21A.
- the second pulley 22 includes a second fixed pulley 22A fixed to the second auxiliary input shaft 13B and a second movable pulley 22B that can approach and leave the second fixed pulley 22A.
- the third reduction gear 39 fixed to the second input shaft 13B meshes with the fourth reduction gear 40 fixed to the auxiliary shaft 14, and the fifth reduction gear 29 and the fifth reduction gear 29 supported relatively rotatably on the auxiliary shaft 14 are output.
- the sixth reduction gear 30 fixed to the shaft 15 meshes, and the final drive gear 31 integral with the sixth reduction gear 30 and the final driven gear 32 provided on the differential gear 33 mesh.
- a reverse drive gear 34 rotatably supported on the countershaft 14 meshes with a reverse idle gear 35 fixed to the idle shaft 16, and a reverse driven gear 36 fixed to the idle shaft 16 meshes with the sixth reduction gear 30. .
- a first output switching mechanism 37 composed of a dog clutch is provided on the outer periphery of the countershaft 14.
- the first output switching mechanism 37 can switch between a neutral position, a right movement position, and a left movement position.
- the fifth reduction gear 29 is coupled to the countershaft 14, and when it moves left from the neutral position, the reverse drive.
- a gear 34 is coupled to the countershaft 14.
- a second output switching mechanism 38 composed of a dog clutch is provided on the outer periphery of the first auxiliary input shaft 13A. The second output switching mechanism 38 can switch between a neutral position and a right movement position.
- the sixth reduction gear 30 and the final drive gear 31 are coupled to the first sub input shaft 13A.
- the rotation of the main input shaft 13 is decelerated by the first and second reduction gears 25 and 26 and transmitted to the first sub input shaft 13A.
- the rotation of the main input shaft 13 is accelerated by the first and second induction gears 27 and 28 and transmitted to the second sub input shaft 13B.
- the first reduction gear 25 and the second reduction gear 26 constitute a first input path IP1 of the present invention
- the first induction gear 27 and the second induction gear 28 constitute a second input path IP2 of the present invention.
- the third reduction gear 39, the fourth reduction gear 40, the fifth reduction gear 29, and the sixth reduction gear 30 constitute the first output path OP1 of the present invention, and between the first pulley 21 and the second output switching mechanism 38.
- the first auxiliary input shaft 13A constitutes the second output path OP2 of the present invention.
- the gear ratio from the first reduction gear 25 to the second reduction gear 26 is i red
- the gear ratio from the first induction gear 27 to the second induction gear 28 is i ind
- i sec i red / i ind gear A ratio
- FIG. 2 shows the LOW mode of the continuously variable transmission T.
- the LOW friction clutch 24A is engaged
- the HI friction clutch 24B is disengaged
- the first output switching mechanism 37 is operated to the right movement position (LOW position)
- the second output switching mechanism 38 is in the neutral position. To be operated.
- the driving force of the engine E is crankshaft 11 ⁇ torque converter 12 ⁇ main input shaft 13 ⁇ LOW friction clutch 24A ⁇ first reduction gear 25 ⁇ second reduction gear 26 ⁇ first auxiliary input shaft 13A ⁇ first pulley 21. ⁇ Endless belt 23 ⁇ Second pulley 22 ⁇ Second auxiliary input shaft 13B ⁇ Third reduction gear 39 ⁇ Fourth reduction gear 40 ⁇ Sub shaft 14 ⁇ First output switching mechanism 37 ⁇ Fifth reduction gear 29 ⁇ Sixth reduction gear 30 ⁇ output shaft 15 ⁇ final drive gear 31 ⁇ final driven gear 32 is transmitted to the differential gear 33 through a path.
- the belt type continuously variable transmission mechanism 20 transmits driving force from the first auxiliary input shaft 13A side to the second auxiliary input shaft 13B side, and the overall transmission of the continuously variable transmission T is changed in accordance with the change of the transmission gear ratio. The ratio is changed.
- FIG. 3 shows the first transition mode 1 in which the LOW mode shifts to the HI mode described later.
- the transition mode 1 the LOW friction clutch 24A is engaged, the HI friction clutch 24B is disengaged, the first output switching mechanism 37 is operated to the right movement position (LOW position), and the second output switching mechanism 38 is moved to the right.
- the moving position HI position
- the above-described LOW mode and a direct connection LOW mode see FIG. 7 described later are simultaneously established.
- FIG. 4 shows a transition mode 2 in the latter half of the transition from the LOW mode to the HI mode described later.
- the transition mode 2 the LOW friction clutch 24A is disengaged, the HI friction clutch 24B is engaged, the first output switching mechanism 37 is operated to the right movement position (LOW position), and the second output switching mechanism 38 is moved to the right.
- the moving position (HI position) an HI mode (see FIG. 5) described later and a direct connection HI mode (see FIG. 8) described later are simultaneously established.
- Transition mode 1 and transition mode 2 are for smooth transition from the LOW mode to the HI mode, details of which will be described later.
- FIG. 5 shows the HI mode of the continuously variable transmission T.
- the LOW friction clutch 24A is disengaged, the HI friction clutch 24B is engaged, the first output switching mechanism 37 is operated to the neutral position, and the second output switching mechanism 38 is moved to the right position (HI position). To be operated.
- the driving force of the engine E is: crankshaft 11 ⁇ torque converter 12 ⁇ main input shaft 13 ⁇ first induction gear 27 ⁇ second induction gear 28 ⁇ HI friction clutch 24B ⁇ second auxiliary input shaft 13B ⁇ second pulley 22 It is transmitted to the differential gear 33 through the path of the endless belt 23, the first pulley 21, the first auxiliary input shaft 13 A, the second output switching mechanism 38, the output shaft 15, the final drive gear 31, and the final driven gear 32.
- the belt-type continuously variable transmission mechanism 20 transmits driving force from the second auxiliary input shaft 13B side to the first auxiliary input shaft 13A side, and the overall transmission of the continuously variable transmission T is changed in accordance with the change of the transmission gear ratio. The ratio is changed.
- FIG. 6 shows the reverse mode of the continuously variable transmission T.
- the reverse mode the LOW friction clutch 24A is engaged, the HI friction clutch 24B is disengaged, the first output switching mechanism 37 is operated to the left movement position (RVS position), and the second output switching mechanism 38 is in the neutral position. To be operated.
- the driving force of the engine E is crankshaft 11 ⁇ torque converter 12 ⁇ main input shaft 13 ⁇ LOW friction clutch 24A ⁇ first reduction gear 25 ⁇ second reduction gear 26 ⁇ first auxiliary input shaft 13A ⁇ first pulley 21. ⁇ Endless belt 23 ⁇ second pulley 22 ⁇ second auxiliary input shaft 13B ⁇ third reduction gear 39 ⁇ fourth reduction gear 40 ⁇ sub shaft 14 ⁇ first output switching mechanism 37 ⁇ reverse drive gear 34 ⁇ reverse idle gear 35 ⁇ It is transmitted in reverse rotation to the differential gear 33 through the path of the idle shaft 16 ⁇ the reverse driven gear 36 ⁇ the sixth reduction gear 30 ⁇ the output shaft 15 ⁇ the final drive gear 31 ⁇ the final driven gear 32.
- the belt-type continuously variable transmission mechanism 20 transmits driving force from the first auxiliary input shaft 13A side to the second auxiliary input shaft 13B side, and the overall transmission of the continuously variable transmission T is changed according to the change in the transmission gear ratio. The ratio is changed.
- FIG. 7 shows the direct connection LOW mode of the continuously variable transmission T.
- the direct connection LOW mode the LOW friction clutch 24A is engaged, the HI friction clutch 24B is disengaged, the first output switching mechanism 37 is operated to the neutral position, and the second output switching mechanism 38 is moved to the right position (HI position). ).
- the driving force of the engine E is crankshaft 11 ⁇ torque converter 12 ⁇ main input shaft 13 ⁇ LOW friction clutch 24A ⁇ first reduction gear 25 ⁇ second reduction gear 26 ⁇ first auxiliary input shaft 13A ⁇ second output switching. It is transmitted to the differential gear 33 through the path of the mechanism 38 ⁇ the output shaft 15 ⁇ the final drive gear 31 ⁇ the final driven gear 32.
- the belt-type continuously variable transmission mechanism 20 does not operate, and the overall transmission ratio of the continuously variable transmission T is constant.
- FIG. 8 shows the direct connection HI mode of the continuously variable transmission T.
- the direct connection HI mode the LOW friction clutch 24A is disengaged, the HI friction clutch 24B is engaged, the first output switching mechanism 37 is operated to the right movement position (LOW position), and the second output switching mechanism 38 is neutral. Manipulated into position.
- the driving force of the engine E is crankshaft 11 ⁇ torque converter 12 ⁇ main input shaft 13 ⁇ first induction gear 27 ⁇ second induction gear 28 ⁇ HI friction clutch 24B ⁇ second auxiliary input shaft 13B ⁇ third reduction gear.
- the belt-type continuously variable transmission mechanism 20 does not operate and the overall transmission ratio of the continuously variable transmission T is constant.
- the overall transmission ratio of the continuously variable transmission T is the same, thereby preventing a shift shock from occurring when the LOW mode is switched to the HI mode.
- the second output switching mechanism 38 moves rightward to the HI position during the transition from the LOW mode to the transition mode 1
- the LOW friction clutch 24A and the HI friction clutch 24B are interchanged during the transition from the transition mode 1 to the transition mode 2.
- the first output switching mechanism 37 moves leftward to the neutral position at the time of transition from the transition mode 2 to the HI mode, the first output switching mechanism 37 and the second output switching mechanism 38 are prevented from causing differential rotation.
- the LOW friction clutch 24A and the HI friction clutch 24B can be smoothly operated.
- the gear ratio i red from the first reduction gear 25 to the second reduction gear 26 is 1.5 and the gear ratio i ind from the first induction gear 27 to the second induction gear 28 is assumed. Is set to 0.75, the minimum transmission ratio i min from the first pulley 21 to the second pulley 22 of the belt-type continuously variable transmission mechanism 20 is set to 0.5, the third reduction gear 39 to the fourth reduction gear 40 and the fifth The gear ratio i sec to the sixth reduction gear 30 through the reduction gear 29 is set to 2.0, and the rotation speed of the main input shaft 13 is set to 1500 rpm.
- the power transmission path in the transition mode 1 includes a power transmission path in the LOW mode and a power transmission path in the direct connection LOW mode.
- the HI mode power transmission path and the direct connection HI power transmission path coexist in the transition mode 2 power transmission path.
- the second sub-transmission path is used.
- the main input shaft 13, the first sub input shaft 13A, the second sub input shaft 13B, the sub shaft 14 and the output shaft. 15 does not change at all, and the speed ratio of the belt type continuously variable transmission mechanism 20 is maintained at i min , so that the first output switching mechanism 37, the second output switching mechanism 38, the LOW friction clutch 24A and the HI
- the friction clutch 24B can be operated smoothly without any differential rotation.
- the belt type continuously variable transmission mechanism 20 transmits power from the first pulley 21 to the second pulley 22 to the second pulley 22 to the first pulley 21.
- torque transmission is temporarily interrupted to switch to the state.
- the direct connection LOW mode and the direct connection HI mode are established and torque is transmitted, so that it is possible to prevent the occurrence of shock due to the interruption of torque transmission.
- the belt-type continuously variable transmission mechanism 20 includes the first reduction gear 25, the second reduction gear 26, the third reduction gear 39, the fourth reduction gear 40, and the fifth reduction gear 29.
- a single belt-type continuously variable transmission mechanism is obtained by combining a speed reduction mechanism including the first induction gear 27 and the second induction gear 28 and a speed reduction mechanism including the sixth reduction gear 30.
- both the LOW-side transmission ratio and the OD-side transmission ratio can be expanded to realize a large overall transmission ratio of 10 or more (see FIG. 11).
- the overall transmission ratio when the transmission ratio of the belt-type continuously variable transmission mechanism 20 is 1.0 is the overall transmission ratio at the OD end of the single belt-type continuously variable transmission mechanism. It can be seen that the effect of increasing the gear ratio on the OD side is particularly remarkable.
- the first output switching mechanism 37 has a double tube structure in which the cylindrical auxiliary shaft 14 is fitted to the outer periphery of the inner output shaft 15, and the auxiliary shaft 14 that transmits a large torque is connected to the outer periphery of the double tube.
- the first output switching mechanism 37 can be provided without any special reinforcement by supporting the main input shaft 13 that is disposed on the side and directly supported by the transmission case, and that supports the main input shaft 13 that transmits a relatively small torque via the auxiliary shaft 14. It becomes possible to support with high rigidity.
- the first output switching mechanism 37 is constituted by a dog clutch capable of selectively coupling the fifth reduction gear 29 and the reverse drive gear 34 supported on the auxiliary shaft 14 to be rotatable relative to the auxiliary shaft 14.
- the drag resistance can be reduced as compared with the case of using the LOW mode, and the LOW mode and the RVS mode can be selectively established only by operating the first output switching mechanism 37 with a single actuator.
- the structure can be simplified.
- first fixed pulley 21A of the first pulley 21 and the second fixed pulley 22A of the second pulley 22 are arranged at diagonal positions
- the second movable pulley 21B of the first pulley 21 and the second of the second pulley 22 are second.
- the movable pulley 22B is disposed at a diagonal position
- the HI friction clutch 24B and the second induction gear 28 are disposed on the back side of the second fixed pulley 22A
- the second output switching mechanism is disposed on the back side of the first fixed pulley 21A.
- 38 and the output shaft 15 are disposed
- the first output switching mechanism 37 is disposed at a position partially overlapping with the second output switching mechanism 38 when viewed in the radial direction.
- the size of the continuously variable transmission T can be reduced by effectively utilizing the dead space formed on the back side of the 22A.
- the LOW friction clutch 24A is disposed on the main input shaft 13 and the HI friction clutch 24B is disposed on the second sub input shaft 13B.
- the LOW friction clutch 24A is disposed on the first sub input shaft 13A.
- the HI friction clutch 24 ⁇ / b> B may be disposed on the main input shaft 13.
- the drive source of the present invention is not limited to the engine E, and may be another type of drive source such as a motor / generator.
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Abstract
Description
14 副軸
15 出力軸
16 アイドル軸
20 ベルト式無段変速機構
21 第1プーリ
21A 第1固定プーリ
21B 第1可動プーリ
22 第2プーリ
22A 第2固定プーリ
22B 第2可動プーリ
23 無端ベルト
24A LOW摩擦クラッチ(第1入力切換機構)
24B HI摩擦クラッチ(第2入力切換機構)
25 第1リダクションギヤ(減速機構)
26 第2リダクションギヤ(減速機構)
27 第1インダクションギヤ(増速機構)
28 第2インダクションギヤ(増速機構)
29 第5リダクションギヤ(第1ドライブギヤあるいはリダクションギヤ)
30 第6リダクションギヤ(ドリブンギヤあるいはリダクションギヤ)
34 リバースドライブギヤ(第2ドライブギヤ)
37 第1出力切換機構
38 第2出力切換機構
39 第3リダクションギヤ(リダクションギヤ)
40 第4リダクションギヤ(リダクションギヤ)
E エンジン(駆動源)
IP1 第1入力経路
IP2 第2入力経路
OP1 第1出力経路
OP2 第2出力経路
Claims (4)
- 駆動源(E)からの駆動力が入力される入力軸(13)と、第1プーリ(21)、第2プーリ(22)および無端ベルト(23)で構成されるベルト式無段変速機構(20)と、前記ベルト式無段変速機構(20)で変速された駆動力を出力する出力軸(15)と、前記駆動源(E)からの駆動力を前記第1プーリ(21)に伝達する第1入力経路(IP1)と、前記駆動源(E)からの駆動力を前記第1入力経路(IP1)側に切り換える第1入力切換機構(24A)と、前記第1入力経路(IP1)に配置されて前記第1プーリ(21)への入力を減速する減速機構(25,26)と、前記駆動源(E)からの駆動力を前記第2プーリ(22)に伝達する第2入力経路(IP2)と、前記駆動源(E)からの駆動力を前記第2入力経路(IP2)側に切り換える第2入力切換機構(24B)と、前記第2入力経路(IP2)に配置されて前記第2プーリ(22)への入力を増速する増速機構(27,28)と、前記第2プーリ(22)からの駆動力を出力する第1出力経路(OP1)と、前記第1プーリ(21)からの駆動力を出力する第2出力経路(OP2)と、前記第1出力経路(OP1)に配置されて第2プーリ(22)からの駆動力を前記出力軸(15)側に切り換える第1出力切換機構(37)と、前記第2出力経路(OP2)に配置されて第1プーリ(21)からの駆動力を前記出力軸(15)側に切り換える第2出力切換機構(38)とを備える無段変速機であって、
前記第1プーリ(21)は第1固定プーリ(21A)および第1可動プーリ(21B)からなり、前記第2プーリ(22)は第2固定プーリ(22A)および第2可動プーリ(22B)からなり、前記第1固定プーリ(21A)および第2固定プーリ(22A)は相互に対角位置に配置され、前記第1可動プーリ(21B)および第2可動プーリ(22B)は相互に対角位置に配置され、
前記第1入力切換機構(24A)は、前記入力軸(13)上あるいは前記第1プーリ(21)の第1可動プーリ(21B)の背面の回転軸上に配置され、前記第2入力切換機構(24B)は、前記第2プーリ(22)の第2固定プーリ(22A)の背面の回転軸上あるいは前記入力軸(13)上に配置され、
前記第1出力切換機構(37)は、前記第1出力経路(OP1)上において前記入力軸(13)の外周に相対回転自在に嵌合する副軸(14)上に配置され、前記第2出力切換機構(38)および前記出力軸(15)は、前記第1プーリ(21)の第1固定プーリ(21A)の背面の回転軸上に配置されることを特徴とする無段変速機。 - 前記第1出力切換機構(37)は、前記副軸(14)に相対回転自在に支持した第1ドライブギヤ(29)および第2ドライブギヤ(34)を該副軸(14)に選択的に結合可能なドグクラッチで構成され、前記第1ドライブギヤ(29)は前記出力軸(15)に設けたドリブンギヤ(30)に接続され、前記第2ドライブギヤ(34)はアイドル軸(16)を経由して前記出力軸(15)に設けたドリブンギヤ(30)に接続されることを特徴とする、請求項1に記載の無段変速機。
- 前記第1出力切換機構(37)は径方向に見て前記第2出力切換機構(38)と一部がオーバーラップする位置に配置されることを特徴とする、請求項1または請求項2に記載の無段変速機。
- 前記減速機構(25,26)のギヤ比をired とし、前記増速機構(27,28)のギヤ比をiind とし、前記第1プーリ(21)および前記第2プーリ(22)間の最小レシオをimin とし、前記第1出力経路(OP1)に配置されるリダクションギヤ(39,40,29,30)のギヤ比をisec としたとき、ired ×imin =iind の関係と、isec =ired /iind の関係とが成立することを特徴とする、請求項1~請求項3の何れか1項に記載の無段変速機。
Priority Applications (6)
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MX2015015991A MX2015015991A (es) | 2013-05-28 | 2014-05-27 | Transmisión continuamente variable. |
DE112014002579.8T DE112014002579T5 (de) | 2013-05-28 | 2014-05-27 | Stufenlos variables Getriebe |
BR112015028781A BR112015028781A2 (pt) | 2013-05-28 | 2014-05-27 | transmissão continuamente variável |
CN201480025773.3A CN105190101B (zh) | 2013-05-28 | 2014-05-27 | 无级变速器 |
US14/894,200 US10030749B2 (en) | 2013-05-28 | 2014-05-27 | Continuously variable transmission |
JP2015519872A JP5922843B2 (ja) | 2013-05-28 | 2014-05-27 | 無段変速機 |
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PCT/JP2014/063990 WO2014192753A1 (ja) | 2013-05-28 | 2014-05-27 | 無段変速機 |
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JP (1) | JP5922843B2 (ja) |
CN (1) | CN105190101B (ja) |
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JP2024051435A (ja) * | 2022-09-30 | 2024-04-11 | 株式会社Subaru | 無段変速機 |
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KR101828191B1 (ko) | 2013-10-08 | 2018-02-09 | 쟈트코 가부시키가이샤 | 부변속기를 구비한 무단 변속기의 제어 장치 |
EP3056773A4 (en) * | 2013-10-08 | 2017-01-25 | Jatco Ltd | Control device for continuously variable transmission equipped with auxiliary transmission |
CN108138927B (zh) * | 2015-10-30 | 2020-10-23 | 爱信艾达株式会社 | 自动变速器 |
US11465496B2 (en) * | 2019-08-29 | 2022-10-11 | Kawasaki Motors, Ltd. | Power unit of utility vehicle |
CN113685527B (zh) * | 2021-09-07 | 2024-01-26 | 芜湖万里扬变速器有限公司 | 一种纵置无级变速器 |
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CN105190101A (zh) | 2015-12-23 |
DE112014002579T5 (de) | 2016-03-17 |
BR112015028781A2 (pt) | 2017-07-25 |
JPWO2014192753A1 (ja) | 2017-02-23 |
US10030749B2 (en) | 2018-07-24 |
MX2015015991A (es) | 2016-10-26 |
US20160102741A1 (en) | 2016-04-14 |
JP5922843B2 (ja) | 2016-05-24 |
CN105190101B (zh) | 2017-09-22 |
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