WO2016098685A1 - Transmission à variation continue - Google Patents

Transmission à variation continue Download PDF

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Publication number
WO2016098685A1
WO2016098685A1 PCT/JP2015/084731 JP2015084731W WO2016098685A1 WO 2016098685 A1 WO2016098685 A1 WO 2016098685A1 JP 2015084731 W JP2015084731 W JP 2015084731W WO 2016098685 A1 WO2016098685 A1 WO 2016098685A1
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WIPO (PCT)
Prior art keywords
gear
planetary gear
variator
pulley
gear mechanism
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PCT/JP2015/084731
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English (en)
Japanese (ja)
Inventor
俊希 宮島
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本田技研工業株式会社
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Priority to JP2016564820A priority Critical patent/JP6280994B6/ja
Publication of WO2016098685A1 publication Critical patent/WO2016098685A1/fr

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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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/58—Gearings having only two central gears, connected by orbital gears with sets of orbital gears, each consisting of two or more intermeshing orbital gears
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • 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

Definitions

  • the present invention relates to a continuously variable transmission, and more particularly to a continuously variable transmission having a transmission ratio width that reduces the variator weight and transmission loss by reducing the transmission power of a variator using frictional transmission and exceeds the variator transmission ratio width. Is.
  • an input shaft is connected to a variator shaft 1 and an output shaft is connected to a variator shaft 2, and the rotation speed ratio between the variator shaft 1 and the variator shaft 2 is continuously changed.
  • the rotation speed ratio between the input shaft and the output shaft can be varied steplessly.
  • one planetary gear mechanism that restricts the degree of freedom of rotation of three elements (for example, sun gear, ring gear, and carrier) to 2 (for example, rotation and revolution of the planetary gear) is provided, and an element that has an intermediate rotational speed among the three elements Are connected to the input shaft, and the remaining two elements are respectively connected to the two variator shafts, and an engagement mechanism is provided between the two variator shafts and the output shaft, so that the output shaft and the two variator shafts are connected.
  • a continuously variable transmission that selectively engages is known (see, for example, Patent Document 2).
  • one planetary gear mechanism that restricts the degree of freedom of rotation of three elements (for example, sun gear, ring gear, and carrier) to 2 (for example, rotation and revolution of the planetary gear) is provided, and an element that has an intermediate rotational speed among the three elements Is connected to the input shaft, and the other element has two independent engagement mechanisms between the remaining one element and the two variator shafts on the output shaft, and between the two variator shafts and the output shaft.
  • Two independent engaging mechanisms selectively engaging the planetary gear element and the two variator shafts as a drive side, and the variator shaft not engaged with the planetary gear element as the output shaft.
  • a continuously variable transmission that is engaged to be driven is known (see, for example, Patent Document 3).
  • the present invention has been made in view of the above-mentioned problems of the prior art, and its purpose is to reduce the size and weight of the variator and reduce the transmission loss associated with frictional transmission, while limiting the variator. It is an object of the present invention to provide a continuously variable transmission having a speed ratio width exceeding the above.
  • a continuously variable transmission includes a planetary gear mechanism that restricts the number of rotations of four elements to two degrees of freedom.
  • the first and third elements are connected to the two variator axes directly or at a fixed speed ratio, and the second element is connected to the input shaft directly or at a fixed speed ratio.
  • the rotation speed ratio of the variator is changed, the product of the shift ratio width of the first element and the shift ratio width of the fourth element exceeds the shift ratio width of the variator.
  • the shift ratio width of the entire transmission when the output 2 from the second element (7) is selectively taken out from the output shaft (13) can exceed the shift ratio width of the variator. Therefore, by continuously engaging the output 1 and the output 2 with the output shaft (13) via the engagement mechanism, a continuously variable transmission having a speed ratio width exceeding the speed ratio width of the variator as a whole is configured. Is possible.
  • the power that has entered the second element (2) from the end on the speed diagram in the path from the input shaft to the output 1 is partly the third element (6) from the end.
  • the variator shaft 2 (17) via the belt is transmitted to the variator shaft 1 (16) via the belt, the rest is transmitted to the first element (5) from the end, and the divided power is output to the output shaft ( 13), the power that passes through the variator is smaller than the transmission power of the transmission.
  • the power that has entered the second element (2) from the end on the speed diagram in the path from the input shaft to the output 2 is partly the first element (5 ) Is transmitted to the variator shaft 1 (16) via the belt, is transmitted to the variator shaft 2 (17) via the belt, returns from the third (6) element from the end to the planetary gear mechanism, and passes through the planetary gear mechanism. Therefore, the power that passes through the variator can be made smaller than the transmission power of the transmission.
  • the power passing through the variator can always be made smaller than the transmission power of the transmission, so power loss due to friction transmission can be suitably reduced and the size and weight of the variator can be reduced. It becomes.
  • the second feature of the continuously variable transmission includes a planetary gear mechanism that regulates the number of rotations of the four elements to two degrees of freedom, and is the first of the four elements arranged on the speed diagram from the end.
  • the second and third elements are connected to the two axes of the variator, the second element is connected to the input shaft, and the first and fourth elements are engaged with the output shaft via the engagement mechanism, respectively.
  • a specific variator speed ratio generally at the end of the variator gear ratio
  • the output shaft rotation speed at that time becomes equal.
  • a third feature of the continuously variable transmission according to the present invention is that an input shaft (1), a carrier (2), a first pinion (3), a second pinion (4), a sun gear (5), and a first ring gear ( 6) and the planetary gear mechanism (19) composed of the second ring gear (7), the first conical member (16a) and the second conical member which are coaxially integrated with the fifth gear (12) and arranged opposite to each other.
  • a first pulley (16) composed of (16b), a third conical member (17a) and a fourth conical member (17b) which are coaxially integrated with and opposed to the first ring gear (6).
  • the winding diameter determined by the distance between the two conical members and the second pulley (17) It can be engaged by a variator (15) capable of changing a rotation speed ratio according to a ratio of a winding diameter determined by a distance between two conical members, the second ring gear (7), and a first clutch (20).
  • a first gear (8), a second gear (9) meshing with the first gear (8), a third gear (10) coaxially integrated with the sun gear (5), and the third gear (10) and the fourth gear (11) meshing with the fifth gear (12), and the second gear (9) can be engaged with the fourth gear (11) by the second clutch (21). And an output shaft (13) integrated with each other.
  • the output shaft (13) is connected to the sun gear (5), the second ring gear (7), and the first pulley (16) via a gear pair, the gear ratio of the gears.
  • the rotation speed of the output shaft (13) can be determined according to the request of the output destination independently of the rotation speed of the planetary gear mechanism and the variator.
  • the fourth feature of the continuously variable transmission according to the present invention is that the third gear (10) is located on the same axis as the input shaft (1) and closest to the input, then the first gear (8), Next, each mechanism element is arranged in the order of the first clutch (20).
  • the fourth gear (11) is next to the output shaft (13) in the axial direction and closest to the input in the axial direction.
  • the second clutch (21) and then the second gear (9) are arranged.
  • the first clutch (20) and the second clutch (21) are separated from each other in the axial direction with the first gear (8) and the second gear (9) interposed therebetween.
  • the diameters do not interfere with each other, and the outer diameter of the clutch can be easily increased in accordance with the transmission torque.
  • the axial dimension of the clutch can be reduced and the axial dimension of the transmission can be reduced.
  • the fifth feature of the continuously variable transmission according to the present invention is that the second pulley (17) is arranged at a position farthest from the input coaxial with the input shaft (1).
  • a sixth feature of the continuously variable transmission according to the present invention is that the first ring gear (6) or the second pulley (17) is provided in three holes of the fixing member (30) having at least three holes, respectively.
  • the fixing member (30) is fixed to the case (40).
  • a seventh feature of the continuously variable transmission according to the present invention includes a first planetary gear mechanism and a second planetary gear mechanism that restrict the rotation speeds of the three elements to two degrees of freedom, respectively, and the first planetary gear mechanism.
  • Two axes of the variator are coupled to the first element and the third element from the end on the velocity diagram, and the input shaft is coupled to the second element, and the first element and the output
  • An engagement mechanism is provided between the shaft and the second element from the end on the velocity diagram of the second planetary gear mechanism and the third element of the first planetary gear mechanism are coupled;
  • a third element from the end of the second planetary gear mechanism is coupled to the output shaft, and an engagement mechanism is provided between the first element from the end of the second planetary gear mechanism and the input shaft.
  • the planetary gear mechanism that restricts the rotational speed of the four elements to two degrees of freedom is provided by using two sets of planetary gear mechanisms that restrict the rotational speed of the three elements to two degrees of freedom.
  • a function equivalent to the continuously variable transmission can be realized.
  • the power that enters the input shaft from the power source is input to the planetary gear mechanism that restricts the four elements to two degrees of freedom,
  • the variator By performing the shift by the variator, it is possible to provide a shift ratio width in which the transmission power of the variator is always smaller than the transmission power of the transmission and exceeds the shift ratio width of the variator. This significantly reduces the size and weight of the variator and reduces the power loss associated with frictional transmission.
  • the assembly workability is improved by assembling the component parts to the fixing member and then fixing them to the case.
  • FIG. 1 shows the speed change principle of a continuously variable transmission according to the present invention (that is, one of four elements arranged on a speed diagram of a planetary gear mechanism that regulates the number of rotations of four elements to two degrees of freedom from the end.
  • the first and third elements are connected to the two variator axes directly or at a fixed speed ratio, and the second element is connected to the input shaft directly or at a fixed speed ratio.
  • the case where power is taken out from the first element is called output 1
  • the case where power is taken out from the fourth element is called output 2.
  • the vertical axis of the velocity diagram indicates the rotational speed
  • the lateral distance indicates the rotational speed ratio of each element of the planetary gear mechanism.
  • the rotation speed of the first element is called N1
  • the rotation speed of the second element is N2
  • the rotation speed of the third element is N3
  • the rotation speed of the fourth element is N4.
  • the first element from the left is coupled to the variator shaft 1 directly or at a fixed rotational speed ratio
  • the third element is coupled to the variator shaft 2 directly or at a fixed rotational speed ratio.
  • r be the rotation speed ratio of N3 to N1.
  • the circle and line segment of the variator shaft 1 and variator shaft 2 imitate the belt type variator.
  • the large circle indicates the maximum state of the winding diameter
  • the small circle indicates the minimum state of the winding diameter.
  • a line segment shows the state of the wound belt.
  • r takes the maximum value r_max, and the number of rotations of each element is a black circle on the upper right line segment on the speed diagram. expressed.
  • the rotation speeds of the three elements of the planetary gear mechanism at this time are N1_min, N3_min, and N4_min.
  • the variator shift ratio width is r_max / r_min.
  • N1 ⁇ (1 + ⁇ 1) / (r + ⁇ 1) ⁇ ⁇ Nin If formula 6 is substituted into formula 1, formula 7 is obtained.
  • N3 ⁇ r ⁇ (1 + ⁇ 1) / (r + ⁇ 1) ⁇ ⁇ Nin
  • N4 ⁇ r ⁇ (1 + ⁇ 2) + ⁇ 1- ⁇ 2 ⁇ / (r + ⁇ 1) ⁇ Nin
  • Equation 10 (N1_min / N1_max) ⁇ (N4_max / N4_min)> r_max / r_min)
  • Formula 10 ⁇ (1 + ⁇ 1) / (r_min + ⁇ 1) ⁇ / ⁇ (1 + ⁇ 1) / (r_max + ⁇ 1) ⁇ ⁇ [ ⁇ r_max ⁇ (1 + ⁇ 2) + ⁇ 1- ⁇ 2 ⁇ / (r_max + ⁇ 1 )] / [ ⁇ r_min ⁇ (1 + ⁇ 2) + ⁇ 1- ⁇ 2 ⁇ / (r_min + ⁇ 1)]> r_max / r_min If the left side of Formula 10 is arranged, Formula 11 is obtained.
  • Equation 11 ⁇ r_max ⁇ (1 + ⁇ 2) ⁇ ( ⁇ 2 ⁇ 1) ⁇ / ⁇ r_min ⁇ (1 + ⁇ 2) ⁇ ( ⁇ 2 ⁇ 1) ⁇ > r_max / r_min Since N4 is always a positive value, using the fact that the denominator on the left side of Equation 11 is always a positive value, both sides of Equation 11 are multiplied by r_min ⁇ ⁇ r_min ⁇ (1 + ⁇ 2)-( ⁇ 2- ⁇ 1) ⁇ . And Equation 12 is obtained.
  • Formula 12 ( ⁇ 2- ⁇ 1) ⁇ (r_max-r_min)> 0 Since ⁇ 2> ⁇ 1 and r_max> r_min, Expression 12 always holds. Since the equation (9), which is equivalent to the equation (12), always holds, the above speed change principle has been proved.
  • the transmission power of the variator is always smaller than the transmission power of the transmission in the above speed change principle.
  • the torque is obtained.
  • the transmission efficiency of the gears and variator is assumed to be 1.
  • the input torque on the axis of the planetary gear mechanism is Tin
  • the torques that enter the four elements on the planetary gear speed diagram are T1, T2, T3, and T4, respectively. Since it is input to the second element from the left in the velocity diagram, Expression 13 always holds.
  • T2 Tin In the speed diagram of the planetary gear, find the torque when outputting from the first element from the left. From the principle of Choshi, T1 can be expressed by Equation 14.
  • T1 ⁇ 1 / (1 + ⁇ 1) ⁇ Tin
  • T3 can be expressed by Equation 15.
  • Formula 15: T3 -1 / (1 + ⁇ 1) ⁇ Tin T4 is zero.
  • the torque balance of the revolution of the planetary gear is expressed by Equation 16.
  • Formula 16: T1 + T2 + T3 + T4 0
  • the torque balance of rotation of the planetary gear is expressed by Equation 17.
  • T1 T3 ⁇ ⁇ 1 + T4 ⁇ ⁇ 2 Since T1 and T3 are connected by a variator, the torque relationship is expressed by Equation 18.
  • Formula 19: T3 - ⁇ 2 / ( ⁇ 1 + r) ⁇ ⁇ T4 Substituting Equation 19 into Equation 16 and rearranging results in Equation 20.
  • Expression 20: T4 ⁇ [( ⁇ 1 + r) / ⁇ 1- ⁇ 2 + ( ⁇ 2 + 1) ⁇ r ⁇ ] ⁇ Tin Substituting Equation 20 into Equation 19 and rearranging results in Equation 21.
  • Formula 25: P1 r / (r + ⁇ 1) ⁇ P
  • P2 the variator transmission power when output from the fourth element from the left. Since this is the power that comes out of the first element from the left, enters the variator shaft 1 and is transmitted to the variator shaft 2, and enters the third element from the left, P2 is expressed by Equation 26.
  • Equation 26: P2 N3 ⁇ T3 where T3 is Equation 21 When formulas 7 and 21 are substituted into formula 26 and rearranged, formula 27 is obtained.
  • the variator transmission power is smaller than the transmission transmission power.
  • Equation 30 ⁇ r ⁇ ⁇ 2 ⁇ (1 + ⁇ 1) ⁇ / [ ⁇ r + ⁇ 1 ⁇ ⁇ ⁇ 1- ⁇ 2 + (1 + ⁇ 2) ⁇ r ⁇ ] ⁇ P ⁇ P Dividing both sides of Equation 30 by P yields Equation 31.
  • Formula 31 ⁇ r ⁇ ⁇ 2 ⁇ (1 + ⁇ 1) ⁇ / [ ⁇ r + ⁇ 1 ⁇ ⁇ ⁇ 1- ⁇ 2 + (1 + ⁇ 2) ⁇ r ⁇ ] ⁇ 1 Since P2 is always positive and the numerator of Equation 31 is always positive, the denominator of Equation 31 is always positive. If formula 31 is arranged using this, formula 32 will be obtained.
  • Expression 32 r ⁇ ⁇ 2 ⁇ (1 + ⁇ 1) ⁇ r + ⁇ 1 ⁇ ⁇ ⁇ 1- ⁇ 2 + (1 + ⁇ 2) ⁇ r ⁇
  • formula 33 r ⁇ 2 + 2 ⁇ ( ⁇ 1- ⁇ 2) / (1 + ⁇ 2) ⁇ r + ⁇ 1 ⁇ ( ⁇ 1- ⁇ 2) / (1 + ⁇ 2) ⁇ > 0 If the left side of Expression 33 is factored with respect to r, Expression 34 is obtained.
  • Equation 34 is the product of two equations, but the first equation is always positive from Equation 36. If the first expression is deleted from the inequality of Expression 34, Expression 37 is obtained. Formula 37: r + [ ⁇ 1- ⁇ 2- ⁇ 2 ⁇ ( ⁇ 2- ⁇ 1) ⁇ (1 + ⁇ 1) ⁇ ⁇ 0.5)] / (1 + ⁇ 2)> 0 When formula 37 is arranged with respect to r, formula 38 is obtained.
  • Formula 38 r> [( ⁇ 2- ⁇ 1) + ⁇ 2 ⁇ ( ⁇ 2- ⁇ 1) ⁇ (1 + ⁇ 1) ⁇ ⁇ 0.5] / (1 + ⁇ 2) Since the minimum value of r is r_min, the condition that satisfies Expression 38 is Expression 39.
  • formula 42 is obtained.
  • FIG. 2 is a block diagram showing a continuously variable transmission (100) of the present invention.
  • the continuously variable transmission (100) includes an input shaft (1), a carrier (2), a first pinion (3), a second pinion (4), a sun gear (5), a first ring gear (6), and a second gear.
  • a planetary gear mechanism (19) composed of a ring gear (7), and a first conical member (16a) and a second conical member (16b) which are coaxially integrated with and arranged opposite to the fifth gear (12).
  • a first pulley (16) configured, and a third conical member (17a) and a fourth conical member (17b) which are coaxially integrated with and disposed opposite to the first ring gear (6).
  • the winding diameter determined by the above and the two conical parts of the second pulley (17) A variator (15) capable of changing the rotation speed ratio according to the ratio of the winding diameter determined by the distance, and the first gear that can be engaged by the second ring gear (7) and the first clutch (20).
  • the first pinion (3) meshes with the first ring gear (6)
  • the second pinion (4) meshes with the sun gear (5) and the second ring gear (7).
  • the first pinion (3) and the second pinion (4) rotate together.
  • the sun gear (5) which is the first element from the left end, is coupled to the shaft of the first pulley (16) with a rotation speed ratio rg2 ⁇ rg3 (fixed value) and 3
  • the first ring gear (6) as the second element is directly coupled to the rotation shaft of the second pulley (17)
  • the carrier (2) as the second element is directly coupled to the input shaft (1)
  • the sun gear (5) as the first element or the second ring gear (7) as the fourth element is selectively engaged with the output shaft (13) by the second clutch (21) or the first clutch (20). It is configured to be.
  • the continuously variable transmission (100) of the present invention satisfies the above-described speed change principle, and the overall speed ratio width of the continuously variable transmission (100) exceeds the speed ratio width of the variator (15) and the variator transmission power. Becomes smaller than the transmission power of the transmission.
  • the number of teeth of the first pinion (3) and the number of teeth of the second pinion (4) of the planetary gear mechanism are both Zp
  • the number of teeth of the sun gear (5) is Zs
  • the number of teeth of the first ring gear (6) is Zr1
  • the number of teeth of the second ring gear (7) is Zr2.
  • the rotation speed ratio of the second gear (9) to the first gear (8) is rg1
  • the rotation speed ratio of the fourth gear (11) to the third gear (10) is rg2
  • the rotation speed ratio to the fourth gear (11) is Let rg3 be the rotation speed ratio of 5 gears (12).
  • the rotation speed ratio of the second pulley (17) to the first pulley (16) is rb (variator rotation speed ratio).
  • Formula 46: ⁇ 2 Zs / Zr2 r is expressed by Equation 47.
  • Formula 47: r rg2 ⁇ rg3 ⁇ rb If the minimum value in the range of rb is rb_min and the maximum value is rb_max, r_min and r_max are expressed by Equation 48 and Equation 49, respectively.
  • Formula 50 is obtained by substituting Formula 45, Formula 46, and Formula 48 into Formula 39 so that the variator transmission power is always smaller than the transmission power of the transmission.
  • the number of teeth of each gear is determined so as to satisfy Equation 50.
  • the power flow when the first clutch (20) is engaged is as shown by the thick line in FIG.
  • the second ring gear (7) is coupled to the output shaft (13) by a gear pair of the first gear (8) and the second gear (9) having a rotation speed ratio rg1.
  • Part of the power from the input shaft (1) is transmitted to the sun gear (5), and the third gear (10), the fourth gear (11), the fifth gear (12), the first pulley (16), and the second gear.
  • R1 ⁇ rb ⁇ rg2 ⁇ rg3 ⁇ Zr1 ⁇ (Zr2 + Zs) + Zs ⁇ (Zr2-Zr1) ⁇ / (rb ⁇ rg2 ⁇ rg3 ⁇ Zr1 ⁇ Zr2 + Zs ⁇ Zr2) ⁇ rg1
  • FIG. 4 is an explanatory diagram showing a speed diagram of the planetary gear mechanism according to the present invention and a power flow specialized for each element when the first clutch is engaged.
  • the rotational speed ratio rb of the second pulley (17) to the first pulley (16) is changed from rb_min to rb_max
  • the rotational speed of the sun gear (5) N1 changes from N1_min to N1_max
  • the rotation speed N3 of the first ring gear (6) changes from N3_min to N3_max
  • the rotation speed N4 of the second ring gear (7) changes from N4_min to N4_max.
  • the transmission power is divided into two in the carrier (2), and a part thereof does not pass through the variator, but is output directly from the second ring gear (7) to the output shaft (13), and the rest passes through the variator and passes through the first ring gear.
  • the motive power is output to the output shaft (13) while merging with the power flow described on the left, whereby the transmission power of the variator can always be made smaller than the transmission power of the transmission.
  • FIG. 6 is an explanatory diagram showing a velocity diagram of the planetary gear mechanism according to the present invention and a power flow specialized for each element when the second clutch is engaged.
  • the variator speed ratio rb is changed from rb_max to rb_min after switching
  • the speed N1 of the sun gear (5) is changed from N1_max to N1_min
  • the speed N3 of the first ring gear (6) is changed from N3_max to N3_min
  • the second ring gear changes from N4_max to N4_min, respectively, and the speed diagram as a whole changes continuously from the solid line to the dotted line around the carrier (2) according to the rotational speed ratio rb of the variator.
  • the transmission power is divided into two in the carrier (2), and a part thereof does not pass through the variator and is output directly from the sun gear (5) to the output shaft (13), and the rest passes through the variator and passes through the fourth gear (11 ) And output to the output shaft (13) while merging with the power flow shown on the left, it can be seen that the transmission power of the variator is always smaller than the transmission power of the transmission.
  • R1 and R2 when the rotational speed ratio of the second pulley (17) to the first pulley (16) is rb_min are R1_min and R2_min, respectively, and the rotational speed ratio of the second pulley (17) to the first pulley (16) If R1 and R2 when rb_max is R1_max and R2_max, respectively, the magnitude relationship between them is expressed by Equation 57.
  • R1_min ⁇ R1_max R2_max ⁇ R2_min
  • the range of the speed ratio of the output shaft (13) to the input shaft (1) of the continuously variable transmission (100) is between R1_min and R2_min, which exceeds the variator speed ratio width as described above. It is.
  • Equation 58 R1_min ⁇ R ⁇ R2_min
  • R 59 the first clutch (20) is engaged.
  • R 60 the second clutch (21) is engaged.
  • Formula 61 either one or both of the first clutch and the second clutch are engaged.
  • rb ⁇ rg1 ⁇ Zs ⁇ (Zr2-Zr1) -R ⁇ Zs ⁇ Zr2 ⁇ / ⁇ R ⁇ rg2 ⁇ rg3 ⁇ Zr1 ⁇ Zr2-rg1 ⁇ rg2 ⁇ rg3 ⁇ Zr1 ⁇ (Zr2 + Zs) ⁇
  • the desired speed ratio can be obtained by determining the variator ratio as shown in Equation 63.
  • FIG. 7 is a velocity diagram according to a modification of the above-described speed change principle of the present invention.
  • a planetary gear mechanism that restricts the rotational speed of the four elements represented by the velocity diagram of FIG. 1 to two degrees of freedom.
  • the three elements are replaced by two sets of planetary gear mechanisms that regulate to two degrees of freedom.
  • the third element of the first planetary gear mechanism and the second element of the second planetary gear mechanism are coupled, and the second element of the first planetary gear mechanism and the second planetary gear mechanism are combined.
  • the first element of the second planetary gear mechanism is coupled to the output shaft via the gear pair.
  • FIG. 8 is a graph comparing the rotational speed ratio of the variator of the transmission in the continuously variable transmission (100) of the present invention with the conventional example.
  • the transmission ratio width of the transmission is wide while the variator transmission ratio width is the same as that of the conventional example.
  • FIG. 9 is a graph comparing the pulley rotation speed in the continuously variable transmission (100) of the present invention with that of the conventional example.
  • the pulley 1 is on the driving side and the pulley 2 is on the driven side. Both are the rotation speeds of the pulley with the rotation speed of the input shaft being constant.
  • the maximum rotation speed N ′ of the pulley is larger than the maximum rotation speed Nmax of the conventional example of FIG. 9A. It turns out that max is small.
  • FIG. 10 is a graph comparing the pulley torque in the continuously variable transmission (100) of the present invention with that of the conventional example.
  • the pulley 1 is on the driving side and the pulley 2 is on the driven side. Both are the rotational speeds of the pulley with the input shaft torque being constant.
  • the maximum torque T'max of the pulley is smaller than the maximum torque Tmax of the conventional example of FIG. 10 (a). I understand that.
  • FIG. 11 is a graph comparing the pulley transmission power in the continuously variable transmission (100) of the present invention with that of the conventional example.
  • the pulley 1 is on the driving side and the pulley 2 is on the driven side. Both are the transmission power of the pulley with the power Pin from the input shaft being constant, and the pulley transmission power is always equal to the power Pin from the input shaft in the conventional example of FIG. 11 (a), but in FIG. 11 (b). In the present invention, it is always smaller than the power Pin from the input shaft.
  • the continuously variable transmission according to the present invention is not limited to the above-described embodiment (the continuously variable transmission (100)), and various design changes may be made without changing the gist of the technical features of the present invention. Is included.
  • planetary gear mechanism (19) that restricts the rotational speed of four elements to two degrees of freedom
  • planetary gear mechanisms according to the first to thirteenth modifications shown in FIGS. 12 to 24 are provided. . A brief description is given below.
  • FIG. 12 is an explanatory diagram showing a planetary gear mechanism (19A) according to Modification 1 of the continuously variable transmission of the present invention and its velocity diagram.
  • This planetary gear mechanism (19A) is modified so that the sun gear (5) meshes with the first pinion (3) in the planetary gear mechanism (19).
  • each of the first to fourth elements from the end arranged on the velocity diagram is the same as the planetary gear mechanism (19).
  • FIG. 13 is an explanatory view showing a planetary gear mechanism (19B) according to Modification 2 of the continuously variable transmission of the present invention and its velocity diagram.
  • This planetary gear mechanism (19B) is obtained by reversing the relationship between the sun gear and the ring gear and the left and right of the planetary gear mechanism (19A).
  • the first gear (8) is disposed on the second pulley (17) side, and the first sun gear (5) and the second pulley (17) are coupled, and the ring gear (6) and the third gear (10) are coupled.
  • a second sun gear (5 ′) is provided in place of the second ring gear (7), which corresponds to a combination of the second sun gear (5 ′) and the first gear (8).
  • the ring gear (6) and the first sun gear (5) are coupled to the first pulley (16) and the second pulley (17), respectively, and the second sun gear (5 ′) is connected via the first clutch (20).
  • the first gear (8) To the first gear (8). Therefore, the first element from the left end on the speed diagram is the ring gear (6), the second element is the carrier (2), the third element is the first sun gear (5), and the fourth element is the second sun gear. (5 ').
  • FIG. 14 is an explanatory view showing a planetary gear mechanism (19C) according to Modification 3 of the continuously variable transmission of the present invention and its velocity diagram.
  • the planetary gear mechanism (19C) is modified so that the ring gear (6) meshes with the second pinion (4) in the planetary gear mechanism (19B).
  • the planetary gear mechanism (19B) is the same as the said planetary gear mechanism (19B).
  • each of the first to fourth elements from the end arranged on the velocity diagram is the same as the planetary gear mechanism (19B).
  • the planetary gear mechanism that restricts the rotational speed of the four elements to two degrees of freedom is controlled by the planetary gear mechanism 2 that restricts the rotational speed of the three elements to two degrees of freedom.
  • This is an example constructed by a set of planetary gear mechanisms.
  • the planetary gear mechanism including the carrier (2) coupled to the input shaft (1) for the two sets of planetary gear mechanisms is referred to as a first planetary gear mechanism, and the other planetary gear mechanisms are referred to as second planetary gear mechanisms. I will call it.
  • FIG. 15 is an explanatory diagram showing a planetary gear mechanism (19D) according to Modification 4 of the continuously variable transmission of the present invention and its velocity diagram.
  • this planetary gear mechanism (19D) the first of the two sets of the first planetary gear mechanism (19D-1) and the second planetary gear mechanism (19D-2) restricts the rotational speed of the three elements to two degrees of freedom.
  • the carrier (2) and the second sun gear (5 ′) and the first ring gear (6) and the second carrier (2 ′) the rotational speeds of the four elements satisfying the speed change principle are reduced to two.
  • a planetary gear mechanism that regulates the degree of freedom is established.
  • the first sun gear (5) which is the first element arranged on the velocity diagram
  • the first ring gear (6), the first pulley (16), and the second pulley (17) which are the third element, respectively.
  • the first carrier (2) that is the second element and the input shaft (1) are coupled, and the first sun gear (5) that is the first element and the second ring gear that is the fourth element.
  • (7) is configured to be selectively engageable with the output shaft (13) via the second clutch (21) and the first clutch (20).
  • FIG. 16 is an explanatory diagram showing a planetary gear mechanism (19E) according to Modification 5 of the continuously variable transmission of the present invention and its velocity diagram.
  • the planetary gear mechanism (19E) connects the first carrier (2) and the second sun gear (5 ′) via the first clutch (20) in the planetary gear mechanism (19D), and outputs an output 2. This corresponds to a direct coupling of the first gear (8) and the second ring gear (7) for removal. Therefore, when the first clutch (20) is engaged to change the rotational speed ratio of the variator, the planetary gear mechanism (19E) restricts the rotational speed of the four elements to two degrees of freedom on the speed diagram.
  • FIG. 17 is an explanatory diagram showing a planetary gear mechanism (19F) according to Modification 6 of the continuously variable transmission of the present invention and its velocity diagram.
  • this planetary gear mechanism (19F) similarly to the planetary gear mechanism (19D), two sets of the first planetary gear mechanism (19F-1) and the second one that restrict the rotation speed of the three elements to two degrees of freedom.
  • the first carrier (2) and the second sun gear (5 ′), and the first ring gear (6) and the second carrier (2 ′) are coupled to each other, whereby the above-described speed change principle is achieved.
  • a planetary gear mechanism that restricts the rotational speeds of the four satisfactory elements to two degrees of freedom is constructed.
  • the second planetary gear mechanism (19F-2) is located on the input side
  • the first planetary gear mechanism (19F-1) is located on the second pulley (17) side. Yes.
  • FIG. 18 is an explanatory diagram showing a planetary gear mechanism (19G) according to Modification 7 of the continuously variable transmission of the present invention and its velocity diagram.
  • the planetary gear mechanism (19G) connects the first carrier (2) and the second sun gear (5 ′) via the first clutch (20) in the planetary gear mechanism (19F), and outputs an output 2. This corresponds to a direct coupling of the first gear (8) and the second ring gear (7) for removal. Therefore, when engaging the first clutch (20) and changing the rotation speed ratio of the variator, the planetary gear mechanism (19G) restricts the rotation speed of the four elements to two degrees of freedom on the speed diagram.
  • FIG. 19 is an explanatory diagram showing a planetary gear mechanism (19H) according to Modification 8 of the continuously variable transmission of the present invention and its velocity diagram.
  • the second planetary gear mechanism (19H-2) that restricts the number of rotations of the three elements to two degrees of freedom is located on the input side in the same manner as the planetary gear mechanism (19F).
  • the first planetary gear mechanism (19H-1) is located on the second pulley (17) side.
  • the first carrier (2) of the first planetary gear mechanism (19H-1) and the second ring gear (7) of the second planetary gear mechanism (19H-2) are coupled, and
  • a planetary gear mechanism is constructed that restricts the rotational speeds of the four elements that satisfy the above-mentioned speed change principle to two degrees of freedom.
  • output 2 is output from the second sun gear (5 ′).
  • the fourth element from the left end arranged on the velocity diagram is the second sun gear (5 ′).
  • FIG. 20 is an explanatory diagram showing a planetary gear mechanism (19I) according to Modification 9 of the continuously variable transmission of the present invention and its velocity diagram.
  • This planetary gear mechanism (19I) is obtained by inverting the relationship between the sun gear and the ring gear and the left and right of the planetary gear mechanism (19H).
  • the first gear (8) is disposed on the second pulley (17) side, and the first sun gear (5) and the second pulley (17) are coupled, and the first ring gear (6) and the third gear (10).
  • the first ring gear (6) and the first sun gear (5) are coupled to the first pulley (16) and the second pulley (17), respectively, and the second sun gear (5 ′) is coupled to the first clutch (20). And is coupled to the first gear (8). Therefore, the first element from the left end on the speed diagram is the first ring gear (6), the second element is the first carrier (2), the third element is the first sun gear (5), and the fourth element. Becomes the second sun gear (5 ').
  • FIG. 21 is an explanatory diagram showing a planetary gear mechanism (19J) according to Modification 10 of the continuously variable transmission of the present invention and its velocity diagram.
  • the first carrier (2) and the second ring gear (7) are coupled in the planetary gear mechanism (19H), and the first sun gear (5) and the second carrier (2 ′) are connected.
  • the first sun gear (5) and the first ring gear (6) are connected to the second pulley (17) and the first pulley (16). Therefore, unlike the planetary gear mechanism (19H), the first element from the left end arranged on the velocity diagram is the first ring gear (6), and the third element is the first sun gear (5).
  • FIG. 22 is an explanatory diagram showing a planetary gear mechanism (19K) according to Modification 11 of the continuously variable transmission of the present invention and its velocity diagram.
  • the first carrier (2) and the second sun gear (5 ′) are coupled to the planetary gear mechanism (19I), and the first sun gear (5) and the second carrier (2 ′). Is coupled to the first sun gear (5) and the first ring gear (6), and the second pulley (17) and the first pulley (16). Therefore, unlike the planetary gear mechanism (19I), the third element from the left end arranged on the velocity diagram is the second ring gear (7).
  • FIG. 23 is an explanatory diagram showing a planetary gear mechanism (19L) according to Modification 12 of the continuously variable transmission of the present invention and its velocity diagram.
  • the planetary gear mechanism (19L) connects the first carrier (2) and the second sun gear (5 ′) via the first clutch (20) in the planetary gear mechanism (19K) and outputs the output 2. This corresponds to a direct coupling of the first gear (8) and the second ring gear (7) for removal. Therefore, when the first clutch (20) is engaged to change the rotation speed ratio of the variator, the planetary gear mechanism (19L) on the speed diagram restricts the rotation speed of the four elements to two degrees of freedom.
  • the operation is similar to that of the planetary gear mechanism (19K), and output 2 is output from the second ring gear (7), which is the fourth element on the velocity diagram, to the output shaft (13).
  • the first planetary gear mechanism (19L-1) is the second element on the speed diagram, the first carrier (2).
  • the second planetary gear mechanism (19L-2) operates around the rotation speed of the second carrier (2 ′), which is the third element on the speed diagram, and the output 1 is the speed.
  • the first ring gear (6) which is the first element on the diagram, is output to the output shaft (13).
  • FIG. 24 is an explanatory view showing a planetary gear mechanism (19M) according to Modification 13 of the continuously variable transmission of the present invention and its velocity diagram.
  • This planetary gear mechanism (19M) like the planetary gear mechanism (19B, 19C), is provided with two sun gears (5, 5 ') for one ring gear (6) and satisfies the above-mentioned speed change principle.
  • the first pinion (3) and the second pinion (4) that can rotate and have different gear pitch circle diameters are coaxially integrated, and the first sun gear (5) and the first pinion are integrated. (3) meshes, and the second sun gear (5 ') and the second pinion (4) mesh.
  • the first pinion (3 ′) and the second pinion (4 ′) that can rotate and have different axial lengths are formed as a gear pair, and the first sun gear ( 5) and the first pinion (3 ′) mesh, the second sun gear (5 ′) and the second pinion (4 ′) mesh, and the first pinion (3 ′) and the second pinion (4 ′) mesh.
  • the first to fourth elements counted from the ends arranged on the velocity diagram are respectively the first sun gear (5), the first carrier (2), the first ring gear (6), and the second sun gear (5 ′).

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne une transmission à variation continue (100), dans laquelle une perte de puissance, qui se produit avec une transmission par frottement, est réduite par réduction de la puissance transmise par un variateur, et les dimensions et le poids d'un variateur (15) sont réduits, la transmission à variation continue ayant une plage de rapport de transmission qui dépasse la plage de rapport de transmission du variateur. Le rapport de vitesse de rotation du variateur (15) est changé afin de changer de vitesses, tandis que, dans un mécanisme d'engrenage planétaire (19) dans lequel quatre éléments sont régulés à deux degrés de liberté, un arbre d'entrée (1) est couplé au deuxième élément à partir de l'extrémité, les premier et troisième éléments à partir de l'extrémité sont couplés à deux arbres du variateur (15), et un arbre de sortie (13) vient en prise de façon sélective avec les premier et quatrième éléments à partir de l'extrémité.
PCT/JP2015/084731 2014-12-18 2015-12-10 Transmission à variation continue WO2016098685A1 (fr)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108386538A (zh) * 2018-03-25 2018-08-10 大连碧蓝节能环保科技有限公司 行星齿轮无级变速减速器

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58109751A (ja) * 1981-12-01 1983-06-30 テイツセン・インドウストリ−・アクチエンゲゼルシヤフト 入力側の動力分岐部を有する静液圧機械的調整連結変速機
JP2006329338A (ja) * 2005-05-26 2006-12-07 Nissan Motor Co Ltd 分流式無段変速機
JP2006327570A (ja) * 2005-04-28 2006-12-07 Toyota Central Res & Dev Lab Inc 動力伝達システム
JP2012202473A (ja) * 2011-03-25 2012-10-22 Jatco Ltd 自動変速機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58109751A (ja) * 1981-12-01 1983-06-30 テイツセン・インドウストリ−・アクチエンゲゼルシヤフト 入力側の動力分岐部を有する静液圧機械的調整連結変速機
JP2006327570A (ja) * 2005-04-28 2006-12-07 Toyota Central Res & Dev Lab Inc 動力伝達システム
JP2006329338A (ja) * 2005-05-26 2006-12-07 Nissan Motor Co Ltd 分流式無段変速機
JP2012202473A (ja) * 2011-03-25 2012-10-22 Jatco Ltd 自動変速機

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108386538A (zh) * 2018-03-25 2018-08-10 大连碧蓝节能环保科技有限公司 行星齿轮无级变速减速器

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