WO2016098685A1 - Stepless transmission - Google Patents

Stepless transmission Download PDF

Info

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
Authority
WO
WIPO (PCT)
Prior art keywords
gear
planetary gear
variator
pulley
gear mechanism
Prior art date
Application number
PCT/JP2015/084731
Other languages
French (fr)
Japanese (ja)
Inventor
俊希 宮島
Original Assignee
本田技研工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 本田技研工業株式会社 filed Critical 本田技研工業株式会社
Priority to JP2016564820A priority Critical patent/JP6280994B6/en
Publication of WO2016098685A1 publication Critical patent/WO2016098685A1/en

Links

Images

Classifications

    • 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 ′).

Landscapes

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

Abstract

Provided is a stepless transmission (100) in which power loss that occurs with frictional transmission is reduced by reducing the power transmitted by a variator, and the dimensions and weight of a variator (15) are reduced, the stepless transmission having a transmission ratio range that exceeds the transmission ratio range of the variator. The rotational speed ratio of the variator (15) is changed to shift gears while, in a planetary gear mechanism (19) in which four elements are regulated to two degrees of freedom, an input shaft (1) is coupled with the second element from the end, the first and third elements from the end are coupled with two shafts of the variator (15), and an output shaft (13) is selectively engaged with the first and fourth elements from the end.

Description

無段変速機Continuously variable transmission
　本発明は無段変速機に関し、より詳細には摩擦伝動を用いるバリエータの伝達動力を減ずることによりバリエータ重量と伝達損失を減じ、かつバリエータ変速レシオ幅を超える変速レシオ幅を有する無段変速機に関するものである。  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.
　従来の摩擦伝動を用いる無段変速機は、入力軸をバリエータ軸１に、出力軸をバリエータ軸２に連結しておき、バリエータ軸１とバリエータ軸２の間の回転数比を無段階に変えることにより、入力軸と出力軸の回転数比を無段階に可変するものがある。 In a conventional continuously variable transmission using friction transmission, 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. In some cases, the rotation speed ratio between the input shaft and the output shaft can be varied steplessly.
　ところで、２つのバリエータ軸と入力軸との間に独立した２つの係合機構を備え、また２つのバリエータ軸と出力軸との間に独立した２つの係合機構を備えてあり、入力軸と２つのバリエータ軸を選択的に係合して駆動側とするとともに入力軸と係合しない方のバリエータ軸を出力軸と係合して従動側とする無段変速機が知られている（たとえば、特許文献１を参照）。 By the way, two independent engagement mechanisms are provided between the two variator shafts and the input shaft, and two independent engagement mechanisms are provided between the two variator shafts and the output shaft. 2. Description of the Related Art A continuously variable transmission is known in which two variator shafts are selectively engaged to drive and a variator shaft not engaged with an input shaft is engaged with an output shaft to be driven (for example, , See Patent Document 1).
　また、３つの要素（たとえばサンギヤ、リングギヤ、キャリア）の回転自由度を２（たとえば遊星歯車の自転と公転）に制限する遊星歯車機構を１つ備え、３つの要素のうち中間回転数となる要素を入力軸に結合し、残りの２つの要素はそれぞれ２つのバリエータ軸に結合してあり、２つのバリエータ軸と出力軸との間に係合機構を備えて、出力軸と２つのバリエータ軸を選択的に係合する無段変速機が知られている（たとえば、特許文献２を参照）。 In addition, 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).
　また、３つの要素（たとえばサンギヤ、リングギヤ、キャリア）の回転自由度を２（たとえば遊星歯車の自転と公転）に制限する遊星歯車機構を１つ備え、３つの要素のうち中間回転数となる要素を入力軸に結合し、もう１つの要素は出力軸に、残り１つの要素と２つのバリエータ軸との間に独立した２つの係合機構を備え、また２つのバリエータ軸と出力軸との間に独立した２つの係合機構を備えてあり、遊星歯車要素と２つのバリエータ軸を選択的に係合して駆動側とするとともに、遊星歯車要素と係合しない方のバリエータ軸を出力軸と係合して従動側とする無段変速機が知られている（たとえば、特許文献３を参照）。 In addition, 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).
特開平７－２９３６６３号公報JP 7-293663 A 特開２００６－３２９３３８号公報JP 2006-329338 A 米国特許第５６４３１３１号公報US Pat. No. 5,643,131
　従来の無段変速機では、変速機の伝達動力の全てがバリエータに入力され、摩擦伝動により出力軸に伝達されるため、伝達損失が増すという問題があった。
　また、伝達動力がすべてバリエータを通過するため伝達動力に応じた強度のバリエータが必要となり、伝達動力を大きくするとバリエータの寸法・重量が増大してしまうという問題があった。
　また、変速機の変速レシオ幅はバリエータの変速レシオ幅に等しいため、変速機の変速レシオ幅はバリエータの変速レシオ幅の制約を受ける。ベルト式又はチェーン式バリエータでは、変速レシオ幅を広げるためにプーリーの巻き掛け径の最大値を大きくするとプーリーの寸法と重量が増大する。またプーリーの巻き掛け径の最小値を小さくするとベルト又はチェーンにかかる荷重が増大する。他の方式においても同様であり、変速機の変速レシオ幅拡大には構造上の限界があるという問題があった。 In the conventional continuously variable transmission, since all of the transmission power of the transmission is input to the variator and transmitted to the output shaft by friction transmission, there is a problem that transmission loss increases.
Further, since all of the transmission power passes through the variator, a variator having a strength corresponding to the transmission power is required. When the transmission power is increased, the size and weight of the variator increase.
Further, since the transmission ratio width of the transmission is equal to the transmission ratio width of the variator, the transmission ratio width of the transmission is restricted by the transmission ratio width of the variator. In the belt-type or chain-type variator, the size and weight of the pulley increase if the maximum value of the pulley winding diameter is increased in order to widen the transmission ratio width. Further, if the minimum value of the pulley winding diameter is reduced, the load applied to the belt or chain increases. The same applies to other systems, and there is a problem in that there is a structural limit in increasing the transmission ratio width of the transmission.
　また、上記特許文献３に記載されている無段変速機では、上記３つの問題点は解決するものの、バリエータに加えて４つの係合機構と１つの遊星歯車機構を備える必要があることから、変速機全体の寸法・重量が大きくなってしまうという問題があった。 Further, in the continuously variable transmission described in Patent Document 3, although the above three problems are solved, it is necessary to include four engagement mechanisms and one planetary gear mechanism in addition to the variator. There was a problem that the overall size and weight of the transmission would increase.
　そこで、本発明は、上記従来技術の問題点に鑑み成されたものであり、その目的は、バリエータの寸法・重量を軽減して、摩擦伝動に伴う伝達損失を削減しながら、バリエータの制約を超える変速レシオ幅を有する無段変速機を提供することにある。 Therefore, 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.
　上記目的を達成するための本発明の無段変速機は、４つの要素の回転数を２つの自由度に規制する遊星歯車機構の，速度線図上に並ぶ４つの要素のうち，端から１番目の要素及び３番目の要素をバリエータの２つの軸と直接または固定された回転数比で結合しておき，２番目の要素を入力軸と直接または固定された回転数比で結合しておき，バリエータの回転数比を変えると１番目の要素の変速レシオ幅と４番目の要素の変速レシオ幅の積が，バリエータの変速レシオ幅を上回ることを特徴とする。 In order to achieve the above object, a continuously variable transmission according to the present invention 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. When 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.
　従って詳細については後述するが、４つの要素の回転数を２つの自由度に規制する上記遊星歯車機構の速度線図上の端から１番目の要素（５）からの出力１と，端から４番目の要素（７）からの出力２とを選択的に出力軸（１３）から取り出す時の変速機全体の変速レシオ幅はバリエータの変速レシオ幅を上回ることが可能となる。従って、出力１と出力２を係合機構を介して選択的に出力軸（１３）に係合することにより，全体としてバリエータの変速レシオ幅を上回る変速レシオ幅の無段変速機を構成することが可能となる。 Therefore, as will be described in detail later, the output 1 from the first element (5) on the velocity diagram of the planetary gear mechanism that restricts the rotational speed of the four elements to two degrees of freedom, and 4 from the end. 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.
　また上記無段変速機においては入力軸から出力１への経路において，速度線図上の端から２番目の要素（２）に入った動力は，一部が端から３番目の要素（６）を経由してバリエータ軸２（１７）に伝達されベルトを介してバリエータ軸１（１６）に伝達され，残りは端から１番目の要素（５）に伝達され，分割された動力は出力軸（１３）で合流して出力されるから，バリエータを通過する動力は変速機の伝達動力より小さくなる。 In the continuously variable 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 1 is partly the third element (6) from the end. Is transmitted to 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.
　さらに、上記無段変速機においては入力軸から出力２への経路において，速度線図上の端から２番目の要素（２）に入った動力は，一部が端から１番目の要素（５）を経由してバリエータ軸１（１６）に伝達されベルトを介してバリエータ軸２（１７）に伝達されて端から３番目（６）の要素から遊星歯車機構へ戻って遊星歯車機構内部を経由する動力と合流して端から４番目の要素（７）から出力されるから，バリエータを通過する動力を変速機の伝達動力より小さくすることができる。 Further, in the continuously variable 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.
　このように，バリエータを通過する動力を変速機の伝達動力より常に小さくすることができるため，摩擦伝動による動力損失を好適に低減することができ，かつバリエータの寸法・重量を小さくすることが可能となる。 In this way, 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.
　本発明の無段変速機の第２の特徴は，４つの要素の回転数を２つの自由度に規制する遊星歯車機構を備え，速度線図上に並ぶ４つの要素のうち，端から１番目の要素と３番目の要素にバリエータの２つの軸が結合され，２番目の要素に入力軸が結合され，１番目の要素と４番目の要素は係合機構を介してそれぞれ出力軸と係合することができ，かつ特定のバリエータの回転数比（一般的にはバリエータ変速レシオ幅の端）で，１番目の要素と係合したときの出力軸回転数と４番目の要素と係合したときの出力軸回転数が等しくなることである。 The second feature of the continuously variable transmission according to the present invention 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. And at a specific variator speed ratio (generally at the end of the variator gear ratio), the output shaft speed when engaged with the first element and the fourth element engaged. The output shaft rotation speed at that time becomes equal.
　上記構成では，一方の係合要素からもう一方の係合要素へ切り替えを行う際に，特定のバリエータの回転数比で切り替えれば，切り替えに際して各要素の回転数は変わらないから，それぞれの係合状態の間に変速比の継ぎ目はなく，かつ変速機の変速レシオ幅をバリエータ変速レシオ幅より大きくとりつつ，バリエータの寸法・重量を小さくすることが可能となる。 In the above configuration, when switching from one engaging element to the other engaging element, if the switching is performed at a specific variator rotational speed ratio, the rotational speed of each element does not change during switching. It is possible to reduce the size and weight of the variator while keeping the transmission ratio seamless between the states and making the transmission ratio width larger than the variator transmission ratio width.
　本発明に係る無段変速機の第３の特徴は，入力軸（１）と，キャリア（２）と第１ピニオン（３）と第２ピニオン（４）とサンギヤ（５）と第１リングギヤ（６）と第２リングギヤ（７）で構成される遊星歯車機構（１９）と，第５ギヤ（１２）と同軸上に一体化され対向配置された第１円錐部材（１６a）と第２円錐部材(１６b)とで構成される第１プーリー（１６）と，前記第１リングギヤ（６）と同軸上に一体化され対向配置された第３円錐部材（１７a）と第４円錐部材（１７b）とで構成される第２プーリー（１７）と，前記第１プーリー（１６）と前記第２プーリー（１７）に巻き掛けられたベルト（１８）とから構成され，前記第１プーリー（１６）の２つの円錐部材の距離により定まる巻き掛け径と前記第２プーリー（１７）の２つの円錐部材の距離により定まる巻き掛け径の比に応じて回転数比を変えることができるバリエータ（１５）と，前記第２リングギヤ（７）と第１クラッチ（２０）により係合することができる第１ギヤ（８）と，前記第１ギヤ（８）とかみ合う第２ギヤ（９）と，前記サンギヤ（５）と同軸上に一体化された第３ギヤ（１０）と，前記第３ギヤ（１０）及び前記第５ギヤ（１２）とかみ合う第４ギヤ（１１）と，第２クラッチ（２１）により前記第４ギヤ（１１）と係合することができかつ前記第２ギヤ（９）と一体化された出力軸（１３）とから構成されていることである。 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). A first pulley (16), a belt (18) wound around the first pulley (16) and the second pulley (17), and two of the first pulley (16). 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.
　上記構成では，前記出力軸（１３）は前記サンギヤ（５）、前記第２リングギヤ（７）及び前記第１プーリー（１６）と歯車対を介してそれぞれ連結されているから，歯車の歯数比を調整すれば，遊星歯車機構及びバリエータの回転数とは独立に，出力先の要求に応じて前記出力軸（１３）の回転数を決めることが可能となる。 In the above configuration, since 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. By adjusting, 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.
　本発明に係る無段変速機の第４の特徴は，前記入力軸（１）と同軸上に最も入力に近い場所に前記第３ギヤ（１０），次に前記第１ギヤ（８），その次に前記第１クラッチ（２０）の順に各機構要素が配置されており，前記出力軸（１３）と同軸上に軸方向で最も入力に近い場所に前記第４ギヤ（１１），次に前記第２クラッチ（２１），その次に前記第２ギヤ（９）が配置されていることである。 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.
　上記構成では，前記第１クラッチ（２０）と前記第２クラッチ（２１）は前記第１ギヤ（８）および前記第２ギヤ（９）を挟んで軸方向に離れているから２つのクラッチの外径同士は干渉せず，伝達トルクに応じたクラッチ外径の拡大が容易となり結果としてクラッチの軸方向の寸法を小さくして変速機の軸方向寸法を小さくすることが可能となる。 In the above configuration, 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. As a result, the axial dimension of the clutch can be reduced and the axial dimension of the transmission can be reduced.
　本発明に係る無段変速機の第５の特徴は，前記入力軸（１）と同軸上の入力から最も遠い場所に第２プーリー（１７）が配置されていることである。 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).
　上記構成では，前記第２プーリー（１７）は同軸配置された要素の端に位置するから，前記第２プーリー（１７）を油圧により作動させる際に，軸端から容易に作動油を供給することが可能となる。 In the above configuration, since the second pulley (17) is located at the end of the coaxially arranged element, when the second pulley (17) is hydraulically operated, hydraulic oil is easily supplied from the shaft end. Is possible.
　本発明に係る無段変速機の第６の特徴は，少なくとも３つの穴があけられた固定部材（３０）の３つの穴に，それぞれ前記第１リングギヤ（６）又は前記第２プーリー（１７）を支持する第１軸受と前記出力軸（１３）の端部を支持する第２軸受と前記第５ギヤ（１２）又は第１プーリー（１６）を支持する第３軸受が固定されており，かつ前記固定部材（３０）がケース（４０）に固定されていることである． 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. A first bearing for supporting the second shaft, a second bearing for supporting the end of the output shaft (13), and a third bearing for supporting the fifth gear (12) or the first pulley (16), and The fixing member (30) is fixed to the case (40).
　上記構成によれば，変速機を構成する部品をあらかじめ前記固定部材（３０）に組み付けておき，これを前記ケース（４０）へ固定することにより組立性が向上する。 According to the above configuration, assembling is improved by previously assembling the parts constituting the transmission to the fixing member (30) and fixing the parts to the case (40).
　本発明に係る無段変速機の第７の特徴は、３つの要素の回転数を２つの自由度にそれぞれ規制する第１遊星歯車機構及び第２遊星歯車機構を備え，該第１遊星歯車機構の速度線図上で端から１番目の要素と３番目の要素に前記バリエータの２つの軸が結合され，２番目の要素に前記入力軸が結合されており，前記１番目の要素と前記出力軸との間に係合機構を備えており，前記第２遊星歯車機構の速度線図上で端から２番目の要素と前記第１遊星歯車機構の前記３番目の要素が結合されており，前記第２遊星歯車機構の端から３番目の要素は前記出力軸と結合されており，該第２遊星歯車機構の端から１番目の要素と前記入力軸との間に係合機構を備えており，２つの係合機構を選択的に係合することができることである。 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. Thus, the two engagement mechanisms can be selectively engaged.
　上記構成によれば、３つの要素の回転数を２つの自由度に規制する遊星歯車機構を２組用いることにより、４つの要素の回転数を２つの自由度に規制する遊星歯車機構を備えた上記無段変速機と同等の機能を実現することが可能となる。 According to the above configuration, 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.
　本発明の無段変速機によれば，摩擦伝動を用いた無段変速機において，動力源から入力軸に入る動力を４つの要素を２つの自由度に規制する遊星歯車機構に入力して，バリエータによる変速を行うことにより，バリエータの伝達動力が変速機の伝達動力より常に小さくかつバリエータの変速レシオ幅を上回る変速レシオ幅を付与することが可能となる。これにより，バリエータの寸法・重量は著しく軽減され，摩擦伝動に伴う動力損失は小さくなる。さらに，本発明の無段変速機によれば，構成部品を固定部材に組み付けたうえでケースに固定することにより，組立作業性が向上する。 According to the continuously variable transmission of the present invention, in the continuously variable transmission using friction transmission, 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, 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. Furthermore, according to the continuously variable transmission of the present invention, the assembly workability is improved by assembling the component parts to the fixing member and then fixing them to the case.
本発明の無段変速機の変速原理を示す速度線図である。It is a speed diagram which shows the speed change principle of the continuously variable transmission of this invention. 本発明の無段変速機を示す構成図である。It is a block diagram which shows the continuously variable transmission of this invention. 第１クラッチを係合した時の本発明の無段変速機の動力伝達経路を示す説明図である。It is explanatory drawing which shows the power transmission path | route of the continuously variable transmission of this invention when a 1st clutch is engaged. 第１クラッチの係合時における本発明に係る遊星歯車機構の速度線図ならびに各要素に特化した動力フローをそれぞれ示す説明図である。It is explanatory drawing which each shows the velocity diagram of the planetary gear mechanism which concerns on this invention at the time of engagement of a 1st clutch, and the motive power flow specialized for each element. 第２クラッチを係合した時の本発明の無段変速機の動力伝達経路を示す説明図である。It is explanatory drawing which shows the power transmission path | route of the continuously variable transmission of this invention when a 2nd clutch is engaged. 第２クラッチの係合時における本発明に係る遊星歯車機構の速度線図ならびに各要素に特化した動力フローをそれぞれ示す説明図である。It is explanatory drawing which each shows the velocity diagram of the planetary gear mechanism which concerns on this invention at the time of engagement of a 2nd clutch, and the motive power flow specialized for each element. 本発明の無段変速機の変速原理に係る変形例を示す速度線図である。It is a speed diagram which shows the modification which concerns on the speed change principle of the continuously variable transmission of this invention. 本発明の無段変速機に係る変速機の回転数比を示す説明図である。It is explanatory drawing which shows the rotation speed ratio of the transmission which concerns on the continuously variable transmission of this invention. 本発明の無段変速機に係るプーリーの回転数を示す説明図である。It is explanatory drawing which shows the rotation speed of the pulley which concerns on the continuously variable transmission of this invention. 本発明の無段変速機に係るプーリートルクを示す説明図である。It is explanatory drawing which shows the pulley torque which concerns on the continuously variable transmission of this invention. 本発明の無段変速機に係るプーリー伝達動力を示す説明図である。It is explanatory drawing which shows the pulley transmission power which concerns on the continuously variable transmission of this invention. 本発明の無段変速機の変形例１に係る遊星歯車機構を示す説明図である。It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 1 of the continuously variable transmission of this invention. 本発明の無段変速機の変形例２に係る遊星歯車機構を示す説明図である。It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 2 of the continuously variable transmission of this invention. 本発明の無段変速機の変形例３に係る遊星歯車機構を示す説明図である。It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 3 of the continuously variable transmission of this invention. 本発明の無段変速機の変形例４に係る遊星歯車機構を示す説明図である。It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 4 of the continuously variable transmission of this invention. 本発明の無段変速機の変形例５に係る遊星歯車機構を示す説明図である。It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 5 of the continuously variable transmission of this invention. 本発明の無段変速機の変形例６に係る遊星歯車機構を示す説明図である。It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 6 of the continuously variable transmission of this invention. 本発明の無段変速機の変形例７に係る遊星歯車機構を示す説明図である。It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 7 of the continuously variable transmission of this invention. 本発明の無段変速機の変形例８に係る遊星歯車機構を示す説明図である。It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 8 of the continuously variable transmission of this invention. 本発明の無段変速機の変形例９に係る遊星歯車機構を示す説明図である。It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 9 of the continuously variable transmission of this invention. 本発明の無段変速機の変形例１０に係る遊星歯車機構を示す説明図である。It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 10 of the continuously variable transmission of this invention. 本発明の無段変速機の変形例１１に係る遊星歯車機構を示す説明図である。It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 11 of the continuously variable transmission of this invention. 本発明の無段変速機の変形例１２に係る遊星歯車機構を示す説明図である。It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 12 of the continuously variable transmission of this invention. 本発明の無段変速機の変形例１３に係る遊星歯車機構を示す説明図である。It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 13 of the continuously variable transmission of this invention.
　以下、図に示す実施の形態により本発明をさらに詳細に説明する。 Hereinafter, the present invention will be described in more detail with reference to embodiments shown in the drawings.
　図１は本発明の無段変速機の変速原理（すなわち、４つの要素の回転数を２つの自由度に規制する遊星歯車機構の，速度線図上に並ぶ４つの要素のうち，端から１番目の要素及び３番目の要素をバリエータの２つの軸と直接または固定された回転数比で結合しておき，２番目の要素を入力軸と直接または固定された回転数比で結合しておき，前記バリエータの回転数比を変えると前記１番目の要素の変速レシオ幅と前記４番目の要素の変速レシオ幅の積が，前記バリエータの変速レシオ幅を上回る、という変速原理）を表す遊星歯車機構の速度線図である。前記１番目の要素から動力を取り出す場合を出力１，前記４番目の要素から動力を取り出す場合を出力２と呼ぶ。
　速度線図の縦軸は回転数を示し，横方向の距離は遊星歯車機構の各要素の回転数比を示す。 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. , A planetary gear representing a shift principle that 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 when the rotation speed ratio of the variator is changed. It is a speed diagram of a mechanism. The case where power is taken out from the first element is called output 1, and 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, and the lateral distance indicates the rotational speed ratio of each element of the planetary gear mechanism.
　左から数えて１番目の要素の回転数をN1，２番目の要素の回転数をN2，３番目の要素の回転数をN3，４番目の要素の回転数をN4と呼ぶ。
速度線図上の左から１番目の要素と２番目の要素との間隔を１としたときの，２番目の要素と３番目の要素との間隔をλ１，２番目の要素と４番目の要素との間隔をλ２とする。２番目の要素と４番目の要素との間隔は，２番目の要素と３番目の要素との間隔より大きくなければ，４番目にはなりえないことからλ２＞λ１となる。左から２番目の要素を入力に結合するからN2=Ninである。左から１番目の要素をバリエータ軸１に直接又は固定された回転数比で結合して，３番目の要素をバリエータ軸２に直接または固定された回転数比で結合する。
　速度線図上でN1に対するN3の回転数比をrとする。 From the left, 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, and the rotation speed of the fourth element is N4.
The distance between the 2nd element and the 3rd element is λ1, 2nd element and 4th element when the distance between the 1st element and the 2nd element from the left on the velocity diagram is 1. Is set to λ2. Since the interval between the second element and the fourth element cannot be the fourth unless it is larger than the interval between the second element and the third element, λ2> λ1. Since the second element from the left is connected to the input, N2 = Nin. The first element from the left is coupled to the variator shaft 1 directly or at a fixed rotational speed ratio, and the third element is coupled to the variator shaft 2 directly or at a fixed rotational speed ratio.
On the velocity diagram, let r be the rotation speed ratio of N3 to N1.
　バリエータ軸１とバリエータ軸２の円と線分はベルト式バリエータを模しており，大きな円は巻き掛け径の最大状態を，小さな円は巻き掛け径の最小状態を示し，円と円を結ぶ線分は巻き掛けられたベルトの状態を示す。
　第１プーリーの巻き掛け径が最小で第２プーリーの巻き掛け径が最大のとき，rは最小値r_minをとり，各要素の回転数は速度線図上の右下がりの線分上の黒丸で表される。このときの遊星歯車機構の３つの要素の回転数はN1_min，N3_min，N4_minとする．なお２番目の要素は入力軸に結合されるから，rが変わってもN2は変化しない。
　第１プーリーの巻き掛け径が最大で第２プーリーの巻き掛け径が最小のとき，rは最大値r_maxをとり，各要素の回転数は速度線図上の右上がりの線分上の黒丸で表される。このときの遊星歯車機構の３つの要素の回転数はN1_min，N3_min，N4_minとする。 
　バリエータ変速レシオ幅はr_max/r_minである。
　N1はr=r_minのとき最大値となり，r=r_maxのとき最小値となる．出力１の変速レシオ幅はN1の最大値と最小値の比に相当するから，N1_min/N1_maxで表される。
　N4はr=r_maxのとき最大値となり，r=r_minのとき最小値となる．出力２の変速レシオ幅はN4の最大値と最小値の比に相当するから，N4_max/N4_minで表される。 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, and the small circle indicates the minimum state of the winding diameter. A line segment shows the state of the wound belt.
When the winding diameter of the first pulley is the minimum and the winding diameter of the second pulley is the maximum, r takes the minimum value r_min, and the rotation speed of each element is a black circle on the lower 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. Since the second element is connected to the input shaft, N2 does not change even if r changes.
When the winding diameter of the first pulley is the maximum and the winding diameter of the second pulley is the minimum, 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 has the maximum value when r = r_min, and the minimum value when r = r_max. Since the shift ratio width of output 1 corresponds to the ratio between the maximum value and the minimum value of N1, it is expressed as N1_min / N1_max.
N4 has the maximum value when r = r_max, and the minimum value when r = r_min. Since the shift ratio width of output 2 corresponds to the ratio between the maximum value and the minimum value of N4, it is expressed as N4_max / N4_min.
　ここで、上記変速原理が成り立つことを証明する。
遊星歯車機構における入力軸回転数をNinとすれば，N1,N2,N3,N4は式１から式４に従う。
式１：N1×r=N3
式２：N2=Nin
式３：(N2-N1)×λ1=N3-N2
式４：(N2-N1)×λ2=N4-N2
式３に式１と式２を代入すれば式５となる。
式５：(Nin-N1)×λ1=N1×r-Nin
式５をN1について解けば式６となる。
式６：N1={(1+λ1)/(r+λ1)}×Nin
式１に式６を代入すれば式７となる。
式７：N3={r×(1+λ1)/(r+λ1)}×Nin
式４に式２と式６を代入してN4について整理すれば式８となる。
式８：N4={r×(1+λ2)+λ1-λ2}/(r+λ1)×Nin Here, it is proved that the above-mentioned speed change principle holds.
If the input shaft speed in the planetary gear mechanism is Nin, N1, N2, N3, and N4 follow Equations 1 to 4.
Formula 1: N1 × r = N3
Formula 2: N2 = Nin
Formula 3: (N2-N1) × λ1 = N3-N2
Formula 4: (N2-N1) × λ2 = N4-N2
If Formula 1 and Formula 2 are substituted into Formula 3, Formula 5 is obtained.
Formula 5: (Nin-N1) × λ1 = N1 × r-Nin
Solving Equation 5 for N1, Equation 6 is obtained.
Formula 6: N1 = {(1 + λ1) / (r + λ1)} × Nin
If formula 6 is substituted into formula 1, formula 7 is obtained.
Formula 7: N3 = {r × (1 + λ1) / (r + λ1)} × Nin
Substituting Equations 2 and 6 into Equation 4 and rearranging N4 results in Equation 8.
Formula 8: N4 = {r × (1 + λ2) + λ1-λ2} / (r + λ1) × Nin
　上記変速原理は，出力１の変速レシオ幅と出力２の変速レシオ幅の積と，バリエータ変速レシオ幅の大小関係が，式９を満たすことと等値である。
式９：(N1_min/N1_max)×(N4_max/N4_min)＞r_max/r_min
式９の左辺に式６と式８を代入すれば式１０となる。
式１０：{(1+λ1)/(r_min+λ1)}/{(1+λ1)/(r_max+λ1)}×[{r_max×(1+λ2)+λ1-λ2}/(r_max+λ1)]/[{r_min×(1+λ2)+λ1-λ2}/(r_min+λ1)]＞r_max/r_min
式１０の左辺を整理すれば式１１となる。
式１１：{r_max×(1+λ2)-(λ2-λ1)}/{r_min×(1+λ2)-(λ2-λ1)}＞r_max/r_min
N4は常に正の値だから式１１の左辺の分母は常に正の値であることを利用して，式１１の両辺にr_min×{r_min×(1+λ2)-(λ2-λ1)}を掛けると式１２となる。
式１２：(λ2-λ1)×(r_max-r_min)＞0
λ2＞λ1かつr_max＞r_minなので式１２は常に成り立つ。
式１２と等値である式９も常に成り立つから，上記変速原理が証明された。 The speed change principle is equivalent to the fact that the product of the speed ratio width of output 1 and the speed ratio width of output 2 and the variator speed ratio width satisfy Expression 9.
Formula 9: (N1_min / N1_max) × (N4_max / N4_min)> r_max / r_min
Substituting Equation 6 and Equation 8 into the left side of Equation 9 yields Equation 10.
Formula 10: {(1 + λ1) / (r_min + λ1)} / {(1 + λ1) / (r_max + λ1)} × [{r_max × (1 + λ2) + λ1-λ2} / (r_max + λ1 )] / [{r_min × (1 + λ2) + λ1-λ2} / (r_min + λ1)]> r_max / r_min
If the left side of Formula 10 is arranged, Formula 11 is obtained.
Expression 11: {r_max × (1 + λ2) − (λ2−λ1)} / {r_min × (1 + λ2) − (λ2−λ1)}> 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 + λ2)-(λ2-λ1)}. And Equation 12 is obtained.
Formula 12: (λ2-λ1) × (r_max-r_min)> 0
Since λ2> λ1 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.
　次に、上記変速原理においてバリエータの伝達動力が変速機の伝達動力より常に小さくなることを示す。
　先ず、トルクを求める。ここでは歯車やバリエータの伝達効率は１と仮定した。遊星歯車機構の軸上での入力トルクをTinとして，遊星歯車の速度線図上の４つの要素に入るトルクを、それぞれT1，T2，T3，T4とする。速度線図で左から２番目の要素に入力されるから，常に式１３が成り立つ。
式１３：T2=Tin
　遊星歯車の速度線図で，左から１番目の要素から出力する場合のトルクを求める。
梃子の原理からT1は式１４で表せる。
式１４：T1=-λ1/(1+λ1)×Tin
同様にT3は式１５で表せる。
式１５：T3=-1/(1+λ1)×Tin
なお，T4はゼロである。
　遊星歯車の速度線図で，左から４番目の要素から出力する場合のトルクを求める．
遊星歯車の公転のトルクつり合いは式１６で表される。
式１６：T1+T2+T3+T4=0
遊星歯車の自転のトルクつり合いは式１７で表される。
式１７：T1=T3×λ1+T4×λ2
T1とT3はバリエータでつながっているから，トルクの関係は式１８で表される。
式１８：T1=-r×T3
式１７に式１８を代入して整理すると，式１９となる。
式１９：T3=-{λ2/(λ1+r)}×T4
式１６に式１９を代入して整理すると，式２０となる。
式２０：T4=-[(λ1+r)/{λ1-λ2+(λ2+1)×r}]×Tin
式１９に式２０を代入して整理すると，式２１となる。
式２１：T3=λ2/{λ1-λ2+(λ2+1)×r}×Tin
式１８に式２１を代入して整理すると，式２２となる。
式２２：T1=-[r×λ2/{λ1-λ2+(λ2+1)×r}]×Tin
以上でトルクが求められた。 Next, it will be shown that the transmission power of the variator is always smaller than the transmission power of the transmission in the above speed change principle.
First, the torque is obtained. Here, 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, and 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.
Formula 13: 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.
Formula 14: T1 = −λ1 / (1 + λ1) × Tin
Similarly, T3 can be expressed by Equation 15.
Formula 15: T3 = -1 / (1 + λ1) × Tin
T4 is zero.
Calculate the torque when output from the fourth element from the left in the planetary gear speed diagram.
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.
Formula 17: T1 = T3 × λ1 + T4 × λ2
Since T1 and T3 are connected by a variator, the torque relationship is expressed by Equation 18.
Formula 18: T1 = −r × T3
Substituting Equation 18 into Equation 17 for rearrangement yields Equation 19.
Formula 19: T3 =-{λ2 / (λ1 + r)} × T4
Substituting Equation 19 into Equation 16 and rearranging results in Equation 20.
Expression 20: T4 = − [(λ1 + r) / {λ1-λ2 + (λ2 + 1) × r}] × Tin
Substituting Equation 20 into Equation 19 and rearranging results in Equation 21.
Formula 21: T3 = λ2 / {λ1-λ2 + (λ2 + 1) × r} × Tin
Substituting Equation 21 into Equation 18 for rearrangement yields Equation 22.
Formula 22: T1 = − [r × λ2 / {λ1-λ2 + (λ2 + 1) × r}] × Tin
Thus, the torque was obtained.
　次に、本発明に係る上記変速原理においてバリエータ伝達動力が変速機の伝達動力より小さくなる効果に関する成立条件を以下に示す。
　変速機の伝達動力をPとすれば，これは回転数とトルクの積だから式２３で表される。
式２３：P=Nin×Tin
　図１の遊星歯車機構の速度線図で，左から１番目の要素から出力した場合のバリエータ伝達動力をP1とする．これは左から３番目の要素から出てバリエータ軸２に入りバリエータ軸１に伝わる動力にほかならないから，P1は式２４で表される。
式２４：P1=-N3×T3 ただしT3は式１５
式２４に式７と式１５を代入して整理すると式２５となる。
式２５：P1=r/(r+λ1)×P
　左から４番目の要素から出力した場合のバリエータ伝達動力をP2とする。これは左から１番目の要素から出てバリエータ軸１に入りバリエータ軸２に伝わり，左から３番目の要素に入る動力だから，P2は式２６で表される。
式２６：P2=N3×T3　ただしT3は式２１
式２６に式７と式２１を代入して整理すると式２７となる。
式２７：P2={r×λ2×(1+λ1)}/[{r+λ1}×{λ1-λ2+(1+λ2)×r}]×P
P1とP2が式２８と式２９を満たす場合，バリエータ伝達動力が変速機の伝達動力より小さい。
式２８：P1＜P
式２９：P2＜P
式２８はλ1＞0だから常に成立する。
式２９に式２７を代入すると式３０となる。
式３０：{r×λ2×(1+λ1)}/[{r+λ1}×{λ1-λ2+(1+λ2)×r}]×P＜P
式３０の両辺をPで割ると式３１となる。
式３１：{r×λ2×(1+λ1)}/[{r+λ1}×{λ1-λ2+(1+λ2)×r}]＜1
P2は常に正であり，式３１の分子も常に正だから，式３１の分母は常に正である．これを利用して式３１を整理すれば式３２となる。
式３２：r×λ2×(1+λ1)＜{r+λ1}×{λ1-λ2+(1+λ2)×r}
式３２をrについて整理すると式３３となる。
式３３：r^2+2×(λ1-λ2)/(1+λ2)×r+{λ1×(λ1-λ2)/(1+λ2)}＞0
式３３の左辺をrについて因数分解すれば式３４となる。
式３４：(r+[λ1-λ2+{λ2×(λ2-λ1)×(1+λ1)}^0.5)]/(1+λ2))×(r+[λ1-λ2-{λ2×(λ2-λ1)×(1+λ1)}^0.5)]/(1+λ2))＞0
式３２の右辺が常に正であることを利用すれば，式３５となる。
式３５：λ1-λ2+r×(1+λ2)＞0
式３５の左辺を1+λ2で割れば式３６となる。
式３６：r+(λ1-λ2)/(1+λ2)＞0
式３４は２つの式の積だが，第１式は式３６から常に正である．式３４の不等式から第１式を削除すれば式３７となる。
式３７：r+[λ1-λ2-{λ2×(λ2-λ1)×(1+λ1)}^0.5)]/(1+λ2)＞0
式３７をrについて整理すると式３８となる。
式３８：r＞[(λ2-λ1)+{λ2×(λ2-λ1)×(1+λ1)}^0.5]/(1+λ2)
rの最小値はr_minだから，式３８を満たす条件は式３９となる。
式３９：r_min＞[(λ2-λ1)+{λ2×(λ2-λ1)×(1+λ1)}^0.5]/(1+λ2)
式３９を満たすようにr_min，λ1，λ2の値を決めれば，常にバリエータ伝達動力が変速機の伝達動力より小さくなる。 Next, conditions for establishing the effect that the variator transmission power becomes smaller than the transmission power of the transmission in the above-described speed change principle according to the present invention will be described below.
If the transmission power of the transmission is P, this is the product of the rotation speed and the torque, so it is expressed by Equation 23.
Formula 23: P = Nin × Tin
In the speed diagram of the planetary gear mechanism in Fig. 1, let P1 be the variator transmission power when output from the first element from the left. Since this is nothing but the power transmitted from the third element from the left to the variator shaft 2 and transmitted to the variator shaft 1, P1 is expressed by Expression 24.
Equation 24: P1 = −N3 × T3 where T3 is Equation 15
Substituting Equation 7 and Equation 15 into Equation 24 and rearranging results in Equation 25.
Formula 25: P1 = r / (r + λ1) × P
Let P2 be 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.
Expression 27: P2 = {r × λ2 × (1 + λ1)} / [{r + λ1} × {λ1-λ2 + (1 + λ2) × r}] × P
When P1 and P2 satisfy Expressions 28 and 29, the variator transmission power is smaller than the transmission transmission power.
Formula 28: P1 <P
Formula 29: P2 <P
Equation 28 always holds because λ1> 0.
Substituting Equation 27 into Equation 29 yields Equation 30.
Expression 30: {r × λ2 × (1 + λ1)} / [{r + λ1} × {λ1-λ2 + (1 + λ2) × r}] × P <P
Dividing both sides of Equation 30 by P yields Equation 31.
Formula 31: {r × λ2 × (1 + λ1)} / [{r + λ1} × {λ1-λ2 + (1 + λ2) × 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 × λ2 × (1 + λ1) <{r + λ1} × {λ1-λ2 + (1 + λ2) × r}
When formula 32 is arranged with respect to r, formula 33 is obtained.
Expression 33: r ^ 2 + 2 × (λ1-λ2) / (1 + λ2) × r + {λ1 × (λ1-λ2) / (1 + λ2)}> 0
If the left side of Expression 33 is factored with respect to r, Expression 34 is obtained.
Formula 34: (r + [λ1-λ2 + {λ2 × (λ2-λ1) × (1 + λ1)} ^ 0.5)] / (1 + λ2)) × (r + [λ1-λ2- {λ2 × (λ2-λ1) ) × (1 + λ1)} ^ 0.5)] / (1 + λ2))> 0
Using the fact that the right side of Expression 32 is always positive, Expression 35 is obtained.
Formula 35: λ1-λ2 + r × (1 + λ2)> 0
If the left side of Expression 35 is divided by 1 + λ2, Expression 36 is obtained.
Formula 36: r + (λ1-λ2) / (1 + λ2)> 0
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 + [λ1-λ2- {λ2 × (λ2-λ1) × (1 + λ1)} ^ 0.5)] / (1 + λ2)> 0
When formula 37 is arranged with respect to r, formula 38 is obtained.
Formula 38: r> [(λ2-λ1) + {λ2 × (λ2-λ1) × (1 + λ1)} ^ 0.5] / (1 + λ2)
Since the minimum value of r is r_min, the condition that satisfies Expression 38 is Expression 39.
Formula 39: r_min> [(λ2-λ1) + {λ2 × (λ2-λ1) × (1 + λ1)} ^ 0.5] / (1 + λ2)
If the values of r_min, λ1, and λ2 are determined so as to satisfy Equation 39, the variator transmission power is always smaller than the transmission transmission power.
　出力１と出力２を選択的に係合して，変速レシオ幅の範囲内で任意の回転数比をとれる無段変速機を構成するためには，バリエータがとりうる回転数比の中に，出力１と出力２のどちらを選んでも入力軸に対する出力軸の回転数比が等しくなるようなバリエータの回転数比が存在する必要がある。そこで，出力１と出力２が，出力軸上で回転数が等しくなるための条件を示す。
　１番目の要素に対する出力軸の回転数比をr1とする。４番目の要素に対する出力軸の回転数比をr2とする。式４０が成立することが，出力軸上で回転数が等しくなる条件である。
式４０：N1×r1=N4×r2
式４０へ式６と式８を代入すると式４１となる。
式４１：(1+λ1)/(r+λ1)×Nin×r1={r×(1+λ2)+λ1-λ2}/(r+λ1)×Nin×r2
式４１を整理すると式４２となる。
式４２：r1/r2={r×(1+λ2)+λ1-λ2}/(1+λ1)
バリエータの回転数比がr=r_minのときに各要素の回転数を変えずに２つの係合機構の切り替えを行う場合は，式４３が成立するようにr1とr2を決める。
式４３：r1/r2={r_min×(1+λ2)+λ1-λ2}/(1+λ1)
一方、バリエータの回転数比がr=r_maxのときに各要素の回転数を変えずに２つの係合機構の切り替えを行う場合は，式４４が成立するようにr1とr2を決める。
式４４：r1/r2={r_max×(1+λ2)+λ1-λ2}/(1+λ1) In order to construct a continuously variable transmission that can take any rotational speed ratio within the range of the speed ratio ratio by selectively engaging the output 1 and the output 2, the rotational speed ratio that the variator can take, Regardless of whether output 1 or output 2 is selected, there must be a variator speed ratio that makes the output shaft speed ratio to the input shaft equal. Therefore, the conditions for the output 1 and the output 2 to have the same rotational speed on the output shaft are shown.
Let r1 be the rotation speed ratio of the output shaft to the first element. Let r2 be the rotation speed ratio of the output shaft to the fourth element. The fact that Expression 40 is satisfied is a condition for equalizing the rotation speed on the output shaft.
Formula 40: N1 × r1 = N4 × r2
Substituting Equation 6 and Equation 8 into Equation 40 yields Equation 41.
Formula 41: (1 + λ1) / (r + λ1) × Nin × r1 = {r × (1 + λ2) + λ1-λ2} / (r + λ1) × Nin × r2
When formula 41 is arranged, formula 42 is obtained.
Formula 42: r1 / r2 = {r × (1 + λ2) + λ1-λ2} / (1 + λ1)
When the two engagement mechanisms are switched without changing the rotation speed of each element when the rotation speed ratio of the variator is r = r_min, r1 and r2 are determined so that Expression 43 is satisfied.
Expression 43: r1 / r2 = {r_min × (1 + λ2) + λ1-λ2} / (1 + λ1)
On the other hand, when the two engagement mechanisms are switched without changing the rotation speed of each element when the rotation speed ratio of the variator is r = r_max, r1 and r2 are determined so that Expression 44 is satisfied.
Formula 44: r1 / r2 = {r_max × (1 + λ2) + λ1-λ2} / (1 + λ1)
　図２は本発明の無段変速機（１００）を示す構成図である。
　この無段変速機（１００）は、入力軸（１）と，キャリア（２）と第１ピニオン（３）と第２ピニオン（４）とサンギヤ（５）と第１リングギヤ（６）と第２リングギヤ（７）で構成される遊星歯車機構（１９）と，第５ギヤ（１２）と同軸上に一体化され対向配置された第１円錐部材（１６a）と第２円錐部材(１６b)とで構成される第１プーリー（１６）と，前記第１リングギヤ（６）と同軸上に一体化され対向配置された第３円錐部材（１７a）と第４円錐部材（１７b）とで構成される第２プーリー（１７）と，前記第１プーリー（１６）と前記第２プーリー（１７）に巻き掛けられたベルト（１８）とから構成され，前記第１プーリー（１６）の２つの円錐部材の距離により定まる巻き掛け径と前記第２プーリー（１７）の２つの円錐部材の距離により定まる巻き掛け径の比に応じて回転数比を変えることができるバリエータ（１５）と，前記第２リングギヤ（７）と第１クラッチ（２０）により係合することができる第１ギヤ（８）と，前記第１ギヤ（８）とかみ合う第２ギヤ（９）と，前記サンギヤ（５）と同軸上に一体化された第３ギヤ（１０）と，前記第３ギヤ（１０）及び前記第５ギヤ（１２）とかみ合う第４ギヤ（１１）と，第２クラッチ（２１）により前記第４ギヤ（１１）と係合することができかつ前記第２ギヤ（９）と一体化された出力軸（１３）とから構成されている。 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 two pulleys (17), the first pulley (16), and the belt (18) wound around the second pulley (17), the distance between the two conical members of the first pulley (16) 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). (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 a fourth gear (11) meshing with the fifth gear (12), and can be engaged with the fourth gear (11) by a second clutch (21) and integrated with the second gear (9). Output shaft (13).
　前記遊星歯車機構（１９）で，前記第１ピニオン（３）は前記第１リングギヤ（６）とかみ合い，前記第２ピニオン（４）は前記サンギヤ（５）及び前記第２リングギヤ（７）とかみ合う．前記第１ピニオン（３）と前記第２ピニオン（４）は一体となって回転する。 In the planetary gear mechanism (19), the first pinion (3) meshes with the first ring gear (6), and 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.
　また、後述する遊星歯車機構の速度線図において、左端から１番目の要素であるサンギヤ（５）が第１プーリー（１６）の軸に回転数比rg2・rg3（固定値）で結合され且つ３番目の要素である第１リングギヤ（６）は第２プーリー（１７）の回転軸に直接結合されており、加えて２番目の要素であるキャリア（２）が入力軸（１）に直結され、且つ１番目の要素であるサンギヤ（５）あるいは４番目の要素である第２リングギヤ（７）は第２クラッチ（２１）又は第１クラッチ（２０）によって選択的に出力軸（１３）に係合されるように構成されている。従って、本発明の無段変速機（１００）は上記変速原理を満足しており、無段変速機（１００）全体の変速レシオ幅はバリエータ（１５）の変速レシオ幅を上回ると共に、バリエータ伝達動力が変速機の伝達動力より小さくなる。 In the speed diagram of the planetary gear mechanism described later, 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), and 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. Therefore, 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.
　遊星歯車機構の第１ピニオン（３）の歯数と第２ピニオン（４）の歯数はいずれもZp，サンギヤ（５）の歯数をZs，第１リングギヤ（６）の歯数をZr1，第２リングギヤ（７）の歯数をZr2とする。
　また，第１ギヤ（８）に対する第２ギヤ（９）の回転数比をrg1，第３ギヤ（１０）に対する第４ギヤ（１１）の回転数比をrg2，第４ギヤ（１１）に対する第５ギヤ（１２）の回転数比をrg3とする。第１プーリー（１６）に対する第２プーリー（１７）の回転数比をrb（バリエータ回転数比）とする。これら構造によるパラメータを速度線図のパラメータに代入していく。
λ1は式４５で表される。
式４５：λ1=Zs/Zr1
λ2は式４６で表される。
式４６：λ2=Zs/Zr2
rは式４７で表される。
式４７：r=rg2×rg3×rb
rbの範囲のうち最小値をrb_min，最大値をrb_maxとすると，r_minとr_maxはそれぞれ式４８と式４９となる。
式４８：r_min=rg2×rg3×rb_min
式４９：r_max=rg2×rg3×rb_max
バリエータ伝達動力が常に変速機の伝達動力より小さくするため，式３９に式４５と式４６と式４８を代入して整理すると式５０となる．
式５０：rb_min＞Zs×[Zr1-Zr2+{(Zr1-Zr2)×(Zr1+Zs)}^0.5]/{rg2×rg3×Zr1×(Zr2+Zs)}
式５０を満たすように各ギヤの歯数を決める。 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.
Further, 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, and 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). The parameters according to these structures are substituted into the parameters of the velocity diagram.
λ1 is expressed by Equation 45.
Formula 45: λ1 = Zs / Zr1
λ2 is expressed by Equation 46.
Formula 46: λ2 = 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 48: r_min = rg2 × rg3 × rb_min
Formula 49: r_max = rg2 × rg3 × rb_max
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.
Formula 50: rb_min> Zs × [Zr1-Zr2 + {(Zr1-Zr2) × (Zr1 + Zs)} ^ 0.5] / {rg2 × rg3 × Zr1 × (Zr2 + Zs)}
The number of teeth of each gear is determined so as to satisfy Equation 50.
　ここではrb_maxのときに２つのクラッチの切り替えを行うことにする。つまり，式４４が成り立つ必要がある。式４４に含まれるr1とr2は，それぞれ式５１と式５２で表される。
式５１：r1=rg2
式５２：r2=rg1
式４５と式４６と式４９と式５１と式５２を，式４４に代入すると式５３となる。
式５３：rg2/rg1={rg2×rg3×rb_max×(1+Zs/Zr2)+Zs/Zr1-Zs/Zr2}/(1+Zs/Zr1)
式５３をrg1について解くと式５４となる。
式５４：rg1={Zr2×(Zr1+Zs)}/{rg2×rg3×rb_max×Zr1×(Zr2+Zs)+Zs×(Zr2-Zr1)}×rg2
式５４の回転数比になるように第１ギヤ（８）と第２ギヤ（９）の歯数比を決定すれば，第１プーリー（１６）に対する第２プーリー（１７）の回転数比が最大のとき，第１クラッチ（２０）と第２クラッチ（２１）のどちらを係合しても，入力軸（１）の回転数に対する各要素の回転数比は変わらない。 Here, the two clutches are switched when rb_max. That is, Formula 44 needs to hold. R1 and r2 included in Expression 44 are expressed by Expression 51 and Expression 52, respectively.
Formula 51: r1 = rg2
Formula 52: r2 = rg1
When Expression 45, Expression 46, Expression 49, Expression 51, and Expression 52 are substituted into Expression 44, Expression 53 is obtained.
Formula 53: rg2 / rg1 = {rg2 × rg3 × rb_max × (1 + Zs / Zr2) + Zs / Zr1-Zs / Zr2} / (1 + Zs / Zr1)
When Formula 53 is solved for rg1, Formula 54 is obtained.
Formula 54: rg1 = {Zr2 × (Zr1 + Zs)} / {rg2 × rg3 × rb_max × Zr1 × (Zr2 + Zs) + Zs × (Zr2-Zr1)} × rg2
If the gear ratio of the first gear (8) and the second gear (9) is determined so that the rotation speed ratio of Equation 54 is obtained, the rotation speed ratio of the second pulley (17) to the first pulley (16) is At the maximum, regardless of which of the first clutch (20) and the second clutch (21) is engaged, the rotation speed ratio of each element with respect to the rotation speed of the input shaft (1) does not change.
　次に，無段変速機（１００）を運転する方法について説明する。
　第１クラッチ（２０）を係合する時の動力の流れは図３の太線のようになる。この場合、第２リングギヤ（７）が出力軸（１３）に回転数比rg1の第１ギヤ（８）と第２ギヤ（９）のギヤ対によって結合される。
　入力軸（１）からの動力は，一部がサンギヤ（５）へ伝わって第３ギヤ（１０）と第４ギヤ（１１）と第５ギヤ（１２）と第１プーリー（１６）と第２プーリー（１７）を順に流れて第１リングギヤ（６）に戻り，遊星歯車内部を流れる残りの動力と合流して第２リングギヤ（７）に伝達されて第１ギヤ（８）と第２ギヤ（９）を経由して出力軸（１３）から出力される。このとき，入力軸（１）に対する出力軸（１３）の回転数比R1（＝rg1×N4/Nin）は、式８に式４５～式４７を代入して整理することにより、式５５で表される。
式５５：R1={rb×rg2×rg3×Zr1×(Zr2+Zs)+Zs×(Zr2-Zr1)}/(rb×rg2×rg3×Zr1×Zr2+Zs×Zr2)×rg1 Next, a method for operating the continuously variable transmission (100) will be described.
The power flow when the first clutch (20) is engaged is as shown by the thick line in FIG. In this case, 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. Flowing through the pulley (17) in sequence and returning to the first ring gear (6), the remaining power flowing through the planetary gear is joined and transmitted to the second ring gear (7) to be transmitted to the first gear (8) and the second gear ( 9) and output from the output shaft (13). At this time, the rotational speed ratio R1 (= rg1 × N4 / Nin) of the output shaft (13) with respect to the input shaft (1) is expressed by Equation 55 by substituting Equation 45 to Equation 47 into Equation 8. Is done.
Formula 55: R1 = {rb × rg2 × rg3 × Zr1 × (Zr2 + Zs) + Zs × (Zr2-Zr1)} / (rb × rg2 × rg3 × Zr1 × Zr2 + Zs × Zr2) × rg1
　図４は、第１クラッチの係合時における，本発明に係る遊星歯車機構の速度線図ならびに各要素に特化した動力フローをそれぞれ示す説明図である。
　本発明の無段変速機（１００）の速度線図では、第１プーリー（１６）に対する第２プーリー（１７）の回転数比rbをrb_minからrb_maxへ変化させると、サンギヤ（５）の回転数N1はN1_min→N1_maxへ、第１リングギヤ（６）の回転数N3はN3_min→N3_maxへ、第２リングギヤ（７）の回転数N4はN4_min→N4_maxへそれぞれ変化し、全体として速度線図はバリエータの上記回転数比rbに応じてキャリア（２）を中心として実線から点線へ連続的に変化する。また、伝達動力はキャリア（２）において二分割され一部がバリエータを通過せずに第２リングギヤ（７）から直に出力軸（１３）に出力され、残りがバリエータを通過して第１リングギヤ（６）で左記動力フローと合流しながら出力軸（１３）に出力され、これによりバリエータの伝達動力を変速機の伝達動力より常に小さくすることができる。 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.
In the speed diagram of the continuously variable transmission (100) of the present invention, when 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, and the rotation speed N4 of the second ring gear (7) changes from N4_min to N4_max. It changes continuously from the solid line to the dotted line around the carrier (2) according to the rotation speed ratio rb. Further, 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. In (6), 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.
　本発明の無段変速機（１００）では、出力軸（１３）はサンギヤ（５）、第２リングギヤ（７）及び第１プーリー（１６）に対し所定のギヤ対を介してそれぞれ結合されているため、１番目の要素の回転数N1×回転数比rg2＝出力１に係る出力軸の回転数、４番目の要素の回転数N4×rg1＝出力２に係る出力軸の回転数、１番目の要素に対する３番目の要素の回転数比ｒ＝バリエータ軸１に対するバリエータ軸２の回転数比rb×回転数比rg2×回転数比rg3、という関係がそれぞれ成立している。その結果、出力軸（１３）の回転数はギヤの歯数比を調整することにより，遊星歯車機構及びバリエータの回転数とは独立に出力先の要求に応じて出力軸（１３）の回転数を決めることが可能となる。 In the continuously variable transmission (100) of the present invention, the output shaft (13) is coupled to the sun gear (5), the second ring gear (7), and the first pulley (16) via a predetermined gear pair. Therefore, the rotational speed N1 of the first element × the rotational speed ratio rg2 = the rotational speed of the output shaft related to the output 1; the rotational speed of the fourth element N4 × rg1 = the rotational speed of the output shaft related to the output 2; The relationship of the rotational speed ratio r of the third element to the element r = the rotational speed ratio rb of the variator shaft 2 to the variator shaft 1 × the rotational speed ratio rg2 × the rotational speed ratio rg3 is established. As a result, the rotational speed of the output shaft (13) is adjusted according to the request of the output destination independently of the rotational speed of the planetary gear mechanism and the variator by adjusting the gear ratio. Can be determined.
　他方、第２クラッチ（２１）を係合すると動力の流れは図５の太線のようになる．
　入力軸（１）からの動力は，一部が第１リングギヤ（６）へ伝わって第２プーリー（１７）と第１プーリー（１６）と第５ギヤ（１２）と第４ギヤ（１１）へ流れる。残りはサンギヤ（５）から第３ギヤ（１０）を経由して第４ギヤ（１１）へ流れて，第４ギヤ（１１）で合流して第２クラッチ（２１）に伝わり出力軸（１３）から出力される。このとき，入力軸（１）に対する出力軸（１３）の回転数比R2（＝rg2×N1/Nin）は、式６に式４５～式４７を代入して整理することにより、式５６で表される。
式５６：R2=(Zr1+Zs)/(rb×rg2×rg3×Zr1+Zs)×rg2 On the other hand, when the second clutch (21) is engaged, the power flow becomes as shown by the thick line in FIG.
Part of the power from the input shaft (1) is transmitted to the first ring gear (6) to the second pulley (17), the first pulley (16), the fifth gear (12), and the fourth gear (11). Flowing. The remainder flows from the sun gear (5) to the fourth gear (11) via the third gear (10), and then merges at the fourth gear (11) and is transmitted to the second clutch (21) to be output to the output shaft (13). Is output from. At this time, the rotational speed ratio R2 (= rg2 × N1 / Nin) of the output shaft (13) with respect to the input shaft (1) is expressed by Equation 56 by substituting Equation 45 to Equation 47 into Equation 6. Is done.
Formula 56: R2 = (Zr1 + Zs) / (rb × rg2 × rg3 × Zr1 + Zs) × rg2
図６は、第２クラッチの係合時における，本発明に係る遊星歯車機構の速度線図ならびに各要素に特化した動力フローをそれぞれ示す説明図である。
切り替え後，バリエータ回転数比rbをrb_maxからrb_minへ変化させると、サンギヤ（５）の回転数N1はN1_max→N1_minへ、第１リングギヤ（６）の回転数N3はN3_max→N3_minへ、第２リングギヤ（７）の回転数N4はN4_max→N4_minへそれぞれ変化し、全体として速度線図はバリエータの上記回転数比rbに応じてキャリア（２）を中心として実線から点線へ連続的に変化する。また、伝達動力はキャリア（２）において二分割され一部がバリエータを通過せずにサンギヤ（５）から直に出力軸（１３）に出力され、残りがバリエータを通過して第４ギヤ（１１）で左記動力フローと合流しながら出力軸（１３）に出力され、これによりバリエータの伝達動力が変速機の伝達動力より常に小さくなることが分かる。 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.
When 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, and the second ring gear. The rotational speed N4 in (7) 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. Further, 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.
　第１プーリー（１６）に対する第２プーリー（１７）の回転数比がrb_minのときのR1とR2を，それぞれR1_minとR2_minとして，第１プーリー（１６）に対する第２プーリー（１７）の回転数比がrb_maxのときのR1とR2を，それぞれR1_maxとR2_maxとすれば，これらの大小関係は，式５７となる。
式５７：R1_min＜R1_max=R2_max＜R2_min
無段変速機（１００）の，入力軸（１）に対する出力軸（１３）の回転数比の取りうる範囲は，R1_minからR2_minの間であり，これがバリエータ変速レシオ幅を上回るのは前述の通りである。 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.
Formula 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.
　次に，入力軸（１）に対する出力軸（１３）の回転数比の目標値をRとして，このレシオになるようなクラッチとバリエータの設定を求める。前提として，Rは式５８を満たす。
式５８：R1_min≦R≦R2_min
　このRに対して，式５９が成り立つ場合は第１クラッチ（２０）を係合し，式６０が成り立つ場合は第２クラッチ（２１）を係合する．式６１が成り立つ場合は第１クラッチと第２クラッチのいずれか一方，あるいは両方を係合する。
式５９：R1_min≦R＜R1_max
式６０：R2_max＜R≦R2_min
式６１：R=R1_max=R2_max
第１クラッチ（２０）を係合しているとき，バリエータレシオを式６２のように決めれば，所望の回転数比が得られる。
式６２：rb={rg1×Zs×(Zr2-Zr1)-R×Zs×Zr2}/{R×rg2×rg3×Zr1×Zr2-rg1×rg2×rg3×Zr1×(Zr2+Zs)}
第２クラッチ（２１）を係合しているとき，バリエータレシオを式６３のように決めれば，所望の回転数比が得られる．
式６３：rb={rg2×(Zr1+Zs)-R×Zs}/(R×rg2×rg3×Zr1)
第１クラッチ（２０）の係合状態から第２クラッチ（２１）の係合状態への切り替えは，rb=rb_maxとしておき，第１クラッチ（２０）を係合したまま第２クラッチ（２１）を係合し，次いで第１クラッチ（２０）を開放する．第２クラッチ（２１）の係合状態から第１クラッチ（２０）の係合状態への切り替えも同様に行う．
以上で，バリエータ変速レシオ幅を上回る変速レシオ幅を有する無段変速機として運転できるようになる． Next, assuming that the target value of the rotation speed ratio of the output shaft (13) to the input shaft (1) is R, the clutch and variator settings are obtained so as to satisfy this ratio. As a premise, R satisfies Equation 58.
Formula 58: R1_min ≦ R ≦ R2_min
When R 59 is satisfied, the first clutch (20) is engaged. When R 60 is satisfied, the second clutch (21) is engaged. When Formula 61 is satisfied, either one or both of the first clutch and the second clutch are engaged.
Formula 59: R1_min ≦ R <R1_max
Formula 60: R2_max <R ≦ R2_min
Formula 61: R = R1_max = R2_max
When the first clutch (20) is engaged, a desired speed ratio can be obtained by determining the variator ratio as shown in Equation 62.
Formula 62: rb = {rg1 × Zs × (Zr2-Zr1) -R × Zs × Zr2} / {R × rg2 × rg3 × Zr1 × Zr2-rg1 × rg2 × rg3 × Zr1 × (Zr2 + Zs)}
When the second clutch (21) is engaged, the desired speed ratio can be obtained by determining the variator ratio as shown in Equation 63.
Formula 63: rb = {rg2 × (Zr1 + Zs) −R × Zs} / (R × rg2 × rg3 × Zr1)
To switch from the engaged state of the first clutch (20) to the engaged state of the second clutch (21), rb = rb_max is set, and the second clutch (21) is engaged with the first clutch (20) engaged. Engage and then release the first clutch (20). The switching from the engaged state of the second clutch (21) to the engaged state of the first clutch (20) is similarly performed.
With the above, it will be possible to operate as a continuously variable transmission having a transmission ratio width exceeding the variator transmission ratio width.
　図７は本発明の上記変速原理の変形例に係る速度線図を示しており，図１の速度線図で表される４つの要素の回転数を２つの自由度に規制する遊星歯車機構を，３つの要素を２つの自由度に規制する２組の遊星歯車機構で置き換えたものである。具体的には速度線図において第１遊星歯車機構の３番目の要素と第２遊星歯車機構の２番目の要素を結合すると共に、第１遊星歯車機構の２番目の要素と第２遊星歯車機構の１番目の要素を係合機構１を介して結合し、第２遊星歯車機構の３番目の要素を歯車対を介して出力軸に結合する。従って、係合機構１を締結すると共に係合機構２を開放しバリエータの回転数比を変える時、速度線図上においてこれら２組の遊星歯車機構は４つの要素の回転数を２つの自由度に規制する遊星歯車機構と等価な動作を示し、出力２が速度線図の左端から４番目の要素から出力される。他方、係合機構１を開放すると共に係合機構２を締結しバリエータの回転数比を変える時、第１遊星歯車機構は速度線図上の左端から２番目の要素の回転数を中心として、第２遊星歯車機構は第１遊星歯車機構の３番目の要素の回転数を中心としてそれぞれ動作し、出力１が速度線図の左端から１番目の要素から出力される。図７のようにλ２がλ１の倍よりも小さい場合は，図１の速度線図上で左から４番目の要素と係合機構を直接結合するよりも，係合機構にかかるトルクを小さくすることができる。後述する変形例のうち図１５、図１７および図２２で有効かつ適用可能である。 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. Specifically, in the velocity diagram, 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. Therefore, when the engagement mechanism 1 is fastened and the engagement mechanism 2 is released to change the rotation speed ratio of the variator, these two planetary gear mechanisms on the velocity diagram can change the rotation speed of the four elements to two degrees of freedom. The output 2 is output from the fourth element from the left end of the velocity diagram. On the other hand, when opening the engagement mechanism 1 and fastening the engagement mechanism 2 to change the rotation speed ratio of the variator, the first planetary gear mechanism is centered on the rotation speed of the second element from the left end on the velocity diagram. The second planetary gear mechanism operates around the rotation speed of the third element of the first planetary gear mechanism, and output 1 is output from the first element from the left end of the velocity diagram. When λ2 is smaller than twice λ1 as shown in FIG. 7, the torque applied to the engagement mechanism is made smaller than when the fourth element from the left is directly coupled to the engagement mechanism on the velocity diagram of FIG. be able to. Of the modified examples to be described later, FIGS. 15, 17 and 22 are effective and applicable.
　図８は本発明の無段変速機（１００）における変速機のバリエータの回転数比を従来例と比較したグラフである．本発明では従来例とバリエータ変速レシオ幅は同一でありながら変速機の変速レシオ幅が広くなることがわかる。 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. In the present invention, it is understood that the transmission ratio width of the transmission is wide while the variator transmission ratio width is the same as that of the conventional example.
　図９は本発明の無段変速機（１００）におけるプーリー回転数を従来例と比較したグラフで，従来例はプーリー１が駆動側でプーリー２が従動側である。
いずれも入力軸の回転数を一定としたプーリーの回転数であり，図９(b)の本発明では，図９(a)の従来例の最大回転数Nmaxよりもプーリーの最大回転数N'maxが小さいことがわかる。 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. In 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. In the present invention of FIG. 9B, 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.
　図１０は本発明の無段変速機（１００）におけるプーリートルクを従来例と比較したグラフで，従来例はプーリー１が駆動側でプーリー２が従動側である。
いずれも入力軸のトルクを一定としたプーリーの回転数であり，図１０(b)の本発明では，図１０(a)の従来例の最大トルクTmaxよりもプーリーの最大トルクT'maxが小さいことがわかる。 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. In 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. In the present invention of FIG. 10 (b), 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.
　図１１は本発明の無段変速機（１００）におけるプーリー伝達動力を従来例と比較したグラフで，従来例はプーリー１が駆動側でプーリー２が従動側である。いずれも入力軸からの動力Pinを一定としたプーリーの伝達動力であり，プーリー伝達動力は図１１(a)の従来例では常に入力軸からの動力Pinと等しくなるが，図１１(b)の本発明では常に入力軸からの動力Pinより小さくなる。 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. In 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.
　なお、本発明の無段変速機は上記実施例（無段変速機（１００））のみに限定されるものではなく、本発明の技術的特徴の要旨を変更しない範囲内において種々の設計変更事項が含まれる。例えば、４つの要素の回転数を２つの自由度に規制する上記遊星歯車機構（１９）については、図１２から図２４に示される変形例１から変形例１３に係る遊星歯車機構が提供される。以下、簡単に説明する。 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. For example, for the 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.
　図１２は、本発明の無段変速機の変形例１に係る遊星歯車機構（１９Ａ）及びその速度線図を示す説明図である。
　この遊星歯車機構（１９Ａ）は、上記遊星歯車機構（１９）においてサンギヤ（５）が第１ピニオン（３）に噛み合うように変更されたものである。その他の構成については上記遊星歯車機構（１９）と同じである。従って、速度線図上に並ぶ端から１番目から４番目の各要素についても上記遊星歯車機構（１９）と同じである。 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). About another structure, it is the same as the said planetary gear mechanism (19). Accordingly, each of the first to fourth elements from the end arranged on the velocity diagram is the same as the planetary gear mechanism (19).
　図１３は、本発明の無段変速機の変形例２に係る遊星歯車機構（１９Ｂ）及びその速度線図を示す説明図である。
　この遊星歯車機構（１９Ｂ）は、上記遊星歯車機構（１９Ａ）のサンギヤとリングギヤの関係および左右を反転させたものである。第１ギヤ（８）を第２プーリー（１７）側に配置し、そして第１サンギヤ（５）と第２プーリー（１７）が結合されると共にリングギヤ（６）と第３ギヤ（１０）が結合され、さらに第２リングギヤ（７）に代わって第２サンギヤ（５'）が備えられ、その第２サンギヤ（５'）と第１ギヤ（８）が結合されたものに相当する。その結果、リングギヤ（６）及び第１サンギヤ（５）は第１プーリー（１６）及び第２プーリー（１７）にそれぞれ結合され、さらに第２サンギヤ（５'）は第１クラッチ（２０）を介して第１ギヤ（８）に結合される。従って、速度線図上に並ぶ左端から１番目の要素はリングギヤ（６）、２番目の要素はキャリア（２）、３番目の要素は第１サンギヤ（５）、４番目の要素は第２サンギヤ（５'）となる。 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. Further, 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). As a result, 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). 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 ').
　図１４は、本発明の無段変速機の変形例３に係る遊星歯車機構（１９Ｃ）及びその速度線図を示す説明図である。
　この遊星歯車機構（１９Ｃ）は、上記遊星歯車機構（１９Ｂ）においてリングギヤ（６）が第２ピニオン（４）に噛み合うように変更されたものである。その他の構成については上記遊星歯車機構（１９Ｂ）と同じである。従って、速度線図上に並ぶ端から１番目から４番目の各要素についても上記遊星歯車機構（１９Ｂ）と同じである。 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). About another structure, it is the same as the said planetary gear mechanism (19B). Accordingly, each of the first to fourth elements from the end arranged on the velocity diagram is the same as the planetary gear mechanism (19B).
　なお、以後の図１５から図２３に示される変形例は、４つの要素の回転数を２つの自由度に規制する遊星歯車機構を、３つの要素の回転数を２つの自由度に規制する２組の遊星歯車機構によって構築した例である。また、２組の遊星歯車機構について入力軸（１）と結合するキャリア（２）を備える遊星歯車機構のことを第１遊星歯車機構と呼び、それ以外の遊星歯車機構を第２遊星歯車機構と呼ぶことにする。 In the following modification examples shown in FIGS. 15 to 23, 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.
　図１５は、本発明の無段変速機の変形例４に係る遊星歯車機構（１９Ｄ）及びその速度線図を示す説明図である。
　この遊星歯車機構（１９Ｄ）では、３つの要素の回転数を２つの自由度に規制する２組の第１遊星歯車機構（１９D-1）及び第２遊星歯車機構（１９D-2）において第１キャリア（２）と第２サンギヤ（５'）並びに第１リングギヤ（６）と第２キャリア（２'）がそれぞれ結合されることにより、上記変速原理を満足する４つの要素の回転数を２つの自由度に規制する遊星歯車機構が構築される。この場合、速度線図上に並ぶ１番目の要素である第１サンギヤ（５）及び３番目の要素である第１リングギヤ（６）と第１プーリー（１６）及び第２プーリー（１７）がそれぞれ結合されており、２番目の要素である第１キャリア（２）と入力軸（１）が結合され、更に１番目の要素である第１サンギヤ（５）と４番目の要素である第２リングギヤ（７）は第２クラッチ（２１）及び第１クラッチ（２０）を介して選択的に出力軸（１３）と係合可能に構成されている。 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.
In 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. By combining 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. In this case, the first sun gear (5), which is the first element arranged on the velocity diagram, and 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).
　図１６は、本発明の無段変速機の変形例５に係る遊星歯車機構（１９Ｅ）及びその速度線図を示す説明図である。
　この遊星歯車機構（１９Ｅ）は、上記遊星歯車機構（１９Ｄ）において第１キャリア（２）と第２サンギヤ（５'）の間を第１クラッチ（２０）を介して結合すると共に，出力２を取り出すための第１ギヤ（８）と第２リングギヤ（７）を直接結合したものに相当する。従って、第１クラッチ（２０）を係合してバリエータの回転数比を変える時、速度線図上においてこの遊星歯車機構（１９Ｅ）は４つの要素の回転数を２つの自由度に規制する上記遊星歯車機構（１９Ｄ）と同様な動作を示し、出力２が速度線図上の４番目の要素である第２リングギヤ（７）から出力軸（１３）へ出力される。他方、第２クラッチ（２１）を係合してバリエータの回転数比を変える時、第１遊星歯車機構（１９E-1）は速度線図上の２番目の要素である第１キャリア（２）の回転数を中心として、第２遊星歯車機構（１９E-2）は速度線図上の３番目の要素である第２キャリア（２'）の回転数を中心としてそれぞれ動作し、出力１が速度線図上の１番目の要素である第１サンギヤ（５）から出力軸（１３）へ出力される。 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. Operation similar to that of the planetary gear mechanism (19D) is shown, 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). On the other hand, when the second clutch (21) is engaged to change the rotation speed ratio of the variator, the first planetary gear mechanism (19E-1) is the second element on the speed diagram, the first carrier (2). The second planetary gear mechanism (19E-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 sun gear (5), which is the first element on the diagram, is output to the output shaft (13).
　図１７は、本発明の無段変速機の変形例６に係る遊星歯車機構（１９Ｆ）及びその速度線図を示す説明図である。
　この遊星歯車機構（１９Ｆ）では、上記遊星歯車機構（１９Ｄ）と同様に、３つの要素の回転数を２つの自由度に規制する２組の第１遊星歯車機構（１９F-1）及び第２遊星歯車機構（１９F-2）において第１キャリア（２）と第２サンギヤ（５'）並びに第１リングギヤ（６）と第２キャリア（２'）がそれぞれ結合されることにより、上記変速原理を満足する４つの要素の回転数を２つの自由度に規制する遊星歯車機構が構築される。上記遊星歯車機構（１９Ｄ）と異なり、第２遊星歯車機構（１９F-2）が入力側に位置し、第１遊星歯車機構（１９F-1）が第２プーリー（１７）の側に位置している。 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.
In 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. In the planetary gear mechanism (19F-2), 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. Unlike the planetary gear mechanism (19D), the second planetary gear mechanism (19F-2) is located on the input side, and the first planetary gear mechanism (19F-1) is located on the second pulley (17) side. Yes.
　図１８は、本発明の無段変速機の変形例７に係る遊星歯車機構（１９Ｇ）及びその速度線図を示す説明図である。
　この遊星歯車機構（１９Ｇ）は、上記遊星歯車機構（１９Ｆ）において第１キャリア（２）と第２サンギヤ（５'）の間を第１クラッチ（２０）を介して結合すると共に，出力２を取り出すための第１ギヤ（８）と第２リングギヤ（７）を直接結合したものに相当する。従って、第１クラッチ（２０）を係合してバリエータの回転数比を変える時、速度線図上においてこの遊星歯車機構（１９Ｇ）は４つの要素の回転数を２つの自由度に規制する上記遊星歯車機構（１９Ｆ）と同様な動作を示し、出力２が速度線図上の４番目の要素である第２リングギヤ（７）から出力軸（１３）へ出力される。他方、第２クラッチ（２１）を係合してバリエータの回転数比を変える時、第１遊星歯車機構（１９G-1）は速度線図上の２番目の要素である第１キャリア（２）の回転数を中心として、第２遊星歯車機構（１９G-2）は速度線図上の３番目の要素である第２キャリア（２'）の回転数を中心としてそれぞれ動作し、出力１が速度線図上の１番目の要素である第１サンギヤ（５）から出力軸（１３）へ出力される。 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. Operation similar to that of the planetary gear mechanism (19F) is shown, 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). On the other hand, when the second clutch (21) is engaged to change the rotation ratio of the variator, the first planetary gear mechanism (19G-1) is the second element on the speed diagram, the first carrier (2). The second planetary gear mechanism (19G-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 sun gear (5), which is the first element on the diagram, is output to the output shaft (13).
　図１９は、本発明の無段変速機の変形例８に係る遊星歯車機構（１９Ｈ）及びその速度線図を示す説明図である。
　この遊星歯車機構（１９Ｈ）は、上記遊星歯車機構（１９Ｆ）と同様に、３つの要素の回転数を２つの自由度に規制する第２遊星歯車機構（１９H-2）が入力側に位置し、同第１遊星歯車機構（１９H-1）が第２プーリー（１７）の側に位置している。上記遊星歯車機構（１９Ｆ）と異なり、第１遊星歯車機構（１９H-1）の第１キャリア（２）と第２遊星歯車機構（１９H-2）の第２リングギヤ（７）が結合され、さらに第１リングギヤ（６）と第２キャリア（２'）が結合されることにより、上記変速原理を満足する４つの要素の回転数を２つの自由度に規制する遊星歯車機構を構築している。その結果、出力２は第２サンギヤ（５'）から出力される。従って、速度線図上に並ぶ左端から４番目の要素は第２サンギヤ（５'）となる。 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.
In the planetary gear mechanism (19H), 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. Unlike the planetary gear mechanism (19F), 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 By combining the first ring gear (6) and the second carrier (2 ′), 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. As a result, output 2 is output from the second sun gear (5 ′). Accordingly, the fourth element from the left end arranged on the velocity diagram is the second sun gear (5 ′).
　図２０は、本発明の無段変速機の変形例９に係る遊星歯車機構（１９Ｉ）及びその速度線図を示す説明図である。
　この遊星歯車機構（１９Ｉ）は、上記遊星歯車機構（１９Ｈ）のサンギヤとリングギヤの関係および左右を反転させたものである。第１ギヤ（８）を第２プーリー（１７）側に配置し、そして第１サンギヤ（５）と第２プーリー（１７）が結合されると共に第１リングギヤ（６）と第３ギヤ（１０）が結合され、さらに第２サンギヤ（５'）と第１ギヤ（８）が結合されたものに相当する。その結果、第１リングギヤ（６）及び第１サンギヤ（５）と第１プーリー（１６）及び第２プーリー（１７）がそれぞれ結合され、さらに第２サンギヤ（５'）は第１クラッチ（２０）を介して第１ギヤ（８）に結合される。従って、速度線図上に並ぶ左端から１番目の要素は第１リングギヤ（６）、２番目の要素は第１キャリア（２）、３番目の要素は第１サンギヤ（５）、４番目の要素は第２サンギヤ（５'）となる。 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). Corresponds to a combination of the second sun gear (5 ′) and the first gear (8). As a result, 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 ').
　図２１は、本発明の無段変速機の変形例１０に係る遊星歯車機構（１９Ｊ）及びその速度線図を示す説明図である。
　この遊星歯車機構（１９Ｊ）は、上記遊星歯車機構（１９Ｈ）において第１キャリア（２）と第２リングギヤ（７）が結合されると共に第１サンギヤ（５）と第２キャリア（２'）が結合され、第１サンギヤ（５）及び第１リングギヤ（６）と第２プーリー（１７）及び第１プーリー（１６）がそれぞれ結合されたものに相当する。従って、上記遊星歯車機構（１９Ｈ）と異なり速度線図上に並ぶ左端から１番目の要素は第１リングギヤ（６）、３番目の要素は第１サンギヤ（５）となる。 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.
In the planetary gear mechanism (19J), 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).
　図２２は、本発明の無段変速機の変形例１１に係る遊星歯車機構（１９Ｋ）及びその速度線図を示す説明図である。
　この遊星歯車機構（１９Ｋ）は、上記遊星歯車機構（１９Ｉ）において第１キャリア（２）と第２サンギヤ（５'）が結合されると共に第１サンギヤ（５）と第２キャリア（２'）が結合され、第１サンギヤ（５）及び第１リングギヤ（６）と第２プーリー（１７）及び第１プーリー（１６）がそれぞれ結合されたものに相当する。従って、上記遊星歯車機構（１９Ｉ）と異なり速度線図上に並ぶ左端から３番目の要素は第２リングギヤ（７）となる。 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.
In the planetary gear mechanism (19K), 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).
　図２３は、本発明の無段変速機の変形例１２に係る遊星歯車機構（１９Ｌ）及びその速度線図を示す説明図である。
　この遊星歯車機構（１９Ｌ）は、上記遊星歯車機構（１９Ｋ）において第１キャリア（２）と第２サンギヤ（５'）の間を第１クラッチ（２０）を介して結合すると共に，出力２を取り出すための第１ギヤ（８）と第２リングギヤ（７）を直接結合したものに相当する。従って、第１クラッチ（２０）を係合してバリエータの回転数比を変える時、速度線図上においてこの遊星歯車機構（１９Ｌ）は４つの要素の回転数を２つの自由度に規制する上記遊星歯車機構（１９Ｋ）と同様な動作を示し、出力２が速度線図上の４番目の要素である第２リングギヤ（７）から出力軸（１３）へ出力される。他方、第２クラッチ（２１）を係合してバリエータの回転数比を変える時、第１遊星歯車機構（１９L-1）は速度線図上の２番目の要素である第１キャリア（２）の回転数を中心として、第２遊星歯車機構（１９L-2）は速度線図上の３番目の要素である第２キャリア（２'）の回転数を中心としてそれぞれ動作し、出力１が速度線図上の１番目の要素である第１リングギヤ（６）から出力軸（１３）へ出力される。 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). On the other hand, when the second clutch (21) is engaged to change the rotation ratio of the variator, 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).
　図２４は、本発明の無段変速機の変形例１３に係る遊星歯車機構（１９Ｍ）及びその速度線図を示す説明図である。
　この遊星歯車機構（１９Ｍ）は、上記遊星歯車機構（１９Ｂ、１９Ｃ）と同様に、１つのリングギヤ（６）に対し２つのサンギヤ（５,５'）が具備され上記変速原理を満足している。上記遊星歯車機構（１９Ｂ、１９Ｃ）では自転可能で互いに歯車ピッチ円径の異なる第１ピニオン（３）と第２ピニオン（４）が同軸で一体化され、第１サンギヤ（５）と第１ピニオン（３）が噛み合い、第２サンギヤ（５'）と第２ピニオン（４）が噛み合う。それに対し、この遊星歯車機構（１９Ｍ）では自転可能な互いに軸方向長さの異なる第１ピニオン（３'）と第２ピニオン（４'）がギヤ対を成して構成され、第１サンギヤ（５）と第１ピニオン（３'）が噛み合い、第２サンギヤ（５'）と第２ピニオン（４'）が噛み合い，第１ピニオン（３'）と第２ピニオン（４'）が噛み合う。なお、速度線図上に並ぶ端から数えて１番目から４番目の各要素は，それぞれ第１サンギヤ（５）、第１キャリア（２）、第１リングギヤ（６）、第２サンギヤ（５'）となる。 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. . In the planetary gear mechanism (19B, 19C), 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. On the other hand, in the planetary gear mechanism (19M), 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. Note that 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 ′). )

Claims (7)

  1. 　４つの要素の回転数を２つの自由度に規制する遊星歯車機構の，速度線図上に並ぶ４つの要素のうち，端から１番目の要素及び３番目の要素をバリエータの２つの軸と直接または固定された回転数比で結合しておき，２番目の要素を入力軸と直接または固定された回転数比で結合しておき，前記バリエータの回転数比を変えると前記１番目の要素の変速レシオ幅と前記４番目の要素の変速レシオ幅の積が，前記バリエータの変速レシオ幅を上回ることを特徴とする無段変速機。 Of the four elements arranged on the velocity diagram of the planetary gear mechanism that regulates the number of rotations of the four elements to two degrees of freedom, the first and third elements from the end are directly connected to the two axes of the variator Alternatively, it is coupled with a fixed rotation speed ratio, and the second element is coupled directly with the input shaft or with a fixed rotation speed ratio. When the rotation speed ratio of the variator is changed, the first element A continuously variable transmission, wherein a product of a transmission ratio width and a transmission ratio width of the fourth element exceeds a transmission ratio width of the variator.
  2. 　４つの要素の回転数を２つの自由度に規制する遊星歯車機構を備え，該遊星歯車機構の速度線図上に並ぶ４つの要素のうち，端から１番目の要素と３番目の要素にバリエータの２つの軸が結合され，２番目の要素に入力軸が結合され，前記１番目の要素と４番目の要素は係合機構を介してそれぞれ出力軸と係合することができ，前記バリエータの変速比範囲内に前記１番目の要素と係合したときの前記出力軸の回転数と前記４番目の要素と係合したときの前記出力軸の回転数が等しくなる変速比が存在することを特徴とする無段変速機。 A planetary gear mechanism that regulates the number of rotations of the four elements to two degrees of freedom is provided. Among the four elements arranged on the speed diagram of the planetary gear mechanism, the variator is arranged on the first element and the third element from the end. Are coupled to each other, the second element is coupled to the input shaft, and the first element and the fourth element can be engaged with the output shaft via an engagement mechanism, respectively. There exists a gear ratio in the gear ratio range in which the rotational speed of the output shaft when engaged with the first element is equal to the rotational speed of the output shaft when engaged with the fourth element. A continuously variable transmission.
  3. 　入力軸と，キャリアと第１ピニオンと第２ピニオンとサンギヤと第１リングギヤと第２リングギヤで構成される遊星歯車機構と，第５ギヤと同軸上に一体化され対向配置された第１円錐部材と第２円錐部材とで構成される第１プーリーと，前記第１リングギヤと同軸上に一体化され対向配置された第３円錐部材と第４円錐部材とで構成される第２プーリーと，前記第１プーリーと前記第２プーリーに巻き掛けられたベルトとから構成され，前記第１プーリーの２つの円錐部材の距離により定まる巻き掛け径と前記第２プーリーの２つの円錐部材の距離により定まる巻き掛け径の比に応じて回転数比を変えることができるバリエータと，前記第２リングギヤと第１クラッチにより係合することができる第１ギヤと，前記第１ギヤとかみ合う第２ギヤと，前記サンギヤと同軸上に一体化された第３ギヤと，前記第３ギヤ及び前記第５ギヤとかみ合う第４ギヤと，第２クラッチにより前記第４ギヤと係合することができかつ前記第２ギヤと一体化された出力軸とから構成されていることを特徴とする請求項１又は２に記載の無段変速機。 A planetary gear mechanism comprising an input shaft, a carrier, a first pinion, a second pinion, a sun gear, a first ring gear and a second ring gear, and a first conical member which is coaxially integrated with and arranged oppositely to the fifth gear. A first pulley composed of a first conical member and a second conical member, a second pulley composed of a third conical member and a fourth conical member which are coaxially integrated with and disposed opposite to the first ring gear; A winding comprising a first pulley and a belt wound around the second pulley, and a winding diameter determined by a distance between two conical members of the first pulley and a distance determined by a distance between two conical members of the second pulley A variator capable of changing the rotation speed ratio according to the ratio of the applied diameter, a first gear that can be engaged with the second ring gear and the first clutch, and a first gear that meshes with the first gear. A gear, a third gear coaxially integrated with the sun gear, a fourth gear meshing with the third gear and the fifth gear, a second clutch and being engageable with the fourth gear; The continuously variable transmission according to claim 1 or 2, comprising an output shaft integrated with the second gear.
  4. 　前記入力軸と同軸上に最も入力に近い場所に前記第３ギヤ，次に前記第１ギヤ，その次に前記第１クラッチの順に各機構要素が配置されており，前記出力軸と同軸上に軸方向で最も入力に近い場所に前記第４ギヤ，次に前記第２クラッチ，その次に前記第２ギヤが配置されていることを特徴とする請求項３に記載の無段変速機。 The mechanism elements are arranged in the order of the third gear, then the first gear, and then the first clutch at a position closest to the input coaxially with the input shaft, and coaxial with the output shaft. 4. The continuously variable transmission according to claim 3, wherein the fourth gear, the second clutch, and then the second gear are arranged at a position closest to the input in the axial direction.
  5. 　前記入力軸と同軸上の入力から最も遠い場所に前記第２プーリーは配置されていることを特徴とする請求項３又は４に記載の無段変速機構。 The continuously variable transmission mechanism according to claim 3 or 4, wherein the second pulley is disposed at a position farthest from an input coaxial with the input shaft.
  6. 　少なくとも３つの穴があけられた固定部材の３つの穴に，それぞれ前記第１リングギヤ又は前記第２プーリーを支持する第１軸受と前記出力軸の端部を支持する第２軸受と前記第５ギヤ又は第１プーリーを支持する第３軸受が固定されており，かつ前記固定部材がケースに固定されていることを特徴とする請求項３から５の何れかに記載の無段変速機。 The first bearing that supports the first ring gear or the second pulley, the second bearing that supports the end of the output shaft, and the fifth gear are respectively inserted into the three holes of the fixing member having at least three holes. 6. The continuously variable transmission according to claim 3, wherein a third bearing supporting the first pulley is fixed, and the fixing member is fixed to the case.
  7. 　３つの要素の回転数を２つの自由度にそれぞれ規制する第１遊星歯車機構及び第２遊星歯車機構を備え，該第１遊星歯車機構の速度線図上で端から１番目の要素と３番目の要素に前記バリエータの２つの軸が結合され，２番目の要素に前記入力軸が結合されており，前記１番目の要素と前記出力軸との間に係合機構を備えており，前記第２遊星歯車機構の速度線図上で端から２番目の要素と前記第１遊星歯車機構の前記３番目の要素が結合されており，前記第２遊星歯車機構の端から３番目の要素は前記出力軸と結合されており，該第２遊星歯車機構の端から１番目の要素と前記入力軸との間に係合機構を備えており，２つの係合機構を選択的に係合することができることを特徴とする無段変速機。 The first planetary gear mechanism and the second planetary gear mechanism that respectively regulate the number of rotations of the three elements to two degrees of freedom are provided, and the first and third elements from the end on the velocity diagram of the first planetary gear mechanism Two shafts of the variator are coupled to the second element, the input shaft is coupled to the second element, and an engagement mechanism is provided between the first element and the output shaft. The second element from the end on the velocity diagram of the two planetary gear mechanism is coupled to the third element of the first planetary gear mechanism, and the third element from the end of the second planetary gear mechanism is An engagement mechanism is connected to the output shaft and is provided between the first element from the end of the second planetary gear mechanism and the input shaft, and selectively engages the two engagement mechanisms. A continuously variable transmission characterized in that
PCT/JP2015/084731 2014-12-18 2015-12-10 Stepless transmission WO2016098685A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2016564820A JP6280994B6 (en) 2014-12-18 2015-12-10 Continuously variable transmission

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014-256632 2014-12-18
JP2014256632 2014-12-18

Publications (1)

Publication Number Publication Date
WO2016098685A1 true WO2016098685A1 (en) 2016-06-23

Family

ID=56126577

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2015/084731 WO2016098685A1 (en) 2014-12-18 2015-12-10 Stepless transmission

Country Status (2)

Country Link
JP (1) JP6280994B6 (en)
WO (1) WO2016098685A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108386538A (en) * 2018-03-25 2018-08-10 大连碧蓝节能环保科技有限公司 Planetary gear stepless speed changing retarder

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58109751A (en) * 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 Static hydraulic mechanical adjusting connecting transmission with power branch section at input side
JP2006327570A (en) * 2005-04-28 2006-12-07 Toyota Central Res & Dev Lab Inc Power transmission system
JP2006329338A (en) * 2005-05-26 2006-12-07 Nissan Motor Co Ltd Shunt type stepless transmission
JP2012202473A (en) * 2011-03-25 2012-10-22 Jatco Ltd Automatic transmission

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58109751A (en) * 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 Static hydraulic mechanical adjusting connecting transmission with power branch section at input side
JP2006327570A (en) * 2005-04-28 2006-12-07 Toyota Central Res & Dev Lab Inc Power transmission system
JP2006329338A (en) * 2005-05-26 2006-12-07 Nissan Motor Co Ltd Shunt type stepless transmission
JP2012202473A (en) * 2011-03-25 2012-10-22 Jatco Ltd Automatic transmission

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108386538A (en) * 2018-03-25 2018-08-10 大连碧蓝节能环保科技有限公司 Planetary gear stepless speed changing retarder

Also Published As

Publication number Publication date
JP6280994B2 (en) 2018-02-14
JP6280994B6 (en) 2018-06-27
JPWO2016098685A1 (en) 2017-08-10

Similar Documents

Publication Publication Date Title
JP5340336B2 (en) Automatic transmission
WO2013175583A1 (en) Power transmission device for vehicle
JP6014968B2 (en) Continuously variable transmission
JP4983301B2 (en) Transmission
JP6137809B2 (en) Dual clutch automatic transmission
WO2013175582A1 (en) Vehicle power transmission device
JP6193092B2 (en) Power transmission device
US10030749B2 (en) Continuously variable transmission
JP2006329338A (en) Shunt type stepless transmission
JP2008144904A (en) Continuously variable transmission of power split type
JP6280994B6 (en) Continuously variable transmission
WO2015137124A1 (en) Automatic transmission
JPWO2016098685A6 (en) Continuously variable transmission
JP5946484B2 (en) Continuously variable transmission
JP2000320630A (en) Continuously variable transmission device
JP2016080108A (en) transmission
WO2015114873A1 (en) Power-dividing continuously variable transmission
JP2017155841A (en) Gear change device
JP5790575B2 (en) transmission
JP6379218B2 (en) Continuously variable transmission
JP5821700B2 (en) Drive train
JP2002122207A (en) Transmission
JP2017115918A (en) Stepless speed change device
JP6533084B2 (en) Power split type continuously variable transmission
WO2013121676A1 (en) Vehicle transmission

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 15869890

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2016564820

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 15869890

Country of ref document: EP

Kind code of ref document: A1