JP6280994B6 - Continuously variable transmission - Google Patents

Description

  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.

  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.

  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).

  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).

  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).

JP 7-293663 A JP 2006-329338 A US Pat. No. 5,643,131

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.

  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.

  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.

  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.

  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.

  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.

  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.

  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.

  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.

  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.

  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 2 of the second pulley (17) Can be engaged by the variator (15) capable of changing the rotation speed ratio according to the ratio of the winding diameter determined by the distance of the conical member, the second ring gear (7) and the 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.

  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.

  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.

  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.

  A fifth feature of the continuously variable transmission according to the present invention is that a second pulley (17) is disposed at a position farthest from an input coaxial with the input shaft (1).

  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.

  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).

  According to the above configuration, the parts constituting the transmission are assembled to the fixing member (30) in advance, and the assembly is improved by fixing the component 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. Thus, the two engagement mechanisms can be selectively engaged.

  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.

  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.

It is a speed diagram which shows the speed change principle of the continuously variable transmission of this invention. It is a block diagram which shows the continuously variable transmission of this invention. 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. 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. 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. 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. It is a speed diagram which shows the modification which concerns on the speed change principle of the continuously variable transmission of this invention. It is explanatory drawing which shows the rotation speed ratio of the transmission which concerns on the continuously variable transmission of this invention. It is explanatory drawing which shows the rotation speed of the pulley which concerns on the continuously variable transmission of this invention. It is explanatory drawing which shows the pulley torque which concerns on the continuously variable transmission of this invention. It is explanatory drawing which shows the pulley transmission power which concerns on the continuously variable transmission of this invention. It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 1 of the continuously variable transmission of this invention. It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 2 of the continuously variable transmission of this invention. It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 3 of the continuously variable transmission of this invention. It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 4 of the continuously variable transmission of this invention. It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 5 of the continuously variable transmission of this invention. It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 6 of the continuously variable transmission of this invention. It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 7 of the continuously variable transmission of this invention. It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 8 of the continuously variable transmission of this invention. It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 9 of the continuously variable transmission of this invention. It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 10 of the continuously variable transmission of this invention. It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 11 of the continuously variable transmission of this invention. It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 12 of the continuously variable transmission of this invention. It is explanatory drawing which shows the planetary gear mechanism which concerns on the modification 13 of the continuously variable transmission of this invention.

  Hereinafter, the present invention will be described in more detail with reference to embodiments shown in the drawings.

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.

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.

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.

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

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.

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.

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.

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)

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).

  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.

  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.

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.

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, the first clutch (20) can be obtained when the rotation speed ratio of the second pulley (17) to the first pulley (16) is maximum. No matter which of the second clutch (21) is engaged, the rotational speed ratio of each element to the rotational speed of the input shaft (1) does not change.

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 Equations 45 to 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

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.

  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.

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

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.

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.

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.

  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.

  FIG. 8 is a graph comparing the speed ratio of the variator of the transmission in the continuously variable transmission (100) of the present invention with that of 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.

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.

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.

  FIG. 11 is a graph comparing the pulley transmission power in the continuously variable transmission (100) of the present invention with a 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.

  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.

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).

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 ').

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).

  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.

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).

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).

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.

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).

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 ′).

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 ').

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).

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).

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).

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)

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, characterized in that the product of the transmission ratio width and the transmission ratio width of the fourth element exceeds the transmission ratio width of the variator.   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.   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 comprised of a first pulley and a belt wound around the second pulley, the winding diameter being determined by the distance between the two conical members of the first pulley and the distance between the 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 second gear that meshes with the first gear. Y, a third gear coaxially integrated with the sun gear, a fourth gear meshing with the third gear and the fifth gear, and a second clutch that can be engaged with the fourth gear; The continuously variable transmission according to claim 1 or 2, comprising an output shaft integrated with the second gear.   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. The continuously variable transmission according to claim 3 or 4, wherein the second pulley is disposed at a position farthest from an input coaxial with the input shaft .   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. 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 axes of the variator is coupled to the element, the input shaft to the second element are coupled, includes an engagement mechanism between the output shaft and the first element, the second 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

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