JP4715794B2 - Continuously variable transmission - Google Patents

Description

  The present invention relates to a continuously variable transmission suitable for use in vehicles such as automobiles, and more particularly to a power circulation mechanism that circulates power by combining forward rotation of an input shaft and continuously variable reverse rotation of a continuously variable transmission. The present invention relates to a continuously variable transmission that can achieve a forward / reverse gear ratio suitable for a vehicle to be mounted.

  In recent years, for example, a continuously variable transmission including a toroidal continuously variable transmission and a power circulation mechanism has been proposed (Patent Document 1). This continuously variable transmission is configured by combining a toroidal-type continuously variable transmission (variator), a power circulation mechanism, and a reverse gear mechanism, and the variable speed rotation of the variator and the input rotation from the input shaft are combined with the power circulation mechanism. Using the power (torque) circulation synthesized in step 1, the reverse gear ratio and the forward start gear ratio are achieved in the low range including gear neutral (GN), and the high speed range that reversely uses the variable speed rotation of the variator Is achieved, and an appropriate forward / reverse speed rotation is obtained as the output rotation of the automobile.

UK Publication GB 2410302 A

  However, as described above, a vehicle that achieves a reverse gear ratio and a forward start gear ratio by power circulation at the boundary of the gear neutral position has a certain reverse speed ratio as a mounted vehicle. Since it is necessary, the setting of the gear ratio in the power circulation mechanism is limited. That is, the power circulation mechanism includes an input gear connected to the input shaft, a continuously variable transmission rotation gear connected to the output disk of the variator, and a circulation rotation that is a combined rotation that is powered and circulated by these two gears. In order to obtain the necessary reverse speed ratio, the gear ratio of the circulation rotation gear with respect to the input gear, and the gear ratio of the circulation rotation gear with respect to the continuously variable rotation gear, Needs to be set to be substantially uniform (the circulation rotation gear is approximately in the middle between the input gear and the continuously variable rotation rotation gear in the direction of the gear ratio axis of the speed diagram). End up. For this reason, there is a problem that the torque sharing between the input shaft and the variator becomes substantially equal as the torque sharing in the power circulation, and the load of the variator cannot be reduced.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a continuously variable transmission that can reduce the load of a continuously variable transmission device while being able to obtain a suitable reverse gear ratio range for a mounted vehicle. It is what.

The present invention according to claim 1 (see, for example, FIG. 1 to FIG. 6) includes a continuously variable transmission (10) capable of continuously variable transmission while reversing the forward rotation of the input shaft (2), and the input shaft (2 A continuously variable transmission (IN) and a continuously variable reverse rotation (Vout) of the continuously variable transmission (10) and a power circulation mechanism (20) capable of power circulation. In (1),
The power circulation mechanism (20)
An input rotation element (R1 in FIGS. 1 and 2; S1 in FIGS. 4 and 5) capable of inputting the forward rotation (IN) of the input shaft (2);
A continuously variable transmission rotating element (S1 in FIGS. 1 and 2; CR1 in FIGS. 4 and 5) for inputting a continuously variable reverse rotation (Vout) from the continuously variable transmission (10);
Rotation of the input rotation element (R1 in FIGS. 1 and 2, S1 in FIGS. 4 and 5) and rotation of the continuously variable rotation element (S1 in FIGS. 1 and 2, CR1 in FIGS. 4 and 5) Accordingly, the power circulation rotation element (CR1, FIGS. 4 and 4 in FIG. 1 and FIG. 2) is rotated by the power circulation rotation (IVout) having a speed ratio width of the forward rotation greater than the speed ratio width of the reverse rotation. 5 S2), and
A reversing gear mechanism (30) capable of reversing the power circulation rotation (IVout) of the power circulation rotation element (CR1 in FIGS. 1 and 2, S2 in FIGS. 4 and 5);
A reverse rotation (OutL) obtained by reversing the power circulation rotation (IVout) of the power circulation rotation element (CR1 in FIGS. 1 and 2, S2 in FIGS. 4 and 5) by the reverse gear mechanism (30) is output shaft (9 A forward engaging element (L) that allows output to be freely output;
A reverse engagement element (R) for freely outputting the power circulation rotation (IVout) of the power circulation rotation element (CR1 in FIGS. 1 and 2, S2 in FIGS. 4 and 5) to the output shaft (9); With
The continuously variable transmission (1) is characterized by the above.

The present invention according to claim 2 (see, for example, FIGS. 1 to 6) is a high engagement that allows the continuously variable reverse rotation (Vout) of the continuously variable transmission (10) to be output to the output shaft (9). An element (H),
The forward engagement element is a low engagement that allows a reverse rotation (OutL) obtained by reversing the normal rotation of the power circulation rotation (IVout) by the reverse gear mechanism (30) to be output to the output shaft (9). Element (L),
The reverse engagement element comprises a reverse engagement element (R) that allows the forward rotation of the power circulation rotation to be freely output to the output shaft (9).
The continuously variable transmission (1) according to claim 1, wherein the continuously variable transmission (1) is provided.

According to a third aspect of the present invention (see, for example, FIGS. 1 to 3), the power circulation mechanism (20) includes a single pinion planetary gear (SP1).
The continuously variable transmission (1 ₁ ) according to claim 1 or 2, characterized in that:

  In addition, although the code | symbol in the said parenthesis is for contrast with drawing, this is for convenience for making an understanding of invention easy, and has no influence on the structure of a claim. It is not a thing.

  According to the first aspect of the present invention, the power circulation mechanism is configured such that the power circulation rotating element rotates by power circulation rotation having a speed ratio width in which the speed ratio width of forward rotation is greater than the speed ratio width of reverse rotation. The reversing rotation obtained by reversing the power circulation rotation by the reversing gear mechanism by the forward engagement element can be output to the output shaft and the power circulation rotation by the reverse engagement element. Since it is configured to be able to output freely to the output shaft, it is possible to obtain a suitable reverse gear ratio range for a vehicle mounted using the power circulation rotation, while the power circulation rotation element for the input rotation element Can be made smaller than the gear ratio of the power circulation rotation element to the continuously variable speed rotation element (the power circulation rotation element is brought closer to the input rotation element in the direction of the tooth number ratio axis of the speed diagram). As a result, it is possible to increase the load on the input shaft and reduce the load on the continuously variable transmission as a share of the torque to be combined in the power circulation, thereby improving the durability of the continuously variable transmission. Can do.

  According to the second aspect of the present invention, when the reverse engagement element is engaged, the forward rotation of the power circulation rotation is output to the output shaft to output the reverse mode for the reverse movement, and the low engagement element is engaged. By rotating the forward rotation of the circulating rotation reversed by the reversing gear mechanism to the output shaft, the low mode for forward start is changed to the continuously variable reverse rotation of the continuously variable transmission by engaging the high engagement element. Is output to the output shaft to achieve high mode for high speed during forward movement. Further, for example, the speed ratio width of the forward rotation in the power circulation rotation is increased as compared with the case where the speed ratio width of the forward rotation and the speed ratio width of the reverse rotation in the power circulation rotation are set substantially equal. Therefore, particularly in the low mode, which is overwhelmingly used compared to the reverse mode, it can be set to decelerate when the power circulation rotation is reversed by the reverse gear mechanism. As a result, the torque can be amplified by the amount of deceleration in the reversing gear mechanism, the torque transmitted by the continuously variable transmission can be reduced by that amount, and the durability of the continuously variable transmission can be further improved. Can do.

  According to the third aspect of the present invention, since the power circulation mechanism can be constituted by a single pinion planetary gear, the continuously variable transmission can be made compact.

<First Embodiment>
A first embodiment according to the present invention will be described below with reference to FIGS. 1 is a skeleton diagram showing a continuously variable transmission according to the first embodiment, FIG. 2 is a velocity diagram of the continuously variable transmission according to the first embodiment, and FIG. 3 is a diagram according to the first embodiment. It is an engagement table | surface of the continuously variable transmission which concerns.

First, it will be described along the continuously variable transmission 1 ₁ of the configuration according to the first embodiment in FIG. CVT (IVT; infinitely variable transmission) 1 1 , as shown in FIG. 1, roughly, be on uniaxially in the transmission case 5, in order from the input side to the output side, the input shaft 2, a toroidal Type continuously variable transmission (hereinafter referred to as “variator”) 10, power circulation mechanism (hereinafter referred to as “power circulation planetary gear”) 20, high clutch (high engagement element) H, reverse gear mechanism 30, A brake (forward engagement element, low engagement element) L, a reverse clutch (backward engagement element, reverse engagement element) R, and an output shaft 9 are provided.

  The variator 10 is of a full toroidal type, and includes two input disks 11A and 11B coupled on the input shaft 2, an output disk 12 whose outer peripheral side is connected to a sun gear S1 and a high clutch H, which will be described later. Power disks 14A, 14B sandwiched between the input disks 11A, 11B and one output disk 12. The input disks 11A and 11B and the output disk 12 have arc-shaped concave grooves 11a and 12a that form part of a circular shape so as to face each other, and are double cavities with two rows of power rollers 14A and 14B interposed therebetween. 13A and 13B are configured to cancel the thrust force between the input disks.

  A plurality of power rollers 14A, 14B are arranged at substantially equal positions in the circumferential direction of the annular double cavities 13A, 13B (for example, three in one cavity), and are composed of spherical bearings, levers, etc. (not shown). The link mechanism is pressed by hydraulic control. Further, the input disks 11A and 11B are pressed in a closed loop by, for example, an L-shaped block and a hydraulic piston installed on the block to sandwich the power rollers 14A and 14B, and the clamping pressure is controlled by the hydraulic pressure. Is done. Then, the contact radius between the input disks 11A, 11B and the output disk 12 is changed by autonomously tilting the power rollers 14A, 14B by the pressure control of the link mechanism and the clamping pressure of the input disks 11A, 11B. To change continuously. In the present variator 10, since the output disk 12 is inverted with respect to the input disks 11A and 11B, the speed ratio is-(minus).

  The power circulation planetary gear 20 includes a carrier CR1 (power circulation rotation element) that rotatably supports one pinion P1, a sun gear S1 (continuously variable rotation element) that meshes with the pinion P1, and a ring gear that meshes with the pinion P1. It is comprised by the single pinion planetary gear SP1 which has R1 (input rotation element).

  The ring gear R1 of the power circulation planetary gear 20 is connected to the input shaft 2, that is, the rotation of a drive source (not shown) such as an engine is transmitted to the input disks 11A and 11B and the ring gear R1 as it is. Since the continuously variable transmission 1 can obtain a gear neutral state as will be described in detail later, it is not necessary to provide a torque converter or the like, and the engine can be directly connected to the input shaft 2.

  The sun gear S 1 of the power circulation planetary gear 20 is connected to the outer peripheral side of the output disk 12. Further, the carrier CR1 is connected to a sun gear S2 of a reverse gear mechanism 30, which will be described in detail later, and is connected to a reverse clutch R and is connected to the output shaft 9 when the reverse clutch R is engaged. .

  The reverse gear mechanism 30 includes a double pinion planetary gear DP2 having a carrier CR2 that rotatably supports two pinions P2 and P3, a sun gear S2 that meshes with the pinion P2, and a ring gear R2 that meshes with the pinion P3. ing. Of these, the sun gear S2 is connected to the carrier CR1 of the power circulation planetary gear 20 as described above, and is connected to the reverse clutch R. When the reverse clutch R is engaged, the sun gear S2 is connected to the output shaft 9. The Further, the ring gear R2 is connected to the low brake L, and when the low brake L is engaged (locked), the ring gear R2 is connected to the transmission case 5 and fixed in rotation. The carrier CR2 is connected to the high clutch H. When the high clutch H is engaged, the carrier CR2 is connected to the output disk 12 and is always connected to the output shaft 9.

The present continuously variable transmission 1 ₁ is to output from an output shaft 9 from rotating in the reverse direction for the forward, which is output from the output shaft 9 of the forward rotation for the reverse, the illustration rotation of the output shaft 9 It is distributed to the left and right drive wheels in an inverted manner by the omitted differential device.

Next will be explained with reference to FIGS. 2 and 3 with reference to FIG. 1, operation of the continuously variable transmission 1 _1.

For example at the time of backward vehicle installed with a continuously variable transmission 1 _1, continuously variable machine 1 ₁ on the basis of the oil pressure control is controlled in the reverse mode for the reverse travel by a shift lever or a hydraulic control device, not shown, As shown in FIG. 3, the reverse clutch R is controlled to be engaged. Then, as shown in FIGS. 1 and 2, the forward rotation IN of the input shaft 2 connected to the engine output shaft is transmitted to the input disks 11 </ b> A and 11 </ b> B of the variator 10 and the ring gear R <b> 1 of the power circulation planetary gear 20. The Among these, the forward rotation of the input shaft 2 input to the input disks 11A and 11B is shifted while being reversed by the variator 10, and the variator output rotation Vout as the continuously variable reverse rotation is output from the output disk 12, and the sun gear S1. Is input.

  When the variator output rotation Vout is input to the sun gear S1, in the power circulation planetary gear 20, the forward rotation IN of the input shaft 2 input to the ring gear R1 and the variator output rotation Vout input to the sun gear S1 are combined by torque circulation. Then, the carrier CR1 is rotated by the power circulation rotation IVout having a speed ratio width in which the speed ratio width of the forward rotation is larger than the speed ratio width of the reverse rotation. The power circulation rotation IVout of the carrier CR1 is controlled between the neutral position (that is, 0) and the speed ratio width of the forward rotation by the shift control of the variator 10, and is directly output to the output shaft 9 via the reverse clutch R. The That is, the power circulation rotation IVout of the carrier CR1 becomes the output rotation OutR in the reverse mode as it is.

  In the reverse mode, the power circulation rotation IVout is set so as to include a gear ratio that is in a neutral state. Therefore, the variator 10 is controlled, and the variator output rotation Vout is controlled to the corresponding gear ratio (in FIG. 2). (To the lower side), the rotation of the carrier CR1 becomes a gear neutral state, that is, the output rotation OutR in the reverse mode becomes a neutral state. In this state, the engine speed (forward rotation IN of the input shaft 2) and the rotation of the output shaft 9 are irrelevant. Therefore, for example, when the shift lever is switched to the reverse range, the gear ratio of the variator 10 is set to this gear. By engaging the reverse clutch R after adjusting to the neutral state, it is not necessary to absorb the rotational speed difference, and there is no need to provide a device for absorbing the rotational speed difference such as a torque converter.

  When the gear ratio of the variator 10 is reduced in accordance with, for example, the vehicle speed and the accelerator opening from the gear neutral state (when the variator output rotation Vout in FIG. 2 is shifted upward), the output shaft 9 The output rotation OutR is increased to the forward rotation side, reversed by a differential device (not shown), that is, increased to the reverse side.

In the present continuously variable transmission 1 _1, the carrier CR2 is connected to the output shaft 9, since the low brake L and the high clutch H is released In this reverse mode, idles reversing gear mechanism 30 Rotation occurs. That is, as shown by the two-dot chain line in FIG. 2, in this reverse mode, the carrier CR2 connected to the output shaft 9 is rotated by the output rotation OutR (power circulation rotation IVout) and also to the sun gear S2. Since the output rotation OutR (power circulation rotation IVout) is input from the carrier CR1, the double pinion planetary gear DP2 is integrally rotated, and the ring gear R2 is also idled by the output rotation OutR (power circulation rotation IVout) as indicated by the arrow IR. .

On the other hand, at the time of forward start of the vehicle, the continuously variable transmission ₁₁ is controlled to a low mode for forward start (for forward low speed travel) based on hydraulic control by a shift lever (not shown) or a hydraulic control device. As shown in FIG. 3, the low clutch L is engaged and controlled. Then, as shown in FIGS. 1 and 2, the forward rotation IN of the input shaft 2 is similarly transmitted to the input disks 11A and 11B and the ring gear R1, and the variator output rotation Vout is transmitted from the output disk 12 to the sun gear. Input to S1.

  As in the reverse mode, when the variator output rotation Vout is input to the sun gear S1, in the power circulation planetary gear 20, the forward rotation IN of the input shaft 2 input to the ring gear R1 and the variator output input to the sun gear S1. The rotation Vout is synthesized by torque circulation, and the carrier CR1 is rotated by the power circulation rotation IVout having a speed ratio width in which the speed ratio width of the forward rotation is larger than the speed ratio width of the reverse rotation. The power circulation rotation IVout of the carrier CR1 is input to the sun gear S2 of the reverse gear mechanism 30.

  When the power circulation rotation IVout is input to the sun gear S2, in the reverse gear mechanism 30, the power circulation rotation IVout of the sun gear S2 is reversed while being decelerated through the ring gear R2 whose rotation is fixed to the transmission case 5. The carrier CR2 rotates in the reverse direction, and the rotation of the carrier CR2 is output to the output shaft 9 as the output rotation OutL in the low mode.

  Also in the low mode, as in the reverse mode, the power circulation rotation IVout is set so as to include a gear ratio that becomes a neutral state. Therefore, the variator 10 is controlled and the variator output rotation Vout is set to the corresponding gear ratio. 2 (downward in FIG. 2), the rotation of the carrier CR1 is in a gear neutral state, the sun gear S2 is also in a neutral state, that is, the output rotation OutL in the low mode is in a neutral state. As described above, in this state, the engine speed (forward rotation IN of the input shaft 2) and the rotation of the output shaft 9 are irrelevant. For example, when the shift lever is switched to the low range, the variator 10 shifts. By engaging the low clutch L after adjusting the ratio to this gear neutral state, it is not necessary to absorb the difference in rotation speed, and it is not necessary to provide a device for absorbing the rotation speed difference such as a torque converter.

  When the gear ratio of the variator 10 is reduced in accordance with, for example, the vehicle speed and the accelerator opening from the gear neutral state (when the variator output rotation Vout in FIG. 2 is shifted upward), the output shaft 9 The output rotation OutL is increased to the reverse rotation side, reversed by a differential device (not shown), that is, increased to the forward side.

Subsequently, in the low mode state described above, the output rotation OutL of the output shaft 9 is increased (the transmission ratio of the variator 10 is reduced), and reaches the transmission ratio of the sync change SC indicated by the broken line in FIG. For example, when a shift is determined according to the vehicle speed or the accelerator opening, the low clutch L is released and the high clutch H is engaged as shown in FIG. 3 based on hydraulic control by a hydraulic control device (not shown). Then, the continuously variable transmission ₁₁ is set to a high mode for medium and high speed running.

  Then, as shown in FIGS. 1 and 2, the forward rotation IN of the input shaft 2 is similarly transmitted to the input disks 11A and 11B and the ring gear R1 of the variator 10 in this high mode state, and the output disk 12 Thus, the variator output rotation Vout is output. The variator output rotation Vout is input to the carrier CR2 of the reversing gear mechanism 30 via the high clutch H and is output to the output shaft 9 as it is as the high mode output rotation OutH.

  In switching between the low mode state and the high mode state at the time of the sync change SC, the gear ratio of each gear is set so that switching is performed at the same gear ratio at which the gear ratio of the variator 10 (variator output rotation Vout) is minimized. Is set. That is, in the low mode state, when the speed change ratio of the variator 10 is reduced, the output rotation OutL is increased. On the contrary, in the high mode state, the speed change ratio of the variator 10 is greatly changed with the sync change SC as a boundary. As it is done, the output rotation OutH is increased.

Incidentally, in the high mode in the continuously variable transmission 1 _1, forward rotation IN of the input shaft 2 is input to the ring gear R1 of the power circulation planetary gear 20, and since the variator output rotation Vout is input to the sun gear S1 The carrier CR1 is rotated by the power circulation rotation IVout, the power circulation rotation IVout is input to the sun gear S2 of the reversing gear mechanism 30, and the low brake L is released, so that the reversing gear mechanism 30 is idling. That is, as shown by a two-dot chain line in FIG. 2, in this high mode, the carrier CR2 connected to the output shaft 9 is rotated by the output rotation OutH (variator output rotation Vout) and also to the sun gear S2. Since the power circulation rotation IVout is input from the carrier CR1, the ring gear R2 released by the low brake L is idled by the rotation indicated by the arrow IH.

According to the continuously variable transmission 1 ₁ according to the first embodiment described above, the carrier CR1, power circulation rotation IVout the gear ratio range of the forward rotation than the speed ratio width of the reverse rotation has a large gear ratio width The ratio of the number of teeth of the power circulation planetary gear 20 is set so as to be rotated by the rotation of the power circulation planetary gear 20 and the reverse rotation OutL obtained by reversing the power circulation rotation IVout by the reversing gear mechanism 30 can be output to the output shaft 9 by the low brake L. In addition, since the power circulation rotation IVout is configured to be freely output to the output shaft 9 by the reverse clutch R, the reverse transmission gear ratio width (OutR of the OutR) suitable for a vehicle mounted using the power circulation rotation IVout is configured. Width), the ratio of the number of teeth of the carrier CR1 with respect to the ring gear R1 is set to the carrier with respect to the sun gear S1. It can be made smaller than the gear ratio of CR1, that is, the carrier CR1 can be brought closer to the ring gear R1 in the direction of the gear ratio axis of the speed diagram. The load on the input shaft 2 can be increased and the load on the variator 10 can be reduced, so that the durability of the variator 10 can be improved.

  Further, for example, as in the conventional IVT type continuously variable transmission, the power circulation rotation is compared with the case where the speed ratio width of the forward rotation and the speed ratio width of the reverse rotation in the power circulation rotation IVout are set substantially equal. Since the speed ratio width of the forward rotation in IVout can be increased, particularly in the low mode where the amount of use is overwhelmingly large compared to the reverse mode, when the power circulation rotation IVout is reversed by the reverse gear mechanism 30. Can be set to slow down. As a result, the torque can be amplified by the amount of deceleration in the reversing gear mechanism 30, the torque transmitted by the variator 10 can be reduced by that amount, and the durability of the variator 10 can be further improved.

Further, since the power circulation planetary gear 20 can be constituted by a single pinion planetary gear SP1, it is possible to compact the continuously variable transmission 1 _1.

<Second Embodiment>
Next, a second embodiment according to the present invention, in which the first embodiment is partially changed, will be described with reference to FIGS. 4 is a skeleton diagram showing a continuously variable transmission according to the second embodiment, FIG. 5 is a speed diagram of the continuously variable transmission according to the second embodiment, and FIG. 6 is a diagram according to the second embodiment. It is an engagement table | surface of the continuously variable transmission which concerns. In the second embodiment, parts that are the same as those in the first embodiment are denoted by the same reference numerals except for a part that is changed, and the description thereof is omitted.

As shown in FIG. 4, the continuously variable transmission 1 ₂ according to the second embodiment is different from the continuously variable transmission 1 ₁ according to the first embodiment shown in FIG. 1, power circulation planetary gear 20 is changed from a single pinion planetary gear to a planetary gear set PS having a step pinion. Further, the low brake is eliminated and the ring gear R3 of the reverse gear mechanism 30 is always fixed to the transmission case 5, and the rotation of the carrier CR3 is output by the low clutch (forward engagement element, low engagement element) L. 9, and a high clutch (high engagement element) H is disposed closer to the output shaft 9 than the reversing gear mechanism 30, and the output disk is connected via the carrier CR 1 of the power circulation planetary gear 20. The variator output rotation Vout from 12 can be freely output to the output shaft 9.

  Specifically, the planetary gear set PS of the power circulation planetary gear 20 meshes with the pinion P1 and a carrier CR1 (continuously variable rotation element) that rotatably supports a step pinion to which a large-diameter pinion P1 and a small-diameter pinion P2 are connected. A sun gear S1 (input rotation element) that engages with the pinion P2 and a sun gear S2 (power circulation rotation element) that engages with the pinion P2.

  The sun gear S1 of the power circulation planetary gear 20 is connected to the input shaft 2, and the carrier CR1 is connected to the outer peripheral side of the output disk 12, and is connected to the high clutch H, the high clutch. When H is engaged, the output shaft 9 is connected. The sun gear S2 is connected to the sun gear S3 of the reversing gear mechanism 30 and is connected to a reverse clutch (reverse engagement element, reverse engagement element) R. When the reverse clutch R is engaged, an output is generated. Connected to the shaft 9.

  The reverse gear mechanism 30 includes a double pinion planetary gear DP3 having a carrier CR3 that rotatably supports two pinions P3 and P4, a sun gear S3 that meshes with the pinion P3, and a ring gear R3 that meshes with the pinion P4. ing. Of these, the ring gear R3 is connected to the mission case 5 and is always fixed in rotation. Further, the sun gear S3 is connected to the sun gear S2 of the power circulation planetary gear 20 and is connected to the reverse clutch R as described above. The carrier CR3 is connected to the low clutch L and is connected to the output shaft 9 when the low clutch L is engaged.

Next, it will be described with reference to FIGS. 5 and 6 with reference to FIG. 4 the operation of the continuously variable transmission 1 _2.

  As shown in FIG. 6, in the reverse mode in which the reverse clutch R is engaged and controlled, as shown in FIGS. 4 and 5, the forward rotation IN of the input shaft 2 causes the input disk 11 </ b> A of the variator 10, 11B and the sun gear S1 of the power circulation planetary gear 20, and the variator output rotation Vout from the output disk 12 of the variator 10 is input to the carrier CR1. When the variator output rotation Vout is input to the carrier CR1, in the power circulation planetary gear 20, the forward rotation IN of the input shaft 2 input to the sun gear S1 and the variator output rotation Vout input to the carrier CR1 are combined by torque circulation. Then, the sun gear S2 is rotated by the power circulation rotation IVout having a speed ratio width in which the speed ratio width of the forward rotation is larger than that of the reverse rotation. The power circulation rotation IVout of the sun gear S2 is controlled between the neutral position (ie, 0) and the speed ratio width of the forward rotation by the shift control of the variator 10, and is directly output to the output shaft 9 via the reverse clutch R. The That is, the power circulation rotation IVout of the sun gear S2 becomes the output rotation OutR in the reverse mode as it is.

  Further, as shown in FIG. 6, in the low mode in which the low clutch L is engaged and controlled, as shown in FIGS. 4 and 5, in the power circulation planetary gear 20, as shown in FIG. The forward rotation IN of the input shaft 2 input to S1 and the variator output rotation Vout input to the carrier CR1 are combined by torque circulation, and the sun gear S2 is rotated by the power circulation rotation IVout.

  The power circulation rotation IVout of the sun gear S2 is input to the sun gear S3 of the reversing gear mechanism 30. In the reversing gear mechanism 30, the power circulation rotation of the sun gear S3 is performed via the ring gear R2 whose rotation is fixed to the transmission case 5. The carrier CR3 rotates in the reverse direction while IVout is reversed while being decelerated, and the rotation of the carrier CR3 is output to the output shaft 9 as the output rotation OutL in the low mode.

  Further, in the low mode, when the gear ratio of the sync change SC indicated by the broken line in FIG. 5 is reached, the low clutch L is released and the high clutch H is engaged and controlled, as shown in FIG. Switch from low mode to high mode. Then, as shown in FIGS. 4 and 5, the variator output rotation Vout is output from the output disk 12 of the variator 10 to the carrier CR1, and is directly output to the output shaft 9 as the high mode output rotation OutH via the high clutch H. Is done.

When the continuously variable transmission _{12 is} in the reverse mode and the high mode, the forward rotation IN of the input shaft 2 is input to the sun gear S1 of the power circulation planetary gear 20, and the variator output rotation Vout is input to the carrier CR1. Therefore, the sun gear S2 is rotated by the power circulation rotation IVout, and the power circulation rotation IVout is input to the sun gear S3 of the reversing gear mechanism 30, but the low brake L is released. Only the idling rotation is generated by the same rotation as in the low mode.

By continuously variable transmission 1 ₂ according to the second embodiment as described above, the sun gear S2, the power recirculation rotation speed ratio width of the forward rotation than the speed ratio width of the reverse rotation has a large gear ratio width The gear ratio of the power circulation planetary gear 20 is set so as to be rotated by IVout, and the reverse rotation OutL obtained by reversing the power circulation rotation IVout by the reversing gear mechanism 30 is freely output to the output shaft 9 by the low clutch L. In addition, since the power circulation rotation IVout can be freely output to the output shaft 9 by the reverse clutch R, the reverse gear ratio width (OutR) suitable for a vehicle mounted using the power circulation rotation IVout is configured. The ratio of the number of teeth of the sun gear S2 to the sun gear S1 is set to the sun gear S to the carrier CR1. 2 can be made smaller than the number of teeth ratio, that is, in the direction of the tooth number ratio axis of the speed diagram, the sun gear S2 can be brought closer to the sun gear S1, thereby sharing the torque to be combined in the power circulation, The load on the input shaft 2 can be increased and the load on the variator 10 can be reduced, so that the durability of the variator 10 can be improved.

  Further, for example, as in the conventional IVT type continuously variable transmission, the power circulation rotation is compared with the case where the speed ratio width of the forward rotation and the speed ratio width of the reverse rotation in the power circulation rotation IVout are set substantially equal. Since the speed ratio width of the forward rotation in IVout can be increased, particularly in the low mode where the amount of use is overwhelmingly large compared to the reverse mode, when the power circulation rotation IVout is reversed by the reverse gear mechanism 30. Can be set to slow down. As a result, the torque can be amplified by the amount of deceleration in the reversing gear mechanism 30, the torque transmitted by the variator 10 can be reduced by that amount, and the durability of the variator 10 can be further improved.

The power circulation planetary gear 20 in the continuously variable transmission 12 according to the _second embodiment is particularly longer in the axial direction than the single pinion planetary gear SP1 according to the first embodiment. Since there is no ring gear, there are few restrictions on the outer diameter side, and the pinion diameter and sun gear diameter can be set relatively freely. In other words, the design freedom in the power circulation planetary gear 20 is increased.

  Since the other configurations and operational effects are the same as those of the first embodiment, the description thereof is omitted.

  In the first and second embodiments described above, a full-toroidal continuously variable transmission is used as an example of a continuously variable transmission. However, of course, a half toroidal continuously variable transmission is used. In addition, the present invention is not limited to these, and any type may be used as long as it can continuously change, such as a belt-type continuously variable transmission.

1 is a skeleton diagram showing a continuously variable transmission according to a first embodiment. FIG. It is a speed diagram of the continuously variable transmission which concerns on 1st Embodiment. It is an engagement table | surface of the continuously variable transmission which concerns on 1st Embodiment. It is a skeleton figure which shows the continuously variable transmission which concerns on 2nd Embodiment. It is a speed diagram of the continuously variable transmission which concerns on 2nd Embodiment. It is an engagement table | surface of the continuously variable transmission which concerns on 2nd Embodiment.

Explanation of symbols

1 continuously variable transmission 2 input shaft 9 output shaft 10 continuously variable transmission (variator)
20 Power circulation mechanism (Power circulation planetary gear)
30 Reverse gear mechanism SP1 Single pinion planetary gear R1 input rotation element (ring gear) in FIGS. 1 and 2
S1 continuously variable speed rotating element (sun gear) in FIGS. 1 and 2
CR1 power circulating rotating element (carrier) in FIGS. 1 and 2
S1 input rotation element (sun gear) in FIGS. 4 and 5
4 and 5 CR1 continuously variable rotation element (carrier)
S2 in FIG. 4 and FIG. 5 Power circulation rotating element (sun gear)
L Forward engagement element, low engagement element (low clutch, low brake)
R Reverse engagement element, reverse engagement element (reverse clutch)
H High engagement element (high clutch, high brake)
IN Forward rotation of input shaft Vout Continuously variable speed reverse rotation (variator output rotation)
IVout Power circulation rotation OutL Reverse rotation (low mode output rotation)

Claims (3)

Power capable of power circulation by synthesizing a continuously variable transmission capable of continuously shifting while reversing the forward rotation of the input shaft, and a continuously rotating rotation of the input shaft and a continuously variable reverse rotation of the continuously variable transmission. A continuously variable transmission including a circulation mechanism,
The power circulation mechanism is
An input rotation element capable of inputting forward rotation of the input shaft;
A continuously variable transmission rotating element for inputting continuously variable reverse rotation from the continuously variable transmission;
A power circulation rotation element that rotates by a power circulation rotation having a speed ratio width in which the speed ratio width of the forward rotation is larger than the speed ratio width of the reverse rotation due to the rotation of the input rotation element and the rotation of the continuously variable speed rotation element. And having
A reversing gear mechanism capable of reversing the power circulation rotation of the power circulation rotation element;
A forward engagement element that freely outputs to the output shaft a reverse rotation obtained by reversing the power circulation rotation of the power circulation rotation element by the reverse gear mechanism;
A reverse engagement element that allows power circulation rotation of the power circulation rotation element to be freely output to the output shaft,
A continuously variable transmission. A high engagement element that allows the continuously variable reverse rotation of the continuously variable transmission to be freely output to the output shaft,
The forward engagement element is composed of a low engagement element that freely outputs a reverse rotation obtained by reversing the normal rotation of the power circulation rotation by the reverse gear mechanism to the output shaft,
The reverse engagement element is composed of a reverse engagement element that allows the forward rotation of the power circulation rotation to be freely output to the output shaft.
The continuously variable transmission according to claim 1. The power circulation mechanism is composed of a single pinion planetary gear.
The continuously variable transmission according to claim 1 or 2.

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