JP6205265B2 - Continuously variable transmission - Google Patents

Description

The present invention relates to a continuously variable transmission that is employed, for example, in an automobile, and more specifically to an improvement in the arrangement structure of a forward / reverse switching mechanism.

A forward / reverse switching mechanism in a continuously variable transmission for an automobile includes a forward clutch, a reverse clutch, an idler shaft, and various gears. Conventionally, for example, Patent Document 1 discloses an arrangement structure of these component parts. In this conventional structure, the forward clutch is arranged on the input side of the input shaft from the drive pulley, and the reverse clutch is arranged on the portion of the drive pulley shaft between the drive pulley and the forward clutch.

JP 2011-80582 A

In the conventional device, since the forward clutch and the reverse clutch are both arranged closer to the input side than the drive pulley, there is a problem that the axial length when viewed in the entire continuously variable transmission is increased. . In addition, since the hydraulic oil for switching and the lubricating oil for the reverse clutch are guided from the torque converter case side, there is a problem that the oil passage structure becomes complicated and the number of processing steps and the number of parts increase.

The present invention has been made in view of the above-described conventional situation, and shortens the radial interval between the idler shaft and the drive pulley shaft while suppressing an increase in the shaft length when viewed in the entire continuously variable transmission. It is an object of the present invention to provide a continuously variable transmission that can be made compact and that can simplify the oil passage for the switching oil and the lubricating oil of the reverse clutch.

According to a first aspect of the present invention, there is provided an input shaft, a drive pulley shaft having a drive pulley to which forward rotation of the input shaft is transmitted via a forward clutch, and a driven pulley having a driven pulley to which rotation of the drive pulley is transmitted. In a continuously variable transmission comprising a pulley shaft, and an idler shaft that converts forward rotation of the input shaft into reverse rotation and transmits it to the drive pulley shaft,
A reverse clutch and a reverse drive gear are disposed on a portion of the idler shaft opposite to the forward clutch with respect to the drive pulley, and the forward clutch of the drive pulley shaft with respect to the drive pulley is arranged. A reverse driven gear is provided on the opposite side portion, and the drive pulley is positioned between the reverse clutch and the forward clutch.

The invention of claim 2 is the continuously variable transmission according to claim 1,
A speed change function component is disposed on the input side of the drive pulley shaft from the drive pulley.

According to the first aspect of the present invention, the reverse clutch and the reverse drive gear are mounted on the idler shaft, and the reverse driven gear is disposed on the drive pulley shaft on the opposite side of the forward clutch with respect to the drive pulley. Since the drive pulley is positioned between the reverse clutch and the forward clutch, the drive pulley is less likely to interfere with the reverse clutch and the like, and as a result, the radial distance between the idler shaft and the drive pulley shaft is increased. It can be narrowed and the device can be made compact.

In addition, since the reverse clutch is disposed in the conventional dead space on the conventional idler shaft extension line and radially outward of the drive pulley, the reverse clutch is disposed on the non-input side of the drive pulley. An increase in the axial length when viewed from the entire apparatus can be suppressed.

In addition, since the reverse clutch is provided on the idler shaft, an oil passage for supplying hydraulic oil and lubricating oil to the clutch is formed in the support wall portion that supports the idler shaft bearing of the transmission case, thereby reducing the oil passage. The oil hole formed in the shaft core of the idler shaft and the valve body for controlling the flow of hydraulic oil can be formed to directly communicate with each other, the structure of the oil passage can be simplified, and the number of processing steps can be reduced.

It is a skeleton block diagram of the continuously variable transmission which concerns on Example 1 of this invention. It is a cross-sectional development view of the continuously variable transmission. It is the shaft arrangement | positioning seen from the input side of the said continuously variable transmission. It is sectional drawing for demonstrating the oil-path structure of the said continuously variable transmission (IV-IV sectional view taken on the line of FIG. 3).

Embodiments of the present invention will be described below with reference to the accompanying drawings.

1-3 is a figure for demonstrating the continuously variable transmission which concerns on Example 1 of this invention.

In the figure, reference numeral 1 denotes a power split type continuously variable transmission for an automobile. The continuously variable transmission 1 includes a CVT (continuously variable transmission) 10, a planetary gear mechanism 13, and a torque converter 2 to which engine rotation is input. It consists of and. The torque converter 2 is accommodated in the torque converter case 3, and the CVT 10 and the planetary gear mechanism 13 are accommodated in the mission case 4. Reference numeral 4 ′ denotes a case cover that closes the rear end opening of the transmission case 4.

The CVT 10 includes an input shaft 5, a driving pulley shaft 6, a driven pulley shaft 7 having a left portion 7 ′ and a right portion 7 ″, and an idler shaft 8 arranged in parallel with each other. The output gear 7b of the driven pulley shaft 7 meshes with the input gear 16a of the differential mechanism 16.

The crank plate 2c of the engine is connected to the drive plate 2a of the torque converter 2, and the input shaft 5 is connected to the turbine runner 2b.

A forward drive unit 9 is disposed on the input shaft 5. The reverse drive unit 9 includes a forward drive gear 9a rotatably attached to the input shaft 5 and a forward clutch 9b that couples or separates the forward drive gear 9a with respect to the input shaft 5. Yes.

The drive pulley shaft 6 has a forward input gear 6a meshed with a forward drive gear 9a of the input shaft 5 fixed to an input-side base end portion 6 ', and a drive pulley 19 attached to an output-side distal end portion 6 ″. Is attached, and a reverse driven gear 6 c is fixed to the opposite side of the drive pulley 19.

The driven pulley shaft 7 is provided with a driven pulley 20 to which the drive pulley 19 is connected via a metal belt 11.

Here, the drive pulley 19 is movable in the axial direction relative to the pulley shaft 6 on the input side of the drive pulley shaft 6 and a fixed pulley half 19a integrally formed on the opposite side of the drive pulley shaft 6. The movable pulley half 19b is mounted so as to be able to transmit rotational force, and an oil chamber 19c is formed on the input side of the movable pulley half 19b, that is, on the forward clutch unit 9 side. By supplying hydraulic pressure to the oil chamber 19c, the movable pulley half 19b moves forward, and the effective pulley diameter of the drive pulley 19 increases and changes to the high speed side.

The driven pulley 20 is movable in the axial direction relative to the pulley shaft 7 on the input side of the driven pulley shaft 7 and the fixed pulley half 20a integrally formed on the input side of the driven pulley shaft 7. The movable pulley half 20b is mounted so as to be capable of transmitting rotational force, and an oil chamber 20c is formed on the opposite side of the movable pulley half 20b. By supplying hydraulic pressure to the oil chamber 20c, the movable pulley half 20b moves forward, and the effective pulley diameter of the driven pulley 20 increases and changes to the low speed side.

Further, an idler gear 8 a that engages with a reverse input gear 5 a fixed to the distal end portion 5 ′ of the input shaft 5 is fixed to the base end portion 8 ′ of the idler shaft 8, and the distal end of the idler shaft 8 is fixed. A reverse drive unit 12 is disposed in the section 8 ″.

The reverse drive unit 12 is a reverse drive gear 12a that is rotatably mounted on the idler shaft 8 and a reverse drive gear that couples the drive gear 12a to the idler shaft 8 so as to be able to transmit rotational force, or separates the drive gear 12a so as to be relatively rotatable. And a clutch 12b.

Specifically, as shown in FIG. 4, the reverse clutch 12b includes a clutch drum 12c coupled to the idler shaft 8 so as to rotate together, and an axially slidable arrangement within the clutch drum 12c. A piston 12d, and a disk 12e formed of a disk locked on the drum side and a disk locked on the gear side. By supplying hydraulic pressure to an oil chamber 12f formed by the clutch drum 12c and the piston 12d, the drum-side disk is pressed against the gear-side disk, and the rotational force of the idler shaft 8 is transmitted to the reverse drive gear 12a. .

Here, the front end 5 'of the input shaft 5 and the base end 8' of the idler shaft 8 are supported by the support wall 4a via bearings 5b and 8d, respectively. The support wall 4 a is formed inside the mission case 4.

Further, a hydraulic oil passage 8b for supplying hydraulic oil to the hydraulic oil chamber 12f and a lubricating oil passage 8c for supplying lubricating oil to the lubricated portion 12g of the reverse clutch 12b are provided in the shaft core portion of the idler shaft 8. It is formed in parallel with the shaft core. The hydraulic oil passage 8b and the lubricating oil passage 8c communicate with the hydraulic oil supply passage 4b and the lubricating oil supply passage 4c formed in the support wall 4a through through holes 8d and 8e. The hydraulic oil supply passage 4b and the lubricating oil supply passage 4c extend through the support wall 4a to the bottom of the transmission case 4, and are disposed at the bottom to supply hydraulic oil and lubricating oil to the respective oil passages. Is connected to a valve body 18 for controlling the control. Reference numeral 19 denotes an oil pan attached to the bottom of the mission case 4.

The planetary gear mechanism 13 is arranged on the input side from the driving pulley planetary gear mechanism 14 disposed on the input side of the driving pulley shaft 6 and the driven pulley 20 of the driven pulley shaft 7. The driven planetary gear mechanism 15 is provided, and both the mechanisms 14 and 15 are connected by a chain 17.

The drive-side planetary gear mechanism 14 has a sun gear 14a rotatably supported by the drive pulley shaft 6, and a pinion gear 14c rotatably supported by a carrier 14b fixed to the drive pulley shaft 6 is engaged with the sun gear 14a. A ring gear 14e is engaged with the pinion gear 14c so as to be relatively rotatable, a drive sprocket 14e is formed on the ring gear 14d, and the rotation of the sun gear 14a is blocked or allowed by a brake 14f.

The driven planetary gear mechanism 15 is fixed to the left portion 7 ′ sun gear 15 a of the driven pulley shaft 7 and is rotatably supported by a carrier 15 b supported relative to the right portion 7 ″ of the driven pulley shaft 7. The pinion gear 15c meshing with the sun gear 15a is meshed with the ring gear 15d so as to be relatively rotatable, and the ring gear 15d is coupled to or separated from the left portion 7 'of the driven pulley shaft 7 by the clutch 15f. The driven sprocket 15e is formed on the carrier 15b, and the driven sprocket 15e is connected to the drive splot 14e of the drive planetary gear mechanism 14 by the chain 17.

  In the first embodiment, the belt drive mode or the power split mode is selected and controlled according to the engine speed, vehicle speed, and the like. During forward travel in the belt drive mode, the forward clutch 9b is turned on, the reverse clutch 12b is turned off, the brake 14f is turned off, and the clutch 15f is turned on. As a result, the engine is rotated from the input shaft 5 to the forward drive gear 9a and forward drive. It is transmitted to the drive pulley shaft 6 via the input gear 6 a, is shifted by the CVT 10, and is transmitted to the drive wheels via the driven pulley shaft 7, the clutch 15 f and the differential mechanism 16.

  On the other hand, during reverse travel, the forward clutch 9b is turned off, the reverse clutch 12b is turned on, the brake 14f is turned off, and the clutch 15f is turned on. As a result, the engine rotation is reversed from the input shaft 5 to the idler shaft 8, and the reverse drive gear. 12a, transmitted to the drive pulley shaft 6 via the reverse driven gear 6c, and transmitted to the drive wheels via the CVT 10, the driven pulley shaft 7, the clutch 15f, and the differential mechanism 16.

  In the power split mode, power is split and transmitted to the CVT 10 and the planetary gear mechanism 13. Specifically, the brake 14f is turned on and the clutch 15f is turned off, and the engine rotation is shifted by the drive-side planetary gear mechanism 14 and transmitted to the driven-side planetary gear mechanism 15, where it is combined with the rotation from the CVT 10 for the difference. Is output to the moving mechanism 16.

According to this embodiment, the reverse drive unit 12 comprising the reverse clutch 12b and the reverse drive gear 12a is mounted on the idler shaft 8, and the forward clutch 9b and the reverse drive for the drive pulley 19 of the drive pulley shaft 6 are mounted. By disposing the reverse driven gear 6c on the opposite side of the input gear 5a and the like, the large-diameter drive pulley 19 is positioned between the large-diameter reverse clutch 12b and the large-diameter forward clutch 9b. Therefore, the drive pulley 19 is less likely to interfere with the reverse clutch 12b and the like, and as a result, the radial interval between the idler shaft 8 and the drive pulley shaft 6 can be reduced, and the apparatus can be made compact.

Further, since the reverse clutch 12b is disposed in the region A, which is a conventional dead space on the extension line of the idler shaft 8 and radially outward of the drive pulley 19, the reverse clutch 12b is provided on the opposite side of the drive pulley 19 from the input side. It is possible to suppress an increase in the axial length when viewed from the entire apparatus while arranging the components.

Further, the reverse clutch 12b is disposed on the idler shaft 8, and the hydraulic oil passage 8b and the lubricating oil passage 8c are formed in the shaft core of the idler shaft 8. Therefore, the hydraulic oil is provided in the hydraulic oil passage 8b and the lubricating oil passage 8c. The hydraulic oil supply passage 4b and the lubricating oil supply passage 4c for supplying the lubricating oil can be formed on the support wall 4a for supporting the idler shaft bearing 8d and the input shaft bearing 5b of the transmission case 4. As a result, both the oil supply passages 4b and 4c can be formed linearly so as to directly communicate with the valve body 18 that controls the flow of hydraulic oil, the structure of the both oil supply passages 4b and 4c can be simplified, and the number of processing steps can be reduced. Can be reduced. By the way, in the conventional device with a reverse clutch on the input shaft, the hydraulic oil supply passage and the lubricating oil supply passage are formed on the wall of the torque converter case, so a communication structure with the transmission case valve body is required. As a result, there is a problem that the structure becomes complicated and the number of processing steps increases.

1 continuously variable transmission 5 input shaft 6 drive pulley shaft 6c reverse drive gear 7 driven pulley shaft 8 idler shaft 9b forward clutch 12a reverse drive gear 12b reverse clutch 13 planetary gear mechanism (transmission function component)
19 Drive pulley 20 Drive pulley

Claims (2)

An input shaft, a drive pulley shaft having a drive pulley to which forward rotation of the input shaft is transmitted via a forward clutch, a driven pulley shaft having a driven pulley to which rotation of the drive pulley is transmitted, and the input shaft A continuously variable transmission including an idler shaft that converts the forward rotation of the forward rotation to the reverse rotation and transmits it to the drive pulley shaft;
A reverse clutch and a reverse drive gear are disposed on the opposite side of the forward clutch relative to the drive pulley of the idler shaft;
A reverse driven gear is disposed on the opposite side of the forward clutch with respect to the drive pulley of the drive pulley shaft;
A continuously variable transmission, wherein the drive pulley is positioned between the reverse clutch and the forward clutch. The continuously variable transmission according to claim 1,
A continuously variable transmission having a speed change function component disposed on an input side portion of the drive pulley shaft from the drive pulley.

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