JPH0557927B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a continuously variable transmission for a vehicle that utilizes a V-belt type continuously variable transmission mechanism.

[Prior Art] A V-belt continuously variable transmission mechanism is used in a vehicle transmission by combining a fluid transmission device such as a torque converter and a fluid coupling as a starting means, and a planetary gear device as a forward/reverse switching mechanism. Ru. In this type of transmission, if both the forward/reverse switching mechanism and the starting device are placed on the output side of the V-belt continuously variable transmission mechanism, reversal of the V-belt continuously variable transmission mechanism during forward/reverse switching can be eliminated. In addition, even when the vehicle suddenly stops, the downshift to the maximum torque ratio of the V-belt continuously variable transmission mechanism is performed reliably, eliminating the shift shock and time lag when switching between forward and reverse directions, and the shock and vibration caused by downshifting when starting the vehicle. The occurrence can be suppressed.

From this point of view, the fluid transmission device and the planetary gear device are connected in a split drive type, the torque share of the fluid transmission device is reduced, the outer diameter is made smaller, and the distance between the input and output shafts is shortened. A V-belt continuously variable transmission for vehicles has been proposed, which is compact enough to be mounted on a vehicle.

[Problem that the invention seeks to solve]

However, in the above conventional technology, the forward/reverse switching mechanism and the fluid transmission device are disposed coaxially on the output shaft side of the V-belt continuously variable transmission mechanism.
The distance between the shaft support parts on the output shaft side becomes longer, and stress deformation becomes larger, resulting in a problem of reduced durability.

The present invention provides a compact continuously variable transmission for vehicles that ensures durability by devising the position of the fluid transmission device disposed on the output shaft side and shortening the interval between the output shaft support parts. The purpose is to

[Means for solving problems]

In order to achieve the above object, the present invention combines a V-belt type continuously variable transmission mechanism, a fluid transmission device, and a forward/reverse switching mechanism, which In the continuously variable transmission for a vehicle in which the fluid transmission device and the forward/reverse switching mechanism are arranged, the fluid transmission device has an input member connected to one end side of the output shaft, and the forward/reverse switching mechanism includes: One of the input members is connected to the other end of the output shaft, and the output shaft is supported by one support member between the output sheave disposed on the shaft and the fluid transmission device. , the output sheave and the forward/reverse switching mechanism are supported by the other support member.

[Operation and effect of the invention]

In the continuously variable transmission for vehicles of the present invention having the above configuration, the output shaft of the V-belt type continuously variable transmission mechanism, which carries a large load in the radial direction, is supported near both sides of the output sheave, and the spacing between the supporting parts is shortened. , stress deformation of the output shaft can be reduced, and sufficient durability can be ensured, including for each member disposed in relation to the output shaft.

[Embodiment] Next, a continuously variable transmission for a vehicle according to the present invention will be described based on an embodiment shown in the drawings.

FIG. 1 is a sectional view of a continuously variable transmission for a vehicle to which the present invention is applied, and FIG. 2 is a partially enlarged view thereof.

The continuously variable transmission 100 for a vehicle includes a V-belt type continuously variable transmission mechanism 200 and a fluid coupling 3 that is a fluid transmission device.
00, the V-belt type continuously variable transmission mechanism 200, and the fluid coupling 300 as inputs.
0, the differential mechanism 500, and the differential mechanism 50 from the forward/reverse switching mechanism 400.
0, a transmission case 700 containing the above components, and a hydraulic control device (not shown).

The V-belt type continuously variable transmission mechanism 200 includes a first input shaft 210 that introduces engine power into the vehicle continuously variable transmission 100 via an engine crankshaft 211 (not shown) and a starter wheel 212 for starting the engine; A fixed flange 221 provided integrally with the first input shaft 210 and the first input shaft 21
The input sheave 2 consists of a movable flange 224 that is slidably provided on the outer circumference of the input sheave 2 and is actuated by a hydraulic actuator 222 and a return means 223.
20, and a second input shaft 2 provided in a parallel position to the first input shaft 210, which is the input shaft of the fluid coupling 300 and the output shaft of the V-belt type continuously variable transmission mechanism 200.
40, a fixed flange 251 integrally provided on the second input shaft 240, and a hydraulic actuator 252 slidably provided on the outer periphery of the second input shaft 240.
and an output sheave 250 consisting of a movable flange 254 actuated by a biasing means 253, and a V-belt 260 that transmits power from the input sheave 220 to the output sheave 250.
0 is supported on both sides of the output sheave 250,
One side is rotatably supported via a roller bearing 2 on the inner periphery of a support member 1 integrally provided with the transmission case 700, and the other side is rotatably supported by the transmission case 700.
A support member 4 that protrudes rearward (on the left side in the figure) is provided on the side wall 4A of the support member 4, which is provided integrally with the transmission case 700, which has an oil passage 3 inside the support member for supplying and discharging hydraulic oil to the hydraulic actuator 252. It is rotatably supported via a roller bearing 6 between the outer periphery of the cylindrical boss portion 5 and the inner periphery of an annular convex portion 251A provided on the side wall of the fixed flange 251 and protruding forward (right side in the figure), and is fixed. Flange 251
Between the annular protrusion 251A and the side wall 4A of the support member 4, there is an annular protrusion 251A and the side wall 4A.
A roller bearing 7 is interposed to prevent sliding resistance between the two.

The fluid coupling 300 receives the second input shaft 240 as an input, and outputs an output to the third input shaft 310 rotatably disposed within the second input shaft 240 . The fluid coupling 300 is spline-fitted to the rear (left side in the figure) ends of the second input shaft 240 and the third output shaft 310, and is connected to the support member 1 via the support member 1 having a pump impeller 331 therein and the sliding bearing 8. a fluid transmission case 330 that is supported by and is an input member of the fluid transmission device;
Power transmission unit 340 with turbine impeller 341
It consists of The fluid transmission case 330 includes a flange portion 332 that is spline-fitted to the outer periphery of the second input shaft 240 and is supported by the support member 1 via the sliding bearing 8, a pump cover 333 that holds the pump impeller 331, and a pump cover 333 that holds the pump impeller 331. Turbine impeller 3
41, and a bearing support cover 335 fixed to the inner periphery of the turbine cover 334. The power transmission member 343 has a flange portion 343A that is spline-fitted on the outer periphery and is fixed to the turbine shell 342, and transmits input and output of the turbine impeller 341 to the outside of the fluid transmission case 330. From the above, the shaft reaction force of the V-belt type continuously variable transmission mechanism 200 applied to the second input shaft 240 is not applied to the fluid coupling 300, and the fluid coupling 300 is connected to the outside of the support member 1 that supports the second input shaft 240. Fluid coupling 3
00 can be easily attached and detached.

The forward/reverse switching mechanism 400 is provided concentrically in front of the second input shaft 240 and the third input shaft 310,
A sun gear Sg constituting one input member provided integrally with the third input shaft 310, a pinion gear Pg meshing with the sun gear Sg, a ring gear Rg meshing with the pinion gear Pg, and a pinion gear Pg are rotatably supported. A planetary gear device 410 consisting of a pinion carrier Pc, and a hydraulic actuator 42
A multi-disc clutch C1 constitutes another input member that engages and disengages the second input shaft 240 and pinion carrier Pc by the operation of the hydraulic actuator 430, and a ring gear Rg by the operation of the hydraulic actuator 430.
and a multi-plate brake B1 that engages and releases the transmission case 700, and a ring gear Rg
is connected to an output boss portion 440 having a flange 441, and the planetary gear set 410 is arranged to form a split type coupling in combination with the fluid coupling 300 when the clutch C1 is engaged.

The transmission mechanism 600 has an input gear 610 spline-fitted to the outer periphery of the output boss portion 440 and meshes with the input gear 610.
and an output gear 620 that outputs zero.

The differential mechanism 500 includes an output gear 6
Differential gear 510 meshing with 20
, a differential pinion shaft 520 attached to a differential case 511 fastened to the differential gear 510, and a differential rotatably attached to the outer periphery of the differential pinion shaft 520. an allencial pinion 530 and the differential pinion 5
30 and transmits power to one side drive shaft 541 and the other side drive shaft 551.

The transmission case 700 includes the starter wheel 21
2. Transmission mechanism 600, differential mechanism 5
A front case 710 that includes the right side of 00 in the figure and rotatably supports the right side of the input gear 610, output gear 620, and differential case 511; It includes the left side of the transmission mechanism 200, the forward/reverse switching mechanism 400, and the differential mechanism 500,
A continuously variable transmission front case 720 that rotatably supports intermediate portions of the first input shaft 210 and the second input shaft 240, and an input gear 610 that is fastened to the continuously variable transmission front case 720. , output gear 62
an internal support 730 that rotatably supports the left side of the first input shaft 210 and the second input shaft 240, which is fastened to the continuously variable transmission front case 720, and a fluid transmission case 330 that rotatably supports the left side of the first input shaft 210 and the second input shaft 240; a continuously variable transmission rear case 740 that rotatably supports the
a rear cover 750 which is fastened to the continuously variable transmission rear case 740 and has a lubricating oil supply path to the V-belt 260 therein; 330 and a fluid coupling case 760 containing the fluid coupling case 330.

When moving forward, this continuously variable transmission 100 for a vehicle engages the multi-disc clutch C1 and engages the multi-disc brake B1.
By releasing , when transmission is performed by the fluid coupling 300, part of the torque is transmitted from the pinion carrier Pc and pinion gear Pg to the output boss part 440 via the ring gear Rg, and the other part of the torque is transmitted to the pinion gear Pg. In order to receive the reaction force of the torque transmitted to the ring gear Rg, the torque is transmitted again to the pinion carrier Pc via the sun gear Sg and the fluid coupling 300, and the torque is circulated. As a result, in a fluid transmission device, power is normally transmitted through fluid, so the power loss that occurs occurs only for the torque transmitted via the fluid coupling 300, and the torque that is transmitted directly from the pinion gear Pg to the ring gear Rg. In this case, there is no loss of power due to the passage of fluid. Furthermore, since the torque transmitted via the fluid coupling 300 is part of the total transmission torque, the transmission torque capacity of the fluid coupling 300 may be small. Therefore, even when a fluid transmission device with a small external size is used, a large torque can be transmitted, and the external size of the continuously variable transmission 100 for a vehicle can be made compact. Furthermore, even when the vehicle suddenly stops and the ring gear Rg of the planetary gear set 410 stops, the second input shaft 240 can rotate while slipping the fluid coupling 300, so the V-belt type continuously variable transmission mechanism 200 maintains a torque ratio. It can rotate sufficiently to the maximum point, and when restarting, it is possible to start smoothly with the maximum torque ratio. Furthermore, the higher the speed of fluid transmission devices such as fluid couplings, the smaller the slip rate.
Furthermore, since the torque transmitted through the fluid coupling 300 is a part of the total transmitted torque, high power transmission efficiency can be achieved during steady running at medium to high speeds without using a direct coupling clutch (lock-up clutch).
Fuel efficiency can be improved.

When moving backward, by releasing the multi-plate clutch C1 and engaging the multi-disc brake B1, the fluid coupling 300 and the planetary gear set 410 are connected in series, fixing the pinion carrier Pc and achieving reverse.
In this embodiment, when moving backward, the V-belt type continuously variable transmission mechanism 2
The reduction ratio of 00 is set near the minimum reduction ratio, the transmission torque of the fluid coupling 300 is suppressed, and the planetary gear device 4
By decelerating at 10, the optimum reverse ratio is obtained.

[Brief explanation of drawings]

FIG. 1 is a sectional view of a continuously variable transmission for a vehicle to which the present invention is applied, and FIG. 2 is a partially enlarged view of FIG. 1. In the figure, 1, 4...support member, 100...vehicle continuously variable transmission, 200...V-belt type continuously variable transmission mechanism, 210...first input shaft, 220...input sheave, 240...number 2 input shaft, 250... output sheave, 300... fluid coupling (fluid transmission device), 31
0... Third input shaft, 330... Fluid transmission case (input member), 400... Forward/forward switching mechanism, 410
...Planetary gear device, C1...Multi-plate clutch (input member).

Claims (1)

[Scope of Claims] 1. A V-belt continuously variable transmission mechanism, a fluid transmission device, and a forward/reverse switching mechanism are combined, and the fluid transmission device is coaxial with the output shaft of the V-belt continuously variable transmission mechanism. and a forward/reverse switching mechanism, wherein the fluid transmission device has an input member connected to one end of the output shaft, and the forward/reverse switching mechanism has an input member connected to one end of the output shaft. one of the output shafts is connected to the other end side of the output shaft, and the output shaft is supported by one support member between the output sheave disposed on the shaft and the fluid transmission device, and the output sheave is connected to the other end side of the output shaft. and the forward/reverse switching mechanism is supported by the other supporting member.