JPH0232924Y2 - - Google Patents

Description

[Detailed description of the invention] (a) Industrial application field The present invention relates to a V-belt type continuously variable transmission for vehicles, and specifically relates to its fluid coupling, planetary gear type forward/reverse switching mechanism, input shaft, and input pulley. It relates to the structure of the first axis consisting of.

(B) Prior Art As shown in FIG. 3, a conventional V-belt type continuously variable transmission for a vehicle has fixed flanges 52A and 56A provided on an input shaft 51 and an output shaft 55, respectively, and a hydraulic servo 53 and a hydraulic servo 53, respectively. The input pulley 52 and the output pulley 56 are composed of movable flanges 52B and 56B driven by the hydraulic servos 53 and 57, and whose effective diameters are variable by the hydraulic servos 53 and 57, and a V-belt 58 that transmits power between these two pulleys. The engine is comprised of a V-belt type continuously variable transmission section, a starting device 210 provided between the engine and the input shaft, and a forward/reverse switching mechanism 220 provided on the output shaft.

Oil pump 10 that supplies hydraulic pressure to the hydraulic servo
1 is provided at the end of the input pulley 52 opposite to the engine, and is driven by an oil pump drive shaft 100 that is inserted into a hollow part of the input shaft and directly connected to the engine. Hydraulic oil is supplied to the hydraulic servos 53 and 57 by forming hollow portions 511 and 551 at the axes of the input shaft 51 and output shaft 55, respectively.
It was supplied and discharged through the hollow part.

In this conventional V-belt type continuously variable transmission, the starting device is composed of a dry centrifugal automatic clutch, and the forward/reverse switching mechanism 220 includes a sliding engagement type clutch mechanism 221 and forward and reverse gears 222, 22.
It consists of 3.

(c) Problems to be Solved by the Invention However, in the conventional V-belt type continuously variable transmission for vehicles configured as described above, the starting device 21
0 is composed of a dry centrifugal automatic clutch, and the forward/reverse switching mechanism 220 includes a sliding engagement clutch mechanism 221 and forward and reverse gears 222, 22.
3, the start control becomes complicated and the forward/reverse switching mechanism becomes large, making the V-belt type continuously variable transmission large.

Therefore, a system has been proposed in which a fluid coupling is used as the starting device and a planetary gear type forward/reverse switching mechanism is provided with frictional engagement elements for forward and reverse and a set of planetary gear mechanisms as the forward/reverse switching mechanism. (Japanese Unexamined Patent Publication No. 1983-46146). And this Japanese Patent Application Publication No. 1983-
In the V-belt type continuously variable transmission shown in Publication No. 46146, in order to make the planetary gear type forward/reverse switching mechanism more compact, the planetary gear type forward/reverse switching mechanism is installed on the input shaft with small transmission torque. It is configured.

However, in the device described in JP-A-56-46146, fluid couplings, V
The input pulley of the belt type continuously variable transmission, the planetary gear type forward/reverse switching mechanism, and the oil pump are arranged in this order, so the input shaft of the forward/reverse switching mechanism and the oil Since the oil pump drive shaft that drives the pump is inserted through the pump and has a triple shaft structure, the shaft structure becomes extremely complicated, and the oil passage for supplying hydraulic pressure to the hydraulic servo of the input pulley provided on the input shaft becomes narrow. , sufficient oil passage area could not be obtained.

By the way, in the V-belt type continuously variable transmission for vehicles,
It is difficult to change gears while the vehicle is stopped, so when the vehicle suddenly stops, the reduction ratio of the V-belt continuously variable transmission must be rapidly changed to the maximum position in order to restart the vehicle smoothly. This rapid increase in the reduction ratio (downshift) requires rapid discharge of the hydraulic pressure in the hydraulic servo of the input pulley, but as shown in the conventional Fig. 3 and Japanese Patent Application Laid-Open No. 56-46146, In the V-belt type continuously variable transmission, there was not enough oil passage area for the hydraulic pressure supply oil passage to the input pulley's hydraulic servo.
There was a problem that when the vehicle came to a sudden stop, the hydraulic pressure in the input pulley's hydraulic servo could not be discharged quickly, the reduction ratio of the V-belt continuously variable transmission did not change to the maximum position, and restarting could not be done smoothly.

Furthermore, the planetary gear type forward/reverse switching mechanism disclosed in JP-A No. 56-46146 consists of a double planetary gear type planetary gear mechanism, in which the sun gear of the planetary gear is connected to an input shaft and also connected to a ring gear via a clutch. A brake is connected to the ring gear, and a carrier is connected to an input pulley.

For this reason, both the frictional engagement elements of the brake and the clutch are connected to the ring gear, and the structure is complicated. The power is transmitted through this path, and the load always acts on the tooth surface and the pinion shaft support surface, which is unfavorable in terms of transmission efficiency, lubrication, and durability.

Therefore, in the present invention, a fluid coupling and a planetary gear type forward/reverse switching mechanism are placed on the engine side with respect to the input pulley, and only the hydraulic servo of the input pulley is placed on the side opposite to the engine with respect to the input pulley. By configuring this, it is possible to increase the area of the oil passage for supplying hydraulic pressure to the hydraulic servo of the input pulley, allowing rapid discharge of the hydraulic pressure in the hydraulic servo of the input pulley in the event of a sudden stop. The reduction ratio of the transmission changes smoothly to the maximum position, allowing smooth restart, and when moving forward, power is directly transmitted exclusively through the carrier and clutch of the double planetary gear type planetary gear mechanism, and the planetary gear It is an object of the present invention to provide a V-belt type continuously variable transmission for a vehicle which is configured so that a large load does not act on the tooth surfaces of the mechanism, the pinion shaft support surface, etc., and which solves the above-mentioned problems.

(d) Means for Solving the Problems The present invention has been made in view of the above-mentioned circumstances. For example, as shown in FIG. Output shaft 4
2, a planetary gear type forward/reverse switching mechanism 6 connected to the
Output elements 67, 6 of the planetary gear type forward/reverse switching mechanism
2', an output shaft 55 disposed parallel to the input shaft, and hydraulic servos 53, 57 provided on the input shaft 51 and output shaft 55 to which hydraulic oil is supplied and discharged. In a V-belt continuously variable transmission for a vehicle, comprising an input pulley 52 and an output pulley 56 whose effective diameters are variable, and a V-belt continuously variable transmission section 2 consisting of a V-belt that transmits power between these two pulleys. , the planetary gear type forward/reverse switching mechanism 6 is arranged in alignment with the output shaft 42 and the input shaft 51 of the fluid coupling and between the fluid coupling 4 and the V-belt continuously variable transmission section 2. It has one set of double planetary gear type planetary gear mechanism, and a clutch 63 is interposed between a sun gear 67 and a carrier 62 in the planetary gear mechanism, and a brake 65 is connected to a ring gear 66.
Based on the connection of 3 and the release of the brake 66,
The output shaft 42 and the input shaft 51 of the fluid coupling are integrally connected via the carriers 62, 62' and the clutch 63, and upon release of the clutch 63 and engagement of the brake 65, the fluid coupling is activated. The rotation of the output shaft 42 is transmitted to the input shaft 51 as reverse rotation, and the input pulley 52
The fixed flange 52A is integrally formed with the input shaft 51 and provided on the side of the planetary gear type forward/reverse switching mechanism 6, and the fixed flange 52A is slidably supported on the input shaft and is connected to the shaft by the hydraulic servo 53. Furthermore, oil passages 511A and 511B are formed at the axis of the input shaft 51 from both ends, respectively, and the ends of these oil passages are separated so as not to communicate with each other. The movable flange 52 is
It is characterized by supplying and discharging hydraulic pressure to the hydraulic servo 53 of B.

(e) Effect Based on the above configuration, engine rotation is transmitted to the planetary gear type forward/reverse switching mechanism 6 via the fluid coupling 4. In the case of the forward mode, the brake 65 of the forward/reverse switching mechanism 6 is in a released state and the clutch 63 is in a connected state, and the torque of the output shaft 42 of the fluid coupling 4 is exclusively applied to the carriers 62, 62'.
The power is directly transmitted to the input shaft 51 via the clutch 63, allowing efficient power transmission. In the case of reverse mode, the clutch 63 of the forward/reverse switching mechanism 6 is in a released state, and the brake 65 is in an activated state, locking the ring gear 66 and transmitting reverse rotation to the input shaft 51.

The rotation of the input shaft 51 is controlled by the input pulley 5.
2. It is transmitted to the output shaft 55 via the belt 58 and the output pulley 56. At this time, the hydraulic servo 53,
By supplying and discharging hydraulic pressure to and from the input pulley 57, the effective diameter of the pulley is changed and the speed is continuously variable. As a result, the shift control is performed quickly, and the responsiveness of the shift control is good. In the event of a sudden stop, the hydraulic pressure from the hydraulic servo 53 is quickly discharged via the oil passage 511B, which has a large oil passage area, and the V-belt type The continuously variable transmission section 2 is returned to the maximum deceleration position, and restart is performed smoothly. In addition, another oil passage 51 formed at the axis of the input shaft 51
Hydraulic oil or lubricating oil or the like can be easily and reliably supplied from 1A to the forward/reverse switching mechanism 6 or the like.

Further, if the hydraulic servo 53 is of a double piston type, the oil can be discharged from the two hydraulic chambers 53A and 53B to the oil passage 511B in parallel, and quick speed change control of the continuously variable transmission section 2 becomes even more reliable.

Note that the symbols inside brackets do not limit the configuration in any way.

(f) Example Next, an example of the present invention will be described based on FIG. 1.

The housing 1 has a fluid coupling room 11 which has an open fastening surface 1A to the engine and stores fluid couplings such as a fluid coupling and a torque converter, and a differential gear 7 which has an open side opposite to the engine. A differential room 12 that supports one output shaft of the differential gear 7, and a differential room 12 that similarly opens on the side opposite to the engine and accommodates the idler gear 8 and supports one of the shafts of the eye idler gear 8. It has an idler gear room 13.

The transmission case 2 has an opening on the side of the engine and covers the transmission room 21 in which the V-belt type continuously variable transmission section is housed, and the differential room 12 of the housing 1, and also covers the opening surface of the differential room 12 of the housing 1. It consists of a differential room 22 that supports the other output shaft of the gear 7, and is bolted to the side 1B of the housing 1 opposite to the engine, and together with the housing and an intermediate case to be described later, the automatic transmission It constitutes the outer shell (case) of.

The intermediate case 3 is configured to pivotally support the transmission shaft between the fluid coupling and the V-belt type continuously variable transmission section. It is bolted to the side 1B opposite to the engine.

In this embodiment, the automatic transmission includes a well-known fluid coupling 4 arranged in a housing 1 and connected to the output shaft of the engine, a V-belt type continuously variable transmission part 5 provided in a transmission case 2, and a planetary gear. It consists of a gear type forward/reverse switching mechanism 6.

The output shaft 42 of the fluid coupling 4 is rotatably supported by a sleeve 31 fitted in the center of the intermediate case 3 via a metal bearing 32.
The hub 46 of the turbine 45 of the fluid coupling 4 is spline-fitted to the engine side end, and the other end has a stepped larger diameter, and the larger diameter portion is connected to the input shaft 60 of the planetary gear type forward/reverse switching mechanism 6. and is supported by the intermediate case 3 via a bearing 33. The output shaft 42 of the fluid coupling 4 and the input shaft 60 of the planetary gear type forward/reverse switching mechanism 6 are formed with hollow shaft centers, and the hollow portions are provided with an oil passage 421 and fitted with a plug 420. The engine side end of the sleeve 422 fixed to the input shaft 51 of the V-belt type continuously variable transmission section 5 is rotatably fitted.

The oil pump cover 10 is fastened to the engine side (fluid coupling side) wall of the intermediate case 3, and an oil pump 101 driven by a hollow shaft 41 integrated with the fluid coupling 4 is housed inside.

The V-belt type continuously variable transmission unit 5 is arranged such that an input shaft 51 having a hollow shaft center and the hollow portion serving as a supply oil path for hydraulic oil and lubricating oil has a coaxial center with the fluid coupling 4, An output shaft 55 having an oil passage formed therein is arranged parallel to the input shaft 51.

This V-belt type continuously variable transmission section 5 has an input shaft 5 integrated with a sun gear 67 of a planetary gear type forward/reverse switching mechanism 6.
1, and a movable flange 52B that is slid in the direction of the fixed flange 52A by a hydraulic servo 53, and is integrated with the output shaft 55 of the V-belt type continuously variable transmission section. a fixed flange 56A formed in;
and an output pulley 56 consisting of a movable flange 56B that is slid in the direction of the fixed flange 56A by a hydraulic servo 57, an input pulley 52, and an output pulley 56.
and a V-belt 58 that transmits power between the two.

The input shaft 51 of the V-belt type continuously variable transmission has an engine side end 51A, which is the sun gear 67 of the planetary gear type forward/reverse switching mechanism, connected to the input shaft 60 of the planetary gear type forward/reverse switching mechanism via the bearing 34. The other end 51B is supported by the intermediate case 3 via the input shaft 60 and the bearing 33, and the other end 51B is supported by the side wall 25 of the transmission case opposite to the engine via the bearing 35. is a lid 26 fastened to the side wall 25;
via a needle roller bearing 27.

The output shaft 55 of the V-belt type continuously variable transmission has an outer spline 55 on the engine side end that fits into an inner spline formed on the support shaft 591 of the output gear.
A is formed, and the support shaft 591 of the output gear and roller bearings 592, 593 are connected by spline fitting.
The other end 55B is supported by the intermediate case 3 and the housing 1 through a ball bearing 92, and the other end 55B is connected to the transmission case side wall 2 opposite to the engine through a ball bearing 92.
Supported by 5B.

The output gear 59 is formed integrally with a hollow support shaft 591, and the engine side end 591A of the support shaft 591 is supported by the side wall of the housing via a roller bearing 592, and the other end 591B is supported by the intermediate support shaft 591 via a roller bearing 593. The output gear 59 is supported by the case 3, and the engine-side side surface 59A of the output gear 59 is brought into contact with the side wall of the housing via a needle bearing 594, and the opposite side surface 59B of the output gear is connected to the intermediate case 3 via a needle bearing 595. An inner spline is formed in contact with the side surface and further on the transmission side of the support shaft 591.

A sensing valve body 552 is fitted in the middle part of the oil passage 551 formed at the axis of the output shaft 55 of this V-belt type continuously variable transmission part, and the entire space of the engine side part 552A of the valve body 552 is Hydraulic pressure supplied from an oil passage 14 communicating with a hydraulic control device formed in the transmission case is an oil passage guided to the hydraulic servo 57, and a portion 552B of the valve body 552 on the side opposite to the engine has a tip end connected to the transmission. A pipe-shaped protrusion 55 of a lid 553 is attached to cover a hole 25B formed in a portion corresponding to the output shaft 55 of the side wall 25 of the case.
4 and is formed in the transmission case and the lid 553 fastened to the transmission case, and is supplied with hydraulic oil for a sensing valve 555 that detects the displacement position of the movable flange 56B from the hydraulic control device. It's summery.

The planetary gear type forward/reverse switching mechanism 6 is disposed between the input shaft 51 of the V-belt type continuously variable transmission section 5 and the output shaft 42 of the fluid coupling 4.

This planetary gear type forward/reverse switching mechanism 6 is connected to an input shaft 60 that is integral with the output shaft 42 of the fluid coupling 4, as shown in FIG.
Carriers 62, 6 are connected to a fixed flange of a V-belt continuously variable transmission section via a multi-plate clutch 63.
2', a ring gear 66 engaged with the intermediate case 3 via a multi-disc brake 65, a sun gear 67 formed integrally with the input shaft 51 of the V-belt type continuously variable transmission section, and a sun gear pivotally supported by the carrier 62; 67
a second planetary gear 64'' that is pivotally supported by the carrier 62 and meshes with the ring gear 66 and meshes with the first planetary gear 64'; a hydraulic servo 68 for operating the brake 65; a hydraulic servo 69 formed on the fixed flange wall for operating the multi-plate clutch 63;
When moving forward, the multi-disc clutch 63 is engaged to rotate the planetary gear mechanism as a unit and transmit power to the input pulley, and when moving backward, the multi-disc brake 65 is actuated to fix the ring gear 66 and input power. It is designed to transmit reverse rotational power to the pulley. At this time, when moving forward, the input shaft 60
The torque is transmitted exclusively through the carriers 62, 62' and the clutch 63 to the input shaft 51 of the linear continuously variable transmission section 5
A, and only a slight surface pressure that prevents rotation of the pinion 64' acts on the pivot shaft surface of the pinion 64' and the contact surface between the pinion 64' and the sun gear 67, and other No load acts on the pivot shaft surface of the pinion 64'' and the contact surface with the ring gear 66.

The differential gear 7 is arranged parallel to the input shaft 51 and the output shaft 55 of the V-belt type continuously variable transmission section 5, and the output shaft 71 is connected to the axle 70.

The idler gear 8 is the differential gear 7
input large gear 72 and the V-belt type continuously variable transmission section 5
is inserted between the output gear 59 of the V-belt type continuously variable transmission section 5 provided at the engine side end of the output shaft 55, and one end is pivotally supported by the housing 1 in parallel to the output shaft 55. The other end is composed of an idler gear shaft 81 that is pivotally supported by the intermediate case 3, an input gear 82 that meshes with the output gear 59 provided on the idler gear shaft 81, and an output gear 83 that meshes with the input large gear 72. be done.

In this embodiment, the output shaft 42 of the fluid coupling 4 and the input shaft 6 of the planetary gear type forward/reverse switching mechanism 6
0, and the input shaft 51 of the V-belt continuously variable transmission section constitute a first shaft, and the output shaft 55 of the V-belt continuously variable transmission section and the output gear 59 constitute a second shaft,
The idler gear shaft 81 constitutes a third shaft.

The V-belt type continuously variable transmission section 5 and the planetary gear type forward/reverse switching mechanism 6 are controlled in a predetermined manner, such as reduction ratio, forward movement, and reverse movement, by a hydraulic control device according to vehicle running conditions such as vehicle speed and throttle opening.

A hollow portion 511A formed at the axis of the input shaft 51 on the engine side of the V-belt type continuously variable transmission section is a first oil passage, and the sleeve 422 is fitted into the hollow portion 511A on the side of the engine. and the sleeve 42
2 is provided with an oil passage 511 at its axial center, and an oil passage 511G for supplying lubricating oil is formed between its outer periphery and the input shaft 51.

The supply and discharge of pressure oil to the hydraulic servo 69 of the multi-disc clutch 63 is controlled by a hydraulic control device (not shown), and the pressure oil discharged by the oil pump 101 is routed through the oil passages (not shown) of the housing 1 and the intermediate case 3. An oil passage 51 formed at the axis of the sleeve 422 passes through an oil passage 301 provided on the sleeve 31 via a hydraulic control device, passes through an oil passage 421 provided on the output shaft 42 of the fluid coupling 4.
1. The oil is supplied to the hydraulic servo 69 through a hollow portion 511A formed at the axis of the input shaft 51 on the engine side and an oil passage 513 formed at the base of the fixed flange 52A. Similarly, the lubricating oil from the hydraulic control device is transmitted from the oil passage formed on the output shaft 42 of the fluid coupling to the oil passage 511G between the oil passage 511A formed on the input shaft 51 and the sleeve 422, It is supplied to each lubricating point of the gear type forward/reverse switching mechanism 6.

On the side of the input shaft 51 of the V-belt type continuously variable transmission unit opposite to the engine, a hollow portion 511B is formed at the center of the shaft, which serves as a second oil passage that is a pressure oil supply and drainage passage for the hydraulic servo 53. A pipe-shaped protrusion 26 of a lid 26 is attached to the end of the hollow portion opposite to the engine so as to close a hole 25A formed in a portion of the side wall 25 of the transmission case corresponding to the input shaft 51.
1 is fitted. The lid 26 is provided with an oil passage 514 that connects a pressure oil supply/drain passage 514A to the hydraulic servo 53 provided in the transmission case 2 and a hollow portion 511B provided in the input shaft.

The hydraulic servo 53 of the input pulley 52 is a reaction force supporter that is oil-tightly fitted into a flange 521 formed on the back surface of the movable flange 52B, and whose base end is fixed together with the drum member 522 by a collar member 523. A first hydraulic servo 53 is provided between the support member 525 and the movable flange 52B.
A, and a piston member 526 is attached to the drum member 522 and the reaction force support member 525 in an oil-tight manner.
are fitted, and the piston member 526 is fitted with the flange 5.
21 and forms a second hydraulic servo 53B with the drum member 522. Therefore, the first hydraulic servo 53A and the second hydraulic servo 53B have a double piston structure that acts in series on the movable sheave 52B.

Supply and discharge of pressure oil from the input pulley 52 to the hydraulic servo 53 is controlled by a hydraulic control device (not shown).
Pressure oil discharged by the oil pump 101 is guided from oil passages (not shown) in the housing 1 and the intermediate case 3 to a pressure oil supply and drainage passage 514A provided in the transmission case 2 via a hydraulic control device, The oil is supplied to the hollow part 511B provided at the axis of the input shaft 51 on the side opposite to the engine through an oil path 514 provided in the lid 26, and is further provided in an oil path 511C provided in the input shaft and a movable flange 52B. The oil is supplied to the oil chamber of the first hydraulic servo 53 through the oil passage 52C, and the oil passage 511D and the reaction force support member 5 are supplied from the hollow part 511C to the input shaft.
The oil is supplied to the second hydraulic servo 53B through an oil passage 52D formed in 26.

Further, the forward/reverse switching mechanism 6 disposed between the input pulley 52 and the intermediate case 3 is supplied with sufficient hydraulic pressure to the hydraulic servo 69 via the oil passage 511A formed in the input shaft 51 as described above. At the same time, sufficient lubricating oil is supplied through the oil passage 511G, which is also formed by the oil passage 511A and the sleeve 422.

(g) Effect of the invention As explained above, according to the invention, the forward/reverse switching mechanism 6 has a double planetary gear type planetary gear mechanism, and its sun gear 67 and carrier 6
Since the clutch 63 is interposed between the clutch 63 and the ring gear 66 and the brake 65 is connected to the ring gear 66, the clutch 63 and the brake 65 are connected to different elements 62 and 66, respectively, and these elements, the clutch and the brake are connected. The structure of the forward/reverse switching mechanism 6 can be simplified. Furthermore, during forward movement, which is the normal operating state of the continuously variable transmission, the transmission is directly from the fluid coupling output shaft 42 to the input shaft 51 exclusively via the clutch 63 and carriers 62, 62', so that the pinions 64', 64″ shaft support surface and other gears 67,
It does not apply a large load to the tooth surface with 66, improves transmission efficiency, and lubricates the shaft support surface, tooth surface, etc. easily and reliably.
Furthermore, durability can be improved by reducing wear on the shaft support surface and gear tooth surface.

In addition, since hydraulic pressure can be quickly supplied and discharged to and from the hydraulic servo 53 of the input pulley 52 via the oil passage 511B formed at the input shaft axis, the responsiveness of speed change control can be improved. Servo 53
The oil pressure is transmitted through the oil passage 511B, which has a large oil passage area.
It is possible to quickly return the V-belt type continuously variable transmission section 2 to the maximum deceleration position and restart the vehicle smoothly. In addition, the input pulley 52
The lubricating oil or hydraulic oil can be reliably supplied to the planetary gear type forward/reverse switching mechanism 6 disposed between the and the fluid coupling 4 via the other oil passage 511A.

[Brief explanation of the drawing]

FIG. 1 is a sectional view showing a continuously variable transmission for a vehicle according to an embodiment of the present invention, and FIG. 2 is a front view showing its double planetary gear type planetary gear mechanism. FIG. 3 is a sectional view showing a conventional continuously variable transmission for vehicles. 2... V-belt type continuously variable transmission section, 4... Fluid coupling, 6... Planetary gear type forward/reverse switching mechanism, 42...
Output shaft of fluid coupling, 51... Input shaft, 52... Input pulley, 52A... Fixed flange, 52B...
Movable flange, 53...Hydraulic servo, 55...Output shaft, 57...Hydraulic servo, 58...V belt,
62, 62'...carrier, 63...clutch,
64, 64'...pinion, 65...brake,
66...Ring gear, 67...Sun gear, 511
A, 511B...Oil road.

Claims (1)

[Claims for Utility Model Registration] A fluid coupling connected to the engine, a planetary gear type forward/reverse switching mechanism connected to the output shaft of the fluid coupling, and a planetary gear type forward/reverse switching mechanism connected to the output element of the planetary gear type forward/reverse switching mechanism. an input shaft, an output shaft disposed parallel to the input shaft, and an input pulley and output whose effective diameter is variable by a hydraulic servo provided on the input shaft and output shaft to supply and discharge hydraulic oil. In a V-belt continuously variable transmission for a vehicle, comprising a pulley and a V-belt that transmits power between the two pulleys, the planetary gear forward/reverse switching mechanism controls the output of the fluid coupling. a pair of double planetary gear type planetary gear mechanisms arranged in alignment with the shaft and the input shaft and arranged between the fluid coupling and the V-belt type continuously variable transmission section, and a sun gear in the planetary gear mechanism; A clutch is interposed between the clutch and the ring gear, and a brake is connected to the ring gear, and upon connection of the clutch and release of the brake, the output shaft and the input shaft of the fluid coupling are integrated via the carrier and the clutch. and transmits the rotation of the output shaft of the fluid coupling to the input shaft as reverse rotation based on the release of the clutch and the locking of the brake, and the input pulley is integrally connected to the input shaft. and a movable flange that is slidably supported on the input shaft and is moved in the axial direction by the hydraulic servo, and further Oil passages are formed at the axis of the input shaft from both ends thereof, and the ends of these oil passages are separated so as not to communicate with each other, and an oil passage is formed on the opposite side from the planetary gear type forward/reverse switching mechanism. Hydraulic pressure is supplied to and discharged from the hydraulic servo of the movable flange via a passage. V-belt continuously variable transmission for vehicles.