JPH0345260B2 - - Google Patents

Description

[Detailed description of the invention]

[Industrial Application Field] The present invention relates to a transmission mounted on a vehicle such as an automobile. More specifically, the present invention relates to a transmission equipped with a belt-type continuously variable transmission and an auxiliary transmission. [Prior Art] Recently, a transmission equipped with a belt-type continuously variable transmission and an auxiliary transmission has been proposed as a transmission for vehicles such as automobiles. A belt type continuously variable transmission has an input pulley and an output pulley each having a circumferential groove with a V-shaped cross section on one rotating shaft and the other rotating shaft. It is wrapped around and passed around. By relatively changing the width of the circumferential groove of the V-shaped cross section of the input pulley and output pulley, the rotational power is transmitted from one rotating shaft to the other rotating shaft in a stepless manner. It's summery. The belt-type continuously variable transmission is configured to only change speed in one direction, and cannot change speed in reverse, that is, change forward or forward. Therefore, in order to use the belt-type continuously variable transmission as a transmission for a vehicle such as an automobile, an auxiliary transmission equipped with a forward/reverse switching transmission mechanism is provided in addition to the belt type continuously variable transmission. The auxiliary transmission is disposed on the output side of the belt-type continuously variable transmission from the viewpoint of reducing the capacity of the belt-type continuously variable transmission and making it more compact. For example, in Japanese Patent Application Laid-Open No. 57-47059, an auxiliary transmission device comprising a brake device, a planetary gear device, and a clutch device is arranged on the output side of a belt type continuously variable transmission device. (Problems to be Solved by the Invention) Conventionally, it has been desired that a transmission mounted on a vehicle such as an automobile be configured as compactly as possible. In particular, it is strongly desired in front-wheel drive cars (front-engine, front-drive cars), and even more so in front-wheel drive cars with horizontally mounted engines due to vehicle width constraints. By the way, the factors that make a transmission equipped with a belt-type continuously variable transmission and an auxiliary transmission compact are to arrange and configure the shaft length of the auxiliary transmission as short as possible, and to reduce the distance between the shafts of the input and output pulleys. The purpose is to arrange and compose as short as possible. However, in the auxiliary transmission device described in the above-mentioned Japanese Patent Application Laid-open No. 57-47059, the brake device,
Since the planetary gear device and the clutch device are each arranged in series in the axial direction, there is a problem that the axial length of the auxiliary transmission device becomes long and the entire transmission becomes larger. Particularly, when the clutch device or brake device of the auxiliary transmission is constructed of a friction multi-disc engagement type, the axial length becomes longer because the friction multi-disc engagement type requires a relatively large space. Further, in order to transmit the increased torque by the belt-type continuously variable transmission, the auxiliary transmission must have a large transmission torque capacity. In order to increase the capacity of the auxiliary transmission, it is undesirable to increase the size of the brake device, planetary gear device, and clutch device in the axial direction because the axial length becomes even longer. However, when the auxiliary transmission is increased in size in the radial direction, a problem arises in that the distance between the axes of the input pulley and output pulley of the belt-type continuously variable transmission becomes large. That is, the hydraulic cylinder devices that respectively drive and control the input pulley and the output pulley of the belt-type continuously variable transmission are arranged on opposite sides in the axial direction in order to use the transmission belt in a straight state. For this reason, the hydraulic cylinder device of the input pulley and the auxiliary transmission device are arranged on the same side, and as the auxiliary transmission device becomes larger in the radial direction, interference between the hydraulic cylinder device of the input pulley and the auxiliary transmission device can be avoided. A problem arises in that the distance between the axes of the input pulley and output pulley increases. Therefore, the problem to be solved by the present invention is that even if an auxiliary transmission device is provided that has sufficient transmission torque capacity to handle the torque increased by the belt-type continuously variable transmission device, it is not possible to configure the transmission compactly. It's about doing. [Means for Solving the Problems] The present invention focuses on the space on the side of the hydraulic cylinder device of the input pulley, and arranges the clutch device and the planetary gear device used in the auxiliary transmission in series on the axis, and By providing a brake device radially outside the gear device or clutch device and arranging the brake device so as to extend into the space,
This is an attempt to solve the above-mentioned problems. Specifically, the present invention takes the following measures. In other words, there is a belt-type continuously variable transmission in which a transmission belt is passed between the input pulley and the output pulley, and the transmission is transmitted from the input pulley to the output pulley in a continuously variable manner. In a transmission equipped with an auxiliary transmission having a friction multi-disc engagement type clutch device and a brake device combined with a planetary gear device disposed in
The hydraulic cylinder device of the input pulley is disposed on one side of the axis of the input pulley, and the clutch device and the planetary gear device of the auxiliary transmission adjacent to the output pulley are arranged in series on the axis of the output pulley and on one side of the axis of the input pulley. The brake device of the auxiliary transmission device is located on the same side as the hydraulic cylinder device, and the brake device of the auxiliary transmission device is located radially outside of the clutch device or planetary gear device on the side far from the output pulley, and It is characterized by the overlap with [Operation] In the transmission including the belt-type continuously variable transmission and the auxiliary transmission of the present invention, the output of the engine is transmitted to the continuously variable transmission. This continuously variable transmission has an input pulley and an output pulley that move in the axial direction to continuously change the gear ratio while transmitting the aforementioned output to the auxiliary transmission. This auxiliary transmission transmits the power through a planetary gear system, transmitting the power in the forward rotational direction when the clutch device is activated, and transmitting the output in the reverse rotational direction when the brake device is activated. It is designed to communicate. The distance between the input pulley and the output pulley is set based on the transmission torque capacity, gear ratio range, etc. of the belt type continuously variable transmission. The diameter of the clutch device and planetary gear device of the auxiliary transmission is determined within a range that does not interfere with the hydraulic cylinder device of the input pulley, and the length in the axial direction is determined so as to provide sufficient transmission torque capacity. However, the brake system
Since it is located radially outward of the clutch device or planetary gearing so as to overlap radially with the hydraulic cylinder device of the input pulley, the diameter of the braking device is large, increasing the braking capacity and reducing the overall auxiliary transmission device. The shaft length becomes shorter. [Example] Hereinafter, an example of the present invention will be described based on the drawings. 1 and 2 show an embodiment according to the invention. FIG. 2 shows a skeleton diagram of a transmission equipped with a belt type continuously variable transmission and an auxiliary transmission. FIG. 1 shows a sectional view of the detailed structure of the transmission shown in FIG. 2. FIG. Note that, in FIG. 1, the reduction gear device and differential gear device shown in FIG. 2 are omitted. The transmission of this embodiment, as shown in FIG.
Broadly divided, fluid coupling device 50, belt type continuously variable transmission 100, auxiliary transmission 200,
It consists of a reduction gear device 300 and a differential gear device 350. Each of these devices is installed within the case member of the transmission. The case members consist of a fluid coupling case member 10, a main case member 12, and a cover member 14. Each of these case members forms a chamber that accommodates each device. A fluid coupling device chamber 52 is formed by the fluid coupling case member 10, and a fluid coupling device 50 is disposed therein. A belt type continuously variable transmission chamber 10 is formed by the main case member 12 and the cover member 14.
2 is formed, and a belt type continuously variable transmission 100 is arranged. Further, as seen in FIG. 2, an auxiliary transmission chamber 202 is formed by the main case member 12 at a lower position of the main case member 12.
00 is placed. Further, as seen in FIG. 2, a differential chamber 302 is formed by the fluid coupling case member 10 at a lower position of the fluid coupling case member 10, and a reduction gear device 30
0, a differential gear device 350 is arranged. Next, each device will be explained. Fluid Coupling Device 50 The fluid coupling device 50 consists of a fluid coupling 54 and a direct coupling clutch 60. The fluid coupler 54 consists of a pump impeller 56 and a turbine impeller 58. The pump impeller 56 is connected to an engine crankshaft (not shown), and the turbine impeller 58 is connected to an input shaft of a belt-type continuously variable transmission 100. input pulley 11
0 rotation shaft 104. As is well known, the fluid coupling 54 transmits power through fluid (oil), and transmits the rotational power of the engine to the belt type continuously variable transmission 100. The direct coupling clutch 60 directly transmits the rotational power of the engine to the rotating shaft 104 of the input pulley 110 by its operation. When power is transmitted via the fluid coupling 54, since it is a fluid transmission, it is transmitted with slippage and deceleration.
When using the direct coupling clutch 60, there is no slippage and the signal is transmitted as it is. This direct coupling clutch 60 is
It is provided to improve the so-called fuel consumption rate, and is normally activated when driving at high speeds. In addition, as shown in FIG. 1, the oil pump 70
However, the rear position of the fluid coupling 54 (first
It is located at the left position (as seen in the figure). The oil pump 70 is driven by a rotation transmission member 72 integrated with the pump impeller 56, and generates hydraulic pressure. The oil pressure is used to control a belt-type continuously variable transmission 100 and an auxiliary transmission 200, which will be described later. Belt type continuously variable transmission 100 The belt type continuously variable transmission 100 has an input pulley 1
10 and an output pulley 150. The input pulley 110 includes a fixed pulley 112 and a movable pulley 11.
It consists of 4. The fixed pulley 112 is formed integrally with the rotating shaft 104, and the movable pulley 11
4 is fitted and attached to this rotating shaft 104. As best shown in FIG.
and the movable pulley 114 are attached with balls 120 engaging with axial grooves 117 and 118 formed in both of them, so that the movable pulley 1
14 is movable in the axial direction with respect to the rotating shaft 104, but is integral in the rotating direction. The rotation shaft 104 of the input pulley 110 has two
It is rotatably supported by the partition wall member 12a of the main case member 12 and the cover member 14 via bearings 122 and 124. Opposing pulley surfaces 112a and 114a of the fixed pulley 112 and the movable pulley 114 are formed in a circumferential groove 116 having a V-shaped cross section. A transmission belt 190 is wound around this circumferential groove 116. In addition, the circumferential groove 1
The width of the pulley 16 can be changed by moving the movable pulley 114 in the axial direction, so that the effective diameter around which the transmission belt 140 is wound can be changed. In FIG. 1, the input pulley 110 is shown with different effective diameters above and below its center line CL. The illustrated state in the upper half shows the minimum effective diameter state of the power transmission belt 190, and the illustrated state in the lower half shows the maximum effective diameter state. The movable pulley 114 is axially moved by a hydraulic cylinder device 130 at the back. As shown in FIG. 1, the hydraulic cylinder device 130 has a first hydraulic fluid chamber 132 and a second hydraulic fluid chamber 134. The first hydraulic oil chamber 132 is connected to the movable pulley 114 and the first hydraulic oil chamber forming member 13.
6. The second hydraulic oil chamber 134 is defined by a piston 138 and a second hydraulic oil chamber forming member 140.
By supplying and discharging hydraulic pressure to the first hydraulic oil chamber 132 and the second hydraulic oil chamber 134, the movable pulley 114 is moved in the axial direction. In FIG. 1, the input pulley 11 is in a state where the upper half of the hydraulic cylinder device 130 is in a state where the working oil pressure is exhausted.
0 is the minimum effective diameter state. The lower half state is the state where the most working oil pressure is supplied, and the input pulley 110 has the largest effective diameter state. The hydraulic pressure is supplied from the first hydraulic pressure 132 through the communication hole 142 to the second hydraulic fluid chamber 134 . And the first hydraulic oil chamber 13
2 and the second hydraulic oil chamber 134 are adapted to operate simultaneously. Note that the reason why two hydraulic oil chambers, the first hydraulic oil chamber 132 and the second hydraulic oil chamber 134, are provided in this way is to increase the operating area of the hydraulic pressure. The output pulley 150 is also approximately the same as the input pulley 11.
It is configured in the same way as 0. That is, it consists of a fixed pulley 152 and a movable pulley 154, and the movable pulley 154 is fitted and attached to a rotating shaft 180 that is integrated with the fixed pulley 152. The movable pulley 154 has axial grooves 156 and 158, similar to the movable pulley 114 of the input pulley 110.
and a ball 160, which are integrally attached to the rotating shaft 180 in the rotational direction but movable in the axial direction. Note that the arrangement of the fixed pulley 152 and the movable pulley 154 of the output pulley 150 is left and right opposite to that of the input pulley 110. This corresponds to each circumferential groove 11 of the input pulley 110 and the output pulley 150.
This is to maintain the positional state of the power transmission belt 190 in a straight state when the width of 6,166 is changed. Similarly to the case of the input pulley 110, the rotation shaft 180 of the output pulley 150 is also supported by the partition member 12a of the main case member 12 and the cover member 14 on both sides via bearings 162 and 164. As seen in FIG. 1, the right end of the rotating shaft 180 is connected to an auxiliary transmission device 200 and a reduction gear device 3, which will be described later.
It is formed separately from these devices so that it can be extracted from the output shaft 310 of 00. Further, opposing pulley surfaces 152a and 154a of the fixed pulley 152 and the movable pulley 154 are formed in a circumferential groove 166 with a V-shaped cross section, and transmission is transmitted to the circumferential groove 166 of the output pulley 150 and the circumferential groove 116 of the input pulley 110. A belt 190 is wrapped around it. The effective diameter of the output pulley 150 at the position around which the transmission belt 190 is wound can also be changed by moving the movable pulley 154 in the axial direction.
In FIG. 1, the illustrated state of the upper half of the output pulley 150 indicates the minimum effective diameter state, and the illustrated state of the lower half indicates the maximum effective diameter state. A hydraulic cylinder device 170 is provided at the back of the movable pulley 154. Hydraulic cylinder device 17
0 has a hydraulic oil chamber 172. Hydraulic oil chamber 1
72 is a movable pulley 154 and a hydraulic oil chamber forming member 17
It is defined and formed by 4. Hydraulic oil chamber 1
72 is supplied with hydraulic pressure, but due to a change in the effective diameter of the input pulley 110, the output pulley 150
The effective diameter of this output pulley 1 is forcibly changed.
Depending on the change in the effective diameter of 50, this hydraulic oil chamber 17
The hydraulic pressure No. 2 is supplied and discharged. As shown in FIG. 1, the power transmission belt 190 is composed of an endless carrier 192 and a power transmission block 194. The endless carrier 192 is formed by laminating a plurality of thin metal hoops. A plurality of power transmission blocks 19 are connected to the pair of endless carriers 192 formed in this way.
4 are arranged adjacent to each other in a daisy chain pattern to form a power transmission belt 190. Since the belt type continuously variable transmission 100 is configured as described above, power is transmitted from the input pulley 110 to the output pulley 150 via the transmission belt 190, and at this time, the effective diameter of the input pulley 110 is changed. The output pulley 15
0 is transmitted in a stepless manner. Note that, as is well known, the distance between the axes of the input pulley 110 and the output pulley 150 is set based on the transmission torque capacity, gear ratio range, etc. of the belt type continuously variable transmission 100. Auxiliary Transmission Device 200 The auxiliary transmission device 200 is disposed on the output side of the belt-type continuously variable transmission device 100 and includes a Ravignio type compound planetary gear device 210 and two brake devices 2.
30, 240 and one clutch device 250. The brake device 240 and the clutch device 250 are
It is constructed using a well-known friction multi-plate engagement type. Brake device 230 is configured in the well-known brake band format. The Ravignio type composite planetary gear device 210 includes a first sun gear 212 and a second sun gear 214,
A first planetary gear 216 that meshes with the first sun gear 212, and this first planetary gear 21
6, a second planetary gear 218 that meshes with the second sun gear 214, and the first planetary gear 21.
6, the first planetary gear 216 and the second planetary gear 21
The carrier 222 rotatably supports the carrier 8. Each element of the above-mentioned Ravignio type compound planetary gear set 210, two brake devices 230, 240, and one clutch device 250 are connected to the output pulley 1.
50 and the output shaft 310 of the reduction gear device 300 are connected as follows.
The first sun gear 212 is connected to the rotating shaft 180 via a clutch device 250, and the second sun gear 212 is connected to the rotating shaft 180 via a clutch device 250.
14 is directly connected to the rotating shaft 180 by spline fitting. Further, the first sun gear 212 is provided with a brake device 230 between it and the partition wall member 12a. Similarly, the ring gear 220 is provided with a brake device 240 between it and the partition member 12a. Then, the carrier 222 serves as an output member.
It is connected to the output shaft 310 of the reduction gear device 300 by spline fitting. With the above-mentioned connection configuration, the auxiliary transmission device 200
By selectively operating two brake devices 230, 240 and one clutch device 250, two forward speeds and one reverse speed can be obtained. Forward 1st speed Brake device 230 is in operation state,
This is established by deactivating the clutch device 250 and the brake device 240. In this state, rotational power is input from the second sun gear 214, which rotates the first planetary gear 216 and the second planetary gear 218, and the first sun gear fixed by the brake device 230. The revolution rotating planetary on 212 is decelerated from carrier 222 and taken out to output shaft 310 . 2nd forward speed clutch device 250 is in operation state,
This is established by deactivating brake devices 230 and 240. In this state, rotational power is simultaneously input from the first sun gear 212 and the second sun gear 214, and the Ravignio type compound planetary gear set 210 is in an integrally rotating state. Therefore, the input rotation is directly output to the carrier 222. Reverse travel is established by placing the brake device 240 in the activated state and the clutch device 250 and the brake device 230 in the deactivated state. In this state, rotational power is input from the second sun gear 214, which causes the first planetary gear 216 and the second planetary gear 218 to rotate, and the rotational power of the ring gear 220 rotated by the brake device 240. The planetary rotation on the teeth is extracted from the carrier 222 in a reverse rotation state and at a reduced speed. By the way, the auxiliary transmission chamber 202 that accommodates the auxiliary transmission 200 and the belt-type continuously variable transmission chamber 10 that accommodates the belt-type continuously variable transmission 100 described above.
2 are partitioned by a partition wall member 12a of the main case member 12. A partition member 12 that partitions this auxiliary transmission chamber 202 and the belt type continuously variable transmission 102
A has a shaped portion in which a stepped portion 400 is formed. As best shown in FIG.
and the auxiliary transmission 200, and consists of a first step 402 with a small diameter and a second step 404 with a large diameter when viewed from the auxiliary transmission chamber 202 side. The input pulley 11 is located at the position of the belt type continuously variable transmission chamber 102 corresponding to the position of the first step portion 402.
0 hydraulic cylinder devices 130 are arranged.
At a position in the auxiliary transmission chamber 202 corresponding to the position of the first step portion 402, a clutch device 250 of a frictional multi-plate engagement type is disposed.
A brake device 230 in the form of a brake band is disposed on the outer periphery of the vehicle 50 . This clutch device 2
50 is determined by the diameter of the first stepped portion 402, but in order to sufficiently transmit the torque increased by the belt-type continuously variable transmission 100, its axial size, that is, The number of friction plates is set. Note that since the brake band type brake device 230 does not require much space in the radial direction, it can be placed at the position of the first step portion 402 having a small diameter. Next, a planetary gear unit 21 is located in the auxiliary transmission chamber 202 at a position corresponding to the position of the second step portion 404.
0 and a friction multi-plate engagement type brake device 240 are arranged. The brake device 240 is located at a radially outer position of the planetary gear device 210 and is arranged to overlap the hydraulic cylinder device 130 of the input pulley 110 in the radial direction. This increases the diameter of the brake device 240, thereby increasing the braking capacity. And the brake device 240
The transmission torque capacity of the planetary gear device 210 located on the radially inner side of the belt type continuously variable transmission device 100 is
Its axial size is set so that it can sufficiently transmit the torque increased by. According to the auxiliary transmission device 200 configured as described above, even if the clutch device 250 and the planetary gear device 210 are configured to sufficiently transmit the torque increased by the belt type continuously variable transmission device 100, the auxiliary transmission device 200 is configured as described above. The axial length of the entire transmission 200 can be shortened. That is, when the planetary gear system 210 and the brake device 240 are arranged side by side in the axial direction, the axial length increases accordingly, but by arranging them side by side in the radial direction as in this embodiment, the axial length is reduced by the amount of the brake device 240. Since it can be made shorter, the axial length of the entire auxiliary transmission 200 can be made shorter. Furthermore, since the diameter of the brake device 240 becomes larger, the brake device 240 is also adjusted to accommodate the increased torque of the belt-type continuously variable transmission 100.
Braking capacity increases. Furthermore, the input pulley 11
The configuration is such that a small-diameter first step portion 402 is arranged at a position corresponding to the hydraulic cylinder device 130 of 0,
By providing the auxiliary transmission device 200, the distance between the shafts of the input pulley 110 and the output pulley 150 does not become long, and the distance between the shafts of the input pulley 110 and the output pulley 150 can be made as short as possible. Therefore, the shaft length of the auxiliary transmission device 200, which has sufficient transmission torque capacity, can be shortened, and the distance between the shafts of the input pulley 110 and the output pulley 130 can be shortened as much as possible, so the transmission can be configured compactly. can. Note that the above-mentioned auxiliary transmission 200 is provided at a position in the power transmission path after the belt-type continuously variable transmission 100, so the belt-type continuously variable transmission 1
00 can be made small. That is, the auxiliary transmission 200 is the belt type continuously variable transmission 100.
In some cases, the belt-type continuously variable transmission 100 is provided at a position earlier in the power transmission path, but in this case, since the torque is increased by the auxiliary transmission 200, it is necessary to configure the belt type continuously variable transmission 100 to have a large capacity and large capacity. arise. However, when it is placed on the output side as in this embodiment, the torque increase is caused by the belt type continuously variable transmission 1.
00, the belt type continuously variable transmission 100 requires less capacity and can be made smaller. Furthermore, when the auxiliary transmission 200 is disposed before the belt-type continuously variable transmission 100, the transmission belt 190 of the belt-type continuously variable transmission 100 rotates in both forward and reverse directions. It may become harsh and the durability may decrease. However, in the case of this embodiment, since the forward/reverse switching is performed after the belt-type continuously variable transmission 100, the transmission belt 190 always rotates in the same direction, improving the durability of the transmission belt 190. be able to. Reduction Gear Device 300 In the reduction gear device 300, a gear 312 provided on an output shaft 310 meshes with a first gear 322 of an intermediate shaft 320, and a second gear 324 of the intermediate shaft 320 is a final reduction gear. 330 and meshes with each other. The meshing of each of these gears is configured to rotate at a reduced speed. As a result, the rotation from the auxiliary transmission device 200 is decelerated by the reduction gear device 300 and transmitted to the differential gear device 350. Differential Gear Device 350 The differential gear device 350 is provided in the final reduction gear 330 with a well-known configuration. That is, pinions 356, 358 supported by a pinion shaft 360 are attached to a pair of left and right side gears 352, 354.
are in mesh with each other, and rotational power is transmitted from the differential case 362 to the pinion shaft 360, pinion 356,
358, to the side gears 352, 354, and from the side gears 352, 354 to the drive shaft 37.
0,372 and is transmitted to wheels (not shown). The differential rotation of the left and right wheels is achieved by pinions 356 and 3.
58 rotation. In addition, in the above-mentioned embodiment, an example of the auxiliary transmission device 200 was explained in which the planetary gear device 210 was arranged on the side far from the output pulley 150.
The auxiliary transmission device 200 may be configured such that the clutch device 250 is disposed on the side far from zero. [Effects of the Invention] According to the present invention, the clutch device of the auxiliary transmission device and the planetary gear device are arranged in series in the axial direction, and the brake device is arranged radially outside and radially input to the planetary gear device or the clutch device. Since the pulley is placed overlapping the hydraulic cylinder device, the clutch device and planetary gear device can be easily adjusted within a range that does not increase the distance between the shafts of the input pulley and output pulley, which is set based on the transmission torque capacity of the belt-type continuously variable transmission. Even if the diameter of the clutch device and the planetary gear device is set, the axial length of the clutch device and the planetary gear device can be set so as to provide sufficient transmission torque capacity while reducing the axial length of the entire auxiliary transmission device. Furthermore, the diameter of the brake device becomes larger, and the braking capacity also becomes larger. Therefore, the shaft length of the auxiliary transmission with sufficient transmission torque capacity can be shortened, and the distance between the shafts of the input pulley and output pulley can be shortened as much as possible. Even if an auxiliary transmission device having a transmission torque capacity sufficient for the torque is provided, the transmission can be configured compactly.

[Brief explanation of drawings]

FIG. 1 is a sectional view showing the detailed structure of an embodiment of a transmission according to the present invention, and FIG. 2 is a skeleton diagram. Explanation of symbols 12a... partition member, 100...
Belt type continuously variable transmission, 102... Belt type continuously variable transmission chamber, 110... Input pulley, 150...
Output pulley, 190... Transmission belt, 200...
Auxiliary transmission, 202...Auxiliary transmission chamber, 21
0... Planetary gear device, 240... Brake device,
250...Clutch device, 400...Step part, 40
2...First step, 404...Second step.

Claims (1)

[Claims] 1. A belt-type continuously variable transmission in which a transmission belt is stretched between an input pulley and an output pulley to transmit transmission from the input pulley to the output pulley in a continuously variable manner, and a belt-type continuously variable transmission. In a transmission equipped with an auxiliary transmission having a clutch device and a brake device of a friction multi-plate engagement type in combination with a planetary gear device disposed on the axis of an output pulley, the hydraulic cylinder device of the input pulley is connected to the input pulley. The clutch device and the planetary gear device of the auxiliary transmission are arranged on one side on the axis of the pulley and adjacent to the output pulley, and the clutch device and the planetary gear device of the auxiliary transmission are arranged in series on the axis of the output pulley and on the same side as the hydraulic cylinder device of the input pulley. and further characterized in that the brake device of the auxiliary transmission device is located radially outside of the clutch device or planetary gear device on the side far from the output pulley, and overlaps with the hydraulic cylinder device in the radial direction. A transmission equipped with a belt-type continuously variable transmission and an auxiliary transmission.