JP2004245329A - Power transmission device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a power transmission device of such constitution that a degree of freedom in setting a speed change ratio is high, that a degree of freedom in setting a position of a shaft is high, and that compactness can be easily achieved. <P>SOLUTION: This power transmission device is provided with a belt type continuously variable transmission mechanism CVT and a stepped rotation transmitting mechanism GT to transmit rotation drive force of a primary shaft 1 driven to rotate by an engine to be speed-changed and transmitted to a counter shaft 3. The continuously variable transmission mechanism is composed of a drive pulley 10, a driven pulley 15, and a V-belt 14. The stepped rotation transmitting mechanism GT comprises a forward gear train to transmit rotation of an input drive gear 31 on the primary shaft 1 through an idler gear 32 to a low driven gear 33 on a secondary shaft 2, a forward output transmission gear train to transmit rotation of the secondary shaft 2 to a counter shaft 3, and a reverse gear train to transmit rotation of the input drive gear 31 through the idler gear 32 to a reverse driven gear 36 on the counter shaft 3. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a power transmission device including a continuously variable transmission mechanism and a stepped rotation transmission mechanism that change the rotational driving force of an input shaft that is rotationally driven by a drive source and transmit the transmission to an output shaft.
[0002]
[Prior art]
A power transmission device configured with such a continuously variable transmission mechanism and a stepped rotation transmission mechanism is disclosed in, for example, Patent Document 1. The power transmission device (transmission) disclosed in Patent Document 1 has a parallel configuration between a torque converter that receives a rotational driving force from an engine, and an input shaft connected to an output shaft of the torque converter and an output shaft connected to a wheel side. , A gear train (gear-type rotation transmission mechanism, that is, a stepped rotation transmission mechanism) and a belt-type continuously variable transmission mechanism.
[0003]
FIG. 7 shows an arrangement of a power transmission member in the device disclosed in Patent Document 1. A drive pulley 501 of a belt-type continuously variable transmission mechanism is provided on an input shaft having a rotation shaft O11. A V-belt 503 is hung between a driven pulley 502 disposed on an intermediate shaft having a pulley, and a stepless speed change control is performed by controlling a pulley width of both pulleys 501 and 502. The rotation of the driven pulley 502 thus shifted is transferred from the output drive gear 510 provided on the intermediate shaft to the output driven gear 511 provided on the output shaft (having the rotating shaft O13) and meshing therewith. Is transmitted.
[0004]
On the other hand, a forward low drive gear 505 is also provided on the input shaft, and meshes with a forward load driven gear 506 provided on the output shaft having the rotating shaft O13, so that a forward low gear can be set. The input shaft is further provided with a reverse drive gear 507, which meshes with the reverse idler gear 508, and the reverse idler gear 508 meshes with the output driven gear 511. As a result, the rotation is transmitted in the reverse direction. A final drive gear 515 is provided on the output shaft, and meshes with a final driven gear 516 formed integrally with a differential mechanism having a rotation axis O14. The transmitted rotational driving force is transmitted to the wheels via the final drive and driven gears 515, 516.
[0005]
[Patent Document 1] Japanese Patent Application Laid-Open No. Hei 1-150065
[0006]
[Problems to be solved by the invention]
By the way, when a transmission (power transmission device) is configured by combining the continuously variable transmission mechanism and the stepped rotation transmission mechanism as described above, many combinations for arranging these two mechanisms in parallel can be considered. It is important how to arrange efficiently and compactly. In particular, there is a need for a configuration that allows setting with as high a degree of freedom as possible according to the total speed ratio range, maximum speed ratio, and minimum speed ratio required for the transmission. In addition, it is required that the configuration be as small and compact as possible.
[0007]
From this point of view, in the case of the transmission configuration (the transmission configuration shown in FIG. 7) of Patent Document 1 described above, the forward low gear that requires a large gear ratio (reduction ratio) is a forward low drive. This is determined by the gear 505 and the forward load-driven gear 506, and it is necessary to reduce the diameter of the forward low-drive gear 505 and increase the diameter of the forward load-driven gear 506. is there. In particular, since the forward low drive gear 505 is disposed on the input shaft and needs to have a diameter larger than the diameter of the input shaft, it is difficult to reduce the diameter of the forward low drive gear 505. However, there is a problem that the diameter of the transmission increases and the transmission tends to increase in size. Further, since the inter-shaft distance between the input shaft and the output shaft is determined by the two gears meshing in this way, the degree of freedom of the set position is small, and the degree of freedom of setting the position of the output shaft with respect to the input shaft is small. There's a problem.
[0008]
The present invention has been made in view of such a problem, and is directed to a power transmission device including a continuously variable transmission mechanism and a stepped rotation transmission mechanism. It is an object of the present invention to provide a power transmission device having a high degree of freedom in setting and easily configured to be small and compact.
[0009]
[Means for Solving the Problems]
In order to achieve such an object, the power transmission device according to the present invention changes the rotational driving force of an input shaft (for example, the primary shaft 1 in the embodiment) that is rotationally driven by a driving source (for example, an engine) and outputs the rotational driving force. A continuously variable transmission mechanism (for example, a belt-type continuously variable transmission mechanism CVT according to the embodiment) for transmitting to a shaft (for example, the counter shaft 3 in the embodiment) and a stepped rotation transmission mechanism. The continuously variable transmission mechanism is configured to continuously change the rotation of the input shaft and transmit the rotation to the intermediate shaft (for example, the secondary shaft 2 in the embodiment). Gear train for transmitting the rotation of the intermediate shaft to the output shaft, and a reverse gear for transmitting the rotation of the input shaft to the output shaft via the idler shaft. And a gear train.
[0010]
In this power transmission device, the forward gear train includes an input drive gear provided on the input shaft, an input drive gear, and an idler gear provided on the idler shaft. A forward driven gear provided on the intermediate shaft, and the reverse gear train comprises the input drive gear, the idler gear, and a reverse driven gear meshed with the idler gear and provided on the output shaft. It is preferable to configure.
[0011]
According to the power transmission device of the present invention having the above-described configuration, the stepped rotation transmission mechanism transmits the rotation of the input shaft (input drive gear) to the intermediate shaft (forward driven gear) via the idler shaft (idler gear). A forward gear train for transmitting, a forward output transmission gear train for transmitting rotation of the intermediate shaft to the output shaft, and an output shaft (reverse driven gear) for rotating an input shaft (input drive gear) via an idler shaft (idler gear). And a reverse gear train that transmits the reverse gear train. As described above, since both the forward gear train and the reverse gear train transmit the rotation through the idler shaft (idler gear), the degree of freedom in setting the gear ratio is high, and the position of each shaft can be freely set. High degree. In particular, since the idler shaft (idler gear) is shared by the forward and reverse gear trains, the number of necessary gears and the number of shafts are reduced, and the transmission is easily reduced in size and size. Also, by sharing the idler shaft (idler gear) in this way, the forward and reverse gear trains can be arranged side by side on the same plane, and the axial size of the transmission can be suppressed, thereby reducing the size of the transmission. -It can be made compact.
[0012]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings.
[0013]
[First Embodiment]
First, a transmission (power transmission device) according to a first embodiment is shown in FIGS. This transmission is configured such that a torque converter TC, a belt-type continuously variable transmission mechanism CVT, a stepped rotation transmission mechanism GT, and a final reduction mechanism FG are arranged in a transmission housing HSG as illustrated. An input member (pump impeller) of the torque converter TC is connected to an output shaft of an engine (not shown), and a primary shaft (input shaft) 1 is connected to an output member (turbine runner) of the torque converter TC. Is transmitted to the primary shaft 1 via the torque converter TC. The rotation center axis of the primary shaft 1 is indicated by reference numeral O1.
[0014]
A secondary shaft (intermediate shaft) 2 extending in parallel with the primary shaft 1 at a predetermined interval is rotatably disposed in the housing HSG, and extends over the primary shaft 1 and the secondary shaft 2 to form a belt type. A continuously variable transmission mechanism CVT is provided. The rotation center axis of the secondary shaft 2 is indicated by reference numeral O2. The belt-type continuously variable transmission CVT includes a drive pulley 10 supported on a primary shaft 1, a driven pulley 15 supported on a secondary shaft 2, and a metal V-belt wound between the drive pulley 10 and the driven pulley 15. 14 is provided.
[0015]
The drive pulley 10 is fixedly disposed on the primary shaft 1 so as to be rotatable relative to the fixed pulley half 11. The drive pulley 10 is integrally rotated with the fixed pulley half 11, and is axially moved so as to approach / separate therefrom. And a movable pulley half 12 movably disposed on the movable pulley half. A drive oil chamber 13 is formed on a side surface of the movable pulley half 12, and a drive control oil pressure is supplied to the drive oil chamber 13 to control the axial movement of the movable pulley half 12. The driven pulley 15 is fixedly connected to the secondary shaft 2 and disposed on the fixed side pulley half 16. The driven pulley 15 is integrally rotated with the fixed side pulley half 16, and is moved in the axial direction so as to approach and separate from the fixed pulley half 16. The movable pulley half 17 is movably disposed. A driven oil chamber 18 is formed on a side surface of the movable pulley half 17, and a driven control oil pressure is supplied to the driven oil chamber 18 to control the axial movement of the movable pulley half 17. .
[0016]
In the continuously variable transmission CVT, the supply of the hydraulic pressure to the drive oil chamber 13 and the driven oil chamber 18 is controlled as described above to variably adjust the pulley widths of the drive pulley 10 and the driven pulley 15, and the winding of the metal V-belt 14 is performed. The hanging radius is variably set, and the speed of the drive pulley 10 is steplessly changed and transmitted to the driven pulley 15 for speed change control. A CVT clutch 21 is disposed on the primary shaft 1 adjacent to the drive pulley 10, and the drive pulley 10 disposed on the primary shaft 1 so as to be rotatable relative to the primary shaft 1 is driven by the CVT clutch 21. 1 can be disengaged.
[0017]
Next, the stepped rotation transmission mechanism GT will be described. The stepped rotation transmission mechanism GT includes a LOW gear train (forward gear train) including an input drive gear 31, an idler gear 32 meshing with the input drive gear 31, and a LOW driven gear 33 meshing with the idler gear 32. The input drive gear 31 is formed integrally with the primary shaft 1. The idler gear 32 is formed integrally with the idler shaft 4 that extends in parallel with the primary shaft 1 at a predetermined interval and is rotatably supported by the housing HSG. The center axis of rotation of the idler shaft 4 is indicated by reference numeral O5. The input driven gear 33 is rotatably disposed on the secondary shaft 2.
[0018]
The one-way clutch 24 is disposed on the inner periphery of the input driven gear 33, and the LOW clutch 22 is disposed adjacent to the input driven gear 33. The LOW clutch 22 connects the input driven gear 33 and the secondary shaft 2 via the one-way clutch 24 so as to be freely engaged and disengaged. As a result, when the LOW clutch 22 is engaged, rotation can be transmitted in the driving direction from the input drive gear 31 to the secondary shaft 2 via the LOW gear train. The rotation is not transmitted in the direction in which the engine brake acts. In a state where the LOW clutch 22 is released, rotation cannot be transmitted via the LOW gear train.
[0019]
The stepped rotation transmission mechanism GT also includes a forward output transmission gear train including a forward drive gear 34 and a forward driven gear 35 meshing with the forward drive gear 34. The forward drive gear 34 is connected to the secondary shaft 2 and disposed. The forward driven gear 35 extends parallel to the secondary shaft 2 at a predetermined interval and is connected to the counter shaft 3 rotatably supported by the housing HSG. It has been arranged. The rotation center axis of the counter shaft 3 is indicated by reference numeral O3. For this reason, the rotation of the secondary shaft 2 is directly transmitted to the counter shaft 3 via the forward output transmission gear train.
[0020]
The stepped rotation transmission mechanism GT is further rotatably disposed on the counter shaft 3 and includes a reverse driven gear 36 that meshes with the idler gear 32. Thus, a reverse gear train including the input drive gear 31, the idler gear 32, and the reverse driven gear 36 is formed. The reverse driven gear 36 is provided with a reverse clutch 23, and the reverse driven gear 23 can disengage the reverse driven gear 36 from the counter shaft 3. Therefore, when the reverse clutch 23 is engaged, the transmission of the rotational power is performed via the reverse gear train.
[0021]
A final drive gear 37 is formed integrally with the countershaft 3, and this final drive gear 37 meshes with a final driven gear 38 to constitute a final reduction mechanism FG. A differential mechanism 40 is attached to the final driven gear 38, and the rotation of the final driven gear 38 is divided and transmitted to the left and right axle shafts 41 and 42 via the differential mechanism 40 to drive left and right wheels (not shown). I do. The rotation center axes of the final driven gear 38 and the differential mechanism 40 are indicated by reference numeral O4.
[0022]
The shift operation of the transmission (power transmission device) configured as described above will be described below. The rotational driving force from the engine is transmitted to the primary shaft 1 via the torque converter TC. When the CVT clutch 21, the LOW clutch 22, and the reverse clutch 23 are released, the rotational driving force is transmitted to the counter shaft 3. Instead, it is in a neutral state.
[0023]
When the LOW clutch 22 is engaged from the neutral state, the rotational driving force of the primary shaft 1 is transmitted to the secondary shaft 2 via the LOW gear train (the input drive gear 31, the idler gear 32, and the LOW driven gear 33), and further moves forward. The power is transmitted to the counter shaft 3 via an output transmission gear train (forward drive gear 34 and forward driven gear 35). Then, it is transmitted to the left and right wheels via the final reduction mechanism FG, and is driven. That is, a LOW range is set. In the LOW range, the rotational driving force in the wheel driving direction is transmitted by the action of the one-way clutch 24, but the rotational driving force in the opposite direction is not transmitted.
[0024]
Next, when the CVT clutch 21 is engaged, the rotational driving force of the primary shaft 1 is transmitted to the drive pulley 10. In this state, the hydraulic pressure supplied to the drive oil chamber 13 and the driven oil chamber 18 is controlled to variably control the pulley widths of the drive pulley 10 and the driven pulley 15, thereby performing the continuously variable transmission control. Thereby, the rotation of the driven pulley 15 is steplessly controlled and transmitted to the secondary shaft 2, further transmitted to the counter shaft 3 via the forward output transmission gear train, and left and right wheels via the final reduction mechanism FG. To be driven. That is, the CVT range (forward continuously variable transmission range) is set.
[0025]
On the other hand, when the reverse clutch 23 is engaged from the neutral state, the rotational driving force of the primary shaft 1 is transmitted to the counter shaft 3 via the reverse gear train (the input drive gear 31, the idler gear 32, and the reverse driven gear 36). . At this time, the rotation direction of the counter shaft 3 is opposite to that in the LOW range and the CVT range, and this rotational driving force is transmitted to the left and right wheels via the final reduction mechanism FG, and is driven in the reverse direction. You. That is, the reverse range is set.
[0026]
[Second embodiment]
Next, a transmission (power transmission device) according to a second embodiment of the present invention will be described with reference to FIG. Since the transmission shown in FIG. 4 has a configuration similar to that of the transmission according to the above-described first embodiment, the same functional components are given the same reference numerals, and redundant description will be omitted.
[0027]
This transmission differs from the transmission according to the first embodiment in the arrangement of the LOW clutch 22 (and the LOW driven gear 33) and the forward drive gear 34 on the secondary shaft 2 first. Further, the arrangement of the forward driven gear 35 on the countershaft 3 differs according to the difference in the arrangement. However, other configurations are the same, and the functions and operations are the same except for the disposition of the clutches and the gears. Thus, the same shift operation as the transmission according to the first embodiment is performed. Done.
[0028]
[Third embodiment]
Next, a transmission according to a third embodiment of the present invention will be described with reference to FIG. Since the transmission shown in FIG. 5 has a configuration similar to that of the transmission according to the above-described first embodiment, the same functional components are denoted by the same reference numerals, and redundant description will be omitted.
[0029]
In this transmission, similarly to the transmission according to the first embodiment, a torque converter TC, a belt-type continuously variable transmission mechanism CVT, a stepped rotation transmission mechanism GT, and a final reduction mechanism FG are illustrated in a transmission housing HSG. It is arranged and configured as follows. First, the torque converter TC and the belt-type continuously variable transmission CVT are the same as those in the first embodiment, and therefore are denoted by the same reference numerals and description thereof is omitted. In addition, the CVT clutch 21 has the same configuration, and a description thereof will be omitted.
[0030]
In this transmission, the configuration of the stepped rotation transmission mechanism GT is different from the transmission of the first embodiment. First, a first idler gear 132a is rotatably provided on an idler shaft 4 (rotation center axis O5), and a second idler gear 132b is provided via a one-way clutch 24 and provided. The configuration is different. That is, the LOW gear train includes the input drive gear 31, a first idler gear 132a meshing with the input drive gear 31, a second idler gear 132b, and a LOW driven gear 133 meshing with the second idler gear 132b. 133 is connected to the secondary shaft 2 and disposed. On the idler shaft 4, a LOW clutch 122 for engaging and disengaging the first idler gear 132a and the idler shaft 4 is provided. For this reason, when the LOW clutch 122 is engaged, rotation transmission in the driving direction from the input drive gear 31 to the secondary shaft 2 can be performed via the LOW gear train. When this is released, rotation transmission via the LOW gear train can be performed. You will not be able to.
[0031]
The forward output transmission gear train is composed of a LOW driven gear 133 that constitutes the LOW gear train, and a forward driven gear 135 that is disposed on the counter shaft 3 and meshes with the LOW driven gear 133. That is, the LOW driven gear 133 also serves as a forward drive gear.
[0032]
A reverse driven gear 136 constituting a reverse gear train is rotatably disposed on the countershaft 3, and the reverse driven gear 136 meshes with the first idler gear 132a. That is, in this embodiment, the input drive gear 31, the first idler gear 132a, and the reverse driven gear 136 form a reverse gear train. The reverse driven gear 136 is provided with a reverse clutch 123, and the reverse driven gear 123 can disengage the reverse driven gear 136 from the counter shaft 3. Therefore, when the reverse clutch 123 is engaged, a state is established in which rotational power is transmitted through the reverse gear train.
[0033]
The configuration of the final deceleration mechanism FG is the same as that of the first embodiment, and a description thereof will be omitted. Further, the shifting operation associated with the engagement and disengagement of each clutch is the same as that of the first embodiment, and therefore the description thereof is omitted.
[0034]
[Fourth embodiment]
Next, a transmission according to a fourth embodiment of the present invention will be described with reference to FIG. The transmission shown in FIG. 6 has a configuration similar to that of the transmission according to the above-described first embodiment, and therefore, the same functional components are given the same reference numerals and redundant description is omitted.
[0035]
In this transmission, similarly to the transmission according to the first embodiment, a torque converter TC, a belt-type continuously variable transmission mechanism CVT, a stepped rotation transmission mechanism GT, and a final reduction mechanism FG are illustrated in a transmission housing HSG. It is arranged and configured as follows. First, the torque converter TC and the belt-type continuously variable transmission CVT are the same as those in the first embodiment, and therefore are denoted by the same reference numerals and description thereof is omitted. In addition, the CVT clutch 21 has the same configuration, and a description thereof will be omitted.
[0036]
In this transmission, the configuration of the stepped rotation transmission mechanism GT is different from the transmission of the first embodiment. First, a first idler gear 232a is connected and disposed on an idler shaft 24 (rotation center axis O5), a second idler gear 232b is rotatably provided, and a third idler gear 232c is also rotatably provided. , LOW gear train and reverse gear train are different. The LOW gear train includes an input drive gear 31, a first idler gear 232a meshing with the input drive gear 31, a second idler gear 232b, and a LOW driven gear 233 meshing with the second idler gear 232b. It is arranged so as to be connected to the secondary shaft 22. On the idler shaft 24, a LOW clutch 222 for engaging and disengaging the second idler gear 232b with the idler shaft 24 is provided via a one-way clutch 24. For this reason, when the LOW clutch 222 is engaged, rotation transmission in the driving direction from the input drive gear 31 to the secondary shaft 22 can be performed via the LOW gear train, and when this is released, rotation transmission via the LOW gear train can be performed. You will not be able to.
[0037]
The forward output transmission gear train is composed of a LOW driven gear 233 constituting the above-mentioned LOW gear train, and a forward driven gear 235 connected to the counter shaft 23 and engaged with the LOW driven gear 233. That is, the LOW driven gear 233 also serves as a forward drive gear.
[0038]
A reverse driven gear 236 constituting a reverse gear train is rotatably disposed on the counter shaft 23, and the reverse driven gear 236 meshes with the third idler gear 232c. That is, in this embodiment, the input drive gear 31, the first idler gear 232a, the third idler gear 232c, and the reverse driven gear 236 form a reverse gear train. The third idler gear 232c is provided with a reverse clutch 223, and the third idler gear 232c can be disengaged from the idler shaft 24 by the reverse clutch 223. Therefore, when the reverse clutch 223 is engaged, the rotational power is transmitted through the reverse gear train.
[0039]
The configuration of the final deceleration mechanism FG is the same as that of the first embodiment, and a description thereof will be omitted. Further, the shifting operation associated with the engagement and disengagement of each clutch is the same as that of the first embodiment, and therefore the description thereof is omitted.
[0040]
【The invention's effect】
As described above, according to the present invention, the drive pulley provided on the input shaft, the driven pulley provided on the intermediate shaft, and the V belt hung between the drive pulley and the driven pulley A continuously variable transmission mechanism configured to have, a forward gear train transmitting the rotation of an input drive gear provided on the input shaft to a forward driven gear provided on the intermediate shaft via an idler gear, A forward output transmission gear train for transmitting the rotation of the intermediate shaft to the output shaft, and a reverse transmission for transmitting the rotation of the input drive gear provided on the input shaft to a driven reverse gear provided on the output shaft via an idler gear. And a stepped rotation transmission mechanism having a gear train for driving, and a power transmission device is thus configured. Since preliminary reverse gear train is configured together to perform rotation transmission via the idler gear, high degree of freedom of the gear ratio setting, high degree of freedom in setting the shaft position. In particular, since the idler gear is commonly used for the forward and reverse gear trains, the number of necessary gears and shafts is reduced, and the transmission is easily reduced in size and size. Further, by sharing the idler gears in this manner, the forward and reverse gear trains can be arranged side by side on the same surface, and the axial size of the transmission can be suppressed, thereby reducing the size and size of the transmission. be able to.
[0041]
In the power transmission device having the above-described configuration, a drive pulley is rotatably disposed on the input shaft, and a CVT clutch for removably connecting the input shaft and the drive pulley is disposed on the input shaft. Is rotatably disposed on the intermediate shaft, a forward clutch (for example, the LOW clutch 22 in the embodiment) for removably connecting the forward driven gear and the intermediate shaft is disposed on the intermediate shaft, and the reverse driven gear is A reverse clutch rotatably disposed on the output shaft and removably connecting the reverse driven gear and the output shaft may be disposed on the output shaft.
[0042]
Alternatively, the idler gear includes a first idler gear rotatably disposed on the idler shaft, and a second idler gear coupled to the idler shaft, and the first idler gear meshes with the input drive gear. A second driven gear is also meshed with the driven gear for reverse drive, a second idler gear is meshed with the driven gear for forward drive, a drive pulley is rotatably disposed on the input shaft, and a CVT clutch for removably connecting the input shaft and the drive pulley is provided on the input shaft. A forward clutch is disposed on the idler shaft for releasably connecting the first idler gear and the idler shaft, a reverse driven gear is rotatably disposed on the output shaft, and the reverse driven gear and the output shaft A reverse clutch is provided on the output shaft to releasably connect the It may be configured to have.
[0043]
The idler gear includes a first idler gear connected to and disposed on the idler shaft, and a second idler gear and a third idler gear rotatably disposed on the idler shaft, respectively. The second idler gear meshes with the forward driven gear, the third idler gear meshes with the reverse driven gear, a drive pulley is rotatably disposed on the input shaft, and the input shaft and the drive pulley can be disengaged. A CVT clutch is disposed on the input shaft, and a forward clutch is disposed on the idler shaft for releasably connecting the second idler gear and the idler shaft, and the third idler gear is removably connected to the idler shaft. With a reverse clutch on the idler shaft. .
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing an internal configuration of a transmission according to a first embodiment of the present invention.
FIG. 2 is a schematic side view showing a shaft arrangement position of the transmission.
FIG. 3 is a skeleton diagram showing a power transmission path configuration of the transmission according to the first embodiment.
FIG. 4 is a skeleton diagram showing a power transmission path configuration of a transmission according to a second embodiment of the present invention.
FIG. 5 is a skeleton diagram showing a power transmission path configuration of a transmission according to a third embodiment of the present invention.
FIG. 6 is a skeleton diagram showing a power transmission path configuration of a transmission according to a fourth embodiment of the present invention.
FIG. 7 is a skeleton diagram showing a power transmission path configuration of a conventional transmission.
[Explanation of symbols]
1 primary shaft (input shaft)
2,22 secondary shaft (intermediate shaft)
3,23 Counter shaft (output shaft)
4,24 idler shaft
10 Drive pulley
14 V belt
15 Driven pulley
21 CVT clutch
22,122,222 LOW clutch
23, 123, 223 Reverse clutch
31 Input drive gear
32 idler gear
132a, 232a First idler gear
132b, 232b Second idler gear
232c Third idler gear
33,133,233 LOW driven gear
34 Forward drive gear
35,135,235 Forward driven gear
36,136,236 Reverse driven gear
CVT belt type continuously variable transmission
GT stepped rotation transmission mechanism
FG final reduction mechanism

Claims (2)

A continuously variable transmission mechanism and a stepped rotation transmission mechanism for shifting the rotational driving force of the input shaft that is rotationally driven by the drive source and transmitting the transmission to the output shaft,
The continuously variable transmission mechanism is configured to continuously change the speed of rotation of the input shaft and transmit the rotation to the intermediate shaft,
A forward gear train for transmitting the rotation of the input shaft to the intermediate shaft via an idler shaft, and a forward output transmission gear train for transmitting the rotation of the intermediate shaft to the output shaft; And a reverse gear train that transmits the rotation of the input shaft to the output shaft via the idler shaft. The forward gear train is provided on the input shaft, the input drive gear, meshes with the input drive gear and idler gear provided on the idler shaft, and meshes with the idler gear and on the intermediate shaft. It consists of a forward driven gear provided,
The power transmission according to claim 1, wherein the reverse gear train includes the input drive gear, the idler gear, and a reverse driven gear that meshes with the idler gear and is provided on the output shaft. apparatus.

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