JPH0772584B2 - Gearbox - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a speed change device, and more particularly to changing the power input to an input shaft in a state in which all the gears are connected without disengaging or changing gears at the time of speed change. , Transmission to the output shaft, and the reverse drive also being related to the transmission arranged in a simple manner.

[0002]

2. Description of the Related Art In general transmissions, gears are shifted by a selection method according to a predetermined gear ratio, and the gears must be disengaged and replaced during the gear shift. First, very careful operation is required. The existing automatic transmission is also structurally very complicated and requires a large installation space, which is disadvantageous in that the manufacturing cost is high.

As a technique for solving the above-mentioned problems, there is US Pat. No. 5,062,823 issued on November 5, 1991, and in this patent, a separate structure must be taken for the reverse drive. There was an inconvenience.
In addition, as a technique that enables even reverse drive, United States Patent Application No. 07 / 903,137 (1992.
6.23), No. 07 / 921,050 (1992.
7.28), and 07 / 920,892 (199)
2.7.28), the present invention was devised by changing the configuration of the above-mentioned prior application. That is, in the prior application, the output shaft was formed integrally with the carrier, and the output shaft was not provided with the output sun gear.

Therefore, according to the present invention, the output sun gear is provided on the output shaft, and it is possible to quickly change gears in response to changes in load without using a clutch or a complicated mechanism. It is an object of the present invention to provide a transmission in which not only the rotational force can be smoothly transmitted to the output shaft, but also the reverse drive can be smoothly performed and the structure is simple.

[0005]

Therefore, according to the present invention, as in the invention described in claim 1, the input sun gear that receives the power generated by the engine as an input and the input that meshes with the input sun gear. A differential gear, an output differential gear and a reverse differential gear formed integrally with the input differential gear, a transmission differential gear meshed with the input differential gear, and a transmission differential gear Of the medium speed differential gear, a fixed pin and a carrier that support each differential gear, a medium speed differential gear, an output sun gear that is meshed with the inside of the output differential gear and integrally formed with the output shaft, A medium speed sun gear that is meshed with the inside and integrally formed with the medium speed adjustment shaft, and a reverse sun gear that is meshed with the inside of the reverse differential gear and integrally formed with the reverse adjustment shaft are provided. Therefore, a low speed adjustment shaft formed integrally with one carrier is provided It is configured to include a coupling gear set. Then, in order to shift gears at each stage, low-speed braking means for applying a braking force to the low-speed adjustment shaft to bring it into a low-speed drive state, and for applying a braking force to the medium-speed adjustment shaft to bring it into a medium-speed drive state The braking means for medium speed, the interlocking means for making a high-speed drive state by providing a rotational difference between the input shaft and the reverse adjustment shaft, or rotating them integrally, and applying braking force to the reverse adjustment shaft. And a reverse braking means for setting a reverse drive state.

A transmission device according to a sixth aspect of the invention is
In the configuration according to the first aspect of the present invention, the hollow medium speed adjusting shaft is pivotally supported on the input shaft, and the hollow reverse adjusting shaft is pivotally supported on the output shaft. The low-speed braking means may be a one-way clutch, for example, and the interlocking means may be a fluid clutch, a torque converter, or an electric or electronic clutch.

Further, in the above construction, the input differential gear, the output differential gear and the reverse differential gear are integrally formed,
The number of teeth may be different from each other, the number of teeth of the output differential gear may be smaller than the number of teeth of the reverse differential gear, and the number of teeth of the output sun gear may be larger than the number of teeth of the reverse sun gear. The number of teeth of each gear can be set according to the output take-out condition.

According to a seventh aspect of the invention, the transmission includes an input sun gear that receives power generated by the engine as an input, an input differential gear that meshes with the input sun gear, and an input differential. A low speed differential gear meshing with the dynamic gear, an output differential gear and a reverse differential gear integrally formed with the low speed gear, and a fixed pin and a carrier for supporting the input, low speed, output and reverse differential gears. , The output sun gear is formed integrally with the output shaft by being meshed with the output differential gear, the low speed sun gear is provided inside the low speed differential gear, and the reverse sun gear is provided inside. A reverse sun gear is provided for meshing, and the two sun gears and the like are configured to include one composite gear set provided with a low speed and reverse adjustment shaft integrally formed with each of them And apply braking force to the low speed adjustment axis Low-speed braking means for maintaining a forward low-speed drive state, and interlocking means for providing a medium-speed and high-speed drive state by imparting a rotational difference between the input shaft and the low-speed adjusting shaft or rotating the shaft integrally. And a reverse braking means for applying a braking force to the reverse adjustment shaft to bring it into a reverse drive state.

According to a twelfth aspect of the present invention, in the transmission according to the seventh aspect of the invention, the reverse gear and the reverse differential gear are removed, and at the same time, the reverse ring gear meshes with the input differential gear. Is provided. In this case as well, the low speed brake means is
For example, a one-way clutch can be used, and the interlocking means can be a fluid clutch, a torque converter, or an electric or electronic clutch.

Further, in the above structure, a low speed differential gear,
The output differential gear and the reverse differential gear are integrally formed, and the number of teeth can be different from each other.The reverse sun gear has more teeth than the low speed sun gear, and the output sun gear has more teeth. The number of teeth of each reverse gear can be set according to the output take-out condition, such as the number of teeth of the reverse sun gear being smaller than the number of teeth of the reverse differential gear being smaller than the number of teeth of the output differential gear.

[0011]

In the transmission having the above-mentioned structure, when the output shaft is stopped by the load, the output differential gear in which the input power meshes with the output sun gear is opposite to the input direction. However, since the power rotates the medium-speed sun gear and the carrier in the direction opposite to the input direction and the reverse sun gear in the same direction as the input direction, the power does not rotate the output shaft in the neutral state. , The carrier, the reverse sun gear, and the medium speed sun gear will only idle.

In the low speed state, braking force is applied through the low speed brake means installed on the low speed adjusting shaft integrated with the carrier to completely stop the carrier idling in the direction opposite to the input direction, and the input differential is applied. The revolution of the gear and output differential gear is stopped and only rotation is performed. Therefore, the rotation of the output sun gear that meshes with the output differential gear, that is, the rotation of the output shaft, gradually increases in proportion to the braking force, resulting in a low speed state.

Further, in the medium speed state, braking force is applied through the medium speed brake means installed on the medium speed adjusting shaft to completely stop the middle speed sun gear and revolve the middle speed differential gear. Then, the revolution causes the output differential gear and the carrier to revolve, and drives the output sun gear meshing with the output differential gear, that is, the output shaft, at a medium speed. In the high speed state, the input shaft and the reverse adjustment shaft are actuated by applying a torque converter or an interlocking means applying a mechanism such as a normal device such as an electric or electronic clutch between the reverse adjustment shaft and the input shaft. Integrate. As a result, the input power is transmitted to the input differential gear via the output sun gear and also to the reverse differential gear via the interlocking means. Then, the transmitted rotational force merges with the carrier to further increase the rotation of the output shaft.

As a reverse drive method, the reverse sun gear is stopped by applying a braking force through the reverse brake means installed on the reverse adjustment shaft, and the reverse differential gear and the carrier are rotated in the rotational direction of the input shaft. Revolves in the opposite direction and thus the power causes the output shaft to rotate in the opposite direction to the input shaft. Further, when the low-speed braking means has a one-way clutch, the braking direction is restricted to only one direction, so that it can rotate only in the rotation direction opposite to the braking direction.

The interlocking means may be a fluid clutch, and the interlocking operation is performed by applying a mechanism such as a torque converter or an ordinary device such as an electric or electronic clutch. . Further, the input differential gear, the output differential gear, and the reverse differential gear are integrally formed, and the number of teeth is different from each other. It is possible to change the rotational speed difference between the gear and the gears that mesh with each other.

Further, by making the number of teeth of the output differential gear smaller than the number of teeth of the reverse differential gear and making the number of teeth of the output sun gear larger than the number of teeth of the reverse sun gear, each of the above-mentioned driving states can be achieved. It will be surely obtained. Further, in the structure according to the invention described in claim 1, the structure according to the invention according to claim 6, wherein the hollow medium speed adjustment shaft is pivotally supported on the input shaft, and the hollow backward adjustment shaft is pivotally supported on the output shaft. Even in this case, the same operation as the operation according to the first aspect is achieved.

Next, in the transmission according to the seventh aspect, when the output shaft is stopped by the load, the input power rotates the low speed sun gear in the direction opposite to the input direction and inputs the reverse sun gear. Since it rotates in the same direction as the direction, in the neutral state, the low speed and reverse sun gears only idle without rotating the output shaft. In the low speed state, braking force is applied through the low speed braking means installed on the low speed adjustment shaft that is idling in the opposite direction to the input direction to stop the low speed sun gear, and the rotation of the output shaft is proportional to the braking force. To gradually increase the speed to a low speed state.

In order to increase the speed from the medium speed state to the high speed state, that is, to rotate the output shaft to the medium speed or high speed state, a torque converter or an electric motor is provided between the low speed adjustment shaft and the input shaft. The rotation of the low speed adjustment shaft is adjusted by using the interlocking means applying a mechanism such as an ordinary device such as an electronic clutch to further increase the rotation of the output shaft. As a reverse drive method, the reverse sun gear is stopped by applying a braking force through the reverse brake means installed on the reverse adjustment shaft, so that the power rotates the output shaft in the direction opposite to the input shaft. .

In addition to the function of the seventh aspect, the low-speed differential gear, the output differential gear, and the reverse differential gear are integrally formed to have different numbers of teeth. Further, it becomes possible to change the rotational speed difference between the respective differential gears and the respective meshing gears. Also,
Make the number of teeth of the reverse sun gear larger than the number of teeth of the low speed sun gear,
By making the number of teeth of the output sun gear smaller than the number of teeth of the reverse sun gear and the number of teeth of the reverse differential gear smaller than the number of teeth of the output differential gear, it is possible to reliably obtain the above-mentioned drive states. Becomes

In addition, in the structure according to the invention described in claim 7, the reverse adjustment shaft and the reverse differential gear are removed, and a reverse ring gear that meshes with the input differential gear is provided. The same operation as the operation according to the described configuration is achieved. That is, in the transmission described above, the power generated from the engine in a state in which all the gears are connected to each other without releasing or changing the clutch or the gear in this way is used for neutral, low speed and medium speed. It is possible to continuously change the speed at high speed and transmit the speed to the output shaft.

[0021]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The embodiments of the transmission of the present invention will be described in detail below with reference to the accompanying drawings. First, claim 1 of the present invention
-The 1st example concerning Claim 5 is described, referring to Drawing 1-Drawing 7. As shown in FIGS. 1 and 2, a transmission (10) according to a first embodiment of the present invention is provided with an input shaft (12) to which a driving force is input from a drive shaft of an engine. The input shaft (12) has a first portion (12A) and a second portion.
It is divided into a part (12B) and an input sun gear (1
4) is formed integrally with the input shaft (12). On the outer periphery of the first portion (12A) of the input shaft (12), a hollow reverse adjustment shaft (16) having a predetermined length and separated from the input sun gear (14) by a required distance is provided. The reverse sun gear (18) is integrally formed at one end (16A) of the reverse adjustment shaft (16). And the input shaft (12)
Bearings (18B, 18B ') are installed so that the reverse adjustment shaft (16) can rotate independently of each other.

The output shaft (22) having the first end (22A) and the second end (22B) has the first end (2).
2A) has a bore portion (20) formed therein, and can rotate independently of the input shaft (12) by the bearing (20B). The bore portion (20) also surrounds the second portion (12B) of the input shaft. An output sun gear (24) is integrally formed with the first end (22A). Then, the first end portion (26
A) and a medium speed adjusting shaft (26) having a second end (26B)
Is supported, and a medium speed sun gear (28) is integrally installed at one end portion (26A) of the medium speed adjusting shaft (26), and the output shaft (2
2) Bearings (28B, 28B ') are installed so that the medium speed adjusting shaft (26) and the medium speed adjusting shaft (26) can rotate independently of each other.

Next, a hollow low speed adjusting shaft (30) having a predetermined length is rotatably supported on the outer periphery of the reverse adjusting shaft (16) near the reverse sun gear (18), and one end of the low speed adjusting shaft (30) is supported. (3
The disk-shaped carrier (32) is integrally supported by 0A), and the bearing (32B) is inserted and installed so as to be rotatable with respect to the reverse adjustment shaft (16). Further, a disk-shaped carrier (34) of the same form is supported on the outer peripheral portion of the medium speed adjusting shaft (26) near the medium speed sun gear (28), and the medium speed adjusting shaft (2
6) and bearings (34
Insert and install B). Then, each fixing pin (36A, 52A) so that the two carriers (32, 34) can rotate together around the input shaft (12) and the output shaft (22).
A large number of fixing pins (36, 52) consisting of are inserted between two carriers (32, 34) and fixed (see FIG. 1).

The input differential gears (38A) and the output differential gears (42A), which are integrally formed with each other and have different sizes, are provided with recesses (40) at regular intervals between them, and they are integrated with each other. A plurality of composite differential gears (38A, 42A, 46A) are provided with recesses (44) at regular intervals between each input differential gear (38A) and each reverse differential gear (46A). Differential gears (38, 42, 46) are rotatably supported on fixed pins (36) by bearings (48B, 48B '). Input differential gear (3 when supporting
The portion of 8) near the output shaft 22 (hereinafter referred to as the latter half) is the input sun gear (14), the output differential gear (42) is the output sun gear (24), and the reverse differential gear (46) is the reverse gear. When the bushing (50) is inserted in the rear side of the output differential gear (42) so that it can be meshed with the sun gear (18), the composite differential gear (38, 42, 46) can be more reliably prevented from floating. can do.

On the other hand, concave portions (56) having a constant interval are provided between the transmission differential gears (54A) and the medium speed differential gears (58A) which are integrally formed although the sizes are different from each other. A large number of compound differential gears (54, 58), which are composed of the respective compound differential gears (54A, 58A), have bearings (54B,
58B) so that it can be freely rotated.
2) Insert on top. At the time of installation, the transmission differential gear (54) is made to mesh with the front half of the input differential gear (38).
The medium speed differential gear (58) is arranged to be able to mesh with the medium speed sun gear (28), and a bushing (60) is provided on the side of the transmission differential gear (54) close to the input shaft 12 (hereinafter referred to as the first half side). When inserted, the composite differential gear (54, 58) can be more reliably prevented from floating.

Here, in this embodiment, the fixing pin (36
A), a compound differential gear (38A, 42A, 46A) and a bushing (50) are provided as one set each for a total of two sets for the safety of the rotating body. Similarly, a fixed pin (52A) and a compound differential are provided. The gears (54A, 58A) and the bushing (60) are provided as one set each for a total of two sets. However, it goes without saying that such a number is not limited.

Here, the number of teeth of each gear can be arbitrarily changed, but in this embodiment, the number of teeth of the output differential gear (42) is larger than that of the reverse differential gear (46). The number of teeth of the output sun gear (24) is larger than the number of teeth of the reverse sun gear (18). Further, a brake means for applying a braking force from the outside to perform a gear shift for each stage, and a rotation difference between the input shaft (12) and the reverse adjustment shaft (16), or to rotate integrally. Interlocking means is provided.

First, in order to adjust the carrier (32) in a low speed state, a low speed brake means (6) using a one-way clutch for restricting the rotation direction on the outer peripheral portion of the low speed adjustment shaft (30).
2) is installed to adjust the middle speed sun gear (28) in a middle speed state, and a middle speed brake means (64) is installed on the outer periphery of the middle speed adjusting shaft (26), and the input shaft is driven for high speed driving. (12)
And an interlocking means (70) (described later) is installed to integrally rotate the reverse adjustment shaft (16). In the reverse drive state, in order to adjust the reverse drive sun gear (18), a reverse drive braking means (66) is installed on the outer periphery of the reverse drive adjustment shaft (16) integrally formed with the reverse drive sun gear (18).

If the braking means is installed on the outer peripheral portion of each adjusting shaft, the braking force can be applied to each adjusting shaft to adjust the rotation of the adjusting shaft. Of course, the position and structure can be different. Further, the above-mentioned low-speed, medium-speed and reverse braking means can be applied to all braking devices such as electric, electronic, hydraulic / pneumatic pressure and rotation resistance devices by automatic control or manual type, and in this embodiment, simpler By installing a brake braking type lining and compressing this lining, a low speed adjusting shaft (30) at low speed and a medium speed adjusting shaft (2
6), the reverse adjustment shaft (16) during reverse travel is braked.

In order to prevent the backward rotation of the low speed adjusting shaft (30) by eliminating the inconvenience of releasing the braking force again after applying the braking force to the low speed braking means (62) at the time of shifting. A one-way clutch was used, but is not limited to this. Next, input shaft (1
2) and the reverse adjustment shaft (16) are provided with a rotation difference or as a device for rotating integrally,
It is possible to use the interlocking means (70) applying a fluid clutch, a torque converter, an electric clutch, an electronic clutch, or the like. However, a detailed description of such a known device will be omitted here.

The power transmission process and the speed change state according to the first embodiment of the thus constituted shift transmission will be described below by classifying them into neutral, low speed, medium speed, high speed and reverse drive states.
Prior to the description, the transmission of the present invention can be used for any mechanism that shifts and outputs the driving force of an automobile, an industrial machine, or the like, but in the present embodiment, the case of an automobile will be described as an example. To do.

For the sake of convenience of explanation, when viewed from the right side of the drawing, the direction of clockwise rotation is defined as the direction of rotation of the input shaft,
The case where the input shaft rotates in the same rotational direction as the rotational direction will be described by defining it as the ↑ direction in each drawing.
First, the neutral state will be described with reference to Table 1 and FIG.

[0033]

[Table 1]

In the neutral state, the driving force of the engine is the output shaft (2
It is not output to 2) and is in a state of idle rotation as shown in FIG. That is, when a load is applied to the output shaft (22), when the rotational force is input from the drive shaft of the engine, the input shaft (12) is rotated, and the input sun gear (14) formed integrally with this shaft is rotated. ) Rotates in the direction A, and the input differential gear (38) meshed with the input sun gear (14) rotates in the direction B opposite to the rotation direction of the input sun gear (14) with respect to the fixed pin (36). Like Further, an output differential gear (42) formed integrally with the input differential gear (38)
Also, the reverse differential gear (46) and the like all rotate in the same direction B as the direction of the input differential gear (38) with respect to the fixed pin (36).

However, since the output sun gear (24) meshed with the output differential gear (42) is stopped by the load, the output differential gear (42) rotates around the output sun gear (24) at the same time as the rotation. It will rotate, or revolve, and will therefore rotate the carrier (32, 34) in a direction C opposite to the direction of rotation of the input sun gear (14).

At the same time, the reverse differential gear (46) integrally formed with the output differential gear (42) shifts the reverse sun gear (18) meshed with the reverse differential gear (46) in the rotational direction of the input sun gear (14). It rotates in the same direction D as. This is because the influence of the rotation force of the reverse sun gear (46) is greater than the influence of the revolution force that rotates with the carrier (32, 34).

The transmission differential gear (54) meshed with the front half of the input differential gear (38) is fixed to the fixed pin (5).
2), the input sun gear (14) rotates in the same direction E as the rotation direction of the input sun gear (14), and thus, the intermediate speed differential gear (58) integrally formed with the transmission differential gear (54). The meshed middle speed sun gear (28) also rotates about the fixed pin (52) in the same direction E as the rotation direction of the input sun gear (14), and meshes with the middle speed differential gear (58). Enter the medium speed sun gear (28)
It is rotated in the direction F opposite to the rotation direction of 4).

Here, all the differential gears (38, 42, 4
6, 54, 58) rotate at the same time as the carrier (32,
34) It will be in the state to revolve with. In this way, the rotational force through the input shaft (12) is not output because the output shaft (22) is in a stopped state due to the load, and the carrier (32,
34) with reverse sun gear (18) and medium speed sun gear (2)
8) is in a neutral state where only idle rotation is performed.

Second, the low speed state will be described with reference to Table 2 and FIG.

[0040]

[Table 2]

In the low speed state, the rotation of the output shaft (22) gradually increases from the neutral state, and as described above, the low speed adjustment shaft (3) is used to adjust the rotation of the carriers (32, 34).
0) When the braking force P1 is applied through the low speed braking means (62) installed on the outer peripheral portion using a one-way clutch, the carrier (in the neutral state, rotating in the direction C opposite to the input shaft (12) ( The rotation of the output shaft (22) is gradually decreased in proportion to the rotation of the carrier (32, 34). . That is, the braking force P1 reduces the revolutions of the input differential gear (38) and the output differential gear (42), which are rotating and revolving in parallel in proportion to the rotation reduction of the carriers (32, 34). Came to stop,
At this time, I will only rotate.

Therefore, the output sun gear (24) meshed with the output differential gear (42) is rotated in the same direction G as the rotation direction of the input shaft (21) by the rotation force of the output differential gear (42). The output shaft (22) formed integrally with the output sun gear (24) also rotates in the same direction G. Comparing the rotation direction of each gear and the like with the rotation direction in the neutral state in such a low speed state, the input shaft (1
The difference is that the carrier (32, 34) rotating in the direction C opposite to the rotating direction of 2) is in the stopped state and the output sun gear (24) in the stopped state rotates in the direction G. After all, (36, 42, 46, 54, 58) and the like are in a state where they do not revolve and only rotate in the same direction as the direction in the neutral state, and the sun gears (18, 28) etc. also rotate in the neutral state. It will rotate in the same direction.

Third, the medium speed state will be described with reference to Table 3 and FIG.

[0044]

[Table 3]

The medium speed state is a state in which the rotation speed of the output shaft (22) is changed when the rotation speed of the output shaft (22) is increased from the low speed state. The medium speed brake means (6) installed on the medium speed adjusting shaft (26).
When the braking force P2 is applied by 4), the rotation of the medium speed sun gear (28) formed integrally with the medium speed adjusting shaft (26) that was rotating in the direction F opposite to the input shaft (12) is reduced and stopped. Come to do. That is, when the rotation of the medium speed sun gear (28) is reduced and stopped, the medium speed differential gear (58) meshed with the medium speed sun gear (28) becomes the medium speed sun gear (28).
The rotation of the carrier (32, 34) is stopped in the low speed state, and the carrier (32, 34) is rotated in the same direction H as the rotation direction of the input shaft (12).
When the medium speed sun gear (28) stops rotating as compared to when it rotates, its orbital force becomes maximum).

At the same time, the input differential gear (38) and the output differential gear (4) integrated with the input differential gear (38)
Also in 2), the revolution that rotates with the carriers (32, 34) increases proportionally. Therefore, the output differential gear (4
2) The output sun gear (24) meshed with the input shaft (1
It will be rotated more quickly in the same direction as 2), and the rotation of the output shaft (22) integrated with this will also increase.

In this state, the reverse differential gear (46)
Also, due to the effect of the increasing revolution force, the rotation of the reverse sun gear (18) is further increased in the same direction as the input shaft (12). Looking at the rotation direction of each gear, etc., the reverse sun gear (18), the carrier (32, 34), the transmission differential gear (5
4) and the medium speed differential gear (58) all rotate in the same direction (DHE) as the input sun gear (14). Fourth, the high speed state will be described with reference to Table 4 and FIG.

[0048]

[Table 4]

In the high speed state, the speed is changed in order to further accelerate the medium speed state, and the braking force P2 applied to the medium speed adjusting shaft (26) is released and input using the interlocking means (70). The shaft (12) and the reverse adjustment shaft (16) are integrally rotated. In this state, the rotational force through the input shaft (12) is separated and transmitted into two systems. That is, the input differential gear (3) is passed through the input shaft (12) and the input sun gear (14).
8) via one system transmitted to 8), the input shaft (12) and the reverse adjusting shaft (16) are integrally rotated via the interlocking means (70), and the reverse differential gear ( 46) is another system.

The rotational force passing through these two systems merges with the carriers (32, 34) and the output sun gear (24) meshed with the output differential gear (42) and the output shaft (22) are connected to the input shaft (12). ) Will be rotated in the same direction as the rotation.
That is, since the rotations input to the input sun gear (14) and the reverse sun gear (18) are in the same rotation and the same direction, the input differential gear (38) and the reverse differential gear (46) meshed with the rotations. The output differential gear (4
2) and transmission differential gear (54) and medium speed differential gear (5)
8), etc. also does not rotate, but the carrier (32,
34) and the output sun gear (24) and output shaft (22) will rotate in the same direction as the input shaft (12).

In such a state, all the gears and the carrier (32, 34) form one rotating body around the two sun gears (14, 18), and the carrier rotates in the direction I. It will be. Here, in the present embodiment, the interlocking means (70) has been described as having a function of connecting the input shaft (12) and the reverse adjustment shaft (16), but the invention is not limited thereto. For example, one that connects the reverse adjustment shaft (16) and the low speed adjustment shaft (30) or the middle speed adjustment shaft (2
6) and the carrier (34) or the output shaft (22), the same function can be achieved even if it has the function of connecting.

Fifth, the reverse state will be described with reference to Table 5 and FIG.

[0053]

[Table 5]

In the reverse drive state, the output shaft (22) rotates in the direction opposite to the rotation direction of the input sun gear (14), and the reverse drive brake means (66) installed on the reverse drive adjustment shaft (16) at the high speed state described above. ) By the braking force P3, the reverse sun gear (18) idling in the same direction D as the rotation direction of the input shaft (12) at neutral stops, so that the rotation of the output shaft (22) causes the input sun to rotate. The gear 14 will rotate in the direction opposite to the rotation direction of the gear 14.

That is, the reverse sun gear (18) which rotates in the direction D in the neutral state stops its rotation due to the braking force P3 and stops, whereby the reverse sun differential gear (46) meshed with the reverse sun gear (18). ), The revolution force rotating around the reverse sun gear increases proportionally, and the increased revolution force rotates in the direction C.
4) is further rotated at an increased speed (of course, the revolution force is the largest when the reverse sun gear (18) is stopped compared to when it is stopped).

At the same time, the input differential gear (38) and the output differential gear (42) integrated with the reverse differential gear (46).
Also, at the same time as the rotation, the revolution of the input sun gear (14) rotating in the opposite direction to the rotation direction of the input sun gear (14) increases in proportion to the rotation of the carrier (32, 34). Therefore, as the revolution of the output differential gear (42) rotating with the carrier increases, the output sun gear (24) meshed with the output differential gear (42) is input without rotating in the same rotation direction as the rotation direction of the input shaft (12). It will be rotated in the direction J opposite to the direction of rotation of the shaft (12). This is because the influence of the increasing revolution force is relatively larger than the influence of the rotation force of the output differential gear (42). Therefore, the output sun gear (24) is in the direction J
When the output shaft (22) is rotated in the same direction, the output shaft (22) is also rotated in the same rotation direction J, that is, the direction opposite to the rotation direction of the input shaft (12).

In this state, the transmission differential gear (5
4) and the medium speed differential gear (58), the influence of the increasing revolution force becomes relatively larger than the rotation force, so that the rotation of the rotating medium speed sun gear (28) in the F direction is rotated by the input shaft ( 12) In the direction opposite to the rotation direction (compared to the neutral state), the amount is further increased. Here, the number of teeth of each gear can be arbitrarily changed, but in the present embodiment, the number of teeth of the output differential gear (42) is particularly smaller than that of the reverse differential gear (46). This occurs when the number of teeth of the output sun gear (42) is larger than the number of teeth of the reverse sun gear (18). When the number of teeth of each gear is different from that of the embodiment, each differential A relative change occurs between the revolution force and the rotation force of the gear.

Next, a second embodiment according to claim 6 of the present invention will be described with reference to FIG. Incidentally, the above-mentioned first
The same components as those in the embodiment are designated by the same reference numerals and the description thereof will be omitted. The transmission (10 ') of the second embodiment of the present invention is shown in FIG.
In the configuration of the first embodiment, as shown in FIG.
2) An embodiment in which the positions of the reverse adjustment shaft (16) of the outer peripheral portion and the medium speed adjustment shaft (26) of the outer peripheral portion of the output shaft (22) are replaced with each other, and the operating method and function thereof are the same as those of the first embodiment. Since they are the same, detailed description thereof will be omitted, and the alternate configuration will be briefly described.

That is, the reverse adjustment shaft (16) installed coaxially with the shaft center of the input shaft (12), the reverse sun gear (18) integral with the reverse adjustment shaft (16), and the reverse braking means (66) are connected to the output shaft (22). ), And a medium speed adjusting shaft (26) installed coaxially with the shaft center of the output shaft (22) in the first embodiment, and a medium speed sun gear (28) and a medium speed brake integrated with this. The means (64) is arranged on the input shaft (12). Therefore, the reverse differential gear (46) meshing with the reverse sun gear (18) is integrally formed with the output differential gear (42) on the rear side of the output differential gear (42), and instead of the reverse differential gear (42). A bushing (50 ') was installed at the position of the gear (46). The transmission differential gear (5) of the first embodiment is used as the above-mentioned middle-speed differential gear (58) meshed with the middle-speed sun gear (28).
The intermediate speed differential gear (58 ') is integrally formed on the first half side of 4), and instead, the bushing (60') is arranged at the position where the intermediate speed differential gear (58) and the recess (56) are installed. I set it up.

That is, as shown in the second embodiment, the transmission according to the present invention can be used by simply changing the structure as needed. here,
Even if the installation location is changed, the operating method and the rotation direction in the medium speed state and the reverse state are the same as those described above, and the operation position is merely changed. In addition, the high speed interlocking means (70) does not connect the input shaft (12) and the reverse adjustment shaft (16), but a middle speed adjustment shaft (26) coaxially installed with the input shaft (12). The only difference is that they are connected so as to rotate.

Next, a third embodiment according to claims 7 to 11 of the present invention will be described with reference to FIGS. 9 to 14. The third embodiment also has an output sun gear on the output shaft as in the first embodiment. As shown in FIGS. 9 and 10, the transmission (100) of the third embodiment of the present invention has an input shaft (11) to which a driving force is input from a drive shaft of an engine.
2) is installed, and the input shaft (112) is divided into a first part (112A) and a second part (112B), while the input sun gear (114) is integrated with the input shaft (112). Let it form. The first part (112) of the input shaft (112)
A) has a first end (112A) and a second end (112A) that are separated from the input sun gear (114) by a required distance.
B) a predetermined length of hollow low speed adjusting shaft (120)
Is supported by one end of the low speed adjustment shaft (120) (120
A low speed sun gear (122) is integrally formed in A). The bearing (12) and the low speed adjusting shaft (120) are rotated so that they can rotate independently of each other.
4B, 124B ') are installed. Low speed adjustment shaft (120)
A hollow reverse adjustment shaft (130) having a predetermined length is rotatably supported on the outer periphery of the reverse adjustment shaft (130), and one end (130A) of the reverse adjustment shaft (130) is supported.
A reverse sun gear (132) is integrally formed therewith. The bearings (134B, 134B ') are installed so that the low speed adjustment shaft (120) and the reverse adjustment shaft (130) can rotate independently of each other.

On the other hand, the output shaft (138) having the first end (138A) and the second end (138B) has the first end (1).
38A) has a bore portion (136) formed therein and can rotate independently of the input shaft (112) by a bearing (136B). The bore portion (136) also surrounds the second portion (112B) of the input shaft. An output sun gear (140) is provided at the first end (138A) of the output shaft.

Next, a disk-shaped carrier (142) is supported on the outer periphery of the reverse adjustment shaft (130) near the reverse sun gear (132), and a bearing (rotatable with the reverse adjustment shaft (130) so as to be rotatable with respect to each other. 142B) is inserted and installed. Further, a disk-shaped carrier (144) having the same shape is supported on the outer peripheral portion of the output shaft (138), and a bearing (144B) is inserted and installed so as to be rotatable with respect to the output shaft (138). Then, the input shaft (112) and the output shaft (138)
Each fixing pin (146A, 148A) so that the two carriers (142, 144) can rotate together around
A large number of fixing pins (146, 148) are inserted between the two carriers (142, 144) and fixed (see FIG. 9).

A large number of input differential gears (150) composed of respective input differential gears (150A) are rotatably supported by bearings (150B, 150B ') on the fixed pin (146). The rear half of the input differential gear (150) is installed so as to mesh with the input sun gear (114). At this time, input differential gear (15
0) Insert the bushing (152) on both fixed pins (146), ie on the front side of the input differential gear (150),
By inserting the other bushing (152 ') on the rear side, it is possible to more reliably prevent the floating of the input differential gear (150).

On the other hand, the low speed operation gears (154A) and the output differential gears (15) which are integrally formed with each other and have different sizes.
8A), the recesses (156) are formed at regular intervals, and the reverse differential gears (160A) are integrally formed on the front side of the low speed differential gears (154A). A large number of composite differential gears (154, 158, 160) composed of such composite differential gears (154A, 158A, 160A) are rotatably supported on the fixed pin (148) by bearings (158B, 160B). To be done. In addition, at the time of support,
The reverse differential gear (160) is near the carrier (142),
The output differential gear (158) is near the carrier (144),
A low speed differential gear (154) is supported in mesh with the low speed sun gear (122) and the front half of the input differential gear (150).

Here, in this embodiment, the fixing pin (146
A), input differential gear (150A) and bushing (15)
2, 152 ') are provided as one set for the stability of the rotating body, and a total of two sets are provided. Similarly, a fixed pin (148A), a low speed differential gear (154A), an output differential gear (158A) and a reverse differential are provided. There are two sets of gears (160A), one set for each. However, it goes without saying that such a number is not limited.

The inside of the rear half of each input differential gear (150A) is meshed with the input sun gear (114), and the front half thereof is meshed with the rear half of each low speed differential gear (154A). Further, the inside of the front half of each low speed differential gear (154A) is meshed with the low speed sun gear (122), each output differential gear (158A) is meshed with the output sun gear (140), and each reverse differential gear ( 160A) meshes with the reverse sun gear (132).

Here, the number of teeth of each gear can be arbitrarily changed, but in the present embodiment, the low speed sun gear (122) is used.
The number of teeth of the reverse sun gear (132) is greater than the number of teeth of the output sun gear (140).
The number of teeth of the reverse differential gear (160) is smaller than the number of teeth of the output differential gear (158).

Further, there are provided braking means for applying a braking force from the outside in order to shift gears at each stage, and interlocking means for imparting a rotational difference between the input shaft and the low speed adjusting shaft or for integrally rotating them. Has been. First, in order to adjust the low speed sun gear (122) in the forward low speed state, a low speed braking means (162) using a one-way clutch for restricting the rotation direction is installed on the outer peripheral portion of the low speed adjustment shaft (120), and the medium speed and Because of the high speed, the interlocking means (170) (described later) is installed. In order to adjust the rotation of the reverse sun gear (132) in the reverse drive state, the reverse drive braking means (164) is installed on the outer periphery of the reverse drive adjustment shaft (130) integrally formed with the reverse drive sun gear (132).

With such a structure that the braking means is installed on the outer peripheral portion of the adjusting shaft, as long as it is possible to apply the braking force to the adjusting shaft to adjust the rotation of the adjusting shaft, the installation position and structure Of course, it can be different.
Then, after applying the braking force to the low speed braking means (162) at the time of fluctuation, a one-way clutch for preventing the inconvenience of releasing the braking force again and the reverse rotation of the low speed adjusting shaft (120), that is, A general device capable of converting the reciprocating rotary motion into a constant direction rotary motion has been used, but is not limited thereto.

Next, the input shaft (11
2) and the low speed adjustment shaft (120) are provided with a rotation difference, or as a device for rotating integrally,
It is possible to use the interlocking means (170) applying a fluid clutch, a torque converter, an electric clutch, an electronic clutch, or the like. However, a detailed description of such a known device will be omitted here.

The power transmission process and the speed change state according to the third embodiment of the speed change device of the present invention constructed as above will be described below by classifying them into neutral, forward low speed, high speed and reverse states.
In the third embodiment as well, for the sake of convenience of description, the clockwise rotation direction is the rotation direction of the input shaft when viewed from the right side of the drawing, and the rotation direction is the same as the rotation direction of the input shaft. In each drawing, the definition will be made in the ↑ direction.

First, the neutral state will be described with reference to Table 6 and FIG.

[0074]

[Table 6]

In the neutral state, the driving force of the engine is the output shaft (13
It is not output to 8) and is in a state of idle rotation as shown in FIG. That is, when a rotational force is input from the drive shaft of the engine while the output shaft (138) is under load, the input shaft (112) is rotated and the input sun gear (114) integrally formed with this shaft is By rotating in the same direction A'and rotating the input sun gear (114),
The input differential gear (150) meshed therewith is rotated with respect to the fixed pin (146) in a direction B'opposite the direction of rotation of the input sun gear (114). Also, a low speed differential gear (154) meshed with the input differential gear (150) and an output differential gear (158) integrally formed with the low speed differential gear.
And the reverse differential gear (160) is in the same direction C ′ as the rotation direction of the input sun gear (114) with respect to the fixed pin (148).
To be rotated. By the way, since the output sun gear (140) meshed with the output differential gear (158) is stopped by the load, the output differential gear (158) rotates around the output sun gear (140) at the same time as the rotation, that is, As a result, the carrier (142, 144) is rotated in the same direction E ′ as the rotation direction of the input shaft (112).

At the same time, the low speed differential gear (154) and the reverse differential gear (160) integrally formed with the output differential gear (158) also revolve, but first, the reverse differential gear ( 160), the reverse differential gear (160) has a reverse sun gear (13) meshed therewith.
2) tries to rotate the input shaft (112) in a direction opposite to that of the input shaft (112), but since the revolution force rotating with the carrier (142, 144) is larger than the rotation force of the reverse differential gear (160), The sun gear (132) is connected to the input shaft (11
It rotates in the same direction F'as in 2). Next, the low speed differential gear (154) will rotate the low speed sun gear (122) meshed therewith in the direction D'opposite to the direction of rotation of the input shaft (112), even though the carrier The low-speed differential gear (154) revolves with (142, 144), but the low-speed sun gear (122) rotates in the direction D'because the rotation force of the low-speed differential gear (154) is larger than the revolution force. The relative magnitude of the force and the rotation force varies depending on the number of teeth of each gear that is meshed.

As described above, the rotational force through the input shaft (112) is not output because the output shaft (138) is in a stopped state due to the load, so that the low speed sun gear (122), the reverse sun gear (132) and the carrier (142) are not output. , 144) in a neutral state in which only idle rotation is performed. Secondly, the forward low speed state will be described with reference to Table 7 and FIG.

[0078]

[Table 7]

In the forward low speed state, the output shaft (13
8) In the state where the rotation is gradually increased, through the low speed braking means (162) installed using a one-way clutch that restricts the rotation direction on the outer periphery of the low speed adjustment shaft (120) in the neutral state. When the braking force P1 ′ is gradually applied, the rotation of the low-speed sun gear (122) that was rotating in the direction D ′ opposite to the input shaft (112) is reduced and stopped,
Therefore, rotation of the output shaft (138) results in rotation of the low speed sun gear (12).
As the rotational force of 2) is reduced, it gradually increases in proportion. That is, the braking force P1 ′ causes the low-speed differential gear (1
54) causes the so-called revolution around the low speed sun gear (122) to increase proportionally, thus causing the carriers (142, 144) to rotate faster in the direction E '. At the same time, an output differential gear (158) and a reverse differential gear (160) integrated with the low speed differential gear (154).
Also, the revolution that rotates with the carriers (142, 144) simultaneously with the rotation increases proportionally (of course, the revolution force becomes the largest when the low-speed sun gear (122) stops rotating as compared with the reduction). . Therefore, as the revolution of the output differential gear (158) that rotates with the carrier increases, the output sun gear (140) meshed with the output differential gear (158) does not rotate in the direction opposite to the rotation direction of the input shaft (112), The rotation is increased in the same direction G'as the input shaft (112). This is because the influence of the revolution force of the increasing output differential gear (158) becomes relatively larger than the influence of the rotation force. Therefore, by increasing the rotation of the output sun gear (140) in direction G ',
The rotation of the output shaft (138) integrated with this also gradually increases. In this state, the reverse differential gear (16
In the case of 0), the influence of the increasing revolution force becomes relatively larger than the rotation force, so that the rotation of the reverse sun gear (132) is further increased in the same direction F ′ as the input shaft.

When it is desired to further increase the rotation of the output shaft (138) as compared with the forward low speed state, the input shaft (112) and the low speed adjusting shaft (120) may be rotated differently or integrally. Known device to rotate to, ie,
The low speed adjusting shaft (120) in a stopped state is rotated in the same direction as the input shaft by using a torque converter or an interlocking device (170) that applies an electric or electronic clutch or the like. In such a state, the rotation of the output shaft (138) is controlled by the low speed adjustment shaft (12
0) increases in proportion to the speed of rotation in the direction of the input shaft (112).

That is, when the low-speed sun gear (122) rotates in the input shaft direction, the low-speed sun gear (122) rotates with the carriers (142, 144) of the input, low-speed, output, and reverse differential gears (150, 154, 158, 160). The revolution force will increase gradually. Thirdly, the high speed state will be described with reference to Table 8 and FIG.

[0082]

[Table 8]

In the high speed state, the speed is changed for further acceleration, and the operating interlocking means (170) is used to integrally rotate the input shaft (112) and the low speed adjusting shaft (120). In this state, the rotational force through the input shaft (112) is separated into two systems and transmitted. First, the input shaft (112)
And a first system that is transmitted through the input sun gear (114) to the input differential gear (150) by rotating the input sun gear (114) and the input shaft (1
12) is a second system in which the low-speed adjustment shaft (120) and the low-speed adjustment shaft (120) are integrally rotated, and at the same time, the low-speed sun gear (122) is rotated in the direction H'and transmitted to the low-speed differential gear (154).

The rotational force passing through these two systems merges with the carriers (142, 144) to rotate the output shaft (138) in the same direction as the rotation of the input shaft (112). That is, the input sun gear (114) and the low speed sun gear (1
Since the rotations input to 22) are the same rotation and the same direction, the input differential gear (150) and the low speed differential gear (154) do not rotate, and the output difference integrated with the low speed differential gear (154). The dynamic gear (158) and the reverse differential gear (16
0) is also the carrier (142,
144) and the output sun gear (140) and the output shaft (13
8) will rotate in the same direction as the input shaft (112). In such a state, all gears and carriers (1
42, 144) are in a state in which the two sun gears (114, 122) as a whole form a single rotating body and rotate in the direction I ′.

Here, in this embodiment, the interlocking means (17
0) has been described as having a function of connecting the input shaft (112) and the low speed adjustment shaft (120), but is not limited to this. For example, even if it has a function of connecting the input shaft 112 and the reverse adjustment shaft 130, the same function can be performed. Fourth, the reverse drive state will be described with reference to Table 9 and FIG.

[0086]

[Table 9]

When the output shaft (138) rotates in the direction opposite to the rotation direction of the input sun gear (114) in the reverse drive state, the reverse brake means installed on the reverse drive adjustment shaft (130) in the high speed state described above. By (164), the braking force P2 '
The reverse sun gear (132) that is idling in the same direction F ′ as the rotation direction of the input shaft (112) stops, and the output shaft (138) is opposite to the rotation of the input sun gear (114). It will rotate in the direction.

That is, the reverse sun gear (132) which rotates in the direction F'in the neutral state is meshed with the reverse sun gear (132) by the braking force P2 ', the rotation thereof gradually decreasing and stopping. Reverse differential gear (160)
The revolution force rotating around the reverse differential gear decreases proportionally, and at the same time, the output differential gear (158) and the low speed differential gear (154) integrated with the reverse differential gear (160).
Also, the revolution that rotates with the carriers (142, 144) is proportionally reduced. At this time, as the revolution force of the output differential carrier (158) is reduced, the influence of the rotation force is relatively increased, and the output sun gear (140) and the output shaft (138) are moved in the direction J ′, that is, the input direction. It will rotate in the opposite direction of the axis (112). In this state, the revolution force of the low speed differential gear (154) is also reduced, so that the influence of the rotation force thereof becomes relatively large, and the low speed sun gear (122) moves in the opposite direction to the input shaft (112). The rotation is increased to D '.

Here, the number of teeth of each gear can be arbitrarily changed, but in this embodiment, in particular, the low speed sun gear (1
The number of teeth of the reverse sun gear (132) is greater than the number of teeth of the reverse sun gear (132), and the number of teeth of the reverse sun gear (132) is larger than that of the output sun gear (1).
40) and the number of teeth of the reverse differential gear (160) is smaller than that of the output differential gear (158), and the number of teeth of each gear is different from that of the embodiment. In the case of, the relative change occurs between the revolution force and the rotation force of each differential gear.

On the other hand, if the number of teeth of the gear or the like used in the present invention is appropriately adjusted depending on the purpose, the required number of rotations of the output shaft can be obtained. For reference, Table 10 shows the number of teeth of each gear in the first embodiment, and Table 11 shows the rotation speed of the output shaft (for one rotation of the input shaft). Similarly, Table 12 exemplifies the number of teeth of each gear in the third embodiment, and Table 13 shows the number of rotations of the output shaft (for one rotation of the input shaft).

[0091]

[Table 10]

[0092]

[Table 11]

[0093]

[Table 12]

[0094]

[Table 13]

The transmission of the present invention is not limited to the above-described first to third embodiments, and the driving force is output in all vehicles and industrial machines based on the spirit of the present invention. It is obvious that various modifications and changes can be made within the scope of the present invention as well as being applicable to a device that shifts and outputs a shaft. For example, in the first embodiment, the number of teeth of the reverse differential gear (46) is made larger than the number of teeth of the output differential gear (42), and the number of teeth of the reverse sun gear (18) meshed with this. If more teeth than the output sun gear (24) are formed and meshed,
The function can be changed so that the output shaft rotates at the lowest speed in the forward drive state opposite to the reverse drive state described above.

As the interlocking means (70), the one for connecting and rotating the input shaft and the reverse adjusting shaft is installed, but as another embodiment, the reverse adjusting shaft (16) and the low speed adjusting shaft ( 30) or by connecting the medium speed adjusting shaft (2
Even if means for connecting 6) and the carrier (34) or the output shaft (22) to rotate is provided, the same action will be achieved.

Further, in the third embodiment, the number of teeth of the reverse differential gear (160) is formed larger than the number of teeth of the output differential gear (158), and the reverse differential gear (13) meshed with this is formed.
If the number of teeth of 2) is made smaller than the number of teeth of the output sun gear (140) and meshed, the function is such that the output shaft rotates at the lowest speed in the forward state opposite to the reverse state described above. It is possible to change.

Further, as the interlocking means (170), the one for connecting and rotating the input shaft (112) and the low speed adjusting shaft (120) is installed, but as another embodiment, the input shaft and the reverse adjustment are arranged. Even if the shaft (130) is connected and rotated, the same function is performed. A fourth embodiment according to the twelfth aspect of the present invention is shown in FIG.

In other words, in the third embodiment, the reverse adjustment shaft (130), the reverse sun gear (132), and the reverse differential gear (160) were used as the reverse method, but instead of using these, the reverse drive was used instead. A ring gear (230) may be provided. That is, when the reverse ring gear (230) is meshed with the outside of the input differential gear (150) and the braking force is applied by using the reverse brake means (264), the same function is performed.

Further, as the braking means in the embodiment of the present invention, a simple pressurizing type brake lining braking system is used to apply the braking force. Various configurations such as locations,
Of course, it is possible to change the method. Also, as the device, various circuit configurations for automatic control of electricity, electronics, oil, pneumatic pressure, etc. are possible, and interlocking means for medium and high speeds have various configurations, implementation methods, installation locations, etc. Of course, the torque converter, electricity,
It is also possible to use a format that applies an electronic or fluid clutch.

[0101]

As described above, according to the structure of the transmission of the first aspect of the present invention, when the power of the engine is shifted and output to the output shaft through the input shaft, the clutch for cutting off the power is provided. It is not necessary to install a device, and the speed ratio can be adjusted smoothly by adjusting the gear ratio without disengagement and replacement of gears, and in particular, there is an effect that the reverse drive can be smoothly performed. Further, the present invention has a simple structure and a small number of parts, and thus the production cost can be reduced. In addition, it can be installed in a narrow space, and has many advantages such as no impact when operating the transmission.

That is, since the structure is simple, the gear shifting operation is very simple, the installation space and the production cost can be minimized, and the rotation transmission can be made very satisfactory. According to the invention as set forth in claim 2, in addition to the effect of the invention as set forth in claim 1, it is not necessary to release the braking force when the vehicle moves backward after applying the braking force at the time of gear shifting.
It is possible to shift gears more easily and smoothly.

According to the invention of claim 3, claim 1
In addition to the effects of the invention described in (1), it is possible to apply a known device, and it is possible to easily expand the application range of the device. According to the fourth and fifth aspects of the invention, in addition to the effect of the first aspect of the invention, the number of teeth is made different to set the difference in rotational speed transmitted to the output shaft. The width can be increased.

According to the invention of claim 6, claim 1
In addition to the effects of the invention described in (1), the configuration can be easily changed in this way, if necessary. Claim 7
According to the invention described in (1), in addition to the effect of the invention described in (1), it is possible to further simplify. According to the invention described in claim 8, in addition to the effect of the invention described in claim 7, it is not necessary to release the braking force when the vehicle moves backward after applying the braking force at the time of gear shifting. It is possible to shift gears more easily and smoothly.

According to the invention of claim 9, claim 7
In addition to the effects of the invention described in (1), it is possible to apply a known device, and it is possible to easily expand the application range of the device. According to the tenth and eleventh aspects of the invention, in addition to the effect of the seventh aspect of the invention, the number of teeth is made different to set the rotational speed difference transmitted to the output shaft. The width can be increased.

According to the twelfth aspect of the invention, in addition to the effect of the first aspect of the invention, the structure can be further simplified. According to the invention of claim 13,
In addition to the effect of the invention as set forth in claim 12, it is possible to apply a known device, and it is possible to easily expand the application range of the device.

[Brief description of drawings]

FIG. 1 is a partially cutaway perspective view showing a first embodiment of a transmission according to the present invention.

FIG. 2 is an assembled sectional view of the first embodiment.

FIG. 3 is a cross-sectional view showing a state in which the transmission according to the first embodiment is idly rotated in a neutral state.

FIG. 4 is a sectional view showing a state in which an input is transmitted to the output shaft at a low speed by the transmission according to the first embodiment.

FIG. 5 is a cross-sectional view showing a state in which an input is transmitted to the output shaft at a medium speed by the transmission according to the first embodiment.

FIG. 6 is a sectional view showing a state in which an input is transmitted at high speed to the output shaft by the transmission according to the first embodiment.

FIG. 7 is a cross-sectional view showing a reverse drive state in which the output shaft rotates in a direction opposite to the input shaft by the transmission according to the first embodiment.

FIG. 8 is an assembled sectional view showing a second embodiment of the transmission according to the present invention.

FIG. 9 is a partially cutaway perspective view showing a third embodiment of the transmission according to the present invention.

FIG. 10 is an assembled sectional view of the third embodiment.

FIG. 11 is a cross-sectional view showing a transmission according to the third embodiment of the same in a neutral state.

FIG. 12 is a cross-sectional view showing a transmission according to the third embodiment, which is in a progressively low speed state.

FIG. 13 is a cross-sectional view showing the transmission according to the third embodiment of the above, in a high speed state.

FIG. 14 is a cross-sectional view showing a transmission according to the third embodiment of the above, in a reverse drive state.

FIG. 15 is an assembled sectional view showing a fourth embodiment of the transmission according to the present invention.

[Explanation of symbols]

 10, 10'110 transmission 12, 112 input shaft 12A, 112A first part 12B, 112B second part 14, 114 input sun gear 16, 130 reverse adjustment shaft 18, 132 reverse sun gear 20, 136 bore part 22, 138 Output shaft 24,140 Output sun gear 26 Medium speed adjustment shaft 28 Medium speed sun gear 30,120 Low speed adjustment shaft 32,142 Carrier 34,144 Carrier 36,52,146,148 Fixed pin 38,150 Input differential gear 42, 158 Output differential gear 46, 160 Reverse differential gear 54 Transmission differential gear 58, 58 'Medium speed differential gear 62, 162 Low speed brake means 64 Medium speed brake means 66, 164, 264 Reverse brake means 70, 170 Movement Means 122 Low Speed Sun Gear 154 Low Speed Differential Gear 230 Reverse Ring Gear

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor, Gao Yanagi, 174-35, 2-dong, Cheongcheon, Buk-gu, Incheon, Republic of Korea

Claims (13)

[Claims] 1. A first part (12A) and a second part (12).
B) and has an input shaft (1
2) and an input sun gear (14) integrally formed with the input shaft (12) between the first portion (12A) and the second portion (12B).
And a reverse sun gear (18) is integrally formed at one end (16A), and can be independently rotated with respect to the input shaft (12) while being separated from the input sun gear (14) by a required distance. As can be seen, it has a hollow backward adjusting shaft (16) pivotally supported on the first part (12A), a first end (22A) and a second end (22B), and a first end ( 22A) is integrally formed with an output sun gear (24), and a bore portion (20) is formed at a first end portion (22A) so as to coaxially surround the second portion (12B) of the input shaft. At the same time, an output shaft (22) that rotates independently with respect to the input shaft and a medium speed sun gear (28) are integrally formed at one end (26A), A hollow medium speed adjusting shaft (2) that is rotatably supported by the output shaft (22).
6), and a hollow low speed adjustment shaft (30) rotatably supported by the reverse adjustment shaft (16) so that it can rotate independently of the reverse adjustment shaft (16), and a low speed adjustment at one end (30A). A carrier (32) integrally formed with the shaft (30) and a carrier (34) supported by the medium speed adjusting shaft (26) so as to be independently rotatable with respect to the medium speed adjusting shaft (26).
In order to rotate both carriers (32, 34) at the same time, a plurality of fixing pins (36, 52) inserted and fixed between the carriers (32, 34) and the fixing pins (36) are rotatably provided. And a plurality of input differential gears (38) that mesh with the input sun gear (14) inside a portion thereof, and integrally formed with the input differential gears (38).
6) A plurality of output differential gears (42) rotatably provided with respect to which the output sun gear (24) meshes.
And an input differential gear (38) integrally formed with a fixing pin (3
6) A plurality of reverse differential gears (46) rotatably provided with respect to which the reverse sun gears (18) mesh with.
A plurality of transmission differential gears (54) rotatably provided on the fixed pin (52) and meshing with other portions of the input differential gear (38) other than the above-mentioned portion; Is formed integrally with the fixing pin (5
2) A plurality of medium-speed differential gears (58) rotatably provided to mesh with the medium-speed sun gear (28) inside thereof.
A low speed braking means (62) for applying a braking force to the low speed adjusting shaft (30) for low speed driving, and a medium speed braking means (64) for applying a braking force to the medium speed adjusting shaft (26) for medium speed driving. ), And an interlocking means (70) for imparting a rotational difference between the input shaft (12) and the reverse adjustment shaft (16) for high speed driving or rotating integrally, and a reverse adjustment shaft (16) for reverse driving. A reverse transmission braking means (66) for applying a braking force to the transmission, and a transmission. 2. The transmission according to claim 1, wherein the low-speed braking means (62) has a one-way clutch. 3. The transmission according to claim 1, wherein the interlocking means (70) is a fluid clutch, a torque converter, an electric or electronic clutch. 4. The input differential gear (38), the output differential gear (42) and the reverse differential gear (46) are integrally formed,
The transmission according to claim 1, wherein the number of teeth is different from each other. 5. The output differential gear (42) has a smaller number of teeth than the reverse differential gear (46), and the output sun gear (2) has a smaller number of teeth.
Transmission according to claim 1, characterized in that the number of teeth of 4) is greater than the number of teeth of the reverse sun gear (18). 6. A first part (12A) and a second part (12).
B) and has an input shaft (1
2) and an input sun gear (14) integrally formed with the input shaft (12) between the first portion (12A) and the second portion (12B).
And an intermediate speed sun gear (28) integrally formed at one end (26A), and independently rotating with respect to the input shaft (12) at a required distance from the input sun gear (14). A hollow medium speed adjusting shaft (26) pivotally supported by the first portion (12A), a first end portion (22A) and a second end portion (22B). An output sun gear (24) is integrally formed on the portion (22A), and a bore portion (20) is formed on the first end portion (22A) so as to coaxially surround the second portion (12B) of the input shaft. An output shaft (22) that is formed and rotates independently of the input shaft, and a reverse sun gear (18) are integrally formed at one end (16A) and are independent of the output shaft (22). A hollow reverse adjustment shaft (1
6), a hollow low speed adjustment shaft (30) rotatably supported by the medium speed adjustment shaft (26) so that it can rotate independently of the medium speed adjustment shaft (26), and one end (30A). A carrier (32) integrally formed with the low speed adjusting shaft (30) and a carrier (34) supported by the reverse adjusting shaft (16) so as to be independently rotatable with respect to the reverse adjusting shaft (16).
In order to rotate both carriers (32, 34) at the same time, a plurality of fixing pins (36, 52) inserted and fixed between the carriers (32, 34) and the fixing pins (36) are rotatably provided. And a plurality of input differential gears (38) that mesh with the input sun gear (14) inside a portion thereof, and integrally formed with the input differential gears (38).
6) A plurality of output differential gears (42) rotatably provided with respect to which the output sun gear (24) meshes.
And a fixed pin (3
0), which is rotatably provided and has a plurality of reverse differential gears (46) meshing with the reverse sun gear (18) inside thereof.
And a fixed pin (52) rotatably provided, a part of which meshes with a part other than the part of the input differential gear (38), and the inside of the part other than the part is a medium speed sun gear. (28) a number of medium speed differential gears (58 '), low speed braking means (62) for applying a braking force to the low speed adjustment shaft (30) for low speed driving, and medium speed for medium speed driving. There is a rotational difference between the medium speed brake means (64) for applying a braking force to the adjusting shaft (26) and the input shaft (12) and the medium speed adjusting shaft (26) for high speed driving, or they rotate integrally. A transmission comprising: an interlocking means (70) for performing a reverse operation, and a reverse braking means (66) for applying a braking force to a reverse adjustment shaft (16) for reverse driving. 7. A first part (112A) and a second part (11).
2B), and an input sun gear that is formed integrally with the input shaft (112) between the first portion (112A) and the second portion (112B) and that receives an input driving force. (114) and a low speed sun gear (122) are integrally formed at one end (120A), and are separated from the input sun gear (114) by a required distance so that they can rotate independently of the input shaft (112). In addition, a hollow low speed adjusting shaft (120) pivotally supported by the first portion (112A) and a reverse sun gear (132) are integrally formed at one end (130A) of the low speed adjusting shaft (120). A hollow reverse adjusting shaft (130) rotatably supported by a low speed adjusting shaft (120) so as to be independently rotatable, a first end (138A) and a second end (138B). Connect the output sun gear (140) to the end (136A). The first end (138A) has a bore (136) so as to coaxially surround the second portion (112B) of the input shaft, and is formed independently of the input shaft. The reverse adjustment shaft (16) near the reverse sun gear (132) so that it can rotate independently of the rotating output shaft (138) and the reverse adjustment shaft (130).
And a carrier (142) supported on the output shaft (138) so that they can rotate independently of each other.
In order to rotate the carrier (144) supported by the output shaft (138) and both the carriers (142, 144) at the same time, a plurality of fixing pins (146, 148) inserted and fixed between the carriers (142, 144). ) And a plurality of input differential gears (150) rotatably mounted on the fixed pin (146) and meshing with the input sun gear (114) inside a part of the fixed pin (146) and rotatably mounted on the fixed pin (148). A plurality of low speed differential gears (1) are provided, one part of which meshes with other parts of the input differential gear (150) other than the one part, and the other part of the input differential gear (150) meshes with the low speed sun gear (122). 154)
And a plurality of output differential gears (1) that are integrally formed with the low speed differential gear (154) and are rotatably provided with respect to the fixed pin (148) and that mesh with the output sun gear (140) inside.
58) and a low speed differential gear (154), which are integrally formed with each other and are rotatably provided with respect to a fixed pin (148), and a large number of reverse differential gears () which mesh with the reverse sun gear (132) inside thereof. 160), a low speed braking means (162) for applying a braking force to the low speed adjusting shaft (120) for forward low speed driving, and between the input shaft (112) and the low speed adjusting shaft (120) for medium speed and high speed driving. An interlocking means (170) for imparting a rotational difference or rotating integrally, and a reverse braking means (164) for applying a braking force to the reverse adjusting shaft (130) for reverse driving. Characteristic transmission. 8. The low speed brake (162) comprises a one-way clutch.
The transmission according to. 9. The interlocking means (170) is a fluid clutch,
The transmission according to claim 7, wherein a torque converter, an electric clutch, and an electronic clutch are applied. 10. The low speed differential gear (154), the output differential gear (158) and the reverse differential gear (160) are integrally formed and have different numbers of teeth.
The transmission according to. 11. The reverse sun gear (132) has more teeth than the low speed sun gear (122), and the output sun gear (140) has less teeth than the reverse sun gear (132). The number of teeth of the reverse differential gear (160) is less than the number of teeth of the output differential gear (158).
The transmission according to. 12. A first part (112A) and a second part (1).
12B) and an input sun (112) that receives an input driving force, and an input sun integrally formed with the input shaft (112) between the first portion (112A) and the second portion (112B). The gear (114) and the low speed sun gear (122) are integrally formed at one end (120A), and are separated from the input sun gear (114) by a required distance independently of the input shaft (112). A hollow low speed adjustment shaft (120) pivotally supported on the first portion (112A) for rotation, a first end (138A) and a second end (138B), An output sun gear (140) is integrally formed on the end portion (136A), and a bore portion (136) is formed on the first end portion (138A) so as to coaxially surround the second portion (112B) of the input shaft. The output that forms the (138), a carrier (142) supported by the low speed adjustment shaft (120) near the low speed sun gear (122) so as to rotate independently of the low speed adjustment shaft (120), and an output shaft (138). The carrier (144) supported by the output shaft (138) so as to be independently rotatable with respect to each other and the carrier (142, 144) are rotated and inserted simultaneously between the carriers (142, 144). A plurality of fixed pins (146, 148), and a plurality of input differential gears (150) rotatably provided on the fixed pin (146) and meshing with an input sun gear (114) inside a part of the fixed pin (146), A pin (148) is rotatably provided, a part of which meshes with a part of the input differential gear (150) other than the part, and the inside of the part other than the part is a low speed sun gear. A number of low speed differential gears (15
4) and a plurality of output differential gears (1) that are integrally formed with the low speed differential gear (154) and are rotatably provided with respect to the fixed pin (148) and that mesh with the output sun gear (140) inside thereof.
58), a reverse ring gear (230) meshing with the input differential gear (150), a low speed brake means (162) for applying a braking force to the low speed adjusting shaft (120) for forward low speed drive, a medium speed and A braking force is applied to the interlocking means (170) for imparting a rotational difference between the input shaft (112) and the low speed adjusting shaft (120) for high speed driving or rotating the shaft integrally, and for the reverse drive ring gear (230) for reverse drive. A reverse transmission braking means (264) to be added, and a transmission. 13. The transmission according to claim 12, wherein the interlocking means (170) is a fluid clutch, a torque converter, an electric or electronic clutch.