JPS6015012Y2 - transmission - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a transmission device that can perform speed conversion in a low speed range.

In addition to normal running speeds, agricultural vehicles and the like are required to run at low speeds, very low speeds, and extremely low speeds depending on the type of work.

Especially when using vehicles such as bulldozers for agricultural work,
Attachments are required for each type of work, and appropriate running speeds are required.

Therefore, a method has been adopted in which an auxiliary transmission is provided in addition to the main transmission, and the aforementioned low speed, very low speed, and extremely low speed are obtained by the auxiliary transmission.

Conventional auxiliary transmissions do not have a very large gear ratio, and therefore, depending on the type of work, they must be rearranged to a low-speed gear train suitable for the job, and have the disadvantage that they cannot be used in a sufficiently wide range.

The object of the present invention is to provide an auxiliary transmission that can easily achieve low speed, very low speed, and very low speed, and has a wide range of use.

The configuration of the present invention, which is a distant relative of this object, includes a sliding gear that is slidably inserted into the input shaft, and a plurality of external teeth with different numbers of teeth that are selectively engaged with the sliding gear. A carrier, a planetary gear supported by the carrier, a sun gear rotation gear provided on the input shaft, and a sun gear having one end provided with a gear that meshes with the sun gear rotation gear, and a sun gear that meshes with the planet gear. a cylindrical sun gear shaft provided at an end and rotatably fitted into a shaft parallel to the input shaft; a transmission gear provided with a ring gear meshing with the planetary gear and rotatably supported on the shaft; It is characterized by comprising a gear that meshes with a transmission gear, and an output shaft that is rotatably fitted into the input shaft.

An embodiment of the transmission device according to the present invention will be described in detail below with reference to the drawings.

FIG. 1 shows a longitudinal section of a sub-transmission which is an embodiment of the present invention, and FIG. 2 shows a longitudinal section of a main part showing its operating state.

This sub-transmission is a device that changes the speed of the output from the engine and returns it as input to the main transmission.

- A cylindrical output shaft 3 is rotatably fitted into the input shaft 2 whose end is supported by the casing 1 through the bearing, and the output shaft 3 is rotatably fitted into the input shaft 2 through the bearing. It is supported by the casing 1.

A spline 4 is formed at the other end of the input shaft 2, to which an engine (not shown) is connected.

A spline 5 is also formed at the outer end of the output shaft 3.
A main transmission (not shown) is connected here.

Further, a gear 6 is formed at the end of the output shaft 3 inside the casing 1.

A spline 7 is formed on the input shaft 2 within the casing 1, and a sliding gear 8 is spline-fitted to the spline 7 so as to be slidable along the axial direction.

The number of teeth of this sliding gear 8 is the same as the number of teeth of the gear 6 of the output shaft 3.

The input shaft 2 includes a sun gear rotation gear 9 and gears 10 and 11.
is fixed.

Also, a low speed gear 1 is located near the spline 7 of the input shaft 2.
2 is rotatably fitted into the input shaft 2.

The sliding gear 8 is provided with a spline 13, and the low-speed gear 12 is provided with an internal spline 14, so that the sliding gear 8 can be coupled to the low-speed gear 12 through its movement.

On the other hand, a shaft 15 is supported by the casing 1 in parallel to the input shaft 2.

This shaft 15 drives a working machine (not shown) P,
T, O axis (Power Take Off 5haft
), and a spline 16 for connecting the working machine side is cut at its outer end.

The shaft 15 has a cylindrical sun gear shaft 17 connected to the shaft 16.
A gear 18 provided at one end thereof is engaged with the gear 9 for rotating the sun gear.

A sun gear 19 is formed at the other end of this sun gear shaft 17.

A transmission gear 2 is attached to the inner end of the shaft 15 and the gauging 1.
0 is rotatably fitted onto the shaft 15 and supported by the casing 1 by bearings.

This transmission gear 20 is always meshed with the gear 6 at the end of the output shaft 3, and also meshes with the sliding gear 8 as the sliding gear 8 moves.

The transmission gear 20 is integrally formed with an internally toothed ring gear 21 in the same plane as the sun gear 19.

A carrier 22 is rotatably fitted to the sun gear shaft 17 via a bearing.

Pin shafts 23 are provided at three equally divided locations on the end of the carrier 22, and a planetary gear 24 that meshes with both the sun gear 19 and the ring gear 21 is rotatably attached to each pin shaft 23.

The sun gear 19, the three planetary gears 24, the carrier 22, and the ring gear 21 constitute a planetary gear mechanism.

In this mechanism, the sun gear 19 and the carrier 22 serve as input parts with different rotational speeds, and the output shaft 3
The ring gear 21 connected to the rotational speed becomes an output section based on this differential rotational speed.

Three external gears 25 with different numbers of teeth are arranged on the circumferential surface of the carrier 22.
, 26.27 are formed.

The external gears 25 and 26 are moved by the sliding gear 8 due to the movement of the sliding gear 8.
The external gear 27 is always in mesh with the low speed gear 12.

The transmission gear 20 and the external gear 25 have the same number of teeth, and the external gear 26 has about two fewer teeth than the gear 20.25.
It is possible to mesh with the sliding gear 8 by adjusting the displacement.

Further, the number of teeth of the external gear 27 is even smaller than the number of teeth of the external gear 26.

In addition, the gear 2 is meshed with gears 10 and 11 on the input shaft 2 side.
8.29 is rotatably attached to the shaft 15.

A spline 30 is cut into the shaft 15 between these gears 28, 29, and a sliding sleeve 31 is fitted therein so as to be movable in the axial direction.

The gears 28 and 29 are also formed with splines 32 and 33 connected to the splines 30, so that the shaft 15 and the gears 28 or 29 can be connected by movement of the sliding sleeve 31.

Next, shifting by this device will be explained in different cases.

When width change is not required, the sliding gear 8 is moved to position A shown in FIG. 2 and meshed with the transmission gear 20.

Since the gear 6 at the end of the output shaft 3 and the sliding gear 8 have the same number of teeth, the input shaft 2 and the output shaft 3 have the same rotational speed, and the sub-transmission does not change the speed, and the input shaft 2 The input becomes the output of the output shaft 3 and is transmitted to the main transmission.

When obtaining a very low speed, the sliding gear 8 is moved to the position shown by B in FIG. 2, and the sliding gear 8 and the external gear 25 of the carrier 22 are meshed.

The carrier 22 is rotated by input from the input shaft 2 .

At the same time, the sun gear 19 is rotated by the input from the input shaft 2 by the sun gear rotation gear 9 and the gear 18 at the end of the sun gear shaft 17, which are always in mesh with each other.

The ring gear 21 rotates at a reduced speed due to the difference in rotation between the sun gear 19 and the carrier 22.

The transmission gear 20 integrated with the ring gear 21 is always connected to the output shaft 3.
By meshing with the side gear 6, the ring gear 2
1 rotation, that is, an extremely low speed, is transmitted to the main transmission as the output of the output shaft 3.

In order to obtain a very low speed, the sliding gear 8 is moved to the position shown by C in FIG.

At the same time, the input from the input shaft 2 causes the sun gear 19 to rotate via the sun gear rotation gear 9 and the gear 18 at the end of the sun gear shaft 17 .

The ring gear 21 rotates at a reduced speed due to the rotation difference between the sun gear 19 and the carrier 22.

The very low speed of rotation of the ring gear 21 is transmitted to the main transmission as an output of the output shaft 3 in the same manner as in the case of the very low speed.

When obtaining low speed, the sliding gear 8 is moved to position D shown in FIG. 2, and the spline 13 of the sliding gear 8 and the internal spline 14 of the low speed gear 12 are connected.

The input from the input shaft 2 is transmitted to the low-speed gear 12, and the carrier 22 is rotated by the low-speed gear 12 and the external gear 27, which are always in mesh with each other.

At the same time, the sun gear 19 rotates because the sun gear rotation gear 9 and the gear 17 at the end of the sun gear shaft 17 mesh with each other.

The ring gear 21 rotates at a reduced speed due to the difference in rotation between the sun gear 19 and the carrier 22.

The low-speed rotation of the ring gear 21 is transmitted to the output shaft 3 via the integrated transmission gear 20, and then to the main transmission.

In this way, multiple speeds can be obtained in the low speed range, and when using such a speed change for agricultural work, the first speed without changing is used for fertilization, seeding, plowing, etc., and the ultra-low speed is used for rotary work, etc. In addition, ultra-low speed can be applied to deep-plow rotary work, packet cutter, trench trencher work, etc., and low speed can be applied to cutter-type trencher work, etc.

Next, an example of calculation of the gear ratio in the device of this embodiment will be described.

The number of teeth of the ring gear 21 is ZR1 The number of teeth of the sun gear 19 is Z
s, the number of teeth of the gear 6 at the end of the output shaft 3 is 4, the number of teeth of the sliding gear 8 is 4, the number of teeth of the sun gear rotation gear 9 is 4, the number of teeth of the low speed gear 12 is 4 degrees, The number of teeth of the gear 18 at the end of the gear shaft 17 is Otsu 8, and the number of teeth of the transmission gear 20 is z2OzExternal gear 25
, 26.27 teeth respectively 43, Z, , Z27
shall be.

However, the gear ratio i at each speed stage is: '2'-6" 218 ultra low speed ratio j
L = (-2°)

4・ZI3 becomes.

As described above in detail with reference to one embodiment, the transmission device of the present invention moves the sliding gear to selectively mesh the plurality of external gears on the carrier circumferential surface, so that the gears differ in the low speed range. You can fight speed and expand its range of application.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal sectional view of a sub-transmission which is an embodiment of the transmission device according to the present invention, and FIG. 2 is a longitudinal sectional view of essential parts showing the operating state of the device shown in FIG. 1. In the drawing, 2 is an input shaft, 3 is an output shaft, 6 is a gear at the end of the input shaft, 8 is a sliding gear, 9 is a sun gear rotation gear, 12 is a low speed gear, 15 is a shaft, and 19 is a sun gear. , 20 is a transmission gear, 21 is a ring gear, 22 is a carrier, 24 is a planetary gear, and 25, 26, and 27 are external gears.

Claims (1)

[Scope of utility model registration request] A sliding gear slidably fitted onto an input shaft, a carrier having a plurality of external teeth with different numbers of teeth that are selectively engaged with the sliding gear, a planetary gear supported by the carrier, and the input shaft. A sun gear rotation gear provided on a shaft, a gear that meshes with the sun gear rotation gear at one end, a sun gear that meshes with the planetary gear at the other end, and is rotatable on a shaft parallel to the input shaft. a cylindrical sun gear shaft fitted into the input shaft; a transmission gear rotatably supported by the shaft, including a ring gear that meshes with the planetary gear; and a gear that meshes with the transmission gear; A transmission characterized by comprising an output shaft fitted in a rotatable manner.