JPH03234951A - Transmission gear for tractor - Google Patents

Abstract

PURPOSE:To make a device more compact as well as to enhance fitness by shortening axial direction through reducing gears in number, which are provided for respective shafts. CONSTITUTION:A gear G5 to which power is transmitted via a master clutch C3, is provided for a first shaft 10, a gear G6 is monolithically fixed onto a second shaft 20, a gear G7 is monolithically fixed onto a third shaft 30, and gears G8 through G11 are provided to each of which the rotation of the shaft 30 is independently transmitted with a clutch switched. Gears G12 through G17 are fixed onto a fourth shaft 40. A fifth shaft 50 is provided with a gear G18 which is meshed with the gear G12 and concurrently transmits the power of the gear G12 to the shaft 50 with a clutch switched, and also provided with a gear 19 which transmits the power of the gear G14 to the shaft 50 with a clutch switched. In addition, a device is provided with a gear G20 which is meshed with the gear G15 and concurrently transmits the power of the gear G15 to the shaft 50 with a clutch switched, and with a gear G21 which is meshed with the gear G17 and concurrently transmits the power of the gear G17 to the shaft 50 with a clutch switched.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Field of Application] The present invention relates to a transmission for a tractor, and particularly to a transmission for a tractor whose length in the axial direction is shortened.

[Prior Art] Conventionally, there has been a transmission device for a tractor having a structure shown in FIG. 5.

That is, in FIG. 5, 1 is the first shaft to which the power rotation from the engine is input, and 2 is the shaft that is connected to the first shaft 1 by passing through the hollow part formed along the center of the shaft. 3. a second shaft which is freely rotatable; , 5 are a third axis, a fourth axis, and a fifth axis arranged parallel to the first axis 1 and the second axis 2.

The first shaft 1 has a gear g for driving the oil pump OP.
1 are integrally provided, and a transmission mechanism consisting of a planetary gear mechanism and a clutch mechanism is provided between the first shaft 1 and the second shaft 2. That is, the first shaft 1 has a 1-
and sun gear g2 integrally fixed to the second clutch.
The sun gear g2 meshes with a first planetary gear g3 supported by the first shaft 1-, and a second planetary gear g4 with a small diameter that rotates together with the first planetary gear g3 is provided. There is. A ring gear g5 is formed on one side of the third clutch 3 provided on the second shaft 2, and meshes with the second planetary gear g4.

Then, by switching the second clutch to the connected state, it is fixed to the body, and at the same time, the first clutch is connected to the first clutch.
When the is opened, the rotation of the first shaft 1 is transmitted to the clutch 3 via the second planetary gear g4 and the ring gear g5, and in this state, by switching the clutch 3 to the connected state, a predetermined speed is achieved. The second shaft 2 is rotationally driven by the ratio.

Also, when the first clutch is switched to the connected state and the second clutch is switched to the open state, the rotation of the first shaft 1 is changed to the sun gear g.
2 through planetary gear g3゜g4 and ring gear g
5 and clutch 3, and in this state, by switching clutch 3 to the connected state, the second shaft 2 is rotationally driven with the reduction ratio by these gears.

Furthermore, the second shaft 2 is provided with gears g6 to g9, and the clutch mechanism is provided with 4. Clutch sleeve S1 provided in 5
, S2, the rotation of the second shaft 2 is selectively transmitted to these gears g6 to g9.

The third shaft 3 includes a gear g10 and a gear g that mesh with the gear g6.
Gear g11 meshes with gear 7, gear g1 meshes with gear g8
2. A gear g13 is provided which meshes with the gear g9 via the reverse gear g20, and the clutch mechanism has 4. The third shaft 3 is rotated according to the switching operation and gear ratio by 5.

The fourth shaft 4 includes a gear g14 that meshes with the gear glo, a gear g15 that meshes with the gear g1.1, a gear g16 that meshes with the gear g12, and a gear g17 that meshes with the gear g1-3. 6. is provided in the clutch mechanism provided on the fourth shaft 4. By operating the clutch sleeves S3 and S4 of 7, the fourth shaft 4 is rotated with a selective gear ratio.

The fifth shaft 5 is integrally provided with a gear g18 that meshes with the gear g14 and a gear g19 that meshes with the gear g15. 7 clutch sleeve S3. By operating S4, the fifth shaft 5 is rotated with a selective gear ratio.

In this way, by switching and operating each clutch, a speed change action of 12 forward speeds and 4 reverse speeds is obtained, and the driving force of the first shaft 1 is transmitted to the fifth shaft 5 on the wheel side.

[Problems to be Solved by the Invention] However, in the conventional tractor transmission having such a configuration, since a large number of transmission gears are provided in series on the first shaft, the axial dimension becomes long. the result,
There were problems such as poor attachment to the tractor.

The present invention has been made in view of such problems,
It is an object of the present invention to provide a tractor transmission with a reduced axial dimension.

[Means for Solving the Problems] In order to achieve such an object, the present invention provides a fifth shaft 10.20.3040. that extracts power from the first shaft to the wheels.
50 in parallel, the first shaft 10 is provided with a gear G5 to which power is transmitted via the master clutch C3, and the second shaft 20 is integrally equipped with a gear G6 that meshes with the gear G5. A gear G7 that meshes with the gear G6 is integrally fixed to the third shaft 30, and a gear G8 to which the rotation of the third shaft 30 is independently transmitted by switching the clutch.
．． C9, G10, and G11 are provided, and a gear G12 and a gear G17 are fixed to the fourth shaft 40, and a gear G13 that meshes with the gear G8, a gear G14 that meshes with the gear G9,
A gear G15 that meshes with the gear G10 via a reverse gear G22 and a gear G16 that meshes with the gear G11 are respectively fixed to the fifth shaft 50. five axes 5
0, a gear G19 that meshes with gear G14 and transmits the power of gear G14 to the fifth shaft 50 by switching the clutch, and a gear G15 that meshes with gear G15 and transmits the power of gear G14 to the fifth shaft 50 by switching the clutch.
Gear G20 and gear G1 that transmit the power to the fifth shaft 50
7 and a gear G2 which transmits the power of the gear G17 to the fifth shaft 50 by the switching operation of the clutch, and by performing the switching operation of the clutch, the gear ratio of each gear in the meshing relationship is It is configured to change gears.

[Function] In the tractor transmission device of the present invention having such a configuration, the number of gears provided on each shaft is reduced, so the axial dimension can be shortened, and the device can be made compact. It becomes possible to change. As a result of this compactness, it is possible to improve the ease of mounting on a tractor.

[Example] Hereinafter, an example of a tractor transmission according to the present invention will be described with reference to the drawings.

First, to explain the configuration, in Fig. 1, 10 is the first shaft to which the power rotation from the engine is input;
0.50 is the second to fifth axes arranged parallel to the first axis 10.

A gear G1 and a clutch C1 are fixed to the first shaft 10, and a gear G2 is provided which rotates together with the first shaft 10 when the clutch C1 is connected. A gear G3 provided on the rotating shaft 60 meshes with the gear G1, and a gear G4 rotatably provided on the rotating shaft 60 meshes with the gear G2.
A clutch C2 is provided between the gears G3 and 64. Note that a steering oil pump SP and a transmission oil pump TP are connected to the rotating shaft 60.

Furthermore, the first shaft 1-0 is provided with a master clutch C3 that rotates integrally with the gear G2, and a gear G5 that rotates integrally with the gear G2 when the master clutch C3 is in a connected state.

G6 is an idler gear that is integrally fixed to the second shaft 20, and transmits the rotation of gear G5 to gear G7 by meshing with gear G5 of the first shaft]-〇 and gear G7 fixed to the third shaft 30. do.

Furthermore, the third shaft 30 has a gear G8. G9. G10.

G11 is rotatably provided, and the clutch mechanism 0
4. C5 is provided, and by switching the clutch sleeve F1 provided on the clutch mechanism C4 to side a or b in the figure, or switching the clutch sleeve F2 provided on the clutch mechanism C5 to side C or d, The connection between the three shafts 30 and the respective gears G8 to G11- is selected.

The fourth shaft 40 includes gears G1-2, gear G which meshes with gear G8, gear G14 which meshes with gear G9, gear G15 which meshes with gear G10 via reverse gear G22,
Gear G that meshes with gear G11], 6, and gear G
17 are integrally provided, and the fourth shaft 40 is rotated in accordance with the switching operation by the clutch mechanisms C4 and C5 and the gear ratio of the gears in meshing relationship with each other.

The fifth shaft 50 has a gear G1 that meshes with the gear G2.
8. Gear G19 meshes with gear G14, gear G20 meshes with gear G15, gear G2 meshes with gear G 1.7
1 is rotatably provided with respect to the fifth shaft 50, and
Clutch mechanisms C6 and C7 are provided, and the clutch sleeve F3 provided on the clutch mechanism 06 can be switched to the e or f side in the figure, and the clutch sleeve F4 provided on the clutch mechanism C7 can be switched to the g or h side. By switching to 1, the fifth shaft 50 is rotated with the gear ratio of the gears in meshing relationship.

Next, the speed change operation of this embodiment having such a configuration will be explained based on FIG. 2. In addition, in Fig. 2, the selected position of each clutch is indicated by a circle, and the case where it is not selected is indicated by a -.
, and the corresponding gear train and gear ratio are shown for each gear stage.

That is, as shown in FIG. 2, by switching the clutch sleeve F4 of the clutch C7 to the h side, the A range,
The B range is set by switching the clutch sleeve F4 to the g side, the C range is set by switching the clutch sleeve F3 of the clutch C6 to the f side, and the D range is set by switching the clutch sleeve F3 to the e side. Further, when clutch C1 is connected and clutch C2 is disconnected, each range is set to low speed mode, whereas when clutch C1 is disconnected and clutch C2 is connected, each range 2 is set to high speed mode. Set. Since the gear ratios of the gears in meshing relationship are set in a predetermined relationship, by performing the clutch selection shown in Fig. 2, 12 forward speeds and 4 reverse speeds can be set in high speed mode and low speed mode, respectively. Switching can be performed.

According to this embodiment, each axis is 10, 20, 30°40.5
Since the number of gears provided at zero is reduced, the axial dimension can be shortened, making it possible to make the device more compact.

Next, another embodiment of the present invention will be described with reference to FIG. In FIG. 3, the same or corresponding parts as in FIG. 1 are indicated by the same reference numerals.

This embodiment is simplified from the previous embodiment shown in FIG. 1 by omitting the clutches C1, C2 and gears 01 to G4 for high/low speed switching, and
The steering oil pump SP and the transmission oil pump TP are driven by transmitting driving force to a gear G23 via a gear G22 provided integrally with the steering oil pump SP and the transmission oil pump TP. Therefore, the driving force of the engine is directly connected and transmitted to the idler gear G6 provided on the second shaft 20 via the gear G5.Hereinafter, the mechanism for transmitting the driving force to the third shaft 30 to the fifth shaft 50 is , has the same structure as the first embodiment.

Therefore, the operation of this embodiment is performed by performing a switching operation as shown in FIG. 4, to switch between 4 forward speeds and 1 reverse speed for each range, that is, to switch between 12 forward speeds and 4 reverse speeds in total. can be done.

[Effects of the Invention] As explained above, according to the tractor transmission device of the present invention, the number of gears provided on each shaft is reduced.
The axial dimension can be shortened, which is effective in making the device more compact and improving wearability.

4

[Brief explanation of drawings]

Figure 1 is an explanatory diagram of the configuration of an embodiment of the present invention, Figure 2 is an explanatory diagram illustrating the speed change function of the embodiment, and Figure 3 is the configuration of another embodiment of the invention. FIG. 4 is an explanatory diagram illustrating the gear shifting function of another embodiment. FIG. 5 is an explanatory diagram of a conventional structure of an example of a conventional tractor transmission device. 01-C7, clutches G1-G21. G22. G23, Gear F1-F4; Clutch sleeve

Claims (1)

[Claims] (1) The fifth shaft (10
, 20, 30, 40, 50) in parallel,
The first shaft (10) is provided with a gear (G5) to which power is transmitted via the master clutch (C3), and the second shaft (20)
A gear (G6) that meshes with the gear (G5) is fixed to the third shaft (30), and a gear (G6) that meshes with the gear (G6) is fixed to the third shaft (30).
7) are fixed together, and gears (G8, G9, G10, G11) are provided to independently transmit the rotation of the third shaft (30) by switching the clutch.
) to which gears (G12) and (G17) are fixed, as well as gear (G13) and gear (G13) that mesh with gear (G8).
9), a gear (G14) that meshes with the gear (G10), a gear (G15) that meshes with the gear (G10) via a reverse gear (G22),
Gears (G16) that mesh with the gear (G11) are fixed respectively, and the gears (G16) mesh with the gear (G12) and the power of the gear (G12) is transferred to the fifth shaft (50) by switching the clutch. ) transmission gear (G18), gear (
A gear (G19) that engages with gear (G14) and transmits the power of gear (G14) to the fifth shaft (50) by switching the clutch; A gear (G20) that transmits power to the fifth shaft (50), a gear (G
17) and transmits the power of the gear (G17) to the fifth shaft (50) by the switching operation of the clutch. A tractor transmission device characterized by changing speed by gear ratio.