JPH0545813B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Field of Application) The present invention provides a method for moving forward 16 by selectively switching a hydraulic clutch.
The present invention relates to a tractor transmission device that performs gear shifting of four reverse gears.

(Conventional technology) Conventionally, forward movement was achieved by selecting the gear ratio using a hydraulic clutch.
As a tractor transmission having a switching function of 16 speeds and 4 reverse speeds, for example, the one shown in FIG. 4 is known.

In Fig. 4, A is an engine, and the power rotation from engine A is first transmitted to transmission B, which has a two-speed switching function, and then to transmission C, which has an eight-speed switching function. The power is then transmitted to the drive shaft E on the wheel side through the chain D.

In other words, forward movement is achieved by a combination of transmission B with a 2-speed switching function and transmission C with an 8-speed switching function.
It has a 16-speed gear shifting function and 4 reverse gears.

(Problems to be Solved by the Invention) However, in the case of such conventional transmission devices, since a two-speed transmission and an eight-speed transmission are combined, the device becomes large and The overall number of hydraulic clutches used increases,
Furthermore, since the transmissions are arranged in series, there is a problem in that power must be transmitted to the drive shaft on the wheel side using a chain.

(Means for Solving the Problems) The present invention has been made in view of the problems of the prior art, and has the minimum number of clutches and shafts, and the gear train itself is compact.
An object of the present invention is to provide a tractor transmission having a transmission function of four speeds and four reverse speeds.

In order to achieve this object, the present invention realizes a device equipped with a gear train consisting of five axes and nine clutches, as shown in FIG.

(Embodiment) FIG. 1 is an explanatory diagram symbolically showing an embodiment of the present invention.

First, to explain the configuration, the drive shafts include a first shaft 1 of the first clutch pack 10 to which power rotation from the engine is input, and a second shaft 2 of the second clutch pack 20.
Five shafts are used: a third shaft 3 of the counter section 30, a fourth shaft 4 of the third clutch pack 40, and a fifth shaft 5 of the fourth clutch pack 50 that extracts the power rotation to the outside. .

On the other hand, the first clutch 11 serves as a hydraulic clutch for switching the gear ratio to 16 forward gears and 4 reverse gears.
~Ninth clutch 19 nine hydraulic clutches are used.

Next, the gear train and clutch mechanism will be explained separately for each clutch pack and counter section.

First, the first part receives the power rotation from the engine.
In a first clutch pack 10 having a shaft 1, a gear a is directly connected to the first shaft 1, and three gears are connected to the first shaft 1 by first, second and third clutches 11, 12 and 13. It is equipped with b, c, and d. Here, the clutch 11 is a clutch for reversing.

Next, in the second clutch pack 20, the first
It has gears e, g, h meshing with gears a, c, d of the clutch pack 10, respectively, and further includes a gear f for connecting to the next stage. Of this gear train, gear e, which meshes with gear a, is directly connected to the second shaft 2, and the power rotation of the first shaft 1 is transferred to the second shaft.
It is transmitted to axis 2. Further, each of the gears f, g, and h is mounted on the second shaft 2 so as to be relatively rotatable.
The gear f is formed integrally with the clutch 14,
When hydraulic pressure is supplied to the clutch 14, the second shaft 2
The power rotation is connected to the next stage. Further, each of the gears g and h is formed integrally with the fifth clutch 15, and is connected to the second shaft 2 by supply of hydraulic pressure. An oil pump 70 is connected to the other end of the second shaft 2 provided on the second clutch pack 20, and the second shaft 2 is constantly subjected to the power rotation of the first shaft 1 due to the meshing of gears e and a. from,
It is used as a drive shaft for the oil pump 70.

Next, in the counter section 30, gears i, j, k, and l are fixed to the third shaft 3, and the gear i meshes with the gear f in the previous stage, and as shown by the broken line, the gear b of the first clutch pack 10. When the first clutch 11 is actuated, the third
Reverse movement is selected by transmitting power rotation to the drive shaft 3. Further, gear k meshes with the gear h at the previous stage, and the remaining gears j and l mesh with the gears at the next stage.

Furthermore, in the third clutch pack 40, the fourth
It has gears m and p fixed to the shaft 4, and gears n and o mounted so as to be relatively rotatable.The gear n is integrally formed with the sixth clutch 16 and meshes with the gear j in the previous stage, and 6 Clutch 16 operates to release the 4th
It is connected to the shaft 4. Also, gear o is the 7th clutch 1
7 and meshes with the preceding gear l, and is connected to the fourth shaft 4 by the operation of the seventh clutch 17. Further, each of gears m and p is provided to transmit power to the next stage.

In the fourth clutch pack 50, which is the final stage, gears q and r are relatively rotatably mounted on the fifth shaft 5, which is the output shaft, and the gear q is connected to the eighth clutch 1.
The gear r is formed integrally with the ninth clutch 19 and meshes with the preceding gear m, and the gear r is formed integrally with the ninth clutch 19 and meshes with the preceding gear p.

In FIG. 1, each of the first to ninth clutches 11 to 19 is a known hydraulic clutch device, and a plurality of clutches are provided on the same shaft, but two or more clutches may not be operated at the same time. Instead, only a single clutch will always be actuated.

Next, the operation of the embodiment shown in FIG. 1 will be explained.

FIG. 2 shows a list of gear ratios and clutch selection states for selecting 16 forward speeds and 4 reverse speeds according to the embodiment shown in FIG. Furthermore, the state of clutch selection is as follows:
For example, when looking at the first stage, gears c, n, and q have circles indicating clutch operation, so the second clutch equipped with gear c is indicated by the symbol of the gear integrally formed with the clutch. 12, the sixth clutch 16 with gear n and the eighth clutch with gear q
Each of the clutches 18 will operate to connect each gear to the shaft.

Therefore, the specific speed change operation will be explained with reference to FIG. 2 as follows.

Now, if we perform a gear shift operation with the number of gears being 1 in Fig. 2, the second clutch 12, sixth clutch 16, and eighth clutch 18, which are integrally equipped with gears c, n, and q, shown by circles, will operate. , gear c on the first shaft 1,
Gear n is connected to fourth shaft 4, and gear q is connected to fifth shaft 5. Therefore, the power rotation from the engine applied to the first shaft 1 is applied to gears c, q, and further gears h, k.
The signal is transmitted to the third shaft 3 of the counter section 30 via. Furthermore, power is transmitted from the counter section 30 to the fourth shaft 4 of the third clutch pack 40 via gears j and n, and further to the fifth shaft 5 connected by the eighth clutch 18 via gears m and q. communicated.

In the case of shifting by clutch selection in this manner, even for gears 2 to 16 in FIG. 2, by selecting the clutches indicated by circles, a shifting output with the gear ratio shown can be obtained.

On the other hand, regarding reversing, for example, the number of stages R in Fig. 2
1 as an example, when the first clutch 11 integrally equipped with a gear b is actuated, the power rotation of the first shaft 1 is transferred to the third clutch of the counter section 30 via the gears b and i, as shown by the dotted line.
Since the rotation is transmitted to the shaft 3 and the gear provided on the second clutch pack 20 does not intervene, the gear rotation of the counter portion 30 is in the opposite direction. This power rotation in the opposite direction in the counter section 30 is performed by the third clutch pack 40.
The signal is transmitted to the fifth shaft 5 at the final stage with a gear ratio determined by the operation of the sixth clutch 16 at the fourth clutch pack 50 and the operation of the eighth clutch 18 at the fourth clutch pack 50. This reverse gear shift is performed by appropriately selecting the clutches 16, 17, 18, 19 of the third and fourth clutch packs 40, 50 with the first clutch 11 being fixedly selected for the remaining gears R2 to R4. , 4 reverse speeds can be selected.

FIG. 3 shows the installed state of the transmission according to the present invention in comparison with the conventional example shown in FIG. side drive shaft E
By determining the arrangement position of the fifth shaft 5 on the output side at the position, it is possible to eliminate the need for power transmission by a chain. Furthermore, since the number of shafts and clutches used is minimized, the transmission itself can be constructed compactly.

(Effects of the invention) As explained above, according to the present invention, progress can be made.
As a tractor transmission with a total of 20 speeds (16 speeds and 4 reverse speeds), it can be realized with a minimal device configuration consisting of 9 clutches, 5 axles, and a gear train. Compared to a combination of a machine and an 8-speed transmission, the number of clutches, shafts, and gear trains used can be kept to the minimum necessary, and the reduction in the number of parts reduces the size and weight of the device and reduces costs. Since it is possible to achieve this and has a minimum configuration, it also greatly contributes to reducing power loss.

[Brief explanation of the drawing]

Fig. 1 is an explanatory diagram symbolically showing an embodiment of the present invention, and Fig. 2 is an advancement of the embodiment of Fig. 1.
An explanatory diagram of a list showing gear ratios and clutch selection states for 16 gears and 4 reverse gears, FIG. 3 is an explanatory diagram of the unit configuration of the present invention, and FIG. 4 is an explanatory diagram of a conventional example. 1: 1st axis, 2: 2nd axis, 3: 3rd axis, 4: 4th axis, 5: 5th axis, 10: 1st clutch pack,
20: Second clutch pack, 30: Counter section,
40: Third clutch pack, 50: Fourth clutch pack, 60: Power take-off, 70: Oil pump, 11-19: 1st-9th clutches, a-
r: gear.

Claims (1)

[Claims] 1. A first shaft 1 to which power rotation from an engine is input, a gear a fixed to the first shaft 1, and a gear a fixed to the first shaft 1.
gears b, c, and d are relatively rotatably mounted on the shaft; and first, second, and third clutches 11, 12, and 13 that connect the gears b, c, and d to the first shaft 1, respectively. a first clutch pack; a second shaft 2; and a first clutch pack fixed to the second shaft 2 and the gear a;
a gear e that meshes with the second shaft 2; a gear f that is relatively rotatably mounted on the second shaft 2; a fourth clutch 14 that connects the gear f to the second shaft 2; A gear g is attached to the gear g so as to be relatively rotatable thereto, a gear h is formed integrally with the gear g and meshes with the gear d, and a fifth clutch 15 connects the gears g and h to the second shaft 2. a second clutch pack; a gear i meshing with the gears f and b; and a gear h
gear k, gear j, and gear l that mesh with the third shaft 3
a counter gear portion fixed to; a fourth shaft 4; and a fourth shaft 4 meshing with the gear j;
a gear n that is relatively rotatably attached to the gear n;
a sixth clutch 16 that connects the gear to the fourth shaft 4; a gear o that meshes with the gear l and is relatively rotatably mounted on the fourth shaft 4; and a seventh clutch that connects the gear o to the fourth shaft 4. 17, and a fourth clutch pack comprising gears m and p fixed to the fourth shaft 4; a fifth shaft 5 for extracting power rotation to the outside; and a fifth shaft 5 that meshes with the gear m and can rotate freely relative to the fifth shaft 5; a gear q attached to the shaft and an eighth shaft connecting the gear q to the fifth shaft 5
The clutch 18 and the fifth shaft 5 are engaged with the gear p.
a gear r that is relatively rotatably attached to the gear r;
and a ninth clutch 19 for connecting the fifth shaft 5 to the fifth shaft 5.