JPS5928912Y2 - Power transmission device in combine harvester - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a power transmission device in a combine harvester that controls a running section based on the load of a handling barrel.

Conventionally, this type of power transmission device operates a continuously variable transmission such as a hydraulic transmission by electrically sensing the rotation speed of the handling cylinder, or one that uses a weight type rotation speed sensing device to determine the traveling speed. There were things that could be changed.

However, electric ones require a drive device etc. for the speed change operation system, resulting in a complicated structure and disadvantages such as increased weight.
Moreover, they were prone to breakdowns and maintenance was complicated.

In addition, although the structure of the weight type is relatively simple, a large force is required to shift the belt type continuously variable transmission to the speed increasing side, which requires a large weight, which increases the load. This also caused an increase in weight.

Furthermore, this weight type has poor responsiveness and cannot accurately link the number of rotations of the handling cylinder to the vehicle speed, resulting in overshooting.
・It also had drawbacks such as causing pinching.

In addition, those in which the traveling speed and the reaping speed are linked have disadvantages such as clogging in the pre-processing section when the speed is extremely low, and deterioration of transfer performance due to the difference between the conveying speed and the feed chain speed.

Furthermore, it is difficult to equip small machines with these items due to load margins, etc. In small combine harvesters, power is transmitted directly from the engine to the threshing/sorting section, traveling section, and preprocessing section, which makes handling difficult. Even when the rotational speed of the barrel decreased, husk culms were continuously supplied from the pretreatment section, making it impossible to thresh and sort the grain, and often causing damage to the equipment.

Therefore, the present invention provides separate transmission lines for transmitting the power of the engine to the handling cylinder and transmission lines for transmitting it to the pre-processing section and the traveling section. A clutch capable of transmission is provided, and both transmission lines are connected when the rotational speed of the handling cylinder reaches a predetermined rotational speed,
Another object of the present invention is to provide a power transmission device for a combine harvester which eliminates the above-mentioned drawbacks by connecting the speed responsive clutch through an intervening speed responsive clutch which is disconnected when the rotational speed becomes lower than a predetermined number of rotations.

Hereinafter, the present invention will be described in detail based on embodiments shown in the drawings.

As shown in FIG. 1, the combine harvester 1 includes a power section 2, a threshing section 3, a pretreatment section 5, a running section 6, and an operation section 7.

As shown in FIG. 2, one output pulley 10 of the engine 8 of the power unit 2 is connected via a belt 15 that can be tensioned and relaxed by a counter shaft 110, a pulley 12, and a tension pulley 13. The counter shaft 11 is connected to a transmission shaft 18 via a reduction gear 16, 17, and the transmission shaft 18 is further connected to a threshing unit 30 and a handling cylinder 23 via a universal joint 20 and a bevel gear 21, 22. are doing.

Further, a pulley 25 that divides the counter shaft 11 into two is disposed, and the pulley 25 is connected to the intermediate shaft 2 through a belt 26.
It is connected to pulley 28 of T.

As shown in detail in FIG. 3, the two-split pulley 25 consists of a fixed flange 30 fixed to the counter shaft 11 and a movable flange 31 slidably supported by the shaft 11. It has a movable boss portion 31a extending through the notch hole 308 of the fixed flange 30.

Links 33&, 33. The weight 35 is connected to the boss portions 31. , 32, a compression spring 36 is interposed between them.

Therefore, this split pulley 25 is connected to the counter shaft 11.
When rotating at a predetermined speed, the centrifugal force acting on the weight 35 moves the movable flange 31 to the left in the drawing against the spring 36, and the belt 26 is clamped between the fixed flange 30 and the movable flange 310. , the rotation of the counter shaft 110 is transmitted to the pulley 28, but when the rotation of the counter shaft 11 becomes less than a predetermined speed, the movable flange 31 is moved to the right in the drawing by the spring 36, and the clamping force acting on the belt 26 is released. The power transmission to the pulley 28 is then cut off.

On the other hand, the other output pulley 10b of the engine 8 is connected to the intermediate shaft 270 and the pulley 40 via a belt 38 which can be tensioned and relaxed by a tension pulley 37.

Further, pulleys 41 and 44 are disposed on the intermediate shaft 27, and the pulley 41 is connected to the running section 6 via a belt 43 on which a tension pulley 42 operated by a pedal is in rolling contact.
The housing pulley 44 is connected to a pulley 50 provided on the drive shaft 5a of the preprocessing section 5 via a belt 48 on which a tension pulley 47 is in rolling contact. There is.

In addition, the operation section I includes a threshing/reaping latch lever 51.
As shown in FIG. 4, the clutch lever 51 is supported by a ball bearing 52 and is movable along an L-shaped guide groove 53 provided in a panel 53.

Two yokes 55 and 56 are connected to the clutch lever 51 so as to move in the y direction in Fig.
(see figure), each yoke 55, 56 is a bowden wire 57
．． 58 to the tension pulleys 13 and 37, respectively.

Therefore, when the clutch lever 51 is moved to the α position, the tension pulley 13 loosens the belt 15, and at the same time, the tension pulley 37 tensions the belt 38. When the lever 51 is moved to the β position, the tension pulley 13 loosens the belt 15. I was nervous, and the tension was 7'-! J 37 Hachert 38
relax.

Further, a yoke 60 is connected to the clutch lever 51 so as to be interlocked with the movement in the x direction in Fig. 4 (see Fig. 6). There is.

Therefore, when the clutch lever 51 is moved to the β position, the tension pulley 47 relaxes the belt 48, and when the lever 51 is moved to the α position, the tension pulley 47 tensions the belt 48.

Since the present invention has the above-described configuration, when the threshing/reaping latch lever 51 is moved from the β position to the α position in FIG. is output pulley 108, belt 1
5 and pulley 12 to the counter shaft 11, and is further transmitted to the reduction gear 16, 17, the transmission shaft 18, and the bevel gear 21.
．． The handling cylinder 23 is rotated via 22.

When the counter shaft 110 rotates, the split pulley 25 also rotates, but when the handling cylinder 23 rotates at a predetermined rotation, the movable flange 31 is rotated by the spring 36 due to the centrifugal force acting on the weight 35 of the split boo 9250. It moves against the opposite direction, clamps the belt 26, and transmits its rotation to the pulley 28.

Further, the tension pulley 47 tensions the belt 48, and the rotation of the intermediate shaft 270 is caused by the pulley 44, the belt 48, and the pulley 5.
0 to the drive shaft 5a of the preprocessing section 5.

At this time, since the tension pulley 42 tensions the belt 43 due to the pedal operation, the rotation of the intermediate shaft 270 is transmitted to the traveling transmission 6a via the pulley 41, the belt 43, and the pulley 46, and the combine harvester 1 travels.

Therefore, the combine harvester 1 is in a working state, and the culms cut by the pretreatment section 5 are sent to the threshing and sorting section 3 via the conveyance chain and the feed chain, and are threshed by the handling drum 23.

Now, the excess shell culm is sent from the pretreatment section 5 to the destructuring section 1.
When an overload occurs on the eight handling cylinder 23, the rotation speed of the counter shaft 11 decreases, the compression spring 36 overcomes the centrifugal force acting on the weight 35, moves the movable flange 31, and releases the belt 26 from being held.

As a result, the rotation of the counter shaft 110 is not transmitted to the intermediate shaft 27, and therefore, the drive to the preprocessing section 5 and the traveling section 6 is cut off.

When the overload acting on the handling cylinder 23 is removed, the counter shaft 11 rotates again at a predetermined speed, and the centrifugal force acting on the weight 35 causes the movable flange 31 to approach the fixed flange 30 and clamp the belt 26. , the rotation is transmitted to the intermediate shaft 27, and the pretreatment section 5 and the traveling section 6 are driven again.

Next, the threshing/reaping latch lever 51 is moved to the β position to release the tension on the belt 48 caused by the tension pulley 47, and after cutting off the drive of the pre-processing section 5, the clutch lever 5
1 to the α position, the tension on the belt 15 caused by the tension pulley 13 is released, and at the same time, the tension on the belt 15 by the tension pulley 13 is released.
This tensions the belt 38.

As a result, the drive of the threshing sorting section 3 is cut off, and the power of the engine 8 is transferred to the output belt 38 and the pulley 4.
0 to the intermediate shaft 27, and further transmitted to the traveling transmission 6a via the pulley 41, belt 43, and pulley 46, and the combine 1 is driven in a non-working state.

Note that even if you try to operate the tension pulley 47 in this state, the clutch lever 51 will not fit into the L-shaped guide groove 53.
Since it is at the α position of a, it cannot be moved in the X direction,
The preprocessing section 5 is never driven.

In addition, when performing only threshing work, clutch lever 5
1 at the β position, the threshing and sorting section 3 is driven, and the tension on the belt 43 caused by the tension clutch 42 is released using the pedal to stop the running section 6.

As explained above, according to the present invention, when an overload occurs on the handling cylinder 23, the drive to the pre-processing section 5 and the traveling section 6 is cut off. In addition, as long as the response to the clutch disengagement side is good, even if the response to the continuation side is slightly delayed,
Traveling and pre-processing section drive is restarted after the load on the handling barrel has been sufficiently reduced, so you can work with plenty of time and there is no hunting or the like that occurs with conventional weight type systems.

Also, compared to the variable speed type, when the load increases, the combine 10 stops traveling, so the workability deteriorates to some extent, but
If the preprocessing section 5 becomes clogged due to a decrease in speed, deterioration of the handover performance can be prevented.

Furthermore, since it is light in weight and does not increase the load, it can be mounted on small machines that do not have the space to mount a hydraulic transmission or a belt-type endless transmission. L-shaped guide groove 53 made of a book
．． Since it is guided by L, it is possible to completely prevent an erroneous operation such as operating only the pre-processing section 5 without operating the threshing section 3.

[Brief explanation of drawings]

Figure 1 is a side view schematically showing the combine harvester, Figure 2 is a schematic diagram showing the transmission device according to the invention, Figure 3 is a side sectional view showing the pulley that splits the harvester into two, and Figure 4 is the threshing/reaping latch. A partially sectional plan view showing the lever, Fig. 5 is Fig. 4 V-■
6 is a sectional view taken along the line VI--VI in FIG. 4. 1... Combine harvester, 5... Pre-processing section,
6... Traveling part, 8... Engine, 10
a=11-12-15.16.17.18,20,2
1.22...Transmission line that transmits to the handling cylinder, 10
．． 27,38°40.41,42,43,44,46,
48゜50...Transmission line transmitting to pre-processing section and traveling section, 13.37...Clutch, 25...
...Speed response clutch (two-split pulley), 35.
... Weight, 47 ... Transmission line clutch to pre-processing section, 51 ... Clutch lever 53a.
...Guide groove.

Claims (3)

[Scope of utility model registration request] (1) In a combine where the power transmission to the pre-processing section and the running section is controlled by the load on the handling barrel, a transmission line that transmits engine power to the handling barrel and a transmission system that transmits it to the pre-processing section and the running section. are provided separately, and a clutch capable of transmitting power to one of these two transmission lines is provided, and both transmission lines are connected when the rotation speed of the handling cylinder reaches a predetermined rotation speed, and when the rotation speed of the handling cylinder reaches a predetermined rotation speed, A power transmission device that is connected via a speed-responsive clutch that disconnects when the speed is below. (2) The power transmission device according to claim 1, wherein the speed responsive clutch is a two-split pulley having a weight. (3) A clutch is provided in the transmission line to the pre-processing section, and the clutch and a clutch for switching between the two transmission lines are configured to be operated by a single clutch lever, and the clutch lever According to the above-mentioned utility model registration claim, the power transmission to the pre-processing section by the clutch can be interrupted and interrupted only when the clutch is switched to the handling cylinder side transmission line by guiding the clutch along an L-shaped guide groove. The power transmission device according to scope 1.