JPH11187757A - Threshing cylinder driving structure for thresher - Google Patents

Abstract

PROBLEM TO BE SOLVED: To compact and to lighten a transmission case and to reduce a cost required for a power transmission mechanism. SOLUTION: A sideways-facing output shaft 27 of an engine 8 is linked and connected to a sideways-facing input shaft 30 of a transmission case 29 through a power transmission mechanism A. A sideways-facing output shaft 38 of the transmission case 29 and a threshing cylinder spindle 17A in the longitudinal direction are reduced in speed and linked and connected through a bevel gear mechanism 40. A speed change mechanism 39 is laid between the input shaft 30 and the output shaft 38 of the transmission case 29.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drum driving structure for a threshing apparatus.

[0002]

2. Description of the Related Art As a drum driving structure for a threshing apparatus, for example, as disclosed in Japanese Patent Application Laid-Open No. 9-191759, a lateral output shaft of an engine and a lateral input shaft 31 of a transmission case 24 are driven by power. The input shaft 31 and the first intermediate shaft 32 along the front-rear direction are interlockingly connected via a bevel gear mechanism, and the input shaft 31 is interlockingly connected via a belt transmission as a transmission mechanism. The second intermediate shaft 33, the second intermediate shaft 33 and the output shaft 34 extending along the front-rear direction, and the output shaft 34 and the handle barrel support shaft 25 extending along the front-rear direction are interlockingly connected via a gear mechanism or the like. 2. There is a structure in which a transmission gear mechanism is provided between the intermediate shaft 33 and the output shaft 34. Conventionally, this type of structure has been configured to transmit power to the transmission case by reducing the speed by a belt transmission device. Although the tension applied to the belt and the torque of the input shaft of the transmission case increase due to the deceleration by the belt transmission, the belt transmission is configured with a three-piece structure and the input shaft is formed with a large diameter. Thus, the tension and torque can be endured.

[0003]

According to the above-mentioned conventional construction, the number of belts of the belt transmission and the number of pulleys for winding the belt are large, and the cost required for the belt transmission is high.

[0004] Further, the transmission case has a total of four shafts of the input / output shaft and the first and second intermediate shafts, and the number of shafts is large. As described above, there is a problem that the gear case becomes heavy due to the large number of shafts and the large diameter of the input shaft of the transmission case.

The present invention has been made in view of the above circumstances, and has as its object to reduce the size and weight of a power transmission case and to reduce the cost required for a power transmission mechanism.

[0006]

The constitution, operation and effect of the invention according to claim 1 are as follows.

[Structure] A lateral output shaft of an engine and a lateral input shaft of a transmission case are interlockedly connected via a power transmission mechanism, and a lateral output shaft of the transmission case and a handle barrel support shaft extending in the front-rear direction. And a speed reduction interlocking connection via a bevel gear mechanism, and a gear transmission mechanism is provided between the input shaft and the output shaft of the transmission case.

[A] [A] Power is transmitted from a lateral output shaft of an engine to a lateral input shaft of a transmission case via a power transmission mechanism, and a handle body extending in the front-rear direction from the lateral output shaft of the transmission case. Power is transmitted to the shaft via a bevel gear mechanism. The deceleration of the handle shaft is mainly performed by a bevel gear mechanism.

[B] Since the speed is reduced via the bevel gear mechanism as described above, if the power transmission mechanism is constituted by, for example, a belt transmission, the belt transmission can be operated at a higher speed than before, and as a result, The tension applied to the belt and the torque of the input shaft of the transmission case become smaller than before.
The number of belts and the number of pulleys around which the belt is wound can be reduced as compared with the conventional one, and the input shaft can be made smaller in diameter than the conventional one. Can be.

[C] As shown in FIG. 6, for example, the transmission case connects the horizontal input shaft 30 and the horizontal output shaft 38 in an interlocking manner, and also has a gear transmission mechanism between the input shaft 30 and the horizontal output shaft 38. 39, a lateral output shaft 38,
Front-rear output shaft 7 concentrically connected to handle barrel support shaft 17A
5, the number of shafts can be reduced to three in total by the input shaft 30, the lateral output shaft 38, and the front-back output shaft 75. Less. The bevel gear mechanism 40
Large-diameter bevel gear 76
However, since there is a relatively large space around the front-rear output shaft portion close to the handling cylinder 17, the large-diameter bevel gear 76 has a sufficiently large diameter to reduce the deceleration rate. The transmission case 29 can be set large, and the transmission case 29 does not become long in the front-rear direction due to the provision of the large-diameter bevel gear 76.

[Effect] Therefore, the above operations [A],
According to [b] and [c], the transmission case can be reduced in size and weight, and the cost required for the power transmission mechanism can be reduced.

The construction, operation and effect of the invention according to claim 2 are as follows.

[Structure] In the invention according to claim 1,
The bevel gear mechanism includes a small-diameter bevel gear provided on a lateral output shaft of the transmission case, and a large-diameter bevel gear provided on a front-rear output shaft that is concentrically connected to the handle support shaft. The small-diameter bevel gear is engaged with the small-diameter bevel gear in a state where the large-diameter bevel gear is disposed closer to the handle cylinder than the laterally-directed output shaft of the transmission case.

[Operation] In addition to the same operation as the operation according to the first aspect, the above-described bevel gear mechanism is configured as described above, and the large-diameter bevel gear is connected to the transmission case by using a laterally extending output shaft. Also, the large diameter bevel gear is engaged with the small diameter bevel gear in a state where the large diameter bevel gear is arranged on the side opposite to the handling cylinder with respect to the lateral output shaft of the transmission case, for example, because the large diameter bevel gear is engaged with the small cylinder bevel gear in the state arranged on the handle cylinder side. As compared with the structure, the transmission case portion on the front side of the handling cylinder axis can be shortened in the front-rear direction.

[Effect] Accordingly, the transmission case can be made more compact and lightweight, and the cost required for the power transmission mechanism can be reduced.

[0016]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows a combine of all culms input type. This combine with all culms is equipped with a threshing device 3 on a traveling machine body 2 supported by a pair of left and right crawler traveling devices 1 and integrally connects a pre-cutting unit 4 and a feeder 5 for conveying culled culms. In this state, the rear end of the feeder 5 is supported by the traveling body 2 so as to be swingable about the horizontal axis O, and the cabin 7 having the driver's seat 6 is positioned right outside the feeder 5. 2, an engine 8 is disposed as a prime mover from the right outside of the feeder 5 to the rear of the cabin 7 and below, and a Glen tank 9 is arranged right outside the threshing device 3 behind the cabin 7. Behind the threshing device 3, a chopper 51 and a dust exhaust fan 58 for cutting the straw waste and discharging the same outside the machine are provided.

The pre-cutting processing unit 4 includes a reel 10 for scraping the rearward of the machine while raising the planted grain stalks, a clipper-type cutting device 11 for cutting the stalked grain stalks, and An auger 13 is provided at one location of the cutting width, and the feeder 5 is configured by covering a conveyor 14 for transporting grain culms collected by the auger 13 to a threshing apparatus with a cover 15.

As shown in FIGS. 1, 2 and 3, in the threshing apparatus 3, a handling chamber 16 communicating with the end of the feeder 5 is formed by front and rear side plates 69, 70 and the like. It has a structure in which it is supported over the side plates 69 and 70, the sorting unit 18 is disposed below the handling room 16, and a receiving net 19 that supplies the processed material from the handling room 16 to the sorting unit 18 is provided. The sorting section 18 is provided with an oscillating sorting case 20, a main Karamin 21, a sub Karamin 32, a first item collecting screw conveyor 22, a second item collecting screw conveyor 23, a second item Karamin 50, and a receiving net 19. The threshing material supplied from the container is sieved and air-sorted while being oscillated backward by the oscillating sorting case 20, and the grains are transferred from the first item collection screw conveyor 22 to the grain conveyor via the bucket conveyor 49. It is configured to be transported to the tank 9, and configured to return the insufficiently sorted second articles from the second article collecting screw conveyor 23 to the swing sorting case 20 via the reduction device 24.

As shown in FIG. 4, a long counter shaft 25 (hereinafter, referred to as a first counter shaft 25) extending in the left-right direction is provided in a space below the feeder 5 in front of the threshing device 3.
The left end of the engine 8 is provided on the left side of the position corresponding to the left side plate 26 in the lateral direction, and the lateral output shaft 27 of the engine 8 is connected to the first counter shaft 25 via the first belt transmission mechanism 28. It is configured to transmit power. The horizontal input shaft 30 of the first gear case 29 (corresponding to a transmission case) attached to the front side plate 69 is made to protrude from the left side plate 26, and the left end of the first counter shaft 25 and the input shaft of the first gear case 29. A second belt transmission mechanism 31 is provided between the end of the first belt 30 and the lateral output shaft 38 of the first gear case 29 and the handlebar support shaft 17A extending in the front-rear direction via a bevel gear mechanism 40. . The first belt transmission mechanism 28, the first counter shaft 25, and the second belt transmission mechanism 31 constitute a power transmission mechanism A.

Further, as shown in FIG. 5, the sorting unit 18 includes the main Karamin 21, the secondary Karamin 32, the first product recovery screw conveyor 22, the second product recovery screw conveyor 23, the second product Karamin 50, and a rocking sorting case. 20, the input shafts 21A, 32A of the chopper 51, the dust exhaust fan 58,
22A, 23A, 50A, 52A, 51A, and 58A protrude from the left side plate 26, and a second gear case 33 as a reversing mechanism is interlockedly connected to an intermediate portion of the first counter shaft 25. The output shaft 34 is projected to the left so that the left end of the output shaft 34 is located substantially at the same position in the horizontal direction as the left end of the input shaft 21A such as the main car 21 and the left end of the output shaft 34 and the sorting unit 18 are selected. Each input shaft 21
A, 32A, 22A, 23A, 50A, 52A, 51
A to 58A, the third to seventh belt transmission mechanisms 3
5, 53, 54, 55 and 56 are provided. As shown in FIG. 4, power is transmitted from the output shaft 27 of the engine 8 to the traveling transmission case 60 and the unloader 61 of the Glen tank 9 via the twelfth belt transmission mechanism 62 and the thirteenth belt transmission mechanism 88. Is transmitted.
In FIG. 4, 36 and 63 are threshing clutches, respectively.
It is a traveling clutch. In FIG. 2, 57 is the left side plate 26.
A decorative plate 57 that covers the input shaft 21A and the like protruding from the outside.

The mounting structure of the first gear case 29 will be described. As shown in FIGS.
The mounting portion 71 provided on the gear case 29 and the handle cylinder support shaft 17
The holding member 73 of the bearing 72 supporting the A is separately applied to the front and rear surfaces of the front plate 69 in a state where the front plate 69 is sandwiched between the mounting member 71 and the front plate 69.
The first gear case 29 and the holding member 73 are fixed to the front side plate 69 by jointly connecting the overlapping portions of the three layers of the holding member 73 and the first gear case 29 with a plurality of bolts 74. Bolt 74
Are elongated holes 9 provided separately in the front side plate 69 and the holding member 73.
0, and the position of the first gear case 29 with respect to the handle cylinder support shaft 17A can be changed and adjusted freely. The holding member 73 includes a flange 73 for preventing the
a is constituted by a dish-shaped disk which is bent and connected.

As shown in FIGS. 4, 5, and 6, the first
A transmission mechanism 39 is provided between the input shaft 30 and the output shaft 38 of the gear case 29. In other words, the first, second, and third transmission gears 43, 42, and 44 having different numbers of teeth are spline-fitted to the input shaft 30 so as to be slidable at intervals from each other.
The shift gear 45 is spline-fitted to the output shaft 38 so as to be slidable, and the fourth and fifth transmission gears 46 and 47 are rotatably fitted on both sides of the shift gear 45 of the output shaft 38 via bearings 48. The first and third transmission gears 43 and 44 on both sides of the central second transmission gear 42 are always engaged with each other. Also, as shown in FIG.
4 is pivotally supported by a stay 66 on the outer wall side of the first gear case 29, and a rod 67 for linking the shift fork 64 and the operation lever 65 is provided with a plurality of shift forks at a plurality of shift positions. A ball detent mechanism 68 for holding the position of each of the balls 64 is provided.

As a result, the shift gear 45 is slid by the operation of the operation lever 65 and the clutch pawl 45a is moved to the clutch pawl 46a of the fourth transmission gear 46 when the shift gear 45 is engaged with the second transmission gear 42 at a low speed. The intermediate speed state in which the gears are engaged with each other, and the high speed state in which the shift gear 45 is slid in the reverse direction so that the clutch pawl 45a is engaged with the clutch pawl 47a of the fifth transmission gear 47.
The gear can be shifted stepwise, and suitable threshing can be performed according to the type of the harvested crop.

The bevel gear mechanism 40 includes a small-diameter bevel gear 59 provided on the output shaft 38 of the first gear case 29, and a front-rear output shaft 75 coaxially connected to the handle support shaft 17A.
The large-diameter bevel gear 76 is engaged with the small-diameter bevel gear 59 in a state where the large-diameter bevel gear 76 is disposed closer to the handle cylinder 17 than the output shaft 38 of the first gear case 29.

[Brief description of the drawings]

FIG. 1 is an overall side view of a combine.

FIG. 2 is an overall plan view of the combine.

FIG. 3 is a vertical side view of the threshing apparatus.

FIG. 4 is a diagram showing a power transmission system of the threshing device.

FIG. 5 is a diagram showing a transmission system of the threshing device.

FIG. 6 is a sectional view showing a first gear case.

FIG. 7 is a sectional view showing a mounting structure of the first gear case.

FIG. 8 is a sectional view showing a mounting structure of the first gear case.

FIG. 9 is a diagram showing a structure of an operation unit of the transmission mechanism.

[Explanation of symbols]

 Reference Signs List 8 engine 17A handle support shaft 27 engine output shaft 29 transmission case 30 input shaft 38 transmission case output shaft 39 gear transmission mechanism 40 bevel gear mechanism 59 small-diameter bevel gear 75 front-rear output shaft 76 large-diameter bevel gear

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Shinzo Kashino 64 Ishizukita-cho, Sakai City, Osaka Prefecture Inside Kubota Sakai Works (72) Inventor Takuji Segawa 64 Ishizukita-cho, Sakai City, Osaka Prefecture Kubota Sakai Co., Ltd. Inside the factory (72) Inventor Yuichi Fumino 64 Ishizu-Kitacho, Sakai City, Osaka Prefecture Inside Kubota Sakai Factory

Claims (2)

[Claims] 1. A lateral output shaft of an engine and a lateral input shaft of a transmission case are interlockedly connected via a power transmission mechanism, and a lateral output shaft of the transmission case and a handle support shaft extending in a front-rear direction. And a speed reducer interlocking connection via a bevel gear mechanism, and a gear shifting mechanism is provided between an input shaft and an output shaft of the transmission case. 2. A bevel gear mechanism comprising: a small-diameter bevel gear provided on a lateral output shaft of the transmission case; and a large-diameter bevel gear provided on a front-rear output shaft which is coaxially connected to the handle barrel support shaft. 2. The handling drum drive structure for a threshing device according to claim 1, wherein the large diameter bevel gear is configured to be engaged with the small diameter bevel gear in a state where the large diameter bevel gear is disposed closer to a handling cylinder than a lateral output shaft of the transmission case. 3.