CN109168575B - Combine harvester - Google Patents

Abstract

The invention can simplify the driving system of the harvesting device and can reliably drive the harvesting device without special maintenance operation. A rotation conversion mechanism (70) for converting the rotation of the intermediate shaft (65) around the transverse axis into the reciprocating rotation around the axis in the front-rear direction is arranged on the intermediate shaft (65), a transmission shaft (74) for transmitting the converted reciprocating rotation power extends towards the front, and the front end part of the transmission shaft (74) is linked with the harvesting device (12).

Description

Combine harvester

The present application is a divisional application of an invention patent application having an application number of 201410829389.0, an application date of 2006, 9, 11, and an invention name of "combine harvester".

Technical Field

The present invention relates to a combine harvester including a harvesting unit provided at a front end of a feeder connected to a front portion of a threshing device, the harvesting unit including a pusher-type harvesting device, a screw conveyor for lateral feeding, and a raking reel.

Background

As a reaping section driving structure in the above-described combine harvester, for example, a structure disclosed in japanese patent application laid-open No. 2005-211010 is known. That is, the power output from the intermediate shaft of the cross frame at the back of the harvesting part is transmitted to the harvesting knife driving box disposed near the lateral side of the harvesting device via the transmission belt, the harvesting knife driving box and the harvesting device are linked and connected, and the screw conveyor and the raking reel are driven by the power output from the intermediate shaft.

In the above-described conventional configuration, since the belt transmission mechanism for linking the intermediate shaft and the harvesting knife drive case is disposed laterally outside the harvesting unit, a large number of parts are required in the harvesting device drive system, which leads to an increase in cost. Further, since the friction transmission is performed via the transmission belt, there is a possibility that transmission slip due to wear or elongation of the transmission belt occurs, cutting performance of the harvesting device is lowered, and the transmission belt must be sufficiently maintained.

Disclosure of Invention

The present invention has been made in view of the above-described problems, and an object of the present invention is to simplify a drive system of a harvesting device and to reliably drive the harvesting device without requiring special maintenance work.

A first aspect of the present invention is a combine harvester including:

a threshing device,

A feeder connected to the front part of the threshing device,

A harvesting device arranged at the front end of the feeder,

A screw conveyor for transverse feeding arranged at the front end of the feeder,

A raking drum arranged at the front end of the feeder,

A feeder driving shaft transversely mounted on the base end of the feeder,

And an intermediate shaft with a cross frame in front of the feeder,

wherein power is transmitted from the feeder drive shaft to the intermediate shaft, and further, the power branch from the intermediate shaft is transmitted to the harvesting device, the screw conveyor and the raking reel,

the intermediate shaft is provided with a rotation conversion mechanism that converts rotation of the intermediate shaft about a transverse axis into reciprocating rotation about a front-rear direction,

the harvesting machine is provided with a transmission shaft for transmitting the reciprocating rotation of the rotation conversion mechanism, the transmission shaft extends towards the front, and the front end part of the transmission shaft is linked with a harvesting device.

According to the above aspect, the swing arm is attached to the front end portion of the transmission shaft that is reciprocally rotated about the axial center in the front-rear direction, and the reciprocally swinging swing arm is linked to the harvesting knife of the harvesting device, whereby the harvesting knife can be reciprocally driven by a predetermined stroke in conjunction with the rotation of the intermediate shaft. In this case, the transmission system for transmitting power from the intermediate shaft to the harvesting device does not include a friction transmission portion, and therefore, the harvesting device can be driven without slippage.

Therefore, compared with the case of belt drive, the drive system for driving the harvesting device from the intermediate shaft can be simplified, the cost of the drive structure can be reduced, and reliable harvesting device driving can be performed without special maintenance.

A second characteristic aspect of the present invention is that the intermediate shaft is linked to a screw conveyor drive shaft in a flexible (winding) linkage manner, and power branched from the screw conveyor drive shaft is transmitted to the raking reel.

For example, if the power split from the intermediate shaft is transmitted to the raking reel, three power split portions for driving the harvesting device, the screw conveyor, and the raking reel are provided on the intermediate shaft so as to protrude outward in the lateral direction of the harvesting unit. Thus, the cantilever projection length of the intermediate shaft becomes long, and a large bending load is likely to be applied, so that the shaft diameter of the intermediate shaft needs to be increased. On the other hand, according to the above aspect, only two power branch points for the harvesting device driving and the screw conveyor driving need be provided on the intermediate shaft, and the cantilever projecting length of the intermediate shaft does not need to be particularly lengthened. Therefore, the bending load applied to the intermediate shaft is reduced, and the diameter of the intermediate shaft may be small enough to transmit the necessary torque.

A third characteristic of the present invention is that a belt transmission mechanism is provided in a transmission system for transmitting power to the raking reel, and a transmission pulley for performing flexible transmission with different transmission ratios is provided in the belt transmission mechanism, and speed change is performed by changing the transmission belt to the transmission pulley.

According to the above-mentioned scheme, the speed change structure of the raking reel can be configured at low cost.

A fourth characteristic aspect of the present invention is that the raking reel includes a bearing member and a support member;

the bearing member has a bearing recess opening radially outward, and a shaft support portion disposed on a tine mounting shaft of a reel frame is positioned and supported on the reel frame via an engagement mechanism and fixed to the reel frame by one bolt;

the bearing member is secured in engagement via the engagement mechanism to prevent disengagement of the tine mounting shaft which is captured in the bearing recess.

According to the above aspect, when attaching the spool attachment shaft to the spool frame, one bolt is used for each of the left and right shaft support portions. For example, in the case of a pentagonal rake reel, only ten bolts are used when five reel mounting shafts are attached to the reel frame. Therefore, as compared with the conventional technique in which two bolts are used for one shaft support portion, only half the number of bolts and the number of man-hours for operation are required. In addition, if the pivot support portion between the auxiliary reel frame and the free end of the rotation restricting arm is also configured to have the same pivot support structure, a total of twenty bolts may be used in the case of a pentagonal rake reel.

Therefore, the tine mounting shaft integrally equipped with the rotation restricting arm can be easily attached and detached to and from the reel frame with a small number of bolt operation man-hours, and the number of parts and the weight can be reduced.

A fifth characteristic aspect of the present invention is that the screw conveyor includes: a spiral conveyor roller, a fixed fulcrum shaft, a rotating fulcrum shaft, a supporting bracket, an eccentric fulcrum shaft and a raking body, wherein the two end parts of the spiral conveyor roller are fixedly provided with cover plates; a pair of left and right side plates provided at both left and right end portions of the conveying table are provided so as to straddle the screw conveyor drum via the fixed support shaft and the rotary support shaft, and are rotatably supported; the fixed support shaft is connected and fixed on one side plate and can penetrate through the center of one cover plate in a rotatable mode; the rotating support shaft is rotatably supported on the other side plate in a penetrating manner and is fixedly connected to the center of the other cover plate; the eccentric support shaft is connected and supported on the inner end of the roller of the fixed support shaft through a support bracket; the raking body is mounted on the screw conveyor roller in a penetrating way from the outer periphery, the base end part of the raking body is pivotally supported on the eccentric fulcrum shaft, and the raking body performs protrusion and retreat actions from the screw conveyor roller by the rotation of the screw conveyor roller; further, an assembly hole having a shape through which the eccentric support shaft and the support bracket can be inserted is formed in one of the cover plates of the spiral conveyor drum.

According to the above aspect, first, the conveying table and the left and right side plates are fixed to the harvesting section frame by welding or the like, the frame of the harvesting section is assembled, and the screw conveyor is assembled across the left and right side plates. At this time, the auger drum from which the fixed pivot shaft and the rotating pivot shaft are removed is inserted between the left and right side plates, and then the rotating pivot shaft bolt inserted through the other side plate from the outside is coupled to the other cover plate of the auger drum.

The end of the eccentric support shaft is connected to the fixed support shaft in a cantilever manner via the support bracket, and then the eccentric support shaft is inserted into the screw conveyor drum together with the support bracket through an assembly hole formed in one side plate and an assembly hole formed in one cover plate of the screw conveyor drum.

Then, the insertion end of the eccentric support shaft is connected to the free end of the support arm rotatably mounted on the inner end of the rotary support shaft, so that the eccentric support shaft can be fixedly arranged at a predetermined position eccentric from the rotary shaft center of the drum in a state of being supported at both ends. Then, the inner end of the raking body penetrating the periphery of the screw conveyor roller is rotatably connected to the eccentric support shaft. The operation of connecting the eccentric support shaft to the support bracket and the operation of pivotally supporting and connecting the raking body to the eccentric support shaft are performed from an assembly hole openably and closably formed in the outer periphery of the auger drum.

Therefore, the screw conveyor can be pivotally supported and mounted across the space between the left and right side plates while the conveying table surface and the left and right side plates of the harvesting section are integrated by welding or the like. Therefore, compared with the conventional method in which the single side plate is mounted at the rear to support the screw conveyor between the left and right side plates, the number of assembly steps can be reduced, and the variation in the side plate mounting strength related to the rigidity of the harvesting portion can be reduced, thereby effectively stabilizing the quality.

A sixth characteristic aspect of the present invention is that the harvesting apparatus is a pusher-type harvesting apparatus in which a pair of left and right movable knives are reciprocally driven in opposite directions above a fixed knife;

the harvesting device has a hood; the cover extends from one of the pair of right and left movable blades to above the end of the other, covering above between the ends of the pair of right and left movable blades.

That is, even if the space between the end portions of the movable blade is opened, the space above the end portions can be covered by the cover, and thus, rice straw or soil is less likely to enter the space between the end portions. Even if rice straw chips or soil intrudes or flies below the cover to be carried or hooked on the fixed knife or the cutter support body, the rice straw chips or soil comes into contact with the cover which extends from one movable knife and reciprocates together with the movable knife, and is easily scraped off by the cover to fall.

Therefore, according to the first aspect of the present invention, even when the movable blade is opened and closed between the end portions, the covering and scraping action by the cover can easily prevent the rice straw scraps, soil, and the like from being accumulated or accumulated between the end portions, and the cutting failure or the driving failure due to the rice straw scraps or soil is less likely to occur, and the harvesting operation can be efficiently performed.

Drawings

Fig. 1 is an overall left side view of the combine harvester.

Fig. 2 is an overall plan view of the combine harvester.

Fig. 3 is an overall right side view of the combine.

FIG. 4 is a driveline diagram.

Fig. 5 is a side view of the harvesting portion.

Fig. 6 is a front view showing a portion of the rake reel.

Fig. 7 is a longitudinal rear view of the rotation conversion mechanism.

Fig. 8 is a front view of the harvesting knife driving structure.

FIG. 9 is a top view of the rake reel shift mechanism.

FIG. 10 is a side view of a rake reel shift mechanism.

Fig. 11 is a side view of the harvesting portion.

Fig. 12 is a side view of the rake reel.

Fig. 13 is an exploded side view of the rake reel.

Fig. 14 is a front view showing the right end portion of the rake roll.

Fig. 15 is a front view showing the left end portion of the rake reel.

Fig. 16 is a side view showing the bearing location of the tine mounting shaft in the rake reel.

Fig. 17 is a front, longitudinal cross-sectional view showing the bearing location of the tine mounting shaft in the rake reel.

Fig. 18 is an exploded perspective view showing the bearing location of the tine mounting shaft in the rake reel.

Fig. 19 is a side view showing the bearing location of the end of the rotation limiting arm in the rake spool.

Fig. 20 is an exploded perspective view showing a bearing portion of the distal end of the rotation restricting arm in the harrow roller.

FIG. 21 is a longitudinal cross-sectional side view of the tine mounting portion.

FIG. 22 is a longitudinal left side view of the screw conveyor.

Fig. 23 is a cross sectional plan view of the screw conveyor.

Fig. 24 is a cross-sectional plan view showing the vicinity of the right end of the screw conveyor.

Fig. 25 is a cross sectional plan view showing the left half of the screw conveyor.

Fig. 26 is a side view showing a main part of the left side plate.

Fig. 27 is a side view showing a main part of the right side plate.

Fig. 28 is an exploded view of the screw conveyor.

Fig. 29 is a top view of a clipper-type harvesting apparatus for a combine harvester.

Fig. 30 is a plan view of the harvesting device at a support mechanism arrangement location.

Fig. 31 is a sectional view of the harvesting device at a support mechanism arrangement site.

Fig. 32 is a top view of the harvesting device at the harvesting knife drive mechanism action site.

Fig. 33 is a front view of the harvesting device at the harvesting knife drive mechanism action site.

Fig. 34 is a plan view of the harvesting device at the cover arrangement location.

Fig. 35 is a sectional view of the harvesting device at a cover arrangement position.

Fig. 36 is a cross-sectional view of the harvesting device.

Detailed Description

(outline of combine harvester)

Fig. 1 shows an overall side of a general type combine harvester of the present invention, and fig. 2 shows an overall top thereof. In the combine, a traveling body 2 having a pair of left and right crawler traveling devices 1 is provided with an axial flow type threshing device 3 and a bagged grain collecting part 4 in parallel on the left and right sides, and a driving part 5 is provided in front of the grain collecting part 4. A feeder 6 for conveying harvested straws is connected to the front part of the threshing device 3 so as to be vertically swingable about a fulcrum P, a harvesting part 7 having a harvesting width substantially corresponding to the transverse width of the machine body is connected to the front end of the feeder 6, and an engine 8 is laterally provided below the driving part 5.

A hydraulic cylinder 9 is provided between the front part of the traveling machine body 2 and the lower part of the feeder 6, and the harvesting part 7 is swung and lifted around the fulcrum P integrally with the feeder 6 by the telescopic operation of the hydraulic cylinder 9. A raking reel 10 is provided above the front of the harvesting part 7, and the raking reel 10 rakes and pulls up the planted straw to the rear.

The harvesting unit 7 includes: the harvesting machine comprises a pair of vertical-wall-shaped left and right seedling-dividing frames 11, a pusher-type harvesting device 12, a screw conveyor 13 for transversely conveying the harvested crops to the middle of the harvesting width, and a conveying table 14 for connecting the lower parts of the left and right seedling-dividing frames 11. The feeder 6 is configured by housing a top-loading conveyor 16 in a cylindrical conveying box 15 penetrating in the front and rear. The gathering conveyor 16 is configured by connecting a conveying rod 16b to a left and right chain 16a wound in the longitudinal direction, and straws fed in the transverse direction by the screw conveyor 13 are gathered and conveyed along the bottom surface of the conveying box 15 and are thrown into the front end of the threshing device 3.

The screw conveyor 13 is provided with left and right screw blades 18 on the outer periphery of a screw conveyor drum 17, the screw conveyor drum 17 is rotationally driven in a certain direction from the front to the lower side, the left and right screw blades 18 feed the harvested straw transversely toward the front end inlet of the feeder 6, and the screw conveyor 13 is provided with a pair of left and right raking fingers 19 which perform a protrusion and retreat operation with the rotation of the drum at four positions in the circumferential direction of the outer periphery of the drum facing the front end inlet, feeds the harvested straw in a wide range transversely along the conveying table 14, closes the harvested straw to the middle of the harvesting width, and forcibly rakes the harvested straw to the front end inlet of the feeder 6 by the raking fingers 19.

An auxiliary raking finger 20 which operates in a lateral feeding action region of the right screw blade 18 is additionally provided on the right side of the outer periphery of the screw conveyor drum 17, and straw which falls on the conveying surface 14 in front of the screw conveyor 13 at a position laterally apart from the front end inlet of the feeder 6 is raked to the lateral feeding action region of the screw blade 18 by the auxiliary raking finger 20 and is conveyed to an action region of the raking finger 19 by the lateral feeding action of the screw blade 18.

As shown in fig. 5, the rake reel 10 is pivotally supported via a support bracket 22 at the front portions of a pair of left and right support arms 21 which are vertically swingable about a base end pivot point a, and the rake action height of the rake reel 10 can be changed by vertically swinging the support arms 21 via a hydraulic cylinder 23, and the rake action position can be adjusted forward and backward by slidably adjusting the support bracket 22 along the support arms 21. As shown in fig. 9 and 10, the support bracket 22 is manually slidably adjusted, and the support bracket 22 is fixed by inserting a coupling pin 26 into a coupling hole 24 provided in the support bracket 22 and coupling holes 25 provided in a plurality of front and rear portions of the support arm 21.

The raking reel 10 includes: a roll driving shaft 31 horizontally supported by the left and right support arms 21 via the support brackets 22, a regular pentagonal roll frame 32 connected and fixed to the left and right sides of the roll driving shaft 31, a tine mounting shaft 33 rotatably horizontally supported between the five tops of the left and right roll frames 32, a plurality of raking tines 34 mounted in parallel on the tine mounting shaft 33, and a regular pentagonal auxiliary roll frame 35 supported rotatably about an eccentric axis c offset rearward with respect to a driving axis b of the roll frame 32, wherein tip end portions of rotation restricting arms 33a fixedly extending rearward from the end portions of the tine mounting shafts 33 are pivotally supported and connected to the respective tops of the auxiliary roll frame 35, and when the roll frame 32 rotates (revolves) about the driving axis b, the auxiliary roll frame 35 rotates synchronously about the eccentric axis c in conjunction therewith, accordingly, the tine mounting shafts 33 rotate synchronously in the opposite direction to the drum rotation direction with respect to the drum frame 32, and the tines 34 of the tine mounting shafts 33 revolve while always maintaining the downward posture, thereby exerting the raking action.

(drive structure)

Next, a transmission structure for transmitting power to each part will be described.

As shown in fig. 4, the power from the engine 8 is divided into a traveling system and a working system, and the power of the traveling system is belt-transmitted to a main transmission 41 via a belt-tensioned main clutch 40. The main transmission mechanism 41 is constituted by a hydraulic continuously variable transmission (HST), and the transmission power of forward rotation (forward movement) or reverse rotation (reverse movement) output from the main transmission mechanism 41 is input to the transmission case 42. The power input to the transmission case 42 is shifted in two stages, high and low, by the gear type sub-transmission mechanism 43, and thereafter branched to the left and right crawler belt traveling devices 1 via the pair of left and right side clutches 44.

The side clutch 44 is coupled to a lever 45 provided at the front of the driver unit 5, and when the lever 45 is positioned at a left-right neutral position, both the left and right side clutches 44 are "engaged" to travel straight, and when the lever 45 is operated in the left direction or the right direction, the lever 44 is "disengaged" by the side clutch 44 on the operating side, and only one crawler travel device 1 is driven, and the travel machine body 2 is turned in the operating direction of the lever 45. The side brake 46 is coupled to the side clutch 44, and when the lever 45 is further lowered after the side clutch 44 is disengaged, the side brake 46 on the side where the side clutch 44 is disengaged is operated, and the crawler travel device 1 whose driving is disengaged is braked, and the machine body is steered by pivot turning (pivot steering). The joystick 45 is configured to be capable of performing a cross operation in the front-rear direction, the left-right direction, and the joystick 45 is connected to a control valve, not shown, of the hydraulic cylinder 9 such that the hydraulic cylinder 9 performs a shortening operation by a forward operation of the joystick 45 to lower the harvesting unit 7, and the hydraulic cylinder 9 performs an extending operation by a backward operation thereof to raise the harvesting unit 7.

The power of the working system branched from the engine power is transmitted to an input shaft of the threshing device 3, i.e., a windmill shaft 52, via a transmission belt 51 that is operated by a belt-tensioned threshing clutch 50. The power transmitted to the windmill shaft 52 is further branched into two systems on the left side of the machine body, and a part of the branched power is transmitted to the primary screw shaft 53 for the lateral feeding of the primary objects, the secondary screw shaft 54 for the lateral feeding of the secondary objects, the swing sorting box drive shaft 55, and the like, which are provided in the threshing device 3, via the transmission belt 56, and the other part of the branched power is transmitted to the input shaft 59 of the bevel gear box 57 provided in the front part of the threshing device 3 via the transmission belt 58, and the power whose direction is converted by the bevel gear box 57 drives the processing drum 60.

The input shaft 59 of the bevel gear box 57 and a feeder drive shaft 61 laterally extending from the base end of the feeder 6 are linked via a belt 63 operated by a belt-tightening harvesting clutch 62, and the upper-collecting conveyor 16, the screw conveyor 13, the harvesting device 12, and the rake reel 10 are driven by power transmitted to the feeder drive shaft 61 as described below.

An intermediate shaft 65 is supported by the right side cross frame on the back of the harvesting unit 7, and a left end portion of the intermediate shaft 65 and a right end portion of the feeder drive shaft 61 are linked and coupled via a chain 66, and a right end portion of the intermediate shaft 65 and a auger drive shaft 67 projecting to the right of the harvesting unit 7 are linked and coupled via a chain 68.

A rotation conversion mechanism 70 is provided near the right end of the intermediate shaft 65, and this rotation conversion mechanism 70 converts rotation of the intermediate shaft 65 about the horizontal axis into reciprocating rotation about the axis. As shown in fig. 7, the rotation conversion mechanism 70 is configured by externally fitting a tilt boss 72 to a tilt head 71 coupled to an intermediate shaft 65 so as to be freely rotatable about a tilt axis d, and coupling a propeller shaft 74 to a pair of fulcrum pins 72a via a yoke 73, the pair of fulcrum pins 72a being provided at diagonal positions on the outer periphery of the tilt boss 72. The rotation of the intermediate shaft 65 about the lateral axis causes the tilt axis d of the tilt hub 72 to pivot in a positive and negative direction, and thereby causes the transmission shaft 74, which is coupled to the tilt hub 72 via the fulcrum pin 72a and the yoke 73, to rotate in a reciprocating manner at a predetermined angle.

As shown in fig. 5, the transmission shaft 74 extends forward and downward along the outer side surface of the right seedling dividing frame 11, and a swing arm 75 connected to the front end of the transmission shaft 74 and the harvesting unit 12 are linked via a relay link 75a, so that the harvesting blade 12a of the harvesting unit 12 is driven to reciprocate left and right at a constant stroke by the reciprocating rotation of the transmission shaft 74.

A relay shaft 81 is provided concentrically with the base end fulcrum a of the support arm 21 on the right side of the base of the support arm 21 equipped with the raking reel 10, the relay shaft 81 and the screw drive shaft 67 are linked together via a chain 82, and the relay shaft 81 and the reel drive shaft 31 are linked together via a belt 83. As shown in fig. 9 and 10, the large-diameter driving pulley 84a and the small-diameter driving pulley 84b are arranged in parallel on the relay shaft 81, and one driven pulley 85 is provided on the reel driving shaft 31, and the rotation speed of the raking reel 10 can be changed in two stages by changing the speed of the driving belt 83 to one of the driving pulleys 84a and 84 b.

The position of the driven pulley 85 in the axial direction is set to correspond to the intermediate position between the right and left ends of the pulleys 84a, 84b arranged in parallel, and the belt 83 can be wound in a slightly twisted state regardless of which of the pulleys 84a, 84b is selected.

A pair of tension rollers 87 are applied to the slack side path of the belt 83, the pair of tension rollers 87 are attached to a tension arm 86 swingably about a fulcrum e in a balance manner by being urged to swing, and the belt can be appropriately tensioned regardless of the change in the front-rear position of the rake reel 10 by the curved winding of the belt 83 by these tension rollers 87.

(detailed construction of Harrow reel)

Next, an example of the detailed structure of the rake reel 10 will be described with reference to fig. 11 to 15. The rake reel 10 is not limited to the following structure.

The rake reel 10 includes: a rotation support shaft 31 which horizontally supports the left and right support brackets 22, a regular pentagonal drum frame 32 which is connected and fixed to the left and right of the rotation support shaft 31, five tine mounting shafts 33 which are rotatably supported at five positions on the top of the left and right drum frames 32, a plurality of tines 34 which are provided in parallel on the tine mounting shafts 33 at a predetermined pitch, and a regular pentagonal auxiliary drum frame 35 which is rotatably supported about an eccentric axis c which is offset rearward by a predetermined distance L with respect to a drum axis b of the drum frame 32.

As shown in fig. 13, the reel frame 32 is composed of a central boss 32a having a disk shape, five arm portions 32b radially extending from the central boss 32a, and a reinforcing rod 32c spanning between the distal ends of the arm portions 32 b. The auxiliary drum frame 35 is also composed of a central boss 35a in the form of a circular plate, five arm portions 35b extending radially from the central boss 35a, and a reinforcing rod 35c spanning the distal ends of the arm portions 35b, and the drum frame 32 and the auxiliary drum frame 35 have the same shape.

As shown in fig. 14, a disc-shaped support plate 88 is fixedly coupled to the inside of the housing of the support bracket 22, and three guide rollers 89 are provided at positions having the same distance from the eccentric axis c on the inner surface near the outer periphery of the support plate 88. On the other hand, a circular hole 90 is press-formed in the central hub 35a of the auxiliary roll frame 35, the circular hole 90 having a diameter such that the circular hole 90 is circumscribed by the group of guide rollers 89, and the auxiliary roll frame 35 is rotatably supported about the eccentric axis c by guiding the circular hole 90 by the group of guide rollers 89.

A rotation restricting arm 91 is integrally projected rearward from both ends of each tine mounting shaft 33, and a free end of the rotation restricting arm 91 is pivotally supported and coupled to each top portion of the auxiliary drum frame 35. The distance from the axis r of each tine mounting shaft 33 to the free end pivot support point s of the rotation restricting arm 91 and the direction of the imaginary line connecting both the pivots r and s coincide with the distance L from the spool axis b to the eccentric axis c and the direction of the imaginary line connecting both the axes b and c, and the spool axis b, the eccentric axis c, the axis r of the tine mounting shaft 33 and the free end pivot support point s of the rotation restricting arm 91 constitute the pivots of the parallel four-link. Therefore, when the reel frame 32 rotates around the reel axis b, the auxiliary reel frame 35 rotates around the eccentric axis c, and the tine mounting shaft 33 rotates around the reel axis b synchronously in the opposite direction around the axis r while revolving around the reel axis, and the tine mounting shaft 33 always maintains a constant rotational posture.

Fig. 16 to 18 show the structure of a shaft support portion that rotatably supports the tine mounting shaft 33 on the top of the drum frame 32.

The arm portion 32b constituting the drum frame 32 is formed of a sheet metal material having a cross-sectional shape of コ formed by punching out the side edge 32ba in the drum rotation direction, and a recess 92 capable of engaging the tine mounting shaft 33 is formed in a radially outward opening at the distal end portion thereof. On both sides of the recess 92, a pair of receiving pieces 32d are provided facing each other with a space through which the tine mounting shaft 33 can pass, and the pair of receiving pieces 32d are formed by bending the distal end portions of the folded-out side 23ba of the arm portion 32b inward.

A bearing member 93 for rotatably supporting the tine mounting shaft 33 is attached to the inner side of the distal end of the arm portion 32 b. The bearing member 93 is made of a hard resin material having excellent sliding properties, and is formed in a substantially triangular shape that enters between the opposed folded-out side edges 23ba of the arm portion 32 b. A bearing recess 94 is formed on the outer end surface of the bearing member 93 so as to open radially outward, and the bearing recess 94 has a width and a depth corresponding to the outer diameter of the tine mounting shaft 33, and the tine mounting shaft 33 is engaged and supported therein. A pair of engaging projections 95 are provided on the outer end surface of the bearing member 93 so as to project on both sides of the bearing recess 94, and the engaging projections 95 are supported by engaging holes 96 formed in the receiving pieces 32d so as to penetrate from the inside.

A plate-shaped support member 97 is provided between the outer end surface of the bearing member 93 and the bearing piece 32d, and the plate-shaped support member 97 blocks the opening of the bearing recess 94 to prevent the tine mounting shaft 33 from coming off the bearing recess 94. The support member 97 is formed with a support hole 98 through which the engagement projection 95 of the bearing member 93 is inserted, and by coupling and fixing the bearing member 93 to the arm portion 32b, the support member 97 supported by the bearing member 93 via the engagement projection 95 is fixed at a predetermined position.

One mounting hole 99 penetrating in the left-right direction is formed on the bottom side of the bearing recess 94 of the bearing member 93, and the bearing member 93 can be positioned and fixed at a predetermined position by screwing a bolt 100 inserted through the mounting hole 99 from the inside of the body into the arm portion 32 b. An annular protrusion 33a that engages with the left and right end surfaces of the bearing member 93 is provided on the outer periphery of the tine mounting shaft 33, and positioning of the tine mounting shaft 33 in the left and right directions is achieved.

Fig. 19 and 20 show a structure of a pivot support coupling portion that rotatably supports the free end of the rotation restricting arm 91 on the top of the sub-drum frame 35 via a pivot support shaft 101. This pivot support coupling is the same as the pivot support structure that rotatably supports the tine mounting shaft 33 on the top of the reel frame 26.

That is, the arm portion 35b constituting the auxiliary drum frame 35 is also formed of a sheet metal material having a コ -shaped cross section formed by punching out the side edge 35ba in the drum rotation direction, and a recess 102 capable of receiving the pivot support shaft 101 is formed in a radially outward opening at the distal end portion thereof. On both sides of the recess 102, a pair of receiving pieces 35d are provided facing each other with a space through which the pivot shaft 101 can pass, the pair of receiving pieces 35d being formed by bending the distal end portions of the folded-out side edges 26ba of the arm portions 35b inward.

A bearing member 103 for rotatably supporting the pivot shaft 101 is attached to the inner side of the distal end of the arm portion 32 b. The bearing member 103 is made of a hard resin material having excellent sliding properties, and is formed in a substantially triangular shape so as to enter between the opposed folded side edges 26ba of the arm portion 35 b. A bearing recess 104 is formed on the outer end surface of the bearing member 103 so as to open radially outward, and the bearing recess 104 has a width and a depth corresponding to the outer diameter of the pivot support shaft 101, and the pivot support shaft 101 is inserted and supported therein. A pair of engaging projections 105 are provided on the outer end surface of the bearing member 103 so as to project on both sides of the bearing recess 104, and the engaging projections 105 are supported by engaging holes 106 formed in the receiving pieces 35d so as to penetrate from the inside.

A plate-like support member 107 is provided between the outer end surface of the bearing member 103 and the bearing piece 35d, and the plate-like support member 107 blocks the opening of the bearing recess 104 to prevent the pivot support shaft 101 from coming off the bearing recess 104. The support member 107 is formed with a support hole 108 through which the engagement projection 105 of the bearing member 103 is inserted, and by coupling and fixing the bearing member 103 to the arm portion 35b, the support member 107 supported by the bearing member 103 via the engagement projection 105 is fixed at a predetermined position.

One mounting hole 109 penetrating in the left-right direction is formed on the bottom side of the bearing recess 104 of the bearing member 103, and the bearing member 103 can be positioned and fixed at a predetermined position by screwing a bolt 110 inserted through the mounting hole 109 from the inside of the body to the arm portion 35 b. An annular projection 101a that engages with the left and right end surfaces of the bearing member 103 is provided on the outer periphery of the pivot shaft 101, and the auxiliary spool frame 35 is positioned in the left-right direction.

Here, the pivot support shaft 101 fixedly provided at the free end of the rotation restricting arm 91 has the same diameter as the tine mounting shaft 33, and the pivot support coupling portion thereof and the shaft support structure for rotatably supporting the tine mounting shaft 33 on the top of the barrel frame 26 are of the same specification, so that the bearing members 93 and 103, the support members 97 and 107, and the bolts 100 and 110 are commonly used, respectively.

In assembling the tine mounting shaft 33, first, the tine mounting shaft 33 is engaged in the recess 92 of the spool frame 32, and then the support member 97 is inserted between the receiving piece 32d and the tine mounting shaft 33 from the side. Then, the bearing member 93 is attached from the spool center side, the engagement projection 95 is inserted through the support hole 98 of the support member 97 into the engagement hole 96 of the receiving piece 32d, and then the bearing member 93 is fixed by the bolt 100. The pivot support shafts 101 of the rotation restricting arms 91 are also assembled to the auxiliary spool frame 35 in the same order. In the event that the tine mounting shaft 33 is to be removed for disassembly for maintenance or replacement, the reverse sequence is followed.

As shown in fig. 14 and 15, the tines 34 are formed in a pair by bending a spring wire downward into a U-shape, and are inserted from above into mounting holes 43 formed in the tine mounting shaft 33 so as to pass through the mounting holes vertically. As shown in fig. 21, the upper cross portion 34a of the tine 34 is bent into a shape wound around the tine mounting shaft 33 when viewed from the lateral side, and the upper cross portion 34a is strongly pressed against the tine mounting shaft 33 to be elastically spread and deformed and to be externally fitted and fixed. The fork 34 can be detached by strongly pulling the fork 34 upward while pushing the upper cross bar portion 34a open.

According to the above configuration, when the roll mounting shaft is mounted to the roll frame, one bolt is used for each of the left and right shaft support portions. For example, in the case of a pentagonal rake reel, only ten bolts are used for mounting five reel mounting shafts to a reel frame, and only half the number of bolts and the number of man-hours for operation can be used as compared with the conventional technique in which two bolts are used for one shaft support portion. Further, if the pivot support portions between the auxiliary reel frame and the free ends of the rotation restricting arms are configured to have the same pivot support structure, twenty bolts may be used as a whole in the case of pentagonal raking the reel.

Therefore, the tine mounting shaft integrally equipped with the rotation restricting arm can be easily attached to and detached from the reel frame with a small number of bolt operation man-hours, and reduction in the number of parts and weight can be achieved.

In addition, since the bolt is mounted to the drum frame from the side, the bolt is located inside the rake drum profile. As a result, the straw planted is not easily hooked, and the threshing accompanying raking can be effectively prevented.

As described above, in the auxiliary drum frame, the pivot support coupling portion of the rotation restricting arm positions and supports the bearing member having the bearing recess opening radially outward via the engagement mechanism, and is fixed to the drum frame by one bolt, and the support member that prevents the rotation restricting arm engaged in the bearing recess from being disengaged from the opening is engaged and fixed via the engagement mechanism. Therefore, when the one-tine mounting shaft is pivotally supported and mounted across the drum frame and the auxiliary drum frame, only four bolts are required, and for example, in the case of a pentagonal rake drum, the five-tine mounting shaft can be mounted with twenty bolts, which is half the number of the conventional art, thereby promoting the above-described effect of the first invention.

Since the bearing member and the support member provided in the shaft support portion of the tine mounting shaft and the bearing member and the support member provided in the pivot support coupling portion of the rotation restricting arm are respectively configured to have the same specification, the parts of the shaft support portion of the tine mounting shaft and the pivot support coupling portion of the rotation restricting arm are promoted to be used in common, which is more advantageous for cost reduction.

(detailed construction of screw conveyor)

Next, an example of the detailed structure of the screw conveyor 17 will be described. The screw conveyor 17 is not limited to the following structure.

As shown in fig. 22 and 23, the harvesting unit 7 has the following frame assembly structure: a back plate 76 constituting the back surface, a conveying table 14 constituting the bottom surface, and a pair of left and right side plates 77, 78 constituting the left and right side surfaces are fixed to a harvesting section frame 79 formed by connecting an angle pipe or an L-shaped member by spot welding or the like, a pusher-type harvesting device 12 is provided across and along the front end of the conveying table 14, and a screw conveyor 17 for transversely feeding harvested crops to the middle of the harvesting width is provided across the left and right side plates 77, 78.

The feeder 6 is configured by installing a gathering conveyor 16 inside a conveying box 15 formed in a rectangular tube shape. The gathering conveyor 16 is configured by a pair of left and right chains 16a wound in the longitudinal direction and a conveying rod 16b connected to the both sides of the chain, and crops fed in the transverse direction by a screw conveyor 17 are gathered and conveyed along the bottom surface of the conveying box 15 and are thrown into the front end of the threshing device 3.

A hydraulic cylinder 9 is provided between the front part of the main frame 80 of the traveling machine body 2 and the lower part of the feeder 6, and the harvesting unit 7 and the feeder 6 are swung up and down around the fulcrum P by the expansion and contraction operation of the hydraulic cylinder 9. A raking reel 10 is provided above the front of the harvesting section 7, and the raking reel 10 pulls the planted crop to the rear and feeds it into a harvesting device 12.

As shown in fig. 22 and 24, the auger 17 is configured to include a pair of left and right auger blades 18 on the outer periphery of the large-diameter auger drum 17, the pair of left and right auger blades 18 functioning to perform lateral feeding toward the front end of the feeder 6 as they rotate forward, and to include two bar-shaped raking fingers 22 (an example of a raking body) protruding from the auger drum 17 in a lateral width region facing the front end inlet 221 of the feeder 6 at four circumferential positions, and to include one auxiliary raking finger 23 (an example of an auxiliary raking body) protruding from the auger drum 17 at a middle position of the right lateral feeding region.

Cover plates 111, 112 are fixedly provided inside the vicinity of both right and left ends of the auger roller 17, and an intermediate support plate 113 is fixedly provided inside a right portion of the auger roller 17. A rotation support shaft 114 penetrates through the center of each of the right cover plate 112 and the intermediate support plate 113, and a coupling flange 114a that is keyed to the rotation support shaft 114 is bolted to the right cover plate 112, so that the rotation support shaft 114 is integrally coupled to the center (auger axial center) x of the auger drum 17.

As shown in fig. 24, the rotary support shaft 114 protruding from the right end of the auger drum 17 is rotatably supported via a bearing 116 by a bearing bracket 115 attached to the right side plate 78, and is rotatably supported by the support hole 26a of the intermediate support plate 113. As shown in fig. 27, an assembly hole 78a having a diameter formed so as to be able to pass through the coupling flange 114a and the bearing bracket 115 is formed in the side plate 78, a rectangular cover plate 117 is bolted from the outside to the side plate 78 so as to close the assembly hole 78a, and the bearing bracket 115 is bolted to the cover plate 117. Inside the side plate 78, a winding prevention plate 118 having a bead disk shape that enters a recessed space formed in the right end of the auger drum 17 is fastened and fixed to the cover plate 117 by a common fastening bolt.

An input sprocket 119 is coupled to an outer end of the rotation support shaft 114 to receive a rotational driving force. An output sprocket 120 for transmitting power to the harrow roller 18 is integrally formed with the input sprocket 119.

As shown in fig. 25, a fixed support shaft 122 is connected and fixed to the left side plate 77 concentrically with the screw axis x via a connecting flange 122a, and the fixed support shaft 122 is rotatably supported through a bearing bracket 123 via a bearing 124, and the bearing bracket 123 is attached to the left side cover plate 111 of the screw drum 17. As shown in fig. 26, an assembly hole 77a having a diameter formed so as to be able to be inserted through the coupling flange 122a and the bearing bracket 123 is formed in the side plate 77, a rectangular cover plate 125 is bolted to the side plate 77 from the outside so as to close the assembly hole 77a, and the bearing bracket 123 is bolted to the cover plate 125. Inside the side plate 77, a winding prevention plate 126 having a bead disk shape that enters a recessed space formed at the left end of the auger drum 17 is fastened together with the cover plate 125 and fixed by bolting.

A support bracket 127 is fixed to an inner end portion of the fixed support shaft 122 by a key connection, and a support bracket 128 is loosely fitted to an inner end side of the rotary support shaft 114 via a bearing 129 so as to be rotatable about the screw axial center x. The eccentric support shaft 130 is mounted parallel to the screw axis x across the end portions of the left and right support brackets 127, 42. The support brackets 127, 42 are fixed in a predetermined posture facing downward in the front direction, and as shown in fig. 22, the axis y of the eccentric support shaft 130 connecting the support brackets between the two support brackets 127, 42 is set at a position offset downward in the front direction with respect to the screw axis x.

Nine mounting bosses 131 are loosely fitted to the eccentric support shaft 130 in accordance with the mounting positions of the raking fingers 22 and the auxiliary raking fingers 23, and the inner ends of the raking bodies 22 and the auxiliary raking bodies 23 are inserted into and screwed to the respective mounting bosses 131. The rake finger 22 and the auxiliary rake finger 23 rotatably mounted on the eccentric support shaft 130 via the mounting shaft bosses 131 are supported by penetrating a resin slide bush 132 mounted at a predetermined position on the outer periphery of the screw conveyor 17. A fitting hole 20a is formed in an appropriate left and right portion of the outer periphery of the auger roller 17, the fitting hole 20a is closed by a detachable cover 133, and a slide bush 132 is attached to the cover 133.

The auger 17 is configured as described above, and when the rotating support shaft 114 is rotationally driven to rotate the auger drum 17 forward, the rake fingers 22 and the auxiliary rake fingers 23 rotate around the axial center y of the eccentric support shaft 130, and at this time, the distance between the eccentric support shaft 44 and the slide bushes 132 changes according to the rotational phase, and the rake fingers 22 and the auxiliary rake fingers 23 protrude and retract from the auger drum 17 accordingly, between the left and right side plates 77 and 12.

In this case, the amount of protrusion of the rake fingers is maximized on the forward extension line connecting the axis x of the screw conveyor and the axis y of the eccentric support shaft 130, and the amount of protrusion of the rake fingers is minimized on the opposite phase. Therefore, the crop transversely fed by the screw blade 18 is raked rearward by the largely protruding raking fingers 22 and the auxiliary raking fingers 23, is conveyed rearward along the conveying surface 14 so as to be submerged below the screw conveyor drum 17, and is fed into the front inlet 221 of the feeder 6.

Next, a procedure for assembling the screw conveyor 17 between the left and right side plates 77, 12 will be described.

In assembling, the connecting flange 114a is preliminarily key-connected to the rotation support shaft 114. On the other hand, a support bracket 123 is mounted on the fixed support shaft 122 via a bearing 124, and a support bracket 127 is keyed. The left end of the eccentric support shaft 130 to which the mounting boss 131 is fitted is coupled and fixed to the free end of the support bracket 127, and the right end of the eccentric support shaft 130 is coupled to the support bracket 128 to which the bearing 129 is mounted.

The auger roller 17 is inserted between the left and right side plates 77, 12 in a state where the winding prevention plates 118, 39 are temporarily assembled and inserted into the recessed spaces at the left and right end portions of the auger roller 17.

Next, the rotation support shaft 114 assembled in advance as described above is inserted into the auger drum 17 through the assembly hole 78a of the side plate 78, and is inserted through the support holes 26a of the right-side cover plate 112 and the intermediate support plate 113. Then, a tool such as a socket wrench is inserted through the assembly hole 78a, and the coupling flange 114a is bolted to the cover plate 112. Then, a bearing bracket 115 to which a cover plate 117 is attached in advance is fitted to the rotation support shaft 114 via a bearing 116, and the cover plate 117 is bolted to the side plate 78 from the outside to close the assembly hole 78 a. In addition, the winding prevention plate 118 is co-fastened to the side plate 78 when the cover plate 117 is bolted to the side plate 78. Thereafter, the input sprocket 119 and the output sprocket 120 are attached to the protruding portions of the rotation support shafts 114.

Next, the fixed support shaft 122, to which the eccentric support shaft 130 and the support brackets 127 and 42 and the like have been previously assembled as described above, is inserted into the auger drum 17 through the assembly hole 77a of the left side plate 77. At this time, since the assembly hole 111a having a shape through which the support brackets 127 and 42 can be inserted is formed in the left cover plate 111, the support brackets 127 and 42 and the eccentric support shaft 130 are inserted between the cover plate 111 and the intermediate support plate 113 through the assembly hole 111 a.

Next, a tool such as a socket wrench is inserted through the assembly hole 77a to bolt the bearing bracket 123 to the cover plate 111, and then the cover plate 125 is attached to the connecting flange 122a, and the cover plate 125 is bolted to the side plate 77 from the outside, whereby the fixing support shaft 122 is fixed to the side plate 77 and the assembly hole 78a is closed. In addition, the winding prevention plate 126 is co-fastened to the side plate 77 when the cover plate 125 is bolted to the side plate 77.

A support bracket 128 connected to the right end of the eccentric support shaft 130 is loosely fitted to the inner end of the rotary support shaft 114 via a bearing 129. This assembly operation is performed through the assembly hole 20a on the right side of the auger roller 17.

Next, a tool is inserted through each of the open assembly holes 20a, and the inner ends of the raking fingers 22 and the auxiliary raking fingers 23 are inserted and coupled to the mounting boss 131 externally fitted to the eccentric support shaft 130. Thereafter, the respective covers 133 are coupled to the auger roller 17 in a state where the rake fingers 22 and the auxiliary rake fingers 23 are inserted into the slide bush 132, and the respective assembly holes 20a are closed.

Through the above operations, the assembly of the auger roller 17 is completed.

(details of harvesting apparatus)

Next, an example of the detailed configuration of the harvesting device 12 will be described with reference to the drawings. However, the detailed structure of the harvesting unit 12 is not limited to the following manner.

As shown in fig. 29, the pusher-type harvesting apparatus 12 is configured by providing one fixed blade 202 and movable blades 206, wherein the fixed blade 202 is supported by the base portions of a plurality of grass-dividing frames 11 arranged at predetermined intervals in the lateral direction of the machine body, and the movable blades 206 are provided above the left and right portions of the fixed blade 202.

The pusher-type harvesting apparatus 12 is provided in a pre-harvesting treatment section of a combine harvester for harvesting and threshing the planted straw introduced into the straw dividing frames from the straw dividing members 200 provided at the end sides of the straw dividing frames 11, and is configured to recover grains from threshing in a threshing box or from a bagging silo for bagging.

As shown in fig. 29, 30, 31, and the like, the fixed blade 202 includes one fixed blade table 203 and a plurality of fixed blades 205, the one fixed blade table 203 is attached to a harvesting blade support 201 (see fig. 36) connected to a lower side of a base portion of each grass frame 11, and the plurality of fixed blades 205 are arranged along a lateral direction of the machine body on an upper surface side of a front edge portion of the fixed blade table 203 and are fixedly attached by rivets 204.

As shown in fig. 29, 30, 31, and the like, each of the movable blades 206 includes a plurality of movable blades 207 arranged in the lateral direction of the machine body at an arrangement pitch having the same length as the arrangement pitch of the fixed blades 205 of the fixed blade 202, and one blade bar 23 fixedly attached to the upper surface side of each of the movable blades 207 by rivets 208 to connect the movable blades 207.

Support mechanisms 215A, 30B, and 30c having a holder 216 function at three positions, i.e., the two end portions and the middle portion of each movable blade 206, and each movable blade 206 is supported by the fixed blade 202 so as to be slidable in the transverse direction of the machine body via the support mechanisms 215A, 30B, and 30 c. The left movable knife 206 is reciprocally driven in a state of sliding reciprocally in the machine body lateral direction with respect to the left side portion of the fixed knife 202 by a knife retracting drive mechanism 221 acting on a movable knife operating body 210, the movable knife operating body 210 being provided in the vicinity of a portion on which the support mechanism 215A located most outward in the machine body lateral direction among the plurality of support mechanisms 215A, 30B, 30c of the movable knife 206 acts. The right movable blade 206 is driven to reciprocate in a state of sliding back and forth in the lateral direction of the machine body with respect to the right portion of the fixed blade 202 by a retracting blade driving mechanism 221 acting on a movable blade operating body 210 provided in the vicinity of a portion on which the supporting mechanism 215A located most outside in the lateral direction of the machine body among the plurality of supporting mechanisms 215A, 30B, 30c of the movable blade 206 acts.

As shown in fig. 29, 32, and 33, each of the harvesting knife drive mechanisms 221 includes a swing link 230, a link 231, and a drive rotating body 223; the swing link 230 includes an operation roller 222 at one end, and the operation roller 222 is formed by a bearing inserted between a pair of left and right operation plates 211 of the movable blade operation body 210 of the movable blade 206 to be driven; one end of the link 231 is relatively rotatably connected to the other end of the swing link 230; the other end of the interlocking bar 231 is connected to the driving rotating body 223 so as to be relatively rotatable at the peripheral edge portion thereof.

The swing link 230 has an intermediate portion rotatably connected to a support shaft 232 provided in the straw conveying device (not shown), and the swing link 230 is reciprocally swung about the axis of the support shaft 232. The driving rotor 223 is rotatably supported via a rotation support shaft 224 at an end of a transmission case 226 constituting a frame of the pre-harvest treatment section.

Thus, each of the harvesting knife drive mechanisms 221 converts the rotational drive force of the drive rotating body 223 driven around the body vertical axis of the rotating support shaft 224 into linear reciprocating power via the interlinking lever 43, transmits the linear reciprocating power to the end of the swing link 230, drives the swing link 230 to swing reciprocally around the body vertical axis of the support shaft 232 at a fixed swing angle, and transmits the reciprocating power of the swing link 230 to the movable knife operating body 210 via the operating roller 222, thereby driving the movable knife 10 reciprocally.

The pair of harvesting knife drive mechanisms 221 reciprocally drive the left and right movable knives 206 in the following states in accordance with the setting of the rotational phase of the drive rotating body 223, and the like: when the left movable knife 206 slides toward the outside of the machine body, the right movable knife 206 also slides toward the outside of the machine body, and when the left movable knife 206 slides toward the inside of the machine body, the right movable knife 206 also slides toward the inside of the machine body, that is, the pair of left and right movable knives 206 slide back and forth in opposite directions.

That is, in the clipper-type harvesting apparatus 12, in a state where the pair of left and right movable blades 206 reciprocate in opposite directions above the fixed blade 202, and, in a state where the space between the end portions of the pair of right and left movable blades 206 is opened and closed above the harvesting knife support 201 provided to the grass frame 11 located at the widthwise central portion of the machine body, the pair of left and right movable blades 206 are reciprocally driven by the pair of harvesting driving mechanisms 221, so that by means of the fixed blade 205 positioned at the left side portion of the fixed blade 202 and the movable blade 207 of the left movable blade 206 relatively moving with respect to the fixed blade 205, the planted straw from the plurality of seedling dividing members 200 positioned at the left side of the harvesting part is harvested, further, by means of the fixed blade 205 positioned at the right side portion of the fixed blade 202 and the movable blade 207 of the right movable blade 206 relatively moving with respect to the fixed blade 205, the planted straw from the plurality of seedling dividing members 200 located on the right side of the harvesting section is harvested.

As is apparent from fig. 34 and 35, the cover 227 is extended from the end of one movable knife 206 to the top of the end of the other movable knife 206 of the pair of left and right movable knives 206, and the cover 227 has a sufficient extension length to cover the space S between the ends of the pair of left and right movable knives 206 and to cover the entire space between the ends even when the movable knives 206 are opened to the maximum size by reciprocating in opposite directions.

Accordingly, the entry of chaff, mud, or the like between the end portions of the left and right movable blades 206 is prevented by the cover 227, and even if the chaff, mud, or the like intrudes or flies into between the end portions and is caught by the fixed blade 202 or the cutting blade support 201 below between the end portions, the chaff, mud, or the like comes into contact with the cover 227 reciprocating together with the movable blade 206, and is easily dropped by the scraping action of the cover 227, so that the harvesting process is performed.

As shown in fig. 30 and 31, the support mechanism 215A for supporting the outer end portion of each movable blade 206 in the lateral direction of the machine body includes: a rear slide guide 218 fixed to the fixed tool rest 203 by a connecting bolt 217; the rear end portion of the holder 216 made of a spring plate is fixed to the fixed base 203 together with the rear slide guide 218 by the coupling bolt 217; the front slide guide 220 is coupled to the front end of the holder 216 by a rivet 219. The support mechanism 215A slidably sandwiches the sliding portion 26 of the blade 209 by the front sliding guide 220 and the rear sliding guide 218, and supports the movable blade 206 so as to slide in the transverse direction of the machine body with respect to the fixed blade 202 by the support mechanism 215A slidably sandwiching the sliding portion 26 of the blade 209 by the front sliding guide 220 and the rear sliding guide 218.

As shown in fig. 33, 34, and 35, the support mechanism 215C that supports the inside end of the movable blade 206 to which the cover 227 is coupled includes: a rear slide guide 218 fixed to the fixed tool rest 203 by a connecting bolt 217; the rear end portion of the holder 216 made of a spring plate is fixed to the fixed base 203 together with the rear slide guide 218 by the coupling bolt 217; the front slide guide 220 is coupled to the front end of the holder 216 by a rivet 219. A rear slide contact portion 229a and a front slide contact portion 229b are provided in the attachment portion 228 of the cap 227 that is connected to the movable blade 206 by the rivet 208, so as to slide on the rear slide guide 218 or the front slide guide 220 of the support mechanism 215C provided in the fixed blade 202, and the rear slide contact portion 229a is disposed between the arbor 209 of the movable blade 206 and the rear slide guide 218; the front slide contact portion 229b is disposed between the knife bar 209 of the movable knife 206 and the front slide guide 220. The attachment portion 228 of the cover 227 is made of a material different from that of the holder 209, and the rear sliding contact portion 229a and the front sliding contact portion 229b have hardness and wear resistance superior to those of the holder 209.

As shown in fig. 32, a driven plate 212 is detachably attached to the pair of left and right operation plates 211 of the movable blade operating body 210 provided in the movable blade 206 via a connecting bolt 213, thereby forming a contact surface 214 with which the operation roller 222 of the swing link 230 comes into contact. Thus, when the contact surface 214 is worn, it is possible to cope with this situation without replacing the movable blade 206 and the movable blade operating body 210 only by replacing the driven plate 212.

As described above, the mounting portion of the cover coupled to the one movable blade includes the sliding contact portion that is located between the blade bar of the one movable blade and the sliding guide of the fixed blade and slides on the sliding guide. That is, as the movable blade is driven to reciprocate, the mounting portion of the cover slides relative to the slide guide body at the slide contact portion, whereby the movable blade can be reciprocated while suppressing the play of the movable blade relative to the fixed blade.

Therefore, the movable blade can be driven quietly with less looseness, and the cover is used as the sliding contact member, which is advantageous in terms of both the structure and the economy.

The pusher-type harvesting device 12 of the present invention is not limited to a combine harvester, and is also applicable to a pusher-type harvesting device 12 equipped in various types of harvesters other than a combine harvester.

[ other examples ]

(1) In the harrow roll drive structure, the driven pulley 85 may be pin-connected to the roll drive shaft 31 so as to be able to change its position according to the axial position of the drive pulleys 84a and 84b, and the drive belt 83 may be wound in a non-twisted state.

(2) A pair of driven pulleys 85 opposed to the driving pulleys 84a and 84b may be mounted in parallel on the drum drive shaft 31, and the driving belt 83 may be wound around the driven pulleys without twisting.

(3) In the structure of the screw conveyor, the engaging projections 95 (105) may be provided so as to protrude from the inner surface of the receiving piece 32d (35 d), and the holes that engage with the engaging projections 95 (105) may be formed in the outer end surfaces of the bearing members 93 (103), so that the bearing members 93 (103) and the support members 97 (107) may be engaged with the engaging projections 95 (105) fixed to the spool frame side.

(4) The shapes of the pair of bearing members 93 (103) and the pair of support members 97 (107) are not limited to the above embodiment, and may be, for example, vertical engagement on engagement surfaces passing through the axial center of the tine mounting shaft 33.

(5) In the above embodiment, the bearing members 93 and 42 and the support members 97 and 107 are used in common by setting the tine mounting shaft 33 and the pivot support shaft 101 of the rotation restricting arm 91 to the same diameter, but it is also possible to design the tine mounting shaft 33 and the pivot support shaft 101 to have different diameters.

(6) In the above embodiments, the general type combine is exemplified, but a semi-feeding type combine may be used.

Claims (15)

1. A combine harvester is provided with:

a threshing device (3);

a feeder (6) connected to the front part of the threshing device (3);

a harvesting part (7) which is connected with the front end of the feeder (6) and is provided with a harvesting device (12), a spiral conveyor (13) for transverse feeding and a raking drum (10);

a feeder drive shaft (61) which is transversely arranged at the base end part of the feeder (6); and

an intermediate shaft (65) which is transversely arranged on the side of the front part of the feeder (6);

the above-mentioned combine-harvester is characterized in that,

the power is transmitted from the feeder driving shaft (61) to the intermediate shaft (65), and the power from the intermediate shaft (65) is transmitted to the harvesting device (12);

a rotation conversion mechanism (70) is provided on the intermediate shaft (65), and the rotation conversion mechanism (70) converts the rotation of the intermediate shaft (65) around the transverse axis into the reciprocating rotation around the axis in the front-rear direction;

a transmission shaft (74) for transmitting the reciprocating rotation of the rotation conversion mechanism (70) to the harvesting device (12), the transmission shaft extending from the back of the harvesting part (7) to the upper side of the harvesting device (12) from the rotation conversion mechanism (70) to the front when viewed from the side;

a swing arm (75) for driving a harvesting knife (12 a) of the harvesting device (12) to reciprocate extends upward from the harvesting device (12), the front end of the transmission shaft (74) is linked with the swing arm (75),

the rotation conversion mechanism (70) comprises a tilting head (71), a tilting hub (72) and a pair of fulcrum pins (72 a), wherein the tilting head (71) and the intermediate shaft (65) are formed as separate members, the tilting head (71) is connected with the intermediate shaft (65), and the tilting hub (72) is externally fitted on the tilting head (71) so as to be rotatable around a tilting axis (d) of the tilting head (71); the pair of fulcrum pins (72 a) are provided at the outer circumferential diagonal positions of the tilt boss (72);

the pair of fulcrum pins (72 a) are connected to the transmission shaft (74) via a yoke (73),

two first bearings are externally fitted to the tilt head (71) in an adjacent state, the tilt hub (72) is externally fitted to the two first bearings,

the intermediate shaft (65) and a screw conveyor drive shaft (67) of the screw conveyor (13) are linked together via a chain (68),

the intermediate shaft (65) protrudes to the lateral outer side of the outer side surface of the seedling dividing frame (11) equipped in the harvesting part (7), the inclined head (71) and a screw conveyor driving sprocket for the chain (68) are arranged on the part of the intermediate shaft (65) protruding to the lateral outer side of the outer side surface of the seedling dividing frame (11),

a second bearing is externally embedded on the part of the intermediate shaft (65) adjacent to the driving chain wheel of the screw conveyor,

the inclined head (71) is located laterally outward of the auger drive sprocket, and the second bearing is located laterally inward of the auger drive sprocket.

2. A combine harvester according to claim 1,

the tilt boss (72) holds the two first bearings and includes the pair of fulcrum pins (72 a).

3. A combine harvester according to claim 2,

a third bearing smaller than the first bearing is externally fitted to the fulcrum pin (72 a), and the yoke (73) is externally fitted to the third bearing.

4. A combine harvester according to claim 1,

the intermediate shaft (65) extends laterally outward from the back of the harvesting section (7), and the rotation conversion mechanism (70) is provided in the extension of the intermediate shaft (65).

5. A combine harvester according to claim 4,

the chain (68) is linked to an extension of the intermediate shaft (65) on the inner side of the machine body relative to the rotation conversion mechanism (70).

6. A combine harvester according to claim 5,

the transmission shaft (74) extends forward along the outer side surface of the seedling dividing frame (11) arranged on the harvesting part (7);

the chain (68) is arranged between the transmission shaft (74) and the outer side surface of the seedling dividing frame (11).

7. A combine harvester according to claim 6,

the power branched from the screw conveyor driving shaft (67) of the screw conveyor (13) is transmitted to the raking reel (10);

a relay shaft (81) is arranged between the screw conveyor driving shaft (67) and the roller driving shaft (31) of the raking roller (10);

the screw conveyor drive shaft (67) and the relay shaft (81) are linked and connected via a chain (82) at a position inside the machine body with respect to the transmission shaft (74) and outside the machine body with respect to the chain (68) that rotates the screw conveyor (13).

8. A combine harvester according to claim 7,

the swing arm (75) is arranged outside the seedling dividing framework (11);

the swing arm (75) and the harvesting device (12) are linked via a relay link (75 a).

9. A combine harvester according to any one of the claims 1-8,

the feeder driving shaft (61) extends along the left and right direction of the machine body;

the power transmitted to one end side of the feeder drive shaft (61) is transmitted from the other end side of the feeder drive shaft (61) to the intermediate shaft (65).

10. A combine harvester according to any one of claims 1 to 8,

a bevel gear box (57) is provided on the front side of the threshing device (3), and power from the working system of the engine (8) is transmitted to an input shaft (59) of the bevel gear box (57);

the threshing device (3) is provided with a processing roller (60) rotating around a front-rear direction axis, and the power transmitted to the input shaft (59) of the bevel gear box (57) is converted to be directed to the rear of the machine body in the bevel gear box (57) and is transmitted from the front side of the processing roller (60) to the front-rear direction axis;

the power input to the input shaft (59) of the bevel gear box (57) is transmitted to the feeder drive shaft (61).

11. A combine harvester according to claim 9,

a bevel gear box (57) is provided on the front side of the threshing device (3), and power from the working system of the engine (8) is transmitted to an input shaft (59) of the bevel gear box (57);

the threshing device (3) is provided with a processing roller (60) rotating around a front-rear direction axis, and the power transmitted to the input shaft (59) of the bevel gear box (57) is converted to be directed to the rear of the machine body in the bevel gear box (57) and is transmitted from the front side of the processing roller (60) to the front-rear direction axis;

the power input to the input shaft (59) of the bevel gear box (57) is transmitted to the feeder drive shaft (61).

12. A combine harvester according to claim 10,

the power of the working system is transmitted to an input shaft (59) of the bevel gear box (57) via an input shaft of the threshing device (3).

13. A combine harvester according to claim 11,

the power of the working system is transmitted to an input shaft (59) of the bevel gear box (57) via an input shaft of the threshing device (3).

14. A combine harvester according to claim 12,

the input shaft of the threshing device (3) is a windmill shaft (52) of the threshing device (3).

15. A combine harvester according to claim 13,

the input shaft of the threshing device (3) is a windmill shaft (52) of the threshing device (3).

Images