JP2014033670A - Harvesting part drive structure of combine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a harvesting part drive structure of a combine capable of suppressing the vibration of a machine body during harvesting work as much as possible.SOLUTION: A harvesting part drive structure of a combine includes: a clipper-type harvester 21 located in the front of a harvesting part; a lateral input shaft 53 located in the back of the harvesting part; a rotation conversion mechanism 71 for converting the rotation power transmitted to the input shaft 53 from a power source into a reciprocatable rotation around a longitudinal axis; a longitudinal relay transmission shaft 72 that extends forward from the rotation conversion mechanism 71; an interlocking operation member 73 for interlocking and connecting the relay transmission shaft 72 and the harvester 21; and a balance weight 82 disposed in the outer circumference of the relay transmission shaft 72.

Description

  The present invention relates to a combine harvester drive structure for a combine equipped with a clipper-type harvesting device in a state of being located at a front portion of the harvester.

  In the conventional combine harvester drive structure, power is transmitted from the traveling machine body to the lateral input shaft located at the rear of the harvester, and the rotation of the lateral axis of the input shaft is reciprocated around the longitudinal axis. A rotation conversion mechanism that converts rotation, and a forward-reverse relay transmission shaft that transmits the reciprocating rotation power converted by the rotation conversion mechanism; a swing arm provided on the relay transmission shaft; and a reaping device; Have been configured to be interlocked and connected via a link (see, for example, Patent Document 1).

JP 2007-159466 A

  In the above conventional configuration, the clipper-type mowing device is driven by the reciprocating rotational power transmitted by the forward-reverse relay transmission shaft, and no slip or the like occurs when the belt transmission mechanism is used. The cutting performance of the reaping device is not likely to deteriorate, and the reaping device can be driven accurately.

  However, the clipper-type cutting device is a device that reciprocally drives a cutting blade that is long in the cutting width direction and has a large mass to the left and right, and the above-described conventional configuration results from the drive structure of the clipper-type cutting device. As a result, there is a high possibility that the aircraft will vibrate, and there is still room for improvement in this respect.

  When considering the vibration of the airframe accompanying the reciprocating drive of the mowing device, the inertial force based on the driving of the mowing blade in the mowing device is directly applied as a cantilevered load to the swing arm of the relay transmission shaft. Due to the inertial force, the relay transmission shaft may receive a driving reaction force in a direction opposite to the swinging direction of the swinging arm to vibrate the airframe, or the relay transmission shaft may be twisted around the axis.

  An object of the present invention is to provide a combine harvester drive structure for a combine that can suppress the vibration of the airframe during the harvesting operation and the load on the relay transmission shaft as much as possible.

  The first characteristic configuration of the combine harvester driving structure according to the present invention is a clipper-type harvesting device positioned at the front of the harvesting unit, a lateral input shaft positioned at the rear of the harvesting unit, and a power source. A rotation conversion mechanism that converts rotational power transmitted to the input shaft into reciprocating rotation around a front-rear axis, a front-rear relay transmission shaft that extends forward from the rotation conversion mechanism, the relay transmission shaft, An interlocking operation member for interlockingly connecting the reaping device and a balance weight provided on an outer peripheral portion of the relay transmission shaft are provided.

  According to the first characteristic configuration, the rotational power transmitted from the power source to the input shaft is converted into the reciprocating rotation around the longitudinal axis by the rotation conversion mechanism, and the reciprocating rotational power around the longitudinal axis is This is transmitted to the clipper-type mowing device via the forward-reverse relay transmission shaft and the interlocking operation member, and the mowing device is driven. And the balance weight is provided in the outer peripheral part of the relay transmission shaft.

  Thus, not only the weight of the cutting device but also the weight of the balance weight acts as an inertial force based on the driving of the cutting blade with respect to the relay transmission shaft that is driven to reciprocally rotate to drive the clipper type cutting device. It will be. The balance weight acts on the relay transmission shaft so that the load cancels the inertial force based on the driving of the cutting blade.

  As a result, the inertial force due to the driving of the cutting blade applied to the relay transmission shaft is balanced by the weight of the balance weight, and accordingly, the vibration of the relay transmission shaft can be suppressed and the reaping device is driven. It is possible to suppress the vibration of the airframe due to the operation, and to suppress the twist due to the inertial force of the cutting blade on the relay transmission shaft.

  Accordingly, it has become possible to provide a combine harvester drive structure for a combine that can suppress the vibration of the airframe during the harvesting operation and the load on the relay transmission shaft as much as possible.

  The second characteristic configuration of the present invention is that the balance weight is provided in an outer peripheral portion of the relay transmission shaft in a state extending along the axial direction.

  According to the second feature configuration, the balance weight is provided on the outer peripheral portion of the relay transmission shaft in a state extending along the axial direction, so that the size of the balance weight in the radial direction of the relay transmission shaft is suppressed to be small. However, the weight required for equalizing the load can be ensured.

  The third characteristic configuration of the present invention is that the balance weight is provided so as to extend across an end portion on the rotation conversion mechanism side and an end portion on the reaping device side of the relay transmission shaft.

  According to the third feature configuration, the balance weight is provided in a state of extending in the axial direction over the end portion on the rotation conversion mechanism side and the end portion on the reaping device side in the relay transmission shaft. By utilizing the outer periphery of the shaft over a wide range in the axial direction, the dimension of the balance weight in the radial direction can be made as small as possible and accommodated in a compact shape.

  According to a fourth feature of the present invention, the balance weight includes a plurality of legs extending along the radial direction of the relay transmission shaft at locations spaced apart in the axial direction of the relay transmission shaft, and the plurality of legs. And a laterally extending portion that connects the radially outer side ends of each other.

  According to the fourth feature configuration, when the balance weight is mounted on the outer periphery of the relay transmission shaft, it is only necessary to fix the plurality of legs to the relay transmission shaft, and the mounting is simplified, but the lateral extension is provided. By providing the portion, it is possible to secure the weight necessary to equalize the load on the relay transmission shaft.

  According to a fifth characteristic configuration of the present invention, the balance weight includes a pair of leg portions located at both ends in the axial direction of the relay transmission shaft, and an intermediate portion between the pair of leg portions on the end side. And an intermediate leg portion located in the section.

  According to the fifth characteristic configuration, the balance weight is fixed to the relay transmission shaft by the pair of end portions located at both end portions in the axial direction, so that it can be stably supported over a wide range. By providing an intermediate leg portion located in the intermediate portion between the end portion side leg portions, the intermediate portion is firmly fixed by fixing the intermediate portion even if the balance weight is elongated in the axial direction. Can be supported.

  A sixth characteristic configuration of the present invention is that the balance weight is provided with a plurality of intermediate leg portions at intervals along the axial direction.

  According to the sixth feature, a plurality of intermediate leg portions are provided at intervals along the axial direction, so that the balance weight can be supported more firmly.

According to a seventh characteristic configuration of the present invention, a weight unit body including a pair of the leg portions and a connecting portion that connects the radially outer side ends of the pair of the leg portions is arranged along the axial direction. A plurality of weight units are provided in a state of being arranged at intervals, and a weight coupling body that integrally couples the coupling portions of each of the plurality of weight unit bodies is provided,
The laterally extending portion is formed by the connecting portion and the weight connecting body of each of the plurality of weight unit bodies.

  According to the seventh characteristic configuration, the balance weight is configured by integrally connecting the connection portions of the plurality of weight unit bodies by the weight connection body. By constructing in this way, for example, when preparing multiple types of balance weights with different weights, it is possible to deal with by sharing the weight unit and using only the weight connected body with different weights, and sharing parts Thus, cost reduction can be achieved.

According to an eighth feature of the present invention, the rotation conversion mechanism includes an inclined head connected to an end of the input shaft, and an outer portion attached to the inclined head portion so as to be rotatable around the inclined axis of the inclined head. A fitted tilted boss, and a yoke that is formed in a substantially U shape in a side view of the body and is pivotally connected to the outer periphery of the tilted boss in a state of straddling the tilted boss,
The relay transmission shaft is connected to the yoke, and the rearmost leg portion of the balance weight is connected to the yoke.

  According to the eighth characteristic configuration, when the tilt head connected to the input shaft rotates along with the rotation of the input shaft, the tilt boss externally fitted to the tilt head portion relatively rotates around the tilt axis of the tilt head. Thus, the head swings in the forward and reverse directions. Then, since the yoke pivotally connected to the outer peripheral portion of the inclined boss in a state straddling the inclined boss reciprocates with the swinging operation of the inclined boss, the relay connected to the yoke via the yoke. The transmission shaft can be reciprocally rotated. Therefore, the rotation converting mechanism can convert the rotation of the input shaft into the reciprocating rotation of the relay transmission shaft without difficulty, and a smooth reciprocating drive suitable for a reaping device that reciprocates at high speed is possible.

  In addition, the balance weight legs on the rear side of the fuselage are fixed not only to the outer periphery of the relay transmission shaft, but also to the yoke, and the balance weight is firmly supported by effectively using the yoke manufactured with relatively high strength. can do.

  A ninth characteristic configuration of the present invention is that the leg portion on the rearmost side of the balance weight and the yoke are connected in a surface contact state.

  According to the ninth feature configuration, since the leg on the rearmost side of the balance weight and the yoke are connected in a surface contact state, the balance weight is contacted with the yoke in a stable and wide area by surface contact. By connecting in a state in which the balance is made, the balance weight can be supported in a strong and stable state.

  According to a tenth characteristic configuration of the present invention, the laterally extending portion is located on the radially outer side with respect to the radially outer end of the yoke.

  According to the tenth characteristic configuration, since the laterally extending portion is located on the radially outer side with respect to the radially outer end portion of the yoke, the rotation conversion mechanism comes into contact with another object when the outer object approaches. The balance weight comes into contact before. In other words, the balance weight can be effectively used to easily avoid the disadvantage that other objects come into contact with the rotation conversion mechanism and are damaged.

  An eleventh characteristic configuration of the present invention is that the interlocking operation member extends downward from the relay transmission shaft, and the balance weight extends upward of the relay transmission shaft. .

  According to the eleventh characteristic configuration, the interlocking operation member is fixedly extended downward from the relay transmission shaft, and the balance weight is fixedly extended upward from the relay transmission shaft. In other words, the drive reaction force against the load of the interlocking operation member is applied to the lower part of the relay transmission shaft, and the drive reaction force against the load of the balance weight is applied to the upper part of the relay transmission shaft. The load applied to the transmission shaft can be equalized in the circumferential direction. As a result, it is possible to suppress the vibration of the airframe due to the driving reaction force applied to the relay transmission shaft, compared to the case where only the driving reaction force is applied to the load of the interlocking operation member. Further, when the balance weight and the interlocking operation member are swung, it is possible to reduce the occupied width in the left-right direction of the machine body, and it is possible to provide a compact arrangement.

The twelfth characteristic configuration of the present invention is provided with an auger that gathers the harvested crops in the middle of the cutting width direction and discharges them to the rear in the cutting part,
The mowing device is located on the front side of the auger, and the input shaft is located on the rear side of the auger,
The rotation conversion mechanism is provided on one end side in the axial direction of the input shaft,
The relay transmission shaft is provided in a state extending in the front-rear direction across the rotation conversion mechanism and the vicinity of the reaping device.

  According to the twelfth characteristic configuration, the crops harvested by the harvesting device are gathered to the center of the trimming width direction by the auger located on the rear side of the harvesting device and discharged backward. This auger is provided with a large diameter in order to efficiently convey the harvested crop, and the relay transmission shaft is provided on one end side in the axial direction of the input shaft located on the rear side of the large diameter auger. The rotation conversion mechanism and the vicinity of the cutting device provided on the front side of the auger are provided in a state of extending in the front-rear direction. Thus, the balance weight can be effectively deployed by using the relay transmission shaft that extends long in the front-rear direction.

The thirteenth characteristic configuration of the present invention is configured to convey a crop from the rear part of the cutting part toward the threshing device at the rear part of the machine body, and includes a feeder that is narrower than the cutting part.
The said input shaft exists in the point provided along the back part located in a laterally outward rather than the connection location with the said feeder in the said cutting part.

  According to the thirteenth characteristic configuration, the crops gathered in the middle of the cutting width direction by the auger and discharged backward are conveyed toward the threshing device at the rear of the machine body by the feeder located behind the auger. This feeder is narrower than the cutting part, the connection part between the cutting part and the feeder is narrower than the horizontal width of the cutting part, and the rear part of the cutting part is formed laterally outside the connection part. become. And using this back surface part, the horizontal input shaft is provided in the state extended toward the side edge part of a cutting part.

A fourteenth characteristic configuration of the present invention includes a bearing device that rotatably supports an end portion of the relay transmission shaft on the front side of the machine body,
The interlocking operation member is provided at a location projecting forward of the fuselage from the bearing device in the relay transmission shaft,
The balance weight is provided between an end of the relay transmission shaft on the side of the rotation conversion mechanism and a portion supported by the bearing member.

  According to the fourteenth characteristic configuration, the end of the relay transmission shaft on which the interlocking operation member that drives the reaping device is provided is stably supported by the bearing device, so that the reaping device can be driven well. Yes. Further, the balance weight can be effectively deployed by utilizing the region between the end of the relay transmission shaft on the rear side of the machine body and the support portion by the bearing member.

It is a whole side view of a combine. It is a whole top view of a combine. It is a partially cutaway side view of a cutting and conveying part. It is a side view of a cutting part. It is a top view of a rotating reel. It is a rear view of a cutting part. It is a rear view which shows the transmission structure with respect to a cutting part. It is a vertical rear view of a torque limiter arrangement part. It is a vertical rear view which shows the transmission mechanism on an input shaft. It is a front view of a cutting drive part arrangement | positioning part. It is a top view of a cutting drive part arrangement | positioning part. It is a perspective view of a balance weight arrangement | positioning part.

Hereinafter, an ordinary combine which is an example of a combine according to the present invention will be described with reference to the drawings.
As shown in FIGS. 1 and 2, the combine harvests crops at the front of a traveling vehicle body 3 having a pair of left and right front wheels 1 and a pair of left and right rear wheels 2 that can be steered. A cutting and conveying unit 4 serving as a cutting and conveying device that conveys rearward is supported by a cutting and lifting cylinder 5 including a hydraulic cylinder as a lifting actuator so as to be driven up and down around a lateral fulcrum. The traveling vehicle body 3 is threshed by the boarding operation unit 7 covered by the cabin 6 on the front side, the threshing device 8 for performing the threshing process of the crops harvested by the cutting and conveying unit 4, and the threshing device 8. The grain tank 9 which stores the grain obtained by this, the engine 10 for a drive as a drive part, etc. are provided.

Next, the configuration of the cutting and conveying unit 4 will be described.
The harvesting and transporting unit 4 harvests crops to be planted with a predetermined trimming width, and harvests the harvested crops to the middle in the trimming width direction, and the harvested and gathered crops to the center at the rear of the aircraft The feeder 12 is configured to be conveyed toward the threshing device 8.

  As shown in FIGS. 2 and 3, the harvesting unit 11 is connected to the transport deck 13 that receives and transports the harvested crop, the pair of left and right side wall portions 14 </ b> R and 14 </ b> L located on the left and right sides of the transport deck 13, and the feeder 12. The cutting part frame 17 has a frame structure in which a rear side part 16 on the rear side in which an opening 15 is formed is fixed. Further, a divider 18 for weeding the planted stems into the cutting target stems and the non-cutting target stems in front of the left and right side wall portions 14R and 14L, and the non-cutting target stems in the laterally outer side of the cutting work area. A guide rod 19 for guiding is provided.

  In the cutting part 11, a lateral feed auger 20 that feeds and gathers the harvested crops to the middle part in the cutting width direction while being brought close to the upper side of the transport deck 13 extends over the left and right side wall parts 14R, 14L. A reaping device 21 is provided that is installed in a state of being erected and that cuts the stock of the crop along the front end of the transport deck 13. In addition, a rotary reel 22 is provided at an upper portion of the front part of the lateral feed auger 20 so that the tip side of a crop to be cut is scraped back.

  The lateral feed auger 20 is provided with a pair of left and right screw blades 24 that feed laterally toward the front end portion of the feeder 12 as it rotates to gather toward the center in the lateral width direction. At the same time, rod-shaped scrambling bodies 25 that are withdrawn from and retracted from the auger drum 23 are provided at a plurality of locations in the circumferential direction at locations facing the front end entrance of the feeder 12.

  As shown in FIG. 3, the scraping body 25 is accompanied by the rotation of the auger drum 23 with respect to the support shaft 25 </ b> A supported in a fixed position at a position eccentric with respect to the rotation axis of the auger drum 23. The auger drum 23 is supported so as to be rotatable, and the amount of protrusion from the outer periphery of the auger drum 23 changes as the auger drum 23 rotates.

  As shown in FIGS. 10 and 11, the cutting device 21 is configured in a clipper shape, and is provided with the fixed blade 21 </ b> A and the movable blade 21 </ b> B overlapping vertically, and the movable blade 21 </ b> B reciprocally slides laterally at a constant pitch. By being driven, the planted crop can be cut.

The rotary reel 22 is provided in a state of being supported by a pair of left and right support arms 26 extending forward from an upper portion on the base end side of the reaper part frame 17.
That is, as shown in FIGS. 4 and 5, a pair of left and right pentagonal reel frames 28 in a side view so as to be integrally rotatable with the left and right ends of the drive shaft 27 rotatably supported at the distal ends of the pair of support arms 26. The tine support members 29 are provided in a state of being laid over the pair of left and right reel frames 28 and being positioned one by one at the five tops. A plurality of tines 30 (scratching nails) are attached in a state of being arranged along the direction.

A well-structured posture holding mechanism 31 is provided to hold the posture so that the tine 30 extends downward from the tine support member 29 regardless of the rotation of the rotary reel 22.
Next, the posture holding mechanism 31 will be briefly described. As shown in FIGS. 4 and 5, a pentagonal auxiliary rotating body 32 is provided on one lateral outer side of the rotary reel 22 in a side view of the body. As the rotating reel 22 rotates, the auxiliary rotating body 32 is rotated around an axis P2 different from the rotating axis P1 of the rotating reel 22 by the driving force transmitted from the rotating reel 22 via the link 33. It is configured. Each tine support member 29 is supported so as to be rotatable relative to the reel frame 28 while being integrally rotated with the link 33. Then, a parallel quadruple link mechanism that connects the rotation axis P1, the rotation axis P2, and the rotation fulcrums on both sides of the link 33 to each other is formed, and the tine 30 of each tine support member 29 is used to rotate the rotation reel 22. Regardless, it is configured to hold a posture extending downward from the tine support member 29.

  A hydraulic cylinder 34 is connected to each of the pair of support arms 26 and the cutting part frame 17, and the pair of hydraulic cylinders 34 causes the pair of supporting arms 26 to move around the axis P <b> 3 on the rear base end side. The rotary reel 22 is supported to be movable up and down by swinging up and down.

  As shown in FIG. 5, the tine support member 29 is made of a metal pipe material, and the tine 30 is fastened and fixed to the tine support member 29 with bolts 35. A pair of adjacent tines 30 is made of metal. The structure is formed integrally with a spring material. That is, the heads of the pair of tines 30 are integrally connected by the connecting part 36, and the attached part 37 is formed in the connecting part 36, and the attached part 37 is applied to the tine support member 29 in the bolted state. It is configured to stop.

  Although not described in detail, the pair of tines 30 are integrally formed so as to be connected in series and hang downward through a helical coil spring portion 38. The coil spring portion 38 causes the bending displacement of the drooping rod-like portion 39 due to the reaction force of the planted cereal and the ground accompanying rotation of the rotary reel 22 by elastic deformation in the reduced diameter direction (or increased diameter direction). It is configured to absorb.

  In addition, the arrangement configuration of the plurality of tines 30 in each of the five tine support members 29 is the same, and the assembly unit in which the plurality of tines 30 are attached to the tine support member 29 has the same configuration in all five groups. To share. In this way, cost reduction is achieved by sharing the members. Incidentally, the plurality of tines 30 are arranged in a state where they are arranged at predetermined intervals in the cutting width direction on the basis of the left and right end portions of the rotary reel 22 so that the gap between the tine 30 is not increased near the end portions on both the left and right sides. Is provided. By configuring in this way, the mistake of scraping the planted stalks is prevented from occurring in the vicinity of the left and right ends of the rotary reel 22.

  As shown in FIG. 3, the feeder 12 is configured such that an engagement conveyance-type conveyance conveyor 41 is provided inside a conveyance case 40 formed in a rectangular tube shape. The conveyor 41 is provided with a pair of left and right endless rotating chains 43 that are wound around a drive sprocket (not shown) supported rotatably around a horizontal axis and a driven wheel body 42. . The conveying bar 44 is horizontally connected at a predetermined pitch across the pair of left and right endless rotating chains 43. When the endless rotating chain 43 is driven and rotated, it is laterally fed by the cutting unit 11. The cultivated crop is scraped and transported by the transport bar 44 in the transport case 40 and transported to be put into the threshing device 8.

  As shown in FIG. 3, a rectangular connection peripheral frame portion 46 that constitutes an opening 45 for connection with the cutting portion 11 is formed at the front end portion of the transport case 40 in the feeder 12. A lower frame portion 47 constituting a lower side frame portion of the peripheral frame portion 46 is provided, and the cutting lift cylinder 5 is connected via a square cylindrical support member 48 connected to the lower frame portion 47.

  As shown in FIG. 6, the back part 16 of the cutting part 11 to which the feeder 12 is connected is provided with square pipe-like frame members 49, 50 extending on the upper and lower side parts over the entire width in the lateral direction. In addition, an opening 15 for connection with the feeder 12 is formed in the back surface portion 16, and a region excluding the connection opening 15 is covered with a wall portion. On both the left and right sides of the connection opening 15, there are provided vertical reinforcing members 51 that are substantially U-shaped in plan view and extend in the vertical direction across the upper and lower frame members 49 and 50.

  As shown in FIGS. 3 and 6, a reinforcing plate 52 made of a plate material having a substantially L-shaped cross section is provided at a corner corresponding to the upper side of the opening 15 in the frame member 49 on the upper side. It is provided in a state where it is fixed to the part by welding. The reinforcing plate 52 is extended to a position slightly laterally outward from the vertical reinforcing members 51 on the left and right sides.

Next, a transmission structure for the cutting unit 11 will be described.
As shown in FIG. 6, the power of the engine 10 from the traveling vehicle body 3 side is stretched along the horizontal side of the feeder 12, and the feeder 12 of the cutting unit 11 Power is supplied to the input shaft 53 laid horizontally along the back surface portion 16 located on the right side.

  As shown in FIGS. 6 and 7, the power supplied to the input shaft 53 is transmitted through the auger transmission mechanism 54, the cutting blade transmission mechanism 55, and the reel transmission mechanism 56. The transmission system is configured to be supplied to the reaping device 21 and the rotary reel 22. The input shaft 53 extends along the lateral width direction of the vehicle body along the back surface portion 16, and is rotatably supported by the bearing member 57 so as to protrude laterally outward from the right side wall portion 14R.

  As shown in FIGS. 4, 7, and 8, the auger transmission mechanism 54 includes a drive sprocket 58 provided on the outer side of the bearing member 57 of the input shaft 53, and the auger drum 23 in the lateral feed auger 20. An endless rotating chain 61 for driving an auger is wound around a driven sprocket 60 provided on a driving shaft 59 that rotates integrally. The auger transmission mechanism 54 is provided with a torque limiter 62 that allows relative rotation when a torque greater than a set value is applied.

  As shown in FIG. 8, the torque limiter 62 is externally fitted so that the driven sprocket 60 is rotatable relative to the drive shaft 59 of the lateral feed auger 20, and is interlocked to rotate integrally with the driven sprocket 60 and the drive shaft 59. An occlusal portion 64 that engages with the member 63 along the axial direction is formed, and includes a spring 65 that presses and urges the driven sprocket 60 in the direction in which they engage.

  The torque limiter 62 engages against the biasing force of the spring 65 when the rotation of the lateral feed auger 20 is blocked by crops being jammed in the lateral feed auger 20 and a torque greater than the set value is applied to the drive shaft 59. The portion 64 is idle so as to allow relative rotation.

  In the torque limiter 62, when the idle rotation of the engagement portion 64 as described above occurs, the spring receiving member 66 that also serves as a set pressure adjusting member rotates due to the idle rotation, and the set pressure changes. It is configured not to do.

  That is, a screw portion 67 is formed at the shaft end portion of the drive shaft 59, and two nuts 68 for receiving and holding the spring receiving member 66 are attached to the screw portion 67. The screw portion 67 formed on the drive shaft 59 is formed with a screw so that the nut 68 does not loosen even when the idling as described above occurs.

  If the explanation is added, during the idling as described above, the rotation of the drive shaft 59 is stopped due to the clogging of the crops, etc., but the biting portion 64 is idling and the driven sprocket 60 continues to rotate. . At that time, as the driven sprocket 60 rotates, the spring 65 and the spring receiving member 66 may rotate. The nut 68 also tries to rotate by such continuous rotation, but the screw portion 67 is provided in such a shape that the nut 68 is screwed to the shaft end side (right side in FIG. 8) during the continuous rotation. Yes.

  Since the two nuts are arranged in a line, even if an idle rotation occurs and the nut 68 positioned on the spring receiving member 66 side tries to rotate so as to screw into the shaft end side (the right side in FIG. 8), The nut 68 does not rotate, and the position of the spring receiving member 66 does not change in the axial direction.

  Further, a plurality of gap adjusting plates (shim) 70 are provided between the spring receiving member 66 and the shaft step portion 69 formed on the drive shaft 59. When changing and adjusting the torque setting pressure, first, After removing the two nuts 68, the number of interval adjusting plates (shims) 70 is changed, and the two nuts 68 are mounted again and screwed to the spring side so that the spring receiving member 66 is moved to the spring side. The torque set pressure of the torque limiter 62 can be changed by moving to and tightening.

  As shown in FIG. 4, the cutting blade transmission mechanism 55 converts the rotation motion of the input shaft 53 around the horizontal axis into a reciprocating rotation around the longitudinal axis, and the rotation conversion mechanism 71. The relay transmission shaft 72 extending in the front-rear direction from the front to the rear, and the swing arm 73 as an interlocking operation member for interlockingly connecting the relay transmission shaft 72 and the reaping device 21.

  As shown in FIG. 9, the rotation conversion mechanism 71 includes an inclined head 74 connected to the end of the input shaft 53, and an inclined head portion 74 that can rotate around the inclined axis d of the inclined head 74. An externally fitted inclined boss 75 and a yoke 76 that is formed in a substantially U shape in a side view of the body and is pivotally connected to the outer peripheral portion of the inclined boss 75 in a state of straddling the inclined boss 75 are provided.

  That is, the inclined head 74 is externally fitted and attached to the right end portion of the input shaft 53 so as to be spline-engaged, and the screw portion 77 formed at the shaft end portion of the input shaft 53 is attached to the inclined head 74. The inclined head 74 is fixed by tightening two nuts 78 to the screw portion 77 from the outer side of the inclined head 74. With this configuration, the inclined head 74 is maintained in a favorable connection state with the input shaft 53.

  In other words, the power transmitted to the input shaft 53 is also transmitted to the lateral feed auger 20, which needs to be rotated in the direction opposite to the normal rotational direction in order to eliminate clogging of crops. Yes, the input shaft 53 may be driven in a reverse rotation state. Even if it is rotated in the reverse direction in this way, the inclined head 74 is spline-engaged, and the two nuts 78 are tightened so that no loosening occurs and the connected state is maintained well. It is done.

  Further, an inclined boss 75 is rotatably fitted around the inclined head 74 so as to be rotatable around the inclined axis d, and a pair of fulcrum pins 79 provided at the outer peripheral diagonal position of the inclined boss 75 A yoke 76 is attached so as to be relatively rotatable around the axis of the fulcrum pin 79. A relay transmission shaft 72 facing in the front-rear direction is integrally connected to the back portion of the yoke 76.

  As the input shaft 53 rotates about the lateral axis, the tilt axis d of the tilt boss 75 is swung forward and backward, and the tilt boss 75 is linked to the yoke 76 via a fulcrum pin 79 and a yoke 76. The relay transmission shaft 72 is reciprocally rotated at a predetermined angle.

  As shown in FIG. 4, the relay transmission shaft 72 extends forward and downward from the rotation converting mechanism 71 along the outer surface of the right side wall 14 </ b> R as one side wall. The end portion is rotatably supported by a bearing device 80 provided on the right side wall portion 14R. A swing arm 73 is connected to a tip end portion of the relay transmission shaft 72 that protrudes from the bearing device 80 toward the front side of the machine body in a spline-fit state so as to be integrally rotatable and radially extending.

  As shown in FIGS. 10 and 11, one end side of the relay link 81 is pivotally connected to the swing end of the swing arm 73 connected to the front end of the relay transmission shaft 72, and the other end side of the relay link 81 is the cutting device 21. Is pivotally connected to the movable blade 21B. That is, the swing arm 73 and the movable blade 21B are interlocked and connected via the relay link 81, and the movable blade 21B is reciprocated to the left and right with a fixed stroke by the reciprocating rotation of the relay transmission shaft 72. . Such a configuration in which the relay transmission shaft 72 such as the swing arm 73 and the relay link 81 and the reaping device 21 are linked together corresponds to the reaping drive unit K.

  As shown in FIGS. 4 and 12, a balance weight 82 is provided on the outer peripheral portion of the relay transmission shaft 72 so as to extend along the axial direction. The balance weight 82 is provided in a state extending over the end portion on the rotation conversion mechanism 71 side and the end portion on the cutting device 21 side of the relay transmission shaft 72.

  The balance weight 82 includes a plurality of leg portions 83 extending along the radial direction of the relay transmission shaft 72 at locations spaced in the axial direction of the relay transmission shaft 72, and radially outward ends of the plurality of leg portions 83. It is the structure provided with the laterally extending part 84 which connects parts. Moreover, as the leg part 83, the intermediate part located in the intermediate part of the leg part 83A of a pair of edge part side located in the axial center direction both ends of the balance weight 82, and these leg part 83A of a pair of edge part side Leg portions 83B, and a plurality (two in the example shown in FIG. 12) of intermediate leg portions 83B at intervals along the axial direction.

  A specific configuration will be described. As shown in FIG. 12, the balance weight 82 includes two weight unit bodies 85 and a weight coupling body 86 that couples the two weight unit bodies 85 to each other. Yes.

  The weight unit body 85 includes a pair of leg portions 83 extending in the radial direction of the relay transmission shaft 72 and a connecting portion 87 that connects the radially outer side ends of the pair of leg portions 83. Two weight units 85 are provided in a state of being arranged at intervals along the axial direction of the relay transmission shaft 72. Specifically, the weight unit body 85 has a shape obtained by bending a band plate material into a substantially U-shape (square U-shape).

  A weight coupling body 86 made of a flat strip-shaped metal material that couples the coupling portions 87 of the two weight unit bodies 85 together by welding and fixing is provided. The laterally extending portion 84 is formed by the connecting portion 87 and the weight connecting body 86 of each of the two weight unit bodies 85.

  Accordingly, the balance weight 82 includes four legs 83, of which the rearmost leg 83 and the foremost leg 83 correspond to the end leg 83A, and an intermediate portion thereof. The two leg portions 83 located at the position correspond to the intermediate leg portion 83B.

  As shown in FIG. 12, the leg 83 on the rear side of the machine body of the balance weight 82 is connected to the outer periphery of the relay transmission shaft 72 and is in surface contact with the outer surface of the bottom of the yoke 76 in the rotation conversion mechanism 71. It is connected and fixed by welding in the applied state. Further, as shown in FIG. 9, the radially outer end of the relay transmission shaft 72 in the balance weight 82 (the radially outer end face of the laterally extending portion 84) is the radially outer end of the yoke 76. It is provided in a state of being positioned radially outward from the portion.

  As shown in FIG. 12, the swing arm 73 is provided in a state of being fixedly extended downward from the relay transmission shaft 72, and the balance weight 82 is fixedly extended toward the upper side of the relay transmission shaft 72. It is prepared in the state to do. With this configuration, the inertia force based on the driving of the movable blade 21B applied to the relay transmission shaft 72 can be canceled by the weight of the balance weight 82, and the vibration of the relay transmission shaft 72 accompanying the driving of the reaping device 21 can be canceled. Can be suppressed.

Next, the reel transmission mechanism 56 will be described.
As shown in FIGS. 4 and 7, a first relay shaft 88 is provided along the lateral width direction of the vehicle body in a state positioned above the input shaft 53, and further positioned above the first relay shaft 88. In this state, a second relay shaft 89 is provided along the vehicle body width direction.

  The first relay shaft 88 is supported by a bearing member 91 fixedly supported by a support member 90 fixed to the rear side portion of the right side wall portion 14 </ b> R so as to be rotatable around a laterally rotating shaft core. A first reel endless rotating chain 94 is wound around a drive sprocket 92 provided on the input shaft 53 and a driven sprocket 93 provided on the first relay shaft 84.

  The second relay shaft 89 is rotatably provided on the same axis as the fulcrum shaft 95 that rotatably supports the support arm 26, the drive sprocket 96 provided on the first relay shaft 88, and the second relay. A second reel endless rotating chain 98 is wound around the driven sprocket 97 provided on the shaft 89.

  A belt continuously variable transmission 99 is provided across the second relay shaft 89 and the drive shaft 27 of the rotary reel 22. A transmission belt 102 for speed change is wound around a driving pulley 100 provided on the second relay shaft 89 and a driven pulley 101 provided on the driving shaft 27. Although not described in detail, the driving pulley 100 is configured as a split pulley type, and the driven pulley 101 is configured as a fixed pulley having a constant belt winding diameter to change the transmission ratio (transmission ratio). A belt continuously variable transmission 99 capable of supporting the above is configured.

  The transmission mechanism provided at one side of the cutting unit 11 as described above, that is, the lateral outer side of the lower portion of the transmission mechanism 55 for the cutting blade, the transmission mechanism 54 for the auger, and the transmission mechanism 56 for the reel. The portion is covered with a lower cover body 103 as a decorative cover, and the laterally outer portion of the belt continuously variable transmission 94 located on the upper side in the reel transmission mechanism 56 is covered with an upper cover body 104 as a decorative cover. It is covered (see FIG. 1).

As shown in FIGS. 4 and 10 to 12, the frame is located on the outer side portion of the right side wall portion 14 </ b> R in the cutting portion 11 and covers the lateral outer side portion and the lower side portion of the cutting drive unit K. A body 105 is provided.
The frame body 105 is composed of a plate material bent in a middle dent shape, and is formed in a state in which respective portions as will be described later are continuously connected by the bent plate material. The frame body 105 is formed of a thick metal plate material having high rigidity.

  The frame body 105 is formed with an outermost projecting portion 106 which is a vertically narrow surface in the front-rear direction in a state of projecting most laterally outward at a position located on the outer side of the cutting drive unit K. Has been. Then, in a state of being connected to the front side of the airframe of the most projecting portion 106, a front side inclination guide portion 107 which is a vertical surface extending in the vertical direction is formed in an inclined posture located on the front side of the airframe in plan view. Has been. Further, in a state of being connected to the rear side of the airframe of the most projecting portion 106, a rear side inclination guide portion 108 which is a vertical posture extending in the vertical direction is formed in an inclined posture that is located closer to the rear side of the airframe in plan view. ing.

  And as shown in FIG. 4, the bottom face part 109 is formed in the lowermost part of the frame body 105 in the state which covers the lower part of the cutting drive part K. As shown in FIG. The bottom surface portion 109 is formed by a rear side bottom surface portion 109a located on the rear side of the body and a front side bottom surface portion 109b connected to the front portion of the rear side bottom surface portion 109a. The front side bottom surface portion 109b is provided so as to be bent in a substantially L shape in a side view so as to be in a front rising inclination posture with respect to the rear side bottom surface portion 109a.

  Further, as shown in FIG. 10, a lower inclined guide portion 110 in an inclined posture is formed so that the lower side in the front view of the machine body is located on the inward side of the machine body so as to continue from the lower end part of the most protruding part 106 to the bottom surface part 109. Has been. As shown in FIG. 4, the lower side inclination guide part 110 is formed in a state of being connected to the lower end parts of the front side inclination guide part 107 and the rear side inclination guide part 108, and is formed as a substantially triangular inclined surface. ing.

  In this frame body 105, the front side mounting portion 111 formed at the front side end portion of the bottom surface portion 109 and the rear side mounting portion 112 formed at the rear side end portion are bolted to the right side wall portion 14R. It is fixed by.

  As shown in FIG. 11, a guide rod 19 provided on the laterally outer side of the right side wall portion 14R includes an inclined guide portion 19A extending from the divider toward the laterally outward rear side, and the inclined guide portion 19A. A laterally connecting portion 19B extending from the rear end portion toward the inboard side and having the inboard end portion fixed to the right side wall portion 14 is configured.

Specifically, the guide rod 19 is formed as an integral shape in which a circular pipe member is bent into a substantially L shape, and the inclined guide portion 19A and the laterally connecting portion 19B are connected in series, and one end portion and the other end portion thereof are formed. Each is attached and fixed to the side wall portion 14R. By configuring the guide rod 19 in this way, for example, the strength of the guide rod 19 is higher than that formed in a cantilever shape, and the guide rod 19 may come into contact with an external object other than the stem rod such as a rod. Will be difficult to break.
An inner guide rod 113 that guides the cutting target stem to the inside of the cutting work area is provided on the inner side in the lateral width direction of the side wall portion 14R.

  As shown in FIG. 11, the right guide rod 19 and the frame body 105 are provided in a state in which the positions of the lateral outer side end portions thereof are the same in a front view of the body. As described above, the strength of the guide rod 19 is increased, and the guide rod 19 can be used as a member for protecting the cutting drive unit K similarly to the frame body 105, and the cutting drive unit K is protected. The function to perform can be improved.

  The right guide rod 19 and the frame body 105 are provided so as to partially overlap in the front-rear direction. That is, as shown in FIG. 4, both are arranged in a state where the rear end side portion of the guide rod 19 and the front end side portion of the frame body 105 partially overlap in the front-rear direction. Specifically, the guide rod 19 is positioned on the upper side and the frame body 105 is positioned on the lower side so that they overlap in a side view. By configuring in this way, it can be arranged compactly in the front-rear direction, and both have the function of protecting against contact with external objects at the overlapping portion, so the function of protecting the cutting drive unit K is enhanced. be able to.

  As shown in FIGS. 1 and 2, the frame body 105 is provided in a state of projecting laterally outward from the laterally outward end position of the lower cover body 103. The body 103 has a function of protecting the body 103 from being damaged by contact with an external object.

[Another embodiment]
(1) In the above embodiment, the balance weight 82 includes two sets of weight unit bodies 85 in a state where the balance weights 82 are arranged at intervals along the axial direction, and the connecting portions of the two sets of weight unit bodies 85 are integrated with each other. However, instead of such a configuration, it may be configured to include three or more weight unit bodies 85, or instead of a configuration including a plurality of weight unit bodies, The balance weight etc. of the structure by which the some leg part spaced apart to the axial center direction of the relay transmission shaft 72 and the connection body which connects these leg parts integrally are integrally formed may be sufficient.

(2) In the above embodiment, the relay transmission shaft 72 is connected to the yoke 76 in the rotation conversion mechanism 71 and the leg 83 on the rearmost side of the balance weight 82 is connected to the yoke 76. The weight 82 may be provided at a location separated from the yoke 76.

(3) In the above embodiment, the balance weight 82 includes the plurality of leg portions 83 and the laterally extending portion 84 that connects the radially outward ends of the plurality of leg portions 83. Not only such a configuration but also a plate-like extension portion that is long in the axial direction of the relay transmission shaft 72 and extends in the radial direction, and a configuration having a massive weight portion on the radially outer side thereof Etc., and can be implemented in various forms. Further, the balance weight 82 may be configured to be narrow along the axial direction instead of being configured to extend long along the axial direction of the relay transmission shaft 72. What is necessary is just to be able to balance the load with 21.

(4) In the above embodiment, a normal combine is exemplified as a combine. However, the present invention can also be applied to a self-decomposing combine.

  The present invention can be applied to a combine equipped with a clipper type mowing device.

DESCRIPTION OF SYMBOLS 10 Motor | movement part 11 Mowing part 12 Feeder 16 Back surface part 21 Mowing apparatus 53 Input shaft 71 Rotation conversion mechanism 72 Relay drive shaft 73 Interlocking operation member 74 Inclination head 75 Inclination boss 76 Yoke 80 Bearing apparatus 82 Balance weight 83 Leg part 83A End side Leg portion 83B Intermediate leg portion 84 Horizontally extending portion 85 Weight unit body 86 Weight link body 87 Connection portion

Claims (14)

  A clipper-type mowing device located at the front of the mowing unit, a lateral input shaft located at the rear of the mowing unit, and rotational power transmitted from a power source to the input shaft. A rotation conversion mechanism for converting the movement, a forward and backward relay transmission shaft extending forward from the rotation conversion mechanism, an interlocking operation member for interlockingly connecting the relay transmission shaft and the reaping device, and the relay transmission shaft. Combine harvester drive structure provided with a balance weight provided on the outer periphery.   The combine harvester drive structure according to claim 1, wherein the balance weight is provided on an outer peripheral portion of the relay transmission shaft along an axial direction.   The combine harvester drive structure according to claim 2, wherein the balance weight is provided so as to extend across an end portion on the rotation conversion mechanism side and an end portion on the mowing device side of the relay transmission shaft.   A plurality of leg portions extending along a radial direction of the relay transmission shaft at locations spaced apart in the axial direction of the relay transmission shaft on the balance weight, and radially outer side ends of the plurality of leg portions 4. The combine harvester driving structure according to claim 2, further comprising a laterally extending portion for connecting the two.   In the balance weight, a pair of end-side legs located at both ends in the axial direction of the relay transmission shaft, and an intermediate-side leg located between the pair of end-side legs The harvesting part drive structure for a combine according to claim 4.   6. The combine harvester drive structure according to claim 5, wherein the balance weight is provided with a plurality of intermediate leg portions at intervals along the axial direction. A plurality of weight unit bodies each including a pair of the leg portions and a connecting portion that connects the radially outer end portions of the pair of leg portions are arranged in a line along the axial direction. And a weight connection body that integrally connects the connection portions of each of the plurality of weight unit bodies,
The combine cutting portion drive structure according to any one of claims 4 to 6, wherein the laterally extending portion is formed by the connecting portion and the weight connecting body of each of the plurality of weight unit bodies. A tilt head coupled to the end of the input shaft, a tilt boss externally fitted to the tilt head portion so as to be rotatable around a tilt axis of the tilt head, and a side surface of the body A yoke that is formed in a substantially U shape as viewed and is pivotally connected to the outer periphery of the inclined boss in a state of straddling the inclined boss;
The combine harvester drive structure according to any one of claims 4 to 7, wherein the relay transmission shaft is coupled to the yoke, and a leg portion on the rearmost side of the balance weight is coupled to the yoke. .   The combine cutting part drive structure according to claim 8, wherein the leg part on the rearmost part side of the balance weight and the yoke are connected in a surface contact state.   The combine cutting part drive structure according to claim 8 or 9, wherein the laterally extending portion is located on a radially outer side than a radially outer end of the yoke.   The said interlocking operation member is extended toward the downward side from the said relay transmission shaft, The said balance weight is extended toward the upper side of the said relay transmission shaft. Combined harvester drive structure. The mowing unit is provided with an auger that collects the harvested crops in the middle of the cutting width direction and discharges them to the rear,
The mowing device is located on the front side of the auger, and the input shaft is located on the rear side of the auger,
The rotation conversion mechanism is provided on one end side in the axial direction of the input shaft,
The combine harvester drive structure according to any one of claims 1 to 11, wherein the relay transmission shaft is provided in a state of extending in the front-rear direction across the rotation conversion mechanism and a portion in the vicinity of the harvesting device. While conveying crops from the rear part of the cutting part toward the threshing device at the rear of the machine body, a feeder having a narrower width than the cutting part is provided,
The combine cutting unit driving device according to any one of claims 1 to 12, wherein the input shaft is provided along a back surface portion located laterally outward from a connection point of the cutting unit with the feeder. Construction. A bearing device that rotatably supports an end portion of the relay transmission shaft on the front side of the machine body is provided,
The interlocking operation member is provided at a location projecting forward of the fuselage from the bearing device in the relay transmission shaft,
The combine harvester according to any one of claims 1 to 13, wherein the balance weight is provided between an end of the relay transmission shaft on the rotation conversion mechanism side and a support portion by the bearing device. Driving structure.

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