JP2005102589A - Reaping harvester - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To enable a lifting limit position of a reaping and conveying device to be set in a state of not being affected by the stretch of a conveying belt. <P>SOLUTION: A screw type lifting and lowering structure comprising a screw shaft and a female screw member, and an engine are connected through a transmission device. The transmission device has a friction-type transmission structure having a pressing plate 83A and a resin plate 83C between an output pulley 53 and a transmission shaft 82. The screw type lifting and lowering structure has a stopper structure for setting the lifting limit position of the reaping and conveying device 3. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a harvesting and harvesting machine in which a harvesting and transporting device is connected to a traveling machine body so as to be movable up and down around a horizontal axis.

  Conventionally, in the harvesting and harvesting machine as described above, the lifting and lowering operation of the harvesting and transporting apparatus is performed by hydraulic pressure (see Patent Document 1).

JP 2001-169642 A (paragraph number [0018] and FIG. 1)

  However, according to the above prior art, in addition to a piping system such as a hydraulic pipe and a joint, hydraulic equipment such as a hydraulic pump, a hydraulic cylinder, and valves is required, so that the manufacturing cost increases, and in particular, the price is reduced. Because there are aspects that are difficult to introduce in the desired small model, and it is necessary to periodically inspect oil and filters, etc., and to replace oil and filters as necessary, In addition to cumbersome maintenance work, maintenance costs have increased.

On the other hand, instead of such a hydraulic lifting mechanism, Japanese Patent Application No. 2001-271653 proposed a mechanism that uses a screw lifting mechanism.
Briefly describing this, as shown in FIGS. 15 and 16, the screw-type lifting operation mechanism 45 transmits power from the engine 38 to the chain-type transmission mechanism 51 via the lifting clutch mechanism 44. When the screw shaft 52 is driven to rotate forward by the power, the cutting and conveying device 3 is raised, the power from the engine 38 is cut off by the lifting clutch mechanism 44, and the screw shaft 52 is reversed by the weight of the cutting and conveying device 3. The cutting and conveying device 3 is lowered, and the screw shaft 52 stops rotating when the brake arm 54 engages and engages with the output pulley 53 of the lifted clutch mechanism 44 in the cut state, so that the cutting and conveying device 3 is lifted and stopped. Has been. The lead angle of the screw shaft 52 and the female screw member 55 screwed to the screw shaft 52 is a large angle at which the screw shaft 52 can be reversed by the weight of the cutting and conveying device 3, that is, the weight of the cutting and conveying device 3 can be lowered. Is set to a large angle.

  From this configuration, when the operating lever is operated to the neutral position, the screw type lifting operation mechanism 45 allows the braking arm 54 to be joined to the output pulley 53 of the lifting clutch mechanism 44 by the biasing of the first spring 59, and By allowing the cutting operation of the tension arm 56 by the urging of the second spring 60, the cutting and conveying device 3 is stopped up and down, and when the operation lever is operated from the neutral position to the forward lowering position, the braking arm 54 is moved to the first position. The spring 59 is moved away from the output pulley 53 against the bias of the spring 59 and the screw shaft 52 is allowed to reverse due to the weight of the cutting and conveying device 3, so that the cutting and conveying device 3 is lowered. When operated from the neutral position to the rearward raised position, the tension arm 56 is entered and operated against the bias of the second spring 60, and the screw shaft 52 is rotated forward by the power from the engine 38. In, and is adapted to increase the conveying device 3 reaper.

  That is, the lifting / lowering operation mechanism 45 is configured as a screw feed type in which the cutting and conveying device 3 is swung up and down by the normal rotation of the screw shaft 52 by the power from the engine 38 and the reverse rotation of the screw shaft 52 by the weight of the cutting and conveying device 3. Therefore, the manufacturing cost and the maintenance cost can be reduced and the maintenance can be facilitated as compared with the case of a hydraulic type that requires a hydraulic pump or a hydraulic cylinder.

As a stop structure at the ascending limit position in such a screw type lifting operation mechanism 45, the following configuration is adopted.
As shown in FIGS. 15 and 16, the machine body frame 12 has a balance arm 62 extending between the U-shaped fitting 61 provided on the cutting frame 13 and the tension arm 56 of the lifting clutch mechanism 44 around the axis P <b> 9 facing left and right. The balance arm 62 is swingably connected. When the cutting and conveying apparatus 3 reaches a predetermined height position, the end 62a on the cutting frame 13 side, which is one end side thereof, is pushed up by the U-shaped fitting 61. As the operation is performed, the end portion 62b on the side of the machine body frame 12 which is the other end side cuts and operates the tension arm 56 of the elevating clutch mechanism 44.

  That is, the balance arm 62 constitutes a mechanical linkage mechanism 63 that switches the lifting clutch mechanism 44 from the transmission state to the cutoff state in conjunction with the reaching of the cutting and conveying device 3 to a predetermined height position. As the cutting and conveying device 3 reaches the predetermined height position, the cutting and conveying device 3 can be automatically raised and stopped, and the linkage mechanism 63 is an electric type that requires a relatively expensive sensor or control device. The manufacturing cost can be reduced as compared with the case of the configuration.

  Reference numeral 64 shown in FIGS. 15 and 16 is an urging spring for urging the one end side 62a of the balance arm 62 against the U-shaped fitting 61. Reference numeral 65 shown in FIG. This spring is a spring that allows the tension arm 56 of the lift clutch mechanism 44 to be turned by the balance arm 62.

  Since the raising / lowering operation mechanism is configured as a screw feed type that raises and lowers the cutting and conveying device by forward and backward rotation of the screw shaft or the female screw member, it is not necessary to perform the raising and lowering operation of the cutting and conveying device by hydraulic pressure. Piping systems such as pipes and joints, and hydraulic equipment such as hydraulic pumps, hydraulic cylinders, and valves can be eliminated, and regular inspections of oil and filters, as well as oil and filter changes There is no need to perform such operations, and only maintenance of grease is required. Therefore, manufacturing costs and maintenance costs can be reduced and maintenance can be facilitated.

  However, in the case of adopting the above configuration, the balance arm 62 displaces the tension arm 56 of the elevating clutch mechanism 44 in a direction that weakens the tension force on the belt as the cutting and conveying apparatus 3 moves up. Therefore, when the belt itself is stretched due to long-term use or the like, the clutch may be disengaged at a position where the amount of displacement is smaller than the planned position of the tension arm 56, and the cutting and conveying device 3 is moved from the ascending limit position. In some cases, it was possible to stop only at a low position.

  An object of the present invention is to make it possible to reduce manufacturing costs and maintenance costs and facilitate maintenance.

〔Constitution〕
In order to achieve the above object, in the invention according to claim 1 of the present invention, the screw type lifting operation mechanism and the driving unit are linked via a transmission device, and the transmission device is connected to a rotary transmission body and a transmission. A frictional transmission mechanism having a frictional transmission mechanism interposed between the shaft and a stopper mechanism for setting a rising limit position of the cutting and conveying device is provided in the screw type lifting operation mechanism. The effects are as follows.

[Action]
According to the first aspect of the present invention, since the transmission device includes the friction transmission mechanism, the power to the screw shaft is transmitted via the friction transmission mechanism, and the screw shaft is driven by the stopper mechanism. Since the rotation of the screw shaft stops when the ascent limit position is reached, slipping occurs in the friction transmission mechanism and the screw shaft is not forcibly rotated, and the cutting and conveying device can be maintained at the ascent limit position.

〔effect〕
Therefore, as described above, the lift limit mechanism is not affected by the belt elongation, unlike the case where the lift limit mechanism is turned off and the lift limit position is maintained. Since only a transmission mechanism of the type is provided, the configuration can be simplified and the manufacturing cost can be reduced.

〔Constitution〕
In order to achieve the above object, in the invention according to claim 2 of the present invention, the transmission device is provided with a brake mechanism for stopping the screw-type lifting operation mechanism. Street.

[Action]
According to the second aspect of the present invention, since the stopped state of the cutting and conveying apparatus can be maintained by the brake mechanism, the cutting and conveying apparatus can be stopped at an arbitrary height position.

〔effect〕
Therefore, the cutting and conveying device can be set at an arbitrary height to perform cutting and maintenance work, and there is no need to maintain a slipping state in the friction transmission mechanism.

〔Constitution〕
In order to achieve the above object, in the invention according to claim 3 of the present invention, in order to constitute the screw type lifting operation mechanism, the cutting and conveying device is moved up and down by forward and reverse rotation of a screw shaft or a female screw member, The lead angle of the screw shaft and the female screw member is set to a large angle that allows the weight reduction of the cutting and conveying device to be lowered, a lifting clutch mechanism is provided in the transmission device, and the lifting clutch mechanism is switched to a disconnected state. The reaping and conveying apparatus is configured to allow its own weight to be lowered, and the operation and effects thereof are as follows.

[Action]
According to the third aspect of the present invention, the lifting operation mechanism is configured as a screw feed type that lifts and lowers the cutting and conveying device by forward and backward rotation of the screw shaft or the female screw member. This eliminates the need for piping systems such as hydraulic pipes and joints, as well as hydraulic equipment such as hydraulic pumps, hydraulic cylinders and valves, and regular oil and filters. It is possible to reduce the manufacturing cost and maintenance cost as well as to facilitate the maintenance because there is no need to perform inspections, oil changes, filter changes, etc. Will be able to.

  In addition, since the lowering of the cutting and conveying apparatus can be performed by the weight of the cutting and conveying apparatus, the forward / reverse switching mechanism required when the cutting and conveying apparatus is moved up and down by driving the screw shaft or the female screw member forward and backward can be omitted. Thus, the configuration of the lifting operation mechanism can be simplified, and the manufacturing cost can be further reduced.

〔effect〕
Accordingly, the structure can be simplified, the manufacturing cost and the maintenance cost can be reduced, and the maintenance can be facilitated. In addition, the lifting operation mechanism can be more reliably prevented from being damaged due to the impact when the cutting and conveying apparatus is lowered and stopped. Therefore, it is possible to perform the descent stop operation of the cutting and conveying apparatus with higher accuracy.

  FIG. 1 shows an overall left side of a self-decomposing combine that is an example of a harvesting harvester, FIG. 2 shows an overall right side thereof, and FIG. 3 shows an overall plane thereof. A cutting and conveying device 3 is connected to a front left side of a traveling machine body 2 provided with a pair of crawler type traveling devices 1 so as to be movable up and down around a left and right axis P1. A boarding operation unit 6 having a driver's seat 5 and the like is formed, and a threshing process and a selection process are performed on the harvested cereals from the harvesting and transporting apparatus 3 at a position behind the harvesting and transporting apparatus 3 and the boarding operation unit 6 in the traveling machine body 2. A threshing device 7 for performing the above and the like is installed, and a waste straw cutting device 8 that shreds the waste straw from the threshing device 7 is provided at the left rear portion of the threshing device 7 in the traveling machine body 2. 7 on the right rear side of the threshing device 7 It is configured by arranging a bagging apparatus 11 packed in grain bag 10 the kernels carried over.

  As shown in FIGS. 1 to 5, the cutting and conveying apparatus 3 scoops up the planted cereals that have fallen on a cutting frame 13 that is supported by the body frame 12 of the traveling body 2 so as to be able to move up and down around a center axis P <b> 1 in the left-right direction. Three dividers 14, left and right pulling devices 15 that cause the planted cereals to fall down, the clipper-shaped reaping device 16 that cuts the planting side of the planted cereals, and the harvested cereals are conveyed backwards. However, a conveying device 17 that changes the posture from the vertical posture to the horizontal posture, and the like are provided so as to cut and convey two strips.

  As shown in FIG. 6, the threshing device 7 has a feed chain 18 disposed on the left outer side sandwiching the stock side of the harvested cereal from the transport device 17 and transporting it backwards, The handling cylinder 19 mounted on the left half of the device 7 rotates around the axial center P2 in the front-rear direction, so that the tip side of the harvested grain culm guided on the receiving net 20 by conveyance by the feed chain 18 is applied. The tangle 21 deployed in the lower left part of the barrel 19 is fed by the threshing process by supplying a sorting wind that rotates around the longitudinal axis P3 and flows toward the right. A wind sorting process is performed on a workpiece leaked from the mesh 20, and the swing sorting mechanism 22 disposed below the receiving mesh 20 is driven to swing in the left-right direction by the rotation of the front-rear drive shaft 23. As a result, the processed material supplied to the swing sorting mechanism 22 is conveyed to the right. The processed product is subjected to a sieve sorting process, and the No. 1 screw 24 disposed on the upper side in the sorting direction below the swing sorting mechanism 22 rotates around the axis P4 in the front-rear direction, thereby swinging. The grain that has leaked from the upper side in the sorting direction of the sorting mechanism 22 is conveyed toward the lifting conveyor 9, and the second screw 25 disposed on the lower side in the sorting direction below the swinging sorting mechanism 22 is directed forward and backward. , The mixture of grains and broken straw leaked from the lower side of the sorting direction of the swinging sorting mechanism 22 is conveyed toward the thrower-type treated product conveying mechanism 26, by rotating around the axis P5. The thrower blade 27 of the processed material transport mechanism 26 rotates integrally with the second screw 25 so that the mixed material is reduced onto the receiving net 20 and reprocessed.

  As shown in FIG. 2 and FIG. 6, among the processed materials, dust such as cut straw and straw scraps conveyed to the rear end of the swing sorting mechanism 22 without leaking from the swing sorting mechanism 22 7 is discharged from a dust outlet 28 formed on the right side on the boarding operation unit 6 side, whereby dust such as straw scraps discharged from the threshing device 7 falls on the uncut grain culm. Inconvenience can be reliably prevented, so that it is possible to avoid a decrease in sorting performance and sorting efficiency caused by the dust that has fallen on the uncut rice cake being fed to the threshing device 7 together with the harvested rice cake. ing.

  As shown in FIG. 7, the drainer cutting device 8 includes a locking pin 30 that is equipped on the first roll 29 that rotates about the axis P <b> 6 that faces in the left-right direction so that it can be withdrawn and retracted as it rotates. The pine needles are squeezed into the second roll 31 that rotates around the axis P7 that is adjacent to the first roll 29 and rotates about the left and right axis P7 by locking the right-and-left drainer from the feed chain 18 to the middle portion thereof. And the pine needle-shaped waste straw is rotated toward the rotary blade 33 that rotates around the fixed blade 32 and the left-right axis P8 by rotating the rolls 29 and 31. A cylinder-type cutter that cuts in order from the refracting edge of the exhaust straw by feeding it in is adopted, and by this, a disc-type cutter that receives the left-side exhaust straw as it is and chops it with multiple disks is adopted If you compare Thus, the left and right lengths of the arrangement space required for the arrangement of the waste straw cutting device 8 can be significantly reduced behind the threshing device 7, and the arrangement space of the bagging device 11 is increased in the left and right directions accordingly. Be able to.

  As shown in FIGS. 1 to 3, the bag filling device 11 has a mounting table 34 formed at the right rear portion of the traveling machine body 2 and a support frame 35 erected on the front portion of the mounting table 34 toward the rear. The left and right grain bags 10 supported by the left and right pair of left and right support rods 36 are connected to the conveying terminal of the lifting conveyor 9. A two-bag type that is guided and fed by a bifurcated discharge cylinder 37 is adopted, so that the bag-packing work efficiency can be improved as compared with the case of using a one-bag type.

  In short, since the rocking sorting mechanism 22 having a length longer than that of the handling cylinder 19 is arranged in the left-right direction, the threshing device 7 is compared with the case where the rocking sorting mechanism 22 is arranged in the front-rear direction. The front and rear lengths can be shortened, and the waste straw cutting device 8 provided at the left rear portion of the threshing device 7 employs a cylinder-type cutter that can save space. Since the two-bag type bag-packing device 11 capable of improving the bag-packing work efficiency is arranged in a horizontally long posture in which the grain bags 10 are arranged side by side on the right-side rear portion, without causing a reduction in work capacity, The front and rear length of the traveling machine body 2 on which they are mounted can be shortened and the weight can be reduced, so that the total length of the combine can be shortened and the total weight can be reduced. , Equipped with boarding driver 6 It can be loaded on a light truck bed even though it is a commercial type, and a ride-type combine with a high work capacity can be used even in fields such as mountainous areas where transportation is limited to light trucks due to road conditions. It can be used.

  As a result, there is no need to walk in a field that is muddy for harvesting and harvesting, as in the case of using a walk-type combine, and the alignment operation is performed to match the position of the harvesting and transporting device 3 and the position of the planted cereal to be harvested. Therefore, it is possible to reduce labor and improve workability when performing harvesting and harvesting work.

  Moreover, the imbalance of the left-right balance resulting from the storage amount of the bagging apparatus 11 produced when the threshing apparatus 7 and the bagging apparatus 11 are juxtaposed in the left-right direction can be avoided, and the heavy threshing apparatus 7 Since it is not necessary to equip the bagging device 11 with a balance weight in order to achieve a balance with the above, further weight reduction can be achieved while improving the stability of the airframe.

  Moreover, in order to shorten the overall length of the combine, it is not necessary to pack the space between the harvesting and conveying device 3 and the threshing device 7, so that it is necessary to change the harvested cereal straw to a suitable posture with respect to the threshing device 7. Can be ensured easily between the reaping device 16 of the reaping and conveying device 3 and the threshing device 7, so that the threshing process is not adversely affected and the reaped cereals are added to the threshing device 7. Manual pillow handling work can be performed well.

  As shown in FIGS. 2 to 5 and FIG. 8, an engine 38 is mounted below the driver seat 5 in the traveling machine body 2 with an output shaft 39 oriented in the front-rear direction, and the power from the engine 38 is The transmission is transmitted to the input shaft 42 of the transmission case 41 via the belt tension type main clutch 40, and is transmitted to the threshing device 7 via the belt tension type threshing clutch 43, and further, the belt tension type lifting clutch mechanism. Via the 44, the cutting and conveying device 3 is transmitted to a screw type lifting operation mechanism 45 that moves up and down.

  As shown in FIG. 9, in the transmission case 41, a gear-type transmission mechanism 46 that can switch the power transmitted to the input shaft 42 between forward power and reverse power and can shift the forward power in three stages. The transmission state in which the power after the shift from the gear-type transmission mechanism 46 is transmitted to the corresponding crawler type traveling device 1 corresponds to the cut-off state in which the power after the speed change is not transmitted to the corresponding crawler type traveling device 1. A pair of left and right side clutch brakes 47 and the like configured to be switchable to a braking state in which the crawler type traveling device 1 is braked and stopped are provided. Each side clutch brake 47 is urged to return to a transmission state by a spring 48.

  Each side clutch brake 47 has its operating arm 49 linked to an operating lever 50 (see FIGS. 1 to 3) mounted on the control tower 4 via a steering operation linkage mechanism (not shown). When the lever 50 is operated to the neutral position, both springs 48 are energized so that both the left and right crawler type traveling devices 1 are driven at a constant speed so that the operation lever 50 is moved straight. When operated in either the left or right direction from the neutral position, the corresponding side is switched from the transmission state to the cutoff state or the braking state against the bias of the spring 48 according to the operation amount, so that one of the crawler types A slow turning state in which the traveling device 1 is idled or a sudden turning state in which one of the crawler traveling devices 1 is braked and stopped appears.

  As shown in FIG. 4, FIG. 5, FIG. 8, FIG. 10, and FIG. In the screw type lifting operation mechanism 45, the power from the engine 38 as a driving part is transmitted to the chain type transmission mechanism 51 via the lifting clutch mechanism 44, and the screw shaft 52 is driven to rotate forward by the power so that the harvesting conveyance is performed. The device 3 is raised, the power from the engine 38 is cut off by the lifting clutch mechanism 44, and the screw shaft 52 is reversed by the weight of the cutting and conveying device 3 to lower the cutting and conveying device 3, and the lifting clutch mechanism 44 in the cut state The output shaft (an example of a rotational transmission body) 53 is configured to be a screw feed type in which the cutting and conveying device 3 is stopped up and down by stopping the rotation of the screw shaft 52 by engaging engagement of a braking arm 54 described later. The lead angle of the screw shaft 52 and the female screw member 55 screwed to the screw shaft 52 is a large angle at which the screw shaft 52 can be reversed by the weight of the cutting and conveying device 3, that is, the weight of the cutting and conveying device 3 can be lowered. Is set to a large angle.

  A transmission structure of the output pulley 53 that receives a driving force from the engine 38 via the lifting clutch mechanism 44 will be described. As shown in FIG. 10, an output pulley 53 is input to one end of a transmission shaft 82 slidably inserted in a cylindrical boss 85 supported in a state of penetrating the body frame 12, and an input of a chain transmission mechanism 51 is input to the other end. A sprocket 51A is attached.

  The friction transmission mechanism 83 will be described. As shown in FIG. 10, an oval transmission structure is provided at one end of the transmission shaft 82, and the transmission shaft end portion is positioned between the pair of large diameter pressing plates 83A and 83A and the large diameter pressing plates 83A and 83A. A small-diameter distance piece 83B is externally fitted so as to rotate integrally. The small-diameter distance piece 83 </ b> B may be integrally formed as a base end boss of the output pulley 53 as a part of the output pulley 53.

  The resin friction plates 83C and 83C are sandwiched between the pair of large diameter pressing plates 83A and 83A and the output pulley 53, and the large diameter pressing plates 83A and 83A and the friction plates 83C and 83C rotate integrally with the transmission shaft 82. The output pulley 53 is rotationally driven. The frictional force is determined by the biasing force of the spring 84 that presses the outer large-diameter pressing plates 83A and 83A.

  A brake mechanism 81 that stops the cutting frame 13 from swinging will be described. As shown in FIGS. 5 and 10, the braking arm 54 and the tension arm 56 of the lifting clutch mechanism 44 are linked to the operation lever 50 via a linkage mechanism 58 for raising and lowering operations including a linkage wire 57 and the like. The brake arm 54 is formed so as to be swingable integrally with a pair of left and right arm portions 54 </ b> A. The left and right arm portions 54 </ b> A and 54 </ b> A hold the brake pad, and the brake pad is attached to the output pulley 53. The braking force is activated by pressing. The left and right arm portions 54 </ b> A are biased by the first spring 59 in the direction of being pulled in the rotation direction of the output pulley 53. The tension arm 56 is urged by a second spring 60.

  From this configuration, when the operating lever 50 is operated to the neutral position, the lifting operation mechanism 45 allows the braking arms 54A and 54A to be joined to the output pulley 53 of the lifting clutch mechanism 44 by the biasing of the first spring. By allowing the cutting operation of the tension arm 56 by the urging of the second spring 60, the cutting and conveying device 3 is lifted and stopped, and when the operation lever 50 is operated from the neutral position to the forward lowering position, the braking arm 54 is moved. By moving away from the output pulley 53 against the bias of the first spring and allowing the screw shaft 52 to reversely rotate due to the weight of the cutting and conveying device 3, the cutting and conveying device 3 is lowered, and conversely, the operation lever 50 Is operated from the neutral position to the rear ascending position, the tension arm 56 is entered against the bias of the second spring 60, and the screw shaft 52 is rotated forward by the power from the engine 38. By causing, so as to increase the transport device 3 reaper.

  That is, the lifting / lowering operation mechanism 45 is configured as a screw feed type in which the cutting and conveying device 3 is swung up and down by the normal rotation of the screw shaft 52 by the power from the engine 38 and the reverse rotation of the screw shaft 52 by the weight of the cutting and conveying device 3. Therefore, the manufacturing cost and the maintenance cost can be reduced and the maintenance can be facilitated as compared with the case of a hydraulic type that requires a hydraulic pump or a hydraulic cylinder.

  As shown in FIGS. 4, 8, 10, and 11, the lifting operation mechanism 45 supports a female screw member 55 and accommodates the screw shaft 52 when the cutting and conveying device 3 is lowered. Is equipped. The front end of the case 67 is pivotally supported by a support shaft 68 extending from the cutting frame 13, and grease 69 is enclosed. Further, a damper 70 is installed over the machine body frame 12 and the cutting frame 13 at substantially the same angle as the screw shaft 52.

The stopper mechanism 75 that sets the upper limit position of the cutting and conveying apparatus 3 will be described.
As shown in FIG. 11, a female screw member 55 is housed in a base end portion of a case 67 that is non-rotatably connected to the cutting frame 13, and the female screw member 55 is attached to and fixed to the case 67 to be non-rotatably supported. The case 67 is configured to slide and move the cutting frame 13 up and down by the rotation of the shaft 52. A thrust bearing 76 is fitted inside the case 67 further inside the inner end of the female screw member 55, and a washer-like plate 77 having a diameter larger than the screw shaft diameter is provided at the inner end located inside the case 67 of the screw shaft 52. It is attached.

With such a configuration, when the case 67 moves in the protruding direction by the rotation of the screw shaft 52, the washer-like plate 77 and the thrust bearing 76 come into contact with each other at the ascending limit position, and the sliding movement of the case 67 stops.
Here, a stopper mechanism 75 is constituted by a washer-like plate 77 and a thrust bearing 76. When the washer-like plate 77 and the thrust bearing 76 come into contact with each other, a resistance is given to the rotation of the screw shaft 52, and this resistance appears as a slip between the friction plate 83C on the lower transmission side and the output pulley 53, The cutting frame 13 stops at the ascending limit position.
Therefore, the ascent end position is not affected by the extension of the transmission belt that drives the output pulley 53.

  With this configuration, when the cutting and conveying device 3 is lowered, the damper 70 suppresses the weight reduction of the cutting and conveying device 3 to prevent a sudden lowering due to the weight of the cutting and conveying device 3, and the lowering of the cutting and conveying device 3. As the screw shaft 52 is accommodated in the case 67, the space 71 in the case 67 is narrowed, and the proportion of the grease 69 in the space 71 is increased, so that the cutting and conveying device 3 is moved to the working height position. Since the grease 69 becomes a resistance when the screw shaft 52 is housed in the case 67 and the weight of the cutting and conveying device 3 is reduced, the working height position of the cutting and conveying device 3 is increased. It is possible to effectively prevent a sudden lowering due to its own weight, so that the lowering and stopping of the cutting and conveying device 3 at the desired work height position can be accurately performed without generating a large impact. It has become.

As shown in FIGS. 9 and 12 to 14, the left and right side clutch brakes 47 are connected to the operation arm 49, the left and right crank arms 97 that swing integrally around the support shaft 96, and the third linkage mechanism 102. It is linked to an operation pedal 103 provided in the control unit 6.

  The third linkage mechanism 102 includes a support shaft 104 that supports the swingable pedal 96 by stepping on the operation pedal 103, a balance arm 105 that is swingably supported by the right support shaft 96, and the support shaft 104 and the balance arm 105. The linkage pins 107 mounted on the balance arm 105 press and operate both the left and right crank arms 97 when the operating pedal 103 is depressed by the linkage springs 106 and the like installed, and the left and right side clutch brakes 47 The shut-off state and the braking state are displayed.

  Further, the control unit 6 is engaged with an engagement pin 108 provided on the operation pedal 103 to hold the operation pedal 103 in the depressed position and maintain the left and right side clutch brakes 47 in a braking state. 109 is equipped.

  In other words, the left and right side clutch brakes 47 can be used both as a traveling brake and a parking brake, so that the configuration can be simplified and the manufacturing cost can be reduced as compared with the case where the traveling brake and the parking brake are equipped. It is like that. In addition, a simple operation of simply depressing the operation pedal 103 has an advantage that a state in which the harvesting and conveying apparatus 3 is driven at a constant speed while stopping the traveling of the machine body can be realized.

  As shown in FIGS. 9 and 12 to 14, the left and right side clutch brakes 47 are connected to the operation arm 49, the left and right crank arms 97 that swing integrally around the support shaft 96, and the fourth linkage mechanism 111. The operation pedal 103 is linked to an operation lever 113 supported so as to be able to swing integrally around a support shaft 104 and to swing relative to a longitudinal support shaft 112.

  The fourth linkage mechanism 111 includes a balance arm 114 that swings integrally around the operation lever 113 and the support shaft 112, and one linkage wire 115 that extends from both ends of the balance arm 114 to the corresponding crank arm 97. In conjunction with the swinging operation in the direction, the side clutch brake 47 corresponding to the operation direction is switched to the transmission state, the cutoff state, and the braking state according to the operation position.

  That is, even from the dismounting position, by swinging the operation lever 113 left and right, the left and right crawler type traveling devices 1 are driven straight at a constant speed, and either the left or right crawler type traveling device 1 is idled. Switching between a slow turning state in which the other crawler type traveling device 1 is driven and a sudden turning state in which one of the left and right crawler type traveling devices 1 is braked and the other crawler type traveling device 1 is driven. Further, by swinging the operation lever 113 in the vertical direction, the traveling state, the cut-off state where transmission to both the left and right crawler type traveling devices 1 is interrupted, and the both left and right crawler type traveling devices 1 are The brake state to be braked can be switched and displayed.

Incidentally, the operation lever 113 is configured to be extendable and contracted, and the above-described switching operation from the dismounting position can be performed by extending the operation lever 113 against the bias of the spring 117 that contracts and holds through the linkage wire 116. It can be made easy to do. As a configuration for maintaining the operation lever 113 in the maximum extended state and the minimum contracted state, although not shown, a ratchet ball type engagement mechanism that urges the ball to the engagement hole with a spring is employed.
A reference numeral 118 shown in FIGS. 12 to 14 is a lock fitting that prevents the operation lever 113 from swinging relative to the operation pedal 103 by engaging with the operation lever 113.

  As shown in FIGS. 1 to 3, the relative positional relationship between the operation lever 113 and the divider 14 is as follows. That is, the grip portion 113A formed at the tip of the operation lever 113 is in a state where it does not protrude from the front end portion of the divider 14 in a state where it is contracted to the shortest. Accordingly, the combiner is not stored in the warehouse or the other lever and the operation lever 113 do not interfere with each other when being loaded on the truck, and the grip portion 113 does not interfere with the divider 14 even if it is swung downward. Because of this, the parking brake can be applied even on the truck loading itself.

  On the other hand, when the operation lever 113 is extended to the maximum, the grip portion 113A is positioned further forward than the front end of the divider 14, so that when the operation lever 113 is operated, the operator's feet are in the divider 14. Because it is further forward, the foot to be steered is wide and easy to operate.

[Another embodiment]
Hereinafter, other embodiments of the present invention will be listed.
(1) The lifting operation mechanism 45 may be equipped with an electric motor that drives the screw shaft 52 to rotate forward.
(2) As the raising / lowering operation mechanism 45, the case 67 may be configured to move up and down the cutting and conveying device 3 by rotating forward and backward together with the female screw member 55.
(3) The lifting operation mechanism 45 may be configured such that the screw shaft 52 side is supported by the cutting frame 13 and the case 67 side is supported by the body frame 12.
(4) The ascending / descending operation mechanism 45 may be configured not to be equipped with the case 67.
(5) As the friction transmission mechanism, a mechanism using a large number of friction plates or a wet type instead of a dry type may be used. As the friction plate, a metal plate with a resin coating or a roughened surface of the resin coating may be used.
(6) As the stopper mechanism 75, a stopper pin may be protruded into the internal space of the cylindrical case instead of the thrust bearing 76.

Combine left side view Combine right side view Overall plan view of combine Longitudinal side view of the main part showing the lifting and lowering operation structure of the cutting and conveying device Rear view of the main part showing the lifting and lowering operation structure of the cutting and conveying device Longitudinal rear view showing configuration of threshing device Longitudinal side view of waste straw cutting device Expanded sectional view showing a part of the transmission structure Configuration diagram of transmission structure of mission case Rear view showing friction transmission mechanism and brake mechanism Longitudinal side view showing screw type lifting mechanism Side view showing the operating mechanism when getting off the vehicle Plan view of FIG. Rear view of FIG. Side view showing conventional structure Rear view of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 2 Traveling machine body 3 Cutting and conveying apparatus 44 Lifting clutch mechanism 45 Screw type lifting operation mechanism 52 Screw shaft 55 Female screw member 75 Stopper mechanism 81 Brake mechanism 82 Transmission shaft 83 Friction transmission mechanism

Claims (3)

A harvesting and harvesting machine connected to a traveling machine body through a screw-type lifting operation mechanism so as to be able to move up and down.
The screw type lifting operation mechanism and the driving part are linked via a transmission device, and the transmission device is provided with a friction type transmission mechanism in which a friction transmission mechanism is interposed between the rotary transmission body and the transmission shaft. A harvesting and harvesting machine provided with a stopper mechanism for setting a rising limit position of the harvesting and transporting device in the screw type lifting operation mechanism. The harvesting and harvesting machine according to claim 1, wherein the transmission device is provided with a brake mechanism for stopping the screw type lifting operation mechanism. The screw-type lifting operation mechanism is configured to raise and lower the cutting and conveying device by forward / reverse rotation of a screw shaft or a female screw member, and to reduce the lead angle of the screw shaft and the female screw member to lower the weight of the cutting and conveying device. 3. A lift angle clutch mechanism is provided in the transmission device, and the lift clutch mechanism is switched to a cut-off state so that the weight reduction of the cutting and conveying device is performed. Harvesting machine.

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