JP2006271240A - Driving structure of reaping part of combine harvester - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a driving structure of a reaping part of a combine harvester, capable of conducting good reaping operation during harvesting work and capable of previously avoiding occurrence of spillage of grains when traveling of the combined harvester is suspended. <P>SOLUTION: This combine harvester is structured so that the reaping part is driven at a prescribed speed regardless of a traveling speed, wherein the combine harvester is equipped with a detection means for detecting a suspended state of the traveling, a clutch operation means for automatically operating engagement and disengagement of a reaping clutch which is mounted on a driving system of the reaping unit, and an automatic clutch control means for automatically operating the reaping clutch to be disengaged by actuating the clutch operation means, when the detection means detects the suspended state of the traveling. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a reaping portion drive structure useful mainly for a full throw-in type (ordinary type) combine.

The harvesting part drive structure in the combine is as follows: (1) In a full throw type combine, the engine power is branched into a traveling system and a working system, and the threshing device and the harvesting part are driven by the power of the working system. And a configuration in which the mowing unit is driven at a constant speed irrespective of the traveling speed (see, for example, Patent Document 1), and (2) in a self-removing combine, there is no hydraulic type. A configuration in which the traveling device and the cutting unit are driven in synchronization with a shift output from the step transmission (see, for example, Patent Document 2), and (3) the cutting unit is driven at a speed synchronized with the traveling speed and travels at a low speed. In the area, a configuration has been developed in which the cutting unit is configured to be driven at a constant speed unrelated to the traveling speed (see, for example, Patent Document 3).
Japanese Patent Laid-Open No. 11-266670 JP 2004-224122 A JP 2004-65015 A

  In the cutting part drive structure according to the above (1) or (3), the cutting part is driven at a predetermined speed even when traveling at a low speed, so that the cutting apparatus can be driven at a speed that does not degrade the cutting performance. It was possible to perform good harvesting, but it was equipped at the front end of the harvesting section when the cutting operation of the harvesting clutch was delayed when the traveling was stopped during harvesting work or at the start of harvesting. There is a possibility that the rake and the pulling device unnecessarily add a scraping action or a pulling action to the uncut crop and cause degranulation.

  On the other hand, in the cutting part drive structure of (2) above, since the driving of the cutting part is stopped simultaneously with the stop of traveling, it does not cause degranulation as described above at the time of stopping traveling. When traveling at a low speed, the cutting device is also driven at a low speed, and the cutting performance may be greatly reduced.

  The present invention has been made paying attention to such points, and can perform good cutting during the harvesting operation, and can also prevent the occurrence of shedding at the time of stoppage in advance. The object is to provide a drive structure.

  According to a first aspect of the present invention, in a combine configured to drive the mowing unit at a predetermined speed regardless of the traveling speed, the detecting means for detecting the traveling stop state and the mowing clutch provided in the transmission system to the mowing unit are automatically turned on and off. Clutch operating means for operating, and automatic clutch control means for operating the clutch operating means to automatically disengage the cutting clutch when the detecting means detects a travel stop state.

  According to the above configuration, during normal harvesting traveling, the mowing device of the mowing unit is driven at a predetermined speed without degrading the cutting performance, and accurate mowing is performed. Further, when the traveling is stopped during harvest traveling or at the time of harvesting, the transmission to the mowing unit is automatically stopped in conjunction with this, and an unreasonable scratching action or raising action is not added to the uncut crop.

  Therefore, according to the first invention, it is possible to perform good cutting during the harvesting operation, and it is possible to avoid the occurrence of grain loss when the traveling is stopped.

According to a second invention, in the first invention,
Selection means for artificially turning on and off the control operation of the automatic clutch control means is provided.

  According to the above configuration, when the automatic clutch control means is selected and set in a state in which the control operation can be performed, the above-described automatic cutting clutch cut-off control associated with the stoppage of travel is executed, but the automatic clutch control means cannot be controlled. If it is selected and set, the mowing unit will continue to be driven even if the running is stopped, so in the case of a full-throw-in type combine, the crop that has been hand-harvested to form the headland is supplied to the mowing unit. Work to send to the threshing device, so-called pillow threshing work can be easily performed.

According to a third invention, in the first or second invention,
A cutting reel that scrapes the planted crop into the cutting part and a changing device that changes the rotation speed of the cutting reel are provided, and the cutting clutch is operated by the automatic clutch control means before the clutch is operated. The transmission is configured to be decelerated and controlled.

  According to the above configuration, the scraping reel can be arbitrarily shifted to perform the scraping suitable for the crop situation, and when the scraping reel is operating at a high speed even when the stoppage of travel is detected, Since the cutting operation of the mowing clutch is executed after the deceleration control is performed, it is possible to avoid damage to the reel drive system due to the sudden stop of the scraping reel having a large rotational inertia while rotating at high speed. .

  FIG. 1 shows the entire side surface of the combine according to the present invention, and FIG. 2 shows the entire plane. The combine includes a traveling unit 2 having a pair of left and right crawler traveling devices 1, a driving unit 3 with a cabin, an axial flow type threshing device 4 configured in a full throwing type, and a screw type unloader 5. A feeder 7 for transporting the harvested crops, which is mounted on the front part of the threshing device 4 so as to be swingable up and down around the fulcrum p, is disposed at the front end of the threshing device 4. A cutting part 8 having a cutting width of substantially the same width is connected to the left end side, and an engine 9 is arranged laterally below the operating part 3.

  As shown in FIG. 1, the crawler traveling device 1 raises and lowers a traveling ground surface with respect to the traveling machine body 2 by raising and lowering a track frame 82 on which a group of grounding wheels 81 are pivotally supported by a hydraulic cylinder 83. The left and right inclined postures of the traveling machine body 2 and the cutting unit 8 connected thereto can be changed by raising and lowering the ground contact surfaces of the left and right crawler traveling devices 1 separately. It is configured as follows.

  As shown in FIG. 1, a wide grounding body 84 that swings up and down following the ground is provided on the left and right of the lower end of the mowing unit 8, and the swinging position of the grounding body 84 is adjusted by a potentiometer or the like. A ground height detection sensor 85 that detects continuously is connected to a control device 87 that controls the operation of the electromagnetic valve 86 of the hydraulic cylinder 83. Based on the ground height detected by both detection sensors 85, the left and right inclination angle of the cutting unit 8 and the ground height (cutting height) are calculated, and the detected left and right inclination angle is adjusted and set by the angle adjuster 88. When the inclination angle deviates beyond the dead zone, the hydraulic cylinders 83 of the left and right crawler travel devices 1 are controlled to perform automatic rolling control that stably maintains the inclination angle of the cutting unit 8 at the target angle. . When the detected ground height deviates beyond the dead zone from the target height adjusted and set by the cutting height adjuster 89, the electromagnetic valve 90 of the hydraulic cylinder 14 is controlled to set the ground height of the cutting unit 8 to the target height. Automatic cutting height control for maintaining the cutting height stably is executed.

  The mowing unit 8 is provided with a mowing device 12 across a pair of left and right weeding frames 11 configured in a vertical wall shape, and an auger 13 that laterally feeds the harvested crop and sends it to the start end of the feeder 7. The cutting portion 8 is moved up and down integrally with the feeder 7 by the expansion and contraction operation of the hydraulic cylinder 14 installed between the feeder 7 and the traveling machine body 2. Further, a scraping reel 15 for scraping the planted crops backward is provided above the front portion of the cutting unit 8.

  Next, the structure of each part in the said feeder 7 and the cutting part 8 is demonstrated.

  As shown in FIGS. 6 and 7, the feeder 7 is configured by housing a scraping conveyor 18 inside a cylindrical transfer case 17 penetrating front and rear. This scraping conveyor 18 conveys a pair of left and right transports across a drive sprocket 20 of a feeder drive shaft 19 that is concentrically supported by the case base and concentrically with the fulcrum p, and an idler drum 21 that is horizontally supported rotatably at the front end of the case. The chain 22 is wound and stretched, and a transport bar 23 is constructed over the left and right transport chains 22, and the crop supplied to the crop inlet a at the front end of the case is placed under the transport chain 22. It is configured such that it is picked up and transported by a transport bar 23 in the path, transported from the crop outlet b at the base end of the case, and put into the beginning of the threshing apparatus 4.

  As shown in FIG. 7, a large-diameter cylinder 24 is interposed between the left and right drive sprockets 20 connected to the feeder drive shaft 19, thereby preventing winding of rags and weeds around the feeder drive shaft 19. Has been.

  The mowing device 12 has a clipper shape, and a mowing blade case 25 that reciprocates the movable blade is attached to the left weeding frame 11.

  As shown in FIG. 6, the auger 13 has a screw 27 that laterally feeds the harvested crop toward the crop inlet a side of the feeder 7 on the outer periphery of a large-diameter drum 26 that is rotationally driven in a certain direction from the front to the bottom. Are provided, and the two fingers on the left and right are equipped with the two fingering fingers 28 that move in and out as the drum rotates at the four circumferential positions of the outer periphery of the drum facing the crop inlet a. The harvested crops are configured to be laterally fed and forcedly fed into the crop entrance a of the feeder 7.

  Here, the lateral position of the lateral feed end portion of the screw 27, the lateral position of the scraping finger 28 that operates at the outermost lateral end of the group of scraping fingers 28, and conveyance in the scraping conveyor 18. The left and right positions of the both ends of the bar 23 substantially coincide with each other, so that the crop which is laterally fed by the screw 27 and then scraped back by the scraping finger 28 is smoothly fed to the crop entrance a. Then, the stagnation conveyor 18 is surely and smoothly delivered without stagnation or catching at the crop entrance a.

  Further, the outer periphery of the large-diameter drum 26 is separately equipped with an auxiliary scraping finger 28a that operates in a lateral feed operation area by the screw 27, and the auger 13 is located at a position away from the crop inlet a of the feeder 7 in the lateral direction. The crops that have fallen on the transport deck in front of are fed into the lateral feed action area of the screw 27 by the auxiliary take-up fingers 28a, and are sent to the action area of the thrust fingers 28 group under the lateral feed action of the screw 27. It is like that.

  As shown in FIG. 4, the take-up reel 15 is supported on the front part of a pair of left and right support arms 30 that can swing up and down around a fulcrum c via a support bracket 31, and is supported by a hydraulic cylinder 32. The height of the scraping action of the picking reel 15 can be changed by swinging up and down 30 and the position of the picking action is adjusted back and forth by sliding the support bracket 31 along the support arm 30. It is possible. The base of the support arm 30 is equipped with an operation arm 34 that is driven to swing back and forth around a fulcrum d by an electric cylinder 33 that is expanded and contracted by a DC electric motor M. The operation arm 34 and the support bracket 31 are also provided. Are coupled to the operation rod 35 and are configured to slide the support bracket 31 back and forth over a predetermined range by driving and swinging the operation arm 34 back and forth.

  The take-up reel 15 includes a reel drive shaft 36 horizontally supported by left and right support arms 30 via a support bracket 31, a regular hexagonal reel frame 37 connected to the left and right of the reel drive shaft 36, A rotary support shaft 38 that is horizontally supported so as to be able to rotate and rotate over the tops of six locations of the reel frame 37, a plurality of tines 39 that are mounted in parallel on the rotary support shaft 38 in the left-right direction, and a drive shaft center of the reel frame 37 a hexagonal auxiliary reel frame 40 supported rotatably about an eccentric shaft center f shifted rearward with respect to e, and fixedly extended rearward from the end of each rotary support shaft 38. The leading end of the arm 38a is pivotally connected to each top of the auxiliary reel frame 40, and the reel frame 37 is rotated (revolved) about the drive axis e. In conjunction with this, the auxiliary reel frame 40 is synchronously rotated in the same direction around the eccentric shaft center f, whereby each rotation support shaft 38 is rotated and rotated in the opposite direction with respect to the reel frame 37. Accordingly, the tine 39 of each rotating support shaft 38 is configured to revolve and maintain a downward posture while exhibiting a scraping action.

  Here, a tapered weeding tool 41 is attached to the front part of the right and left weeding frame 11 in the cutting part 8, and a bar-shaped guide member diagonally rearward on the outside and inside of each weeding tool 41. 42 and 43 are provided to smoothly push the uncut crop and the crop to be cut introduced into the cutting width. As shown in FIG. 8, the horizontal position of the rear end of the inner guide member 43 is located on the inner side of the horizontal position of the reel frame 37 in the take-up reel 15 and is the most laterally outer tine. 39 is located outside the left-right position. As a result, the planted crop at a position close to the inner surface of the weeding tool 41 is pushed inward by the guide member 43 to the cutting width, so that the crop is placed between the reel frame 37 and the weeding frame 11 on the take-up reel 15. In addition to avoiding being caught by the guide member 43, the crop pushed inward by the guide member 43 can be reliably scraped by the tine 39 that rotates without interfering with the guide member 43.

  Further, the lower end turning trajectory of the tine 39 is located near the ground in the state where the scraping reel 15 is lowered most, and in the state where the scraping reel 15 is adjusted most forward than the front end of the weeding tool 41. The forward movement limit of the take-up reel 15 is set so that the take-up reel 15 does not protrude forward.

  Next, the transmission structure to each part is demonstrated.

  As shown in FIG. 3, the power from the engine 9 is divided into a traveling system and a working system, and the traveling system power is input to a hydrostatic continuously variable transmission (HST) 45 and then shifted to a transmission case 46. Is transmitted to the left and right crawler travel devices 1. The power of the work system is divided into two systems, one of which is transmitted to the counter shaft 47 of the threshing device 4 via a tension type threshing clutch C1, and the other branching power is used for the hydraulic pump 48, air conditioning. Compressor 49, the unloading bottom screw 6a and the unloader 5 of the grain tank 6 are driven.

  The power transmitted to the countershaft 47 of the threshing device 4 is further divided into two systems, and one of the branching power is transmitted to each operating part of the threshing device 4 via the countershaft 47 and the other branching power is fed to the feeder. 7 and the cutting unit 8 are used for driving.

  That is, the counter shaft 47 and the right end (engine side) end of the feeder drive shaft 19 are belt-linked via the tension type mowing clutch C 2, and the feeder 7 is first scratched by the power input to the feeder drive shaft 19. The raising conveyor 18 is driven. Then, with the power extracted from the projecting end portion of the feeder drive shaft 19 to the left side of the machine body, the cutting unit 8 is disposed through the feeder 7 and the winding transmission mechanism 50 provided along the left outer surface of the cutting unit 8. The reaping device 12, the auger 13, and the take-up reel 15 are driven as follows.

  A mowing unit counter shaft 51, a reel transmission shaft 52, an auger support shaft 53, and the like are disposed on the left outer side of the mowing unit 8, and the left end portion of the feeder drive shaft 19 and the mowing unit counter shaft 51 are connected to each other. The reel transmission shaft 52 is wound and interlocked along the winding path of the chain 54 while being interlocked and connected via a chain 54. The cutting unit counter shaft 51 and the auger support shaft 53 are interlocked and connected via a chain 55, and the input shaft 56 and the cutting unit counter shaft 51 provided in the cutting blade drive case 25 are connected via a belt 57. Linked together.

  The reel transmission shaft 52 serves as an input shaft of a belt-type continuously variable transmission 58, and the transmission output taken out from the output shaft 59 of the continuously variable transmission 58 is decelerated and transmitted to the relay shaft 61 via the chain 60. After that, the speed is transmitted to the reel drive shaft 36 through the chain 62 at a reduced speed.

  As shown in FIG. 5, a large-diameter sprocket 63 to which the transmission output of the continuously variable transmission 58 is decelerated and transmitted via the chain 60 is loosely supported on the relay shaft 61, and the reel drive shaft is coupled via the chain 62. A small-diameter sprocket 64 that transmits power to 36 is fixed to the end of the relay shaft 61, and a clutch C3 that interrupts power transmission from the large-diameter sprocket 63 to the relay shaft 61 is provided. The clutch C3 is configured such that a movable clutch member 66 fitted on a spline so as to be shiftable to the relay shaft 61 is engaged with the large-diameter sprocket 63 from the axial direction. It is biased in the nail occlusion direction. Accordingly, when the movable clutch member 66 is engaged with the large-diameter sprocket 63, power is transmitted from the large-diameter sprocket 63 to the movable clutch member 66, the relay shaft 61 and the small-diameter sprocket 64 are driven and rotated, and the movable clutch member The power transmission is interrupted by 66 being reversely shifted against the spring 67.

  The movable clutch member 66 is engaged with a shift fork 68 that swings laterally around a vertical fulcrum g. A lever guide 69 is extended from the shift fork 68 to the left and right to operate a lever guide. By selectively locking one end of the U-shaped groove 70a of 70, the movable clutch member 66 can be switched and shifted between the clutch engagement position and the clutch disengagement position. Thus, when the clutch C3 is disengaged, the take-up reel 15 can be rotated forward and backward by hand, which can be used conveniently for removing clogging of the take-up reel 15 and replacing the tines 39.

  Here, the engagement claw 71 provided on the large-diameter sprocket 63 and the engagement claw 72 of the movable clutch member 66 are respectively formed with a transmission engagement surface sa and a climbing inclined surface sb, and the transmission engagement surface sa. The above-mentioned power transmission is performed by engaging each other, and the movable clutch member 66 on the driven side is reeled from the large-diameter sprocket 63 on the driving side by the climbing action of the climbing inclined surface sb. It is possible to rotate in advance in the driving direction F. That is, the clutch C3 is also configured as a one-way clutch in which the driven side can be rotated in advance in the normal reel driving direction.

  Accordingly, when the cutting clutch C2 is disengaged while the take-in reel 15 is being driven in, the large-diameter sprocket 63 is stopped by stopping the continuously variable transmission 58, but is interlocked with the take-in reel 15. The relay shaft 61 is reversely driven in the reel driving direction F due to the large rotational inertia of the take-up reel 15, and the movable clutch member 66 that receives this reverse driving force rides on the inclined surface sb. Due to the action, the spring 67 is retracted by its own force in the occlusion separation direction against the spring 67, and the inertial rotation of the take-up reel 15 is maintained. As a result, it is possible to prevent the take-up reel 15 having a large rotational inertia from being suddenly stopped, and it is possible to prevent the transmission member from being damaged in the chain transmission system in the lower transmission than the continuously variable transmission 58 or the chain 62 from coming off. It will be avoided. It should be noted that the fork groove 66a of the movable clutch member 66 is formed wide with a retreat margin so that the movable clutch member 66 can climb and retreat to the clutch disengagement position by itself as described above even when the shift fork 68 is in the clutch engagement position. ing.

  As shown in FIG. 4, the continuously variable transmission 58 is configured by winding a belt 77 around a variable-diameter pulley 75 on the driving side and a variable-diameter pulley 76 on the driven side, and has a detailed structure. Although explanation is omitted, a rotating cam mechanism (not shown) incorporated in the center of each variable diameter pulley 75, 76 is operated by a push-pull rod 79 that is screwed forward and backward by an electric motor 78 to change both variable diameters. It is configured to change the transmission ratio steplessly by changing the winding diameter of the pulleys 75 and 76 in a contradictory manner. The electric motor 78 can be freely rotated in the forward and reverse directions by operating a reel speed change switch 91 provided in the operation unit 3, and the driving speed of the take-up reel 15 can be arbitrarily set while observing the work situation. It is possible to change and adjust. The solenoid valve 92 of the hydraulic cylinder 32 for raising and lowering the reel and the electric cylinder 33 for adjusting the front and rear of the reel are adjusted by operating the reel up and down switch 93 and the reel front and rear adjustment switch 94 provided in the operation unit 3. It is possible to adjust the operating position of the insert reel 15.

  In addition, in the slack side path of the chain 62 that transmits the shift output of the continuously variable transmission 58 to the take-up reel 15, a tension mechanism that automatically absorbs the looseness of the chain 62 in response to a large front-rear position change of the take-up reel 15. 80 is provided.

  In the above transmission structure, in the present invention, the cutting clutch C2 that performs power connection to the feeder 7 and the cutting unit 8 is controlled as follows.

  As shown in the control block diagram of FIG. 9, the reaping clutch C <b> 2 is configured to be forcibly turned by an electric cylinder 95 connected to the control device 87 while being urged by a spring in the clutch engagement direction. The transmission case 46 is equipped with a rotation sensor 96 for detecting the traveling speed and is connected to the control device 87, and also includes a cutting clutch on / off switch 97 and an auto clutch on / off switch 98 provided on the operating unit 3. It is connected to the control device 87.

  As shown in the control flow chart of FIG. 10, when the auto clutch on / off switch 98 is selected to be “off”, the electric cylinder 95 is operated based on the operation of the clutch operation switch 97, and optionally the cutting clutch C2 Can be turned on and off (# 1 to # 5).

  When the automatic clutch on / off switch 98 is selected to be “ON”, when it is determined that the vehicle is running based on the detection information from the rotation sensor 96, the automatic cutting clutch on / off control is executed (# 1, # 6, # 7, # 5) When it is determined from the detection information from the rotation sensor 96 that the traveling speed is 0.05 m / s or less (considered as traveling stop), the automatic cutting clutch cut-off control is executed (# 1, # 6, # 8, # 4). In this case, if the drive speed of the take-up reel 15 detected from the operating position of the electric motor 78 is equal to or lower than a predetermined low speed set in advance, the mowing clutch automatic cut-off control is immediately executed. If the speed is higher than a predetermined low speed, the control for decelerating the scraping reel 15 is performed in advance (# 9), and then the automatic trimming clutch disconnection control is executed (# 4). In addition, after the automatic cutting clutch cut-off control is performed, when it is detected that the running has been resumed and the running speed has exceeded 0.05 m / s, the automatic cutting clutch engagement control is executed.

  [Other Examples]

  (1) In the above-described embodiment, the traveling drive system and the cutting unit driving system are completely independent, and the cutting unit 8 is driven at a predetermined speed regardless of the fast speed in the entire traveling speed range. However, when the cutting unit 8 is driven by the PTO power of the speed synchronized with the traveling speed taken out from the mission case 46, and the traveling speed V1 reaches a low speed range below the setting, the driving speed V2 of the cutting unit 8 is changed to the traveling speed V1. Is configured so as to have a constant speed Va that is not related to the driving speed, and during normal operation traveling, the cutting unit 8 is driven at a speed synchronized with the traveling speed V1, and when the harvesting operation is performed by traveling at a very low speed, The present invention can also be applied to a configuration in which driving is performed with driving characteristics (see FIG. 11) that are not driven unduly late.

  (2) The present invention is the same as the type installed in the self-removing combine harvester, and the type of full-pile thrower equipped with a cutting mechanism 8 and a transport mechanism for holding and transporting the harvested cereal grains in the auger. It can also be applied to type combine.

Left side view of the entire combine Top view of the entire combine Transmission system diagram Left side view of the cutting part Front view of partially cut-out clutch for take-up reel Plan view of auger and feeder start end Transverse plan view of feeder end Front view showing the left front end of the cutting part Control block diagram Cutting clutch control flow chart Characteristic diagram showing the relationship between the running speed and the cutting unit drive speed in another embodiment

Explanation of symbols

8 Mowing part 15 Take-in reel 58 Transmission C2 Mowing clutch

Claims (3)

  In a combine configured to be able to drive the cutting unit at a predetermined speed regardless of the traveling speed, a detecting unit for detecting a traveling stop state, a clutch operating unit for automatically turning on and off a cutting clutch provided in a transmission system to the cutting unit, A combine mowing unit drive structure comprising: an automatic clutch control unit that operates the clutch operating unit to automatically disengage the mowing clutch when the detecting unit detects a travel stop state.   2. The combine harvester drive structure according to claim 1, further comprising selection means for artificially turning on and off the control operation of the automatic clutch control means.   A cutting reel for scraping the planted crop into the cutting portion and a transmission for changing the rotation speed of the cutting reel are provided, and the cutting clutch is operated by the automatic clutch control means before the clutch is operated. The combine mowing unit drive structure according to claim 1 or 2, wherein the transmission is configured to be controlled to be decelerated.

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