JP2008263865A - Combine harvester - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a combine harvester enabling the normal and reverse rotation of a reaping part with a simple structure at a low cost. <P>SOLUTION: A transmission case 36 is provided with a case input shaft 37 to which the driving power of an engine 20 is transmitted, and a threshing cylinder output shaft 38 directed in the longitudinal direction of the traveling machine body and engaged with the case input shaft 37 through a bevel gear mechanism 43 to transmit the driving power of the case input shaft 37 to the threshing cylinder 5a, and the case 36 is placed at the front side of the traveling body of the threshing apparatus 5. The transmission case 36 is provided with a reaping output shaft 39 engaged with the case input shaft 37 through the bevel gear mechanism 43 in a manner to be driven in a direction reverse to the rotational direction of the case input shaft 37. The case input shaft 37 to transmit the driving power of the normal rotational direction to the reaping input shaft 42 of the reaping part 10 is engaged with the reaping input shaft 42 with a normal rotation clutch 40. The reap output shaft 39 to transmit the driving power of the reverse rotational direction to the reaping input shaft 42 of the reaping part 10 is engaged with the reaping input shaft 42 through a reverse rotation clutch 41. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a case input shaft to which a driving force from an engine is transmitted, and a front and rear handling body linked to the case input shaft via a bevel gear mechanism so as to transmit the driving force of the case input shaft to a handling cylinder. The present invention relates to a combine provided with a transmission case equipped with a trunk output shaft on a front side of a traveling machine body of a threshing device.

Conventionally, there has been one disclosed in Patent Document 1 as the above-described combine.
The combine shown by patent document 1 is provided with the gear case (equivalent to a transmission case) attached to the front surface of the threshing apparatus. The gear case includes an input shaft protruding leftward, a gear transmission mechanism and a bevel gear mechanism housed in the gear case.
The input shaft is linked to the engine output shaft via a belt transmission mechanism, a first output shaft of a counter case, a first counter shaft, and a belt transmission mechanism. The gear case shifts the driving force of the input shaft by the gear transmission mechanism, changes the direction by the bevel gear mechanism, and transmits it to the handling cylinder.

  Conventionally, there has been one disclosed in Patent Document 2 as a power combiner that is capable of forward drive and reverse drive of a cutting part in a combine.

Patent Document 2 describes three types of power transmission mechanisms.
The first power transmission mechanism transmits the driving force of the output shaft of the engine to the input shaft of the counter case, transmits the driving force of the cutting output shaft of the counter case to the cutting input shaft of the cutting portion, A power switching mechanism provided inside is provided.
The power switching mechanism includes a gear provided on a cutting transmission shaft that transmits a driving force of the input shaft to the cutting output shaft and a reverse gear, and includes a slide gear provided slidably on the cutting output shaft. ing. When the gear of the cutting transmission shaft and the slide gear mesh with each other, the power switching mechanism transmits power in the forward rotation direction to the cutting input shaft, and is engaged with the reverse gear of the cutting transmission shaft. And the slide gear mesh with each other, power in the reverse direction is transmitted to the cutting input shaft.

The second power transmission mechanism transmits the driving force of the output shaft of the engine to the input shaft of the threshing device side transmission case via the drive shaft with a universal joint, and travels the driving force of the output shaft of the threshing device side transmission case. A cutting output shaft that is transmitted to the HST of the transmission case and provided in the threshing device side transmission case and a work output shaft that protrudes from the traveling transmission case are provided.
The reaping output shaft of the threshing device side transmission case transmits power to the reaping input shaft of the reaping portion via the one-way clutch and the forward rotating clutch. The work output shaft of the traveling mission case transmits power to the cutting input shaft via a cutting reverse clutch.
When the mowing forward rotation clutch is operated to be engaged, the normal rotation power is transmitted to the mowing input shaft, and when the mowing reverse rotation clutch is operated to be engaged, the reverse rotation power is transmitted to the mowing input shaft.

The third power transmission mechanism transmits the driving force of the output shaft of the engine to the input shaft of the threshing device side transmission case via the drive shaft with a universal joint, and the driving force of the harvesting output shaft of the threshing device side transmission case is transmitted. , The belt, the one-way clutch, and the forward-rotation clutch are transmitted to the cutting input shaft of the cutting portion, and the driving force of the cutting input shaft is transmitted to the cutting two shafts via the power switching mechanism. A bevel gear for forward rotation and a bevel gear for reverse rotation supported rotatably on the cutting input shaft, a bevel gear fixed to the cutting input shaft in mesh with the forward bevel gear and the reverse bevel gear, and a spline on the cutting input shaft And a fitted sliding member. When the sliding member is inserted into the groove portion of the forward rotation bevel gear, the power switching mechanism transmits the normal rotation power to the cutting two shaft, and when the sliding member is inserted into the groove of the reverse rotation bevel gear, Transmits the power of reverse rotation.

Japanese Patent Laid-Open No. 11-266670 (paragraphs [0021], [0022], FIGS. 1-4)

JP-A-2004-121123 (paragraphs [0016]-[0023], [0028], [0029], [0033], [0035], [0036], FIGS. 4, 6, and 8)

  In the combine, when the cutting portion is clogged, the clogging can be easily eliminated if the cutting portion can be driven in the direction of rotation opposite to the normal rotation direction that is driven during operation.

  When the above-described conventional technology is adopted to enable the forward / reverse drive of the mowing part, the entire forward / reverse switching mechanism is mounted on the transmission case or the mowing input shaft, or the reverse power is supplied from the driving transmission system. It will be equipped with a reverse transmission mechanism that takes it out and transmits it to the cutting input shaft. Then, the cost tends to be high due to the production and equipment of the forward / reverse switching mechanism and the reverse transmission mechanism. In addition, the structure of the entire transmission device tends to be complicated.

  An object of the present invention is to provide a combine capable of performing forward / reverse driving of a cutting portion at low cost and with a simple structure.

The first aspect of the present invention is a case input shaft to which a driving force from an engine is transmitted, and a longitudinal direction of the traveling machine body that is linked to the case input shaft via a bevel gear mechanism so as to transmit the driving force of the case input shaft to a handling cylinder. In a combine provided with a transmission case equipped with a barrel output shaft of the threshing device on the front side of the traveling machine body,
The transmission case is equipped with a cutting output shaft linked to the case input shaft via the bevel gear mechanism so as to be driven in a rotation direction opposite to the rotation direction of the case input shaft,
A positive rotation clutch is provided for interlocking the cutting input shaft with one of the case input shaft and the cutting output shaft so as to transmit the driving force in the positive rotation direction to the cutting input shaft of the cutting unit,
A reverse rotation clutch is provided for interlocking the cutting input shaft with the other of the case input shaft and the cutting output shaft so as to transmit a driving force in the reverse rotation direction to the cutting input shaft of the cutting portion.

According to the configuration of the first aspect of the invention, when the forward rotation clutch is operated in the on state and the reverse rotation clutch is operated in the disengaged state, the forward rotation clutch of the case input shaft and the cutting output shaft is interlocked. One driving force is transmitted to the cutting input shaft. Then, since the rotation direction of the case input shaft and the rotation direction of the cutting output shaft are opposite to each other due to the bevel gear mechanism, the cutting input shaft is driven to rotate forward.
On the other hand, when the forward rotation clutch is operated in the disengaged state and the reverse rotation clutch is operated in the engaged state, the driving force of the case input shaft and the harvesting output shaft, which is associated with the reverse rotation clutch, is input to the trimming input. Transmitted to the shaft. Then, since the rotation direction of the case input shaft and the rotation direction of the cutting output shaft are opposite to each other due to the bevel gear mechanism, the cutting input shaft is driven in reverse.

  As a result, even if the cutting portion is clogged, the bevel gear mechanism can be used as the rotation direction conversion means at a low cost while the cutting portion is driven in reverse to easily eliminate the clogging, and transmission The entire structure of the apparatus can be simplified and the weight can be reduced as much as possible.

  In the second aspect of the invention, the case input shaft and the cutting output shaft are arranged in the lateral direction of the traveling machine body with the handling cylinder output shaft interposed therebetween.

  According to the configuration of the second aspect of the invention, the case input shaft and the cutting output shaft are arranged in a straight line or in a state close to the lateral direction of the traveling machine body, and the size of the transmission case in the side view of the traveling machine body is minimized. Can do.

  Thereby, what is easy to eliminate clogging by driving the cutting part in reverse can be obtained in a simple state in which the transmission case is compactly arranged on the front side of the threshing device.

  In the third aspect of the invention, the reverse rotation clutch is kept in the engaged state by human operation.

  According to the configuration of the third aspect of the present invention, it is possible to obtain what can easily remove the clogging by driving the mowing part in the reverse direction in a state where it is easy to avoid the trouble caused by the reverse driving of the mowing part.

  In other words, if the mowing unit is driven reversely for a long time, an excessive force may be applied to the device of the mowing unit. According to the configuration of the third aspect of the invention, it is necessary to consciously maintain the reverse rotation clutch in the engaged state. As a result, when the mowing part is driven in reverse, it is easy to be careful not to make the reverse driving of the mowing part longer than necessary, for example, by intermittently switching to the engaged state of the reverse rotation clutch.

Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is an overall side view of a combine according to an embodiment of the present invention. FIG. 2 is an overall plan view of the combine according to the embodiment of the present invention. As shown in these drawings, a combine according to an embodiment of the present invention is configured to be self-propelled by a pair of left and right crawler traveling devices 1 and 1 and has a driving unit 3 equipped with a driver seat 2. A threshing device 5 and a grain bagging unit 6 provided with a traveling machine body, arranged side by side in the lateral direction of the self-propelled machine body on the rear side of the machine body frame 4 of the self-propelled machine body, and a feeder 11 at the front of the threshing device 5 Are connected to each other. This combine harvests grains such as rice and wheat and is configured as follows.

  In addition to the feeder 11, the mowing unit 10 includes a preprocessing device 13 in which a preprocessing frame 12 is connected to the front end of the feeder 11.

  The mowing unit 10 is in a descending work state in which the platform 14 located at the lower part of the pretreatment frame 12 is lowered near the ground by the vertical swinging operation of the feeder 11 with respect to the threshing device 5, and the platform 14 is raised above the ground. Ascend and descend to the raised non-working state. When the cutting unit 10 is moved down and the self-propelled machine body is driven, the pretreatment device 13 uses the pair of left and right dividers 15 and 15 located at the front part of the preprocessing frame 12 to establish the planted culm to be cut. The non-trimmed planted culm is weeded, and the clipper-shaped stalk is scraped into the rear side of the pretreatment frame 12 by the rotary reel 17 positioned above the trimming device 16. The reaping process is performed by the reaping device 16, and the reaped cereals are moved to the front side of the feeder 11 by the auger 18 located on the upper surface side of the platform 14, and the reaped cereals located on the front side of the feeder 11 are rotated integrally with the auger It feeds into the entrance (not shown) of the feeder 11 with the scraping bar 19 provided freely. The feeder 11 conveys the harvested cereal from the raking culm 19 to the rear end of the feeder 11 by a feeder conveyor 11a (see FIG. 3) located inside the feeder 11, and a discharge port ( The whole from the root of the harvested cereal to the tip is supplied to the handling room (not shown) of the threshing device 5 from the not shown.

  The threshing device 5 threshs the harvested cereal supplied to the handling room with a handling cylinder 5a (see FIG. 3) that rotates around the axis of the traveling machine in the front-rear direction. The threshing grains are supplied to the bagging tank 6a of the grain bagging unit 6.

  As shown in FIGS. 1 and 2, the grain bag filling unit 6 includes the bag filling tank 6 a and corresponds to each of two grain discharge cylinders 6 b arranged in the longitudinal direction of the traveling machine body of the bag filling tank 6 a. A bag support rod 6c provided below the bag filling tank 6a, a work deck 6d which is also disposed below the bag support rod 6c and provided on the machine frame 4 and serves as a bag receiving deck, and the machine frame 4 And an auxiliary deck 6e supported at the lateral end of the. The auxiliary deck 6e is supported so as to be swingable up and down, and is in a lowered use posture that protrudes horizontally from the machine body frame 4 to the lateral side of the traveling machine body, and rises and swings from the lowered use attitude along the vertical direction of the traveling machine body. Switch to the raised storage position.

  The self-propelled aircraft includes an engine 20 provided below the driver seat 2. FIG. 3 is a diagram of a transmission mechanism that transmits the driving force of the engine 20 to the traveling device 1, the threshing device 5, and the mowing unit 10. As shown in this figure, the traveling transmission portion of the transmission mechanism transmits the driving force of the output shaft 20a of the engine 20 to the input shaft 22a of the traveling transmission device 22 via the belt transmission mechanism 21, and this traveling shift is performed. The driving force of the output shaft 22 b of the device 22 is input to the traveling mission 23 and transmitted to the pair of left and right traveling devices 1, 1 through the traveling mission 23.

  The travel transmission 22 is connected to the case of the travel mission 23. The travel transmission 22 includes a variable displacement axial plunger type hydraulic pump including the input shaft 22a as a pump shaft, and an axial plunger type hydraulic motor driven by pressure oil from the hydraulic pump. It is configured. That is, the travel transmission 22 is a hydrostatic continuously variable transmission.

  The work transmission section of the transmission mechanism causes the output shaft 20a of the engine 20 to be linked to one end side of the tang drive shaft 26 of the threshing device 5 via the belt transmission mechanism 25, and the other end side of the tang drive shaft 26 is connected to the belt. The power take-off shaft 30 provided in the belt transmission mechanism 27 is linked to the first screw conveyor 28 and the second screw conveyor 29 of the threshing device 5 via the transmission mechanism 27, and the threshing device 5 is connected via the belt transmission mechanism 31. It is linked to the sorting device drive shaft 32.

  The work transmission unit of the transmission mechanism is configured to provide a driving force output from the output shaft 20a of the engine 20 to the belt transmission mechanism 25, the rotary drive shaft 26, and the other end side of the hot drive shaft 26. The power is transmitted to the case input shaft 37 of the transmission case 36 via the transmission mechanism 35, and the driving force of the case input shaft 37 is transmitted from the threshing output shaft 38 of the transmission case 36 to the handling cylinder 5 a. The driving force is transmitted to the cutting input shaft 42 of the cutting unit 10 through the forward rotation clutch 40 or through the cutting output shaft 39 of the transmission case 36 and the reverse rotation clutch 41. This power transmission will be described in further detail as follows.

  That is, as shown in FIGS. 2 and 4, the transmission case 36 is supported by the front wall portion of the threshing device 5 on the front side of the traveling machine body of the threshing device 5 and above the rear end portion of the feeder 11. It is provided. As shown in FIG. 3, the transmission case 36 includes the handling cylinder output shaft 38 arranged at the center of the transmission case 36 in the lateral direction of the traveling machine body in the longitudinal direction of the traveling machine body. The transmission case 36 has the case input shaft 37 and the cutting output shaft 39 distributed in one end side and the other end side in the lateral direction of the traveling body of the transmission case 36, and the cylinder output shaft 38. Further, the case input shaft 37 and the cutting output shaft 39 are arranged side by side in the horizontal direction of the traveling machine body. The handling cylinder output shaft 38 is connected to a rotating spindle of the handling cylinder 5a so as to be integrally rotatable.

  The transmission case 36 accommodates a bevel gear mechanism 43 having a bevel gear 43 a provided at the end of the case input shaft 37 so as to be integrally rotatable. The bevel gear mechanism 43 includes the bevel gear 43a, a bevel gear 43b provided integrally with an end of the cutting output shaft 39, and a bevel gear 43a meshed with the bevel gears 43a and 43b. A bevel gear 43c provided so as to be integrally rotatable is provided. In other words, the bevel gear mechanism 43 enables the traveling machine body sideways case input shaft 37 and the traveling machine body front and rear threshing output shaft 38 to be linked, and the rotation direction of the case input shaft 37 and the rotation direction of the cutting output shaft 39 are The case input shaft 37 and the cutting output shaft 39 are interlocked with each other in the reverse rotational direction.

  As shown in FIGS. 3 and 4, in the forward rotation clutch 40, a transmission belt 40a wound around the case input shaft 37 and one end of the cutting input shaft 42 is stretched by a tension ring body 40c of a tension member 40b. The belt tension clutch is switched to the on state and the off state by switching between the state and the loose state. The tension member 40 is swingably supported at the end of the transmission case 36. When the forward rotation clutch 40 is switched to the on state, the driving force of the case input shaft 37 is transmitted to the cutting input shaft 42 as the driving force for driving the cutting portion 10 in the forward rotation direction.

  As shown in FIGS. 3 and 4, the reverse rotation clutch 41 includes a transmission belt 41a wound around the cutting output shaft 39 and the other end of the cutting input shaft 42 by a tension ring body 41c of a tension member 41b. The belt tension clutch is switched to the on state and the off state by switching between the tension state and the relaxed state. The tension member 41b is swingably supported at the end of the transmission case 36. When the reverse rotation clutch 41 is switched to the engaged state, the driving force of the cutting output shaft 39 is transmitted to the cutting input shaft 42 as the driving force for driving the cutting unit 10 in the reverse rotation direction.

  As shown in FIG. 3, the cutting input shaft 42 is a conveyor drive shaft that drives the feeder conveyor 11a. The cutting input shaft 42 is linked to the drive shaft 45 of the cutting device 16 via a transmission chain 44. The drive shaft 45 and the drive shaft 46 of the auger 18 are interlocked by a transmission chain 47. The drive shaft 46 of the auger 18 and the drive shaft 48 of the rotary reel 17 are interlocked by an interlocking mechanism using a transmission chain 49 and a transmission belt 50.

  When the driving force in the forward rotation direction is transmitted, the reaping input shaft 42 forwards the feeder conveyor 11a, the auger 18, the reaping device 16, and the rotating reel 17 of the reaping unit 10 so as to perform normal preprocessing work and transport work. When driven in the rotation direction and the driving force in the reverse rotation direction is transmitted, the feeder conveyor 11a, the auger 18, the mowing device 16, and the rotary reel 17 of the cutting unit 10 are rotated in the direction opposite to the normal rotation direction for work. To drive.

  FIG. 4 shows a structure in a front view of an operation unit provided in the operation unit 3 so as to perform a switching operation between the forward rotation clutch 40 and the reverse rotation clutch 41 and a speed control operation of the engine 20. . FIG. 6 is a perspective view of the operation unit. As shown in FIG. 2 and FIG. 2, the operation unit includes an operation panel 51 provided on the lateral side of the driver's seat 2 and a lever-shaped right side panel provided on the operation panel 51 in the lateral direction of the traveling machine body. A rolling clutch operating tool 52, a lever-type accelerator operating tool 53, and a lever-type reverse clutch operating tool 54 provided on the laterally outer side opposite to the driver seat side of the operation panel 51 are provided.

  The forward rotation clutch operating tool 52 is supported by a support member 56 via a rotation support shaft 55 that is connected to the base of the operation tool 52 so as to be integrally rotatable. Swing around. The support member 56 is attached to the back side of the operation panel 51. The forward rotation clutch operating tool 52 includes an oscillating arm 61 provided with a swinging arm 61 which is provided so as to be integrally rotatable at the end of the rotating support shaft 55 opposite to the side to which the forward rotation clutch operating tool 52 is connected. 60 is linked to the tension member 40 b of the forward rotation clutch 40.

  As shown in FIGS. 6 and 7, the interlock mechanism 60 includes the swing arm 61, and one end of the swing mechanism 61 is connected to the free end of the swing arm 61 via a connecting pin 62 so as to be relatively rotatable. The swing link 63 and an operation cable 64 in which the other end of the swing link 63 is linked to the tension member 40b of the forward rotation clutch 40 by an inner cable.

  FIG. 7 shows an operation state of the forward rotation clutch operating tool 52 to the entering position “entering”. As shown in this figure, the forward rotation clutch operating tool 52 is swung in the longitudinal direction of the traveling machine body along the guide groove 51a (see FIG. 4) of the operation panel 51 around the lateral axis of the traveling machine body of the rotating support shaft 55. When operated and positioned on the front end side of the guide groove 51a, the forward rotation clutch operating tool 52 enters the entering position “entering”. Then, the forward rotation clutch operating tool 52 raises the swing link 63 by operating the swing arm 61 up and swinging. As a result, the inner cable of the operation cable 64 is pulled, and the tension member 40b is swung so as to press the transmission belt 40a, so that the transmission belt 40a becomes tensioned and the forward rotation clutch 40 is engaged.

  FIG. 8 shows the operating state of the forward clutch operating tool 52 to the cut position “cut”. As shown in this figure, when the forward rotation clutch operating tool 52 is positioned on the rear end side of the guide groove 51a, the forward rotation clutch operating tool 52 is in the cut position “cut”. Then, the forward rotation clutch operating tool 52 operates to lower the swing link 63 by lowering and swinging the swing arm 61. As a result, the inner cable of the operation cable 64 is loosened and the tension member 40b is swung so as to release the pressure of the transmission belt 40a, the transmission belt 40a is loosened and the forward rotation clutch 40 is disengaged. .

  As shown in FIGS. 4, 6, and 7, the reverse clutch operating tool 41 is connected to a tension member 41b of the reverse rotation clutch 41, and swings to the end of the transmission case 36 via the tension member 41b. It is supported freely.

  FIG. 8 shows the operating state of the reverse clutch operating tool 41 to the entering position “entering”. As shown in this figure, when the reverse rotation clutch operating tool 41 is lifted and swung around the shaft center of the cutting output shaft 39 in the lateral direction of the traveling machine body, the reverse rotation clutch operating tool 41 enters the “in” position. Then, the reverse clutch operating tool 41 swings the tension member 41b toward the entry side. As a result, the tension roller 41c tensions the transmission belt 41a, and the reverse rotation clutch 41 enters the engaged state. At this time, the reverse rotation clutch 41 is maintained in the engaged state by the reverse rotation clutch operating tool 41 being maintained in the engaged position “entered” by human operation.

  FIG. 7 shows an operation state of the reverse clutch operating tool 54 to the cut position “cut”. As shown in this figure, when the maintenance operation of the reverse clutch operating tool 54 to the on position “on” is released, the reverse clutch operating tool 54 naturally swings downward to the cut position “cut”. Then, the reverse clutch operating tool 54 swings the tension member 41b to the cutting side. As a result, the tension roller 41e releases the tensioning operation of the transmission belt 41a, the transmission belt 41a is loosened, and the reverse rotation clutch 41 is disengaged.

  As shown in FIG. 4, the accelerator operating tool 53 is supported by a support member 58 via a support shaft 57 inserted through the base end side of the accelerator operation tool 53, and swings around a shaft center of the support 57 in the lateral direction of the traveling machine body. Move. The support member 58 is attached to the back side of the operation panel 51. The accelerator operation tool 53 is linked to an accelerator device (not shown) of the engine 20 by an operation cable (not shown) in which one end side of the inner cable is connected to the base end portion of the accelerator operation tool 53.

  FIG. 7 shows the operating state of the accelerator operating tool 53 to the high speed position “high”. As shown in this figure, the accelerator operating tool 53 is swung around the lateral axis of the traveling machine body of the support shaft 57 along the guide groove 51b (see FIG. 4) of the operation panel 51, and the rear of the guide groove 51b. Position it on the end side. Then, the accelerator operating tool 53 becomes the high speed position “high” and operates the accelerator device in a high speed state. Thereby, it will be in the high-speed state for work which the engine 20 rotates with the high rotation speed set for work.

  FIG. 8 shows the operating state of the accelerator operating tool 53 to the low speed position “low”. As shown in this figure, the accelerator operating tool 53 is positioned on the front end side of the guide groove 51b. Then, the accelerator operation tool 53 is moved to the low speed position “low” to operate the accelerator device in the low speed state. As a result, the engine 20 is in a non-working low speed state in which the engine 20 rotates at a low rotational speed set for the reverse rotation driving of the cutting unit 10.

  As shown in FIGS. 4, 6, and 7, the operation unit is connected to the accelerator operating tool 53 and the check mechanism 70 having a check body 71 formed of a strip plate member connected to the swing arm 61 at one end side. And a high-speed reverse rotation check mechanism 80 having a high-speed reverse rotation check body 81 constituted by the bent frame.

  The check mechanism 70 includes the check body 71 and a contact portion 73 formed by a bending rod 72 extending from the tension member 41b toward the upper surface of the operation panel 51.

  Since the check body 71 is formed of a strip plate connected to the swing arm 61, the check body 71 is supported by the forward clutch operating tool 52 via the swing arm 61 and the rotation support shaft 55, and is rotated forward. It moves integrally with the clutch operating tool 52. The contact portion 73 is formed by a bending rod 72 extending from the tension member 41b to which the reverse clutch operating tool 54 is connected, and thus provided in the reverse clutch operating tool 54 so as to move integrally with the reverse clutch operating tool 54. It is in the state.

  FIG. 7 is a side view of the check mechanism 70 in the operating state. As shown in this figure, when the forward rotation clutch operating tool 52 is operated to the “ON” position, the checker 71 is raised by the swing arm 61 to the same arrangement height as the operation panel 51. . Then, the check body 71 becomes an operation position in which the check making portion 71a formed by the end portion of the band plate material enters the movement path of the contact portion 73. As a result, when the check body 71 attempts to switch the reverse rotation clutch operation tool 54 from the cut position “cut” to the turn position “enter”, the reverse rotation clutch operation 71 is brought into contact with the check making portion 71 a and the contact portion 73. The movement of the tool 54 to the entry position “enter” is disabled.

  That is, when the forward rotation clutch 40 is in the engaged state, the check mechanism 70 enters the reverse clutch operation tool 54 by abutment between the check production portion 71a of the check body 71 and the contact portion 73 provided in the reverse rotation clutch operation tool 54. The switching to the position “ON” is suppressed, and thereby the operation state is set to check the switching of the reverse rotation clutch 41 to the ON state.

  FIG. 8 is a side view of the check mechanism 70 in a released state. As shown in this figure, when the forward rotation clutch operating tool 52 is operated to the cut position “cut”, the check body 71 is lowered by the swing arm 61 to a position lower than the arrangement height of the operation panel 51. Then, the check body 71 is in a release position retracted to the outside from the movement path of the contact portion 73, and the reverse clutch operating tool 54 is switched from the cut position “cut” to the turn position “enter”. Contact between the contact portion 73 and the check making portion 71a is avoided.

  In other words, when the forward rotation clutch 40 is in the disconnected state, the checking mechanism 70 releases the switching check to the engaged position “entered” of the reverse rotation clutch operation tool 54, thereby switching the reverse rotation clutch 41 to the engaged state. It will be in the release state to release the check.

  The high-speed reverse rotation check mechanism 80 includes the high-speed reverse rotation check body 81 and a contact portion 82 formed by the bending rod 72.

  The high-speed reverse rotation check body 81 is configured by a bending rod connected to the accelerator operation tool 53, so that it is supported by the accelerator operation tool 53 and moves integrally with the accelerator operation tool 53. The contact portion 82 is configured by a bent rod 72 extending from the tension member 41b to which the reverse clutch operating tool 54 is connected, and thus provided in the reverse clutch operating tool 54 so as to move integrally with the reverse clutch operating tool 54. It is in the state. The high-speed reversal check body 81 includes a check making part 83 formed of a bent portion of a bending frame constituting the high-speed reverse check body 81. The high-speed reverse rotation check body 81 is a part located between the part connected to the accelerator operating tool 53 and the check making part 83 and is movably maintained by the holder 84 supported by the operation panel 51. Yes. The holder 84 is supported by the operation panel 51.

  FIG. 7 is a side view of the high speed reverse rotation check mechanism 80 in the operating state. As shown in this figure, when the accelerator operation tool 53 is operated to the high speed position “high”, the high speed reverse rotation checker 81 is moved and operated to the rear side of the traveling machine body by the accelerator operation tool 53. Then, the high-speed reverse rotation check body 81 is in the operating position, and when the reverse rotation clutch operating tool 54 is to be switched from the cut position “cut” to the turn position “enter”, the check making section 83 and the hit section 82 The contact gives resistance to the movement of the reverse clutch operating tool 54 to the entering position “entering”.

  That is, when the engine 20 is in a high speed working state, the high speed reverse rotation check mechanism 80 operates the reverse rotation clutch by the contact between the check production portion 83 of the high speed reverse rotation check body 81 and the contact portion 82 provided in the reverse rotation clutch operating tool 54. The tool 54 is made difficult to move to the entering position “entering”, and thereby, the switching to the engaged state of the reverse rotation clutch 41 is suppressed.

  FIG. 8 is a side view of the high speed reverse rotation check mechanism 80 in the released state. As shown in this figure, when the accelerator operation tool 53 is operated to the low speed position “low”, the high speed reverse rotation checker 81 is moved and operated forward by the accelerator operation tool 53. Then, the high-speed reverse rotation check body 81 is in the release position, and reversely rotates with the check production part 83 of the high-speed reverse rotation check body 81 when the reverse rotation clutch operating tool 54 is switched from the cut position “cut” to the turn position “on”. Contact with the contact portion 82 of the clutch operating tool 54 is avoided.

  That is, when the engine 20 is in the non-working low speed state, the high speed reverse rotation check mechanism 80 releases the reverse rotation clutch operating tool 54 from being switched to the on position “on”, and thereby the reverse rotation clutch 41 is brought into the on state. It will be in the release state to release the switching check.

  In other words, when performing work, the accelerator operating tool 53 is operated to the high speed position “high”, the reverse rotation clutch operating tool 54 is operated to the cut position “cut”, and the forward rotation clutch operation tool 52 is operated to the enter position “on”. To do. Then, the engine 20 rotates at a high working speed, and the driving force from the output shaft 20a of the engine 20 is transmitted to the case input shaft 37 of the transmission case 36 via the belt transmission mechanism 25, the Karatsu drive shaft 26, and the belt transmission mechanism 35. The case input shaft 37 is driven and the driving force of the case input shaft 37 is transmitted to the cutting output shaft 39 via the bevel gear mechanism 43 so that the cutting output shaft 39 is rotated in the rotational direction of the case input shaft 37. Are driven in the opposite direction of rotation. When the forward rotation clutch 40 is engaged, the driving force of the case input shaft 37 is transmitted to the cutting input shaft 42 by the forward rotation clutch 40, and the reverse rotation clutch 41 is disconnected and the driving force of the cutting output shaft 39 is cut. Without being transmitted to the input shaft 42, the cutting input shaft 42 is driven in the normal rotation direction at the working rotational speed. The driving force of the cutting input shaft 42 is driven directly to the conveying terminal side of the feeder conveyor 11, to the driving shaft 45 of the cutting device 16 via the transmission chain 44, and to the drive of the auger 18 via the transmission chain 44 and the transmission chain 47. The shaft 46 is transmitted to the drive shaft 48 of the rotary reel 17 through the transmission chain 44, the transmission chain 47, and the transmission belt 50, respectively, and the feeder conveyor 11a, the auger 18, the mowing device 16, and the rotary reel 17 are rotated in the forward rotation direction. Driven at a rotation speed suitable for work.

  When the cereal clogging occurs in the mowing unit 10, the accelerator operating tool 53 is switched to the low speed position “low”, the forward clutch operating tool 52 is switched to the cutting position “cut”, and the reverse clutch operating tool 54 is turned on. Switch to the entry position “On”. At this time, the switching operation of the accelerator operating tool 53 to the low speed position “low” is performed to cancel the switching check of the reverse rotation clutch 41 by the high speed reverse rotation checking mechanism 80 and the forward rotation clutch operation tool 52 is moved to the cutting position “cut”. After switching the reverse rotation clutch 41 by the check mechanism 70 is released, the reverse rotation clutch operating tool 54 is switched to the on position “on”.

  Then, the engine 20 rotates in a non-working low speed state, and the driving force from the output shaft 20a of the engine 20 is transmitted to the case input shaft of the transmission case 36 via the belt transmission mechanism 25, the Karatsu drive shaft 26, and the belt transmission mechanism 35. 37, the driving force of the case input shaft 37 is transmitted to the cutting output shaft 39 via the bevel gear mechanism 43, and the cutting output shaft 39 is driven in a rotation direction opposite to the rotation direction of the case input shaft 37. Is done. When the forward rotation clutch 40 is in the disengaged state, the driving force of the case input shaft 37 is not transmitted to the cutting input shaft 42, and the reverse rotation clutch 41 is engaged and the driving force of the cutting output shaft 39 is driven by the reverse rotation clutch 41. This is transmitted to the cutting input shaft 42, and the cutting input shaft 42 is driven in the reverse rotation direction at a non-working rotational speed. The driving force of the cutting input shaft 42 is driven directly to the conveying terminal side of the feeder conveyor 11, to the driving shaft 45 of the cutting device 16 via the transmission chain 44, and to the drive of the auger 18 via the transmission chain 44 and the transmission chain 47. The shaft 46 is transmitted to the drive shaft 48 of the rotary reel 17 through the transmission chain 44, the transmission chain 47, and the transmission belt 50, respectively, and the feeder conveyor 11a, the auger 18, the mowing device 16, and the rotary reel 17 are rotated in the reverse rotation direction. It is driven at a rotation speed suitable for clogging, and the clogging of cereals becomes easy. At this time, the reverse rotation clutch 41 is engaged and the reaping portion 10 is driven to rotate in the reverse direction only while the reverse rotation clutch operation tool 54 is artificially maintained at the “in” position. When the maintenance operation to the entering position “entering” is released, the reverse rotation clutch operating tool 54 is naturally switched to the disengaging position “cutting”, the reverse rotation clutch 41 is disengaged, and the reverse rotation driving of the cutting unit 10 is stopped. .

  FIG. 5 is a side view of a chain transmission mechanism having the transmission chain 44. As shown in this figure, the chain transmission mechanism includes a guide ring body 89 wound so that the transmission chain 44 is guided, and has a tension arm 91 supported by the lateral side wall portion 11 b of the feeder 11. The chain tensioning mechanism 90 is provided.

  As shown in FIGS. 5 and 10, the chain tensioning mechanism 90 includes the tension arm 91 and a spring 92 connected to the tension arm 91, and the tension arm 91 is configured by the spring 92. By swinging and energizing around the support shaft 93, the tension ring body 94 included in the tension arm 91 is pressed and urged against the transmission chain 44, thereby applying tension to the transmission chain 44. .

  The side of the spring 92 opposite to the side connected to the tension arm 91 is connected to a spring support rod 96 supported by a lateral wall 11b of the feeder 11 via a bracket 95. The tension ring body 94 acts on a portion 44a on the loosening side of the transmission chain 44 when the cutting unit 10 is driven to rotate forward. The tension arm 91 includes a tension regulating body 97 attached over the tension arm 91 and the spring support rod 96.

  As shown in FIGS. 9 and 10, the tension regulating body 97 and the spring support rod 96 are connected via a connecting pin 98 so as to be relatively rotatable. The tension regulating body 97 and the tension arm 91 are connected by a support shaft 99 that supports the tension ring body 94 so as to freely rotate. The support shaft 99 is slidably inserted through a restriction long hole 100 provided in the tension restriction body 97.

  FIG. 9A shows a chain tensioning operation state of the tension ring body 94 when the cutting unit 10 is driven to rotate forward. As shown in this figure, when the cutting unit 10 is driven to rotate forward, a portion 44a of the transmission chain 44 on which the tension ring body 94 acts becomes the loose side. Then, the tension ring body 94 tensions the chain portion 44 a by a pulling operation by the spring 92.

  FIG. 9 (b) shows the operating state of the tension regulating body 97 when the cutting unit 10 is driven in reverse. As shown in this figure, when the cutting unit 10 is driven in reverse, the tension regulating body 97 regulates movement against the spring 92 of the tension ring body 94. Thereby, the part 44b which becomes the loose side of the transmission chain 44 for the reverse drive of the cutting part 10 becomes difficult to remove | deviate from the guide forest 9.

  That is, when the portion 44a of the transmission chain 44 where the tension ring body 94 acts becomes the tension side, the tension ring body 94 is moved and operated against the spring 92 due to this tension force. Then, the tension regulating body 97 supports the tension ring body 94 via the support shaft 99 so as to regulate the movement against the spring 92 of the tension ring body 94. As a result, the tension regulating body 97 has a loosening allowance for the portion 44b so that the portion 44b on the loosening side of the transmission chain 44 is not loosened so as to be disengaged from the guide ring body 89 in order to drive the cutting part 10 in the reverse direction. Suppress.

[Another Example]
Instead of the transmission mechanism of the above-described embodiment, the case input shaft 37 is driven in the reverse rotation direction and the cutting output shaft 39 is driven in the forward rotation direction, and the case input shaft 37 and the cutting input shaft 42 are reversed. A transmission mechanism having a configuration in which the cutting output shaft 39 and the cutting input shaft 42 are interlocked by a positive rotation clutch, and the case input shaft 37 and the cutting output shaft 39 are both connected to the handling cylinder output shaft 38 by the rotary clutch. Alternatively, a transmission mechanism having a configuration located on the left side of the traveling machine body or on the right side of the traveling machine body may be employed. In these cases also, the object of the present invention can be achieved.

Combine side view Overall plan view of combine Transmission mechanism diagram Front view of transmission case placement and operation section Side view of chain transmission mechanism Perspective view of the operation unit The operating state of the forward rotation clutch operating tool to the entering position, the operating state of the accelerator operating tool to the high speed position, the operating state of the reverse rotation clutch operating tool to the disengagement position, and the operating state of the check mechanism and the high speed reverse rotation check mechanism Side view showing The operating state of the forward clutch operating tool to the cut position, the operating state of the accelerator operating tool to the low speed position, the operating state of the reverse clutch operating tool to the entering position, the release state of the check mechanism and the high speed reverse check mechanism Side view showing (A) is a side view of the tension ring body in the chain tension operation state, (B) is a side view showing the action state of the tension regulating body. Cross section of chain tension mechanism

Explanation of symbols

5 Threshing device 20 Engine 36 Transmission case 37 Case input shaft 38 Cylinder output shaft 39 Cutting output shaft 40 Forward rotation clutch 41 Reverse rotation clutch 42 Cutting input shaft 43 Bevel gear mechanism

Claims (3)

A case input shaft to which a driving force from the engine is transmitted, and a front and rear cylinder output shaft coupled to the case input shaft via a bevel gear mechanism so as to transmit the driving force of the case input shaft to the barrel. Is a combine provided with a transmission case equipped on the front side of the traveling machine body of the threshing device,
The transmission case is equipped with a cutting output shaft linked to the case input shaft via the bevel gear mechanism so as to be driven in a rotation direction opposite to the rotation direction of the case input shaft,
A positive rotation clutch is provided for interlocking the cutting input shaft with one of the case input shaft and the cutting output shaft so as to transmit the driving force in the positive rotation direction to the cutting input shaft of the cutting unit,
The combine provided with the reverse rotation clutch which interlocks the other of the said case input shaft and the said cutting output shaft, and the said cutting input shaft so that the driving force of a reverse rotation direction may be transmitted to the said cutting input shaft of the said cutting part.   The combine according to claim 1, wherein the case input shaft and the cutting output shaft are arranged in a lateral direction of the traveling machine body with the handling cylinder output shaft interposed therebetween.   The combine according to claim 1 or 2, wherein the reverse rotation clutch is maintained in an engaged state by human operation.

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