JP2014033654A - Sorting device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a sorting device capable of suppressing effectively kinetic inertia resulting from rocking motion of a sieve case with a comparatively simple structure.SOLUTION: A rocking drive mechanism 30 of a sieve case 40 is constituted of an eccentric drive mechanism in which an output transfer spot to the sieve case 40 is positioned eccentrically to the shaft center x1 of a drive shaft 31, and a vibration-damping balance weight 36 for imparting kinematic inertia reverse to the vertical rocking direction of the sieve case 40 is provided in the eccentric drive mechanism, and a flywheel part 37 in which the weight is distributed equally or approximately equally over the whole area in the circumferential direction around the same shaft center as the shaft center x1 of the drive shaft 31 is also provided.

Description

  The present invention relates to a sheave case configured to select one of the workpieces for specific gravity by swinging up and down at the other end and swinging the other end of the sheave case. The present invention relates to an improvement of a sorting apparatus including a drive mechanism.

  Conventionally, as a sorter of this type, a swing drive mechanism that swings the end of a sheave case transmits an output to the sheave case with respect to the axis of the drive shaft that is pivotally supported by the side wall of the threshing device. There is an eccentric drive mechanism in which the location is eccentric, and the eccentric drive mechanism is provided with a balance weight for damping so as to give a motion inertia in a direction opposite to the vertical swing direction in the sheave case (for example, , See Patent Document 1).

JP-A-8-191624 (paragraph numbers [0015], [0017], FIG. 2, FIG. 3)

According to this sorting device, the balance weight is positioned at a phase opposite to the output location that is eccentric with respect to the rotation axis, thereby providing a motion inertia in the direction opposite to the swinging direction of the sheave case, This is useful in that the occurrence of airframe vibration due to the motion inertia of the case can be reduced.
However, the swing of the sheave case is almost a reciprocating motion, and the motion inertia accompanying the swing of the sheave case hardly acts in the direction orthogonal to the reciprocating direction. Nevertheless, the motion inertia accompanying the rotation of the balance weight existing at a position eccentric with respect to the rotational axis acts in all radial directions. For this reason, if the balance weight is so large that it cancels the movement inertia of the sheave case, a large movement by the balance weight in the direction in which the movement inertia of the sheave case is not acting, that is, the direction orthogonal to the reciprocating direction of the sheave case Inertia acts and this may cause airframe vibration.
Therefore, conventionally, in order to avoid the fact that the movement inertia due to the balance weight causes the airframe vibration, the mass of the balance weight is not so large as to completely cancel the movement inertia of the sheave case. Both the movement inertia and the movement inertia of the balance weight in the direction orthogonal to the reciprocation direction of the sheave case were both moderately reduced. Therefore, it is difficult to sufficiently suppress the movement inertia accompanying the swing of the sheave case, and there is room for improvement in this respect.

  An object of the present invention is to provide a sorting device that can effectively suppress the movement inertia associated with the swinging movement of the sheave case with a relatively simple structure.

In order to achieve the above object, the sorting apparatus of the present invention employs the following technical means.
[Solution 1]
In the invention according to the solution 1, the sheave case configured to select one of the workpieces for specific gravity by swinging the other end side up and down and swinging the other end side of the sheave case. An oscillation transmission mechanism that moves the oscillation drive mechanism with respect to the axis of the drive shaft that is pivotally supported by the side wall of the threshing device. The eccentric drive mechanism includes an eccentric drive mechanism that is positioned eccentrically, and the eccentric drive mechanism includes a balance weight for vibration suppression that imparts a motion inertia in the direction opposite to the vertical swing direction on the other end side of the sheave case. In addition, a technical means is provided in which a flywheel portion having a weight distribution equally or substantially uniformly distributed over the entire region in the circumferential direction around the same axis as the axis of the drive shaft is provided.

[Operation and effect of invention according to Solution 1]
According to the above solution, the balance weight capable of reducing the occurrence of airframe vibration due to the motion inertia of the sheave case by giving the motion inertia opposite to the swing direction of the sheave case, and the rotational motion of the swing drive mechanism In combination with a flywheel portion that smoothes the movement, the inertia of the sheave case can be effectively suppressed.
In other words, the balance weight is used to effectively give the motion inertia in the opposite direction to the sheave case swinging direction and to reduce the vibration caused by the sheave case swinging. On the other hand, a flywheel portion that is driven to rotate around the same axis as the axis of the drive shaft is provided so that the smoothness in the rotation direction of the drive shaft is maintained. Vibration due to the inertia of the balance weight in the orthogonal direction is easily reduced, and there is an advantage that it is easy to suppress the shaking of the airframe due to the sheave swinging movement and the eccentric movement of the balance weight for damping as a whole.

[Solution 2]
Another technical means of the present invention taken to solve the above problem is that the flywheel portion is provided so as to be driven integrally with the drive shaft.

[Operation and effect of invention according to Solution 2]
According to the configuration of the invention relating to the above solution 2, since the flywheel unit is driven integrally with the drive shaft, there is an advantage that it is easy to simplify the power transmission structure from the drive shaft to the flywheel unit. .

[Solution 3]
Another technical means of the present invention taken to solve the above problem is that the flywheel portion is provided so as to be integrally driven with an eccentric cam constituting the eccentric drive mechanism.

[Operation and effect of invention according to Solution 3]
According to the configuration of the invention relating to the above solution 3, since the flywheel portion is configured to be integrally driven with the eccentric cam, the flywheel portion can be driven using the drive structure of the eccentric cam, It is easy to simplify the structure.

[Solution 4]
Another technical means of the present invention taken in order to solve the above-mentioned problem is that the flywheel part is constructed integrally with an eccentric cam constituting the eccentric drive mechanism.

[Operations and effects of invention according to Solution 4]
According to the configuration of the invention relating to the solving means 4 described above, since the flywheel portion is configured integrally with the eccentric cam, the eccentric cam can be used as a support means for the flywheel portion, and the structure can be simplified. There are benefits to get.

[Solution 5]
Another technical means of the present invention taken to solve the above problem is that the flywheel portion is disposed on the opposite side of the balance weight with the eccentric cam interposed therebetween.

[Operation and effect of invention according to Solution 5]
According to the configuration of the invention relating to the above solution 5, the flywheel portion and the balance weight are arranged on both sides of the eccentric cam, and the flywheel portion and the balance weight are arranged on one side of the eccentric cam. Compared to the case, there is an advantage that the balance of the weight acting on the eccentric cam is improved and smooth rotation is easily performed.

[Solution 6]
Another technical means of the present invention taken in order to solve the above-mentioned problem is that the flywheel unit is integrated with an input pulley provided on the drive shaft that extends outward from the side wall of the threshing device. It is composed.

[Operations and Effects of Invention According to Solution 6]
According to the structure of the invention concerning said solution means 6, there exists an advantage which can set the space for arrangement | positioning of a flywheel part outside the side wall part of a threshing apparatus, and can simplify the internal structure of a threshing apparatus.

It is the whole left side view of a normal type combine. It is a whole top view of a normal combine. It is a vertical left side view of a threshing apparatus. It is a front view which shows the partition plate of a handling cylinder. It is a diagram which shows the transmission system of a normal type combine. It is a top view which shows a rocking drive mechanism. It is a side view which shows the operation state of a rocking drive mechanism. It is a top view which shows the rocking | fluctuation drive mechanism in another embodiment. It is a conceptual diagram which shows the rocking | fluctuation drive mechanism in another embodiment, (a) is a conceptual diagram of the whole rocking drive mechanism in a top view, (b) is description which shows the positional relationship of a pair of eccentric cam and balance weight. FIG. It is a conceptual diagram which shows the rocking | fluctuation drive mechanism in another embodiment.

  Hereinafter, an embodiment in which the sorting device of the present invention is applied to an ordinary type (all-fired type) combine will be described with reference to the drawings.

〔overall structure〕
As shown in FIGS. 1 and 2, the ordinary combine has a boarding operation part 7 formed in the front right side region of the traveling vehicle body 1 equipped with a pair of left and right crawler type traveling devices 6 at the lower part of the body frame 5. .
On the front side of the traveling vehicle body 1, a cutting and conveying apparatus 2 that harvests and transports the harvested culm backward is mounted so as to be able to move up and down using the cutting input shaft 14 on the rear end side as a swinging fulcrum. A threshing device 3 is mounted on the left half of the traveling machine body 1 on the rear end side of the cutting and conveying device 2 for threshing and sorting the workpiece supplied from the cutting and conveying device 2. The right half part of the traveling vehicle body 1 is a well-known bagging device 4 that stores the single-grained grains from the processed material obtained by the threshing process and the sorting process in the threshing device 3 and enables the filling into the bag. The chopper 19 which shreds the waste straw discharged | emitted from the threshing apparatus 3 in the back side of the threshing apparatus 3 is provided.

  As the traveling vehicle body 1 travels, the harvesting and conveying device 2 separates the unharvested cereals into the harvested cereals and the unharvested cereals by the dividers 8 provided at the left and right ends of the front part thereof. The tip of the harvested culm is scraped backward by a rotating reel 9 arranged at the upper front of the transport device 2, and the stock of the harvested culm is harvested by the clipper-type cutting mechanism 10 provided at the bottom of the harvesting and transport device 2. The side is cut and the harvested cereal is taken in. Then, the harvested cereals are gathered to a predetermined place in the left-right direction by a screw transport type auger 11 arranged behind the cutting mechanism 10 and sent backward, and the scraped up from the predetermined place over the rear threshing device 3 The feed type feeder 12 is configured to be fed and transported to the threshing apparatus 3 as an object to be processed.

  The lifting / lowering swinging of the cutting and conveying device 2 is performed after the feeder 12 serving as a connection end portion with the threshing device 3 in the cutting and conveying device 2 by an expansion and contraction operation of a hydraulic lifting cylinder 13 installed over the body frame 5 and the feeder 12. This is performed using the left-right cutting input shaft 14 provided at the end as a fulcrum.

[Threshing equipment]
As shown in FIGS. 3 and 4, the threshing apparatus 3 includes a threshing unit 3 </ b> A that performs a threshing process on the harvested cereal straw supplied by the feeder 12. The lower part includes a sorting unit 3B that performs a sorting process on the processed product obtained by the handling process in the threshing unit 3A, and a collecting unit 3C that collects the collected processing product obtained by the sorting process. is there.

The threshing portion 3A is chopped and conveyed by rotating clockwise around the front and rear cylinder shafts 18 in a handling chamber 15 formed with a U-shaped receiving net 16 or the like mounted on the upper part in the upper part. A bar-type handling cylinder 17 for handling the harvested cereal meal from the apparatus 2 is provided.
This bar-type handling cylinder 17 has bar members 17a with toothed teeth disposed at predetermined intervals in the circumferential direction across the outer peripheral portions of a pair of disc-shaped receiving plates 17b, 17b provided at both front and rear ends. It is formed in the shape of a bowl by spanning a plurality.

A pair of disc-shaped receiving plates 17b and 17b provided at the front and rear ends are connected and fixed to the barrel shaft 18, and the rotational power of the barrel shaft 18 is transmitted to each bar member 17a so that the teeth are handled. It is comprised so that a threshing process may be performed. However, the intermediate receiving plate 17c provided at the intermediate position in the longitudinal direction of the bar member 17a is formed in an annular shape having an opening portion 17d on the center side as shown in FIG. 4, and is connected to each bar member 17a. However, it is not connected to the barrel 18.
That is, the intermediate receiving plate 17c connects and reinforces the intermediate positions in the longitudinal direction of the bar members 17a, but does not transmit power of the barrel 18 and is formed at the center. By providing the opening 17d, it is easy to pass the sorting wind and the workpiece.

  The sorting unit 3B is a threshing unit for swinging sorting means 20 that swings and sorts the processed material leaked from the receiving net 16 while moving backward, and for supplying the sorting sorter 20 with the sorting wind for sorting. It is arranged below 3A.

  The collection unit 3C collects the single-grained grains that have been leaked from the front side of the rocking sorting means 20 and flowed down while receiving the sorting wind from the Kara 21 below the rocking sorting means 20 as the first thing. The No. 1 recovery unit 22 and the No. 2 recovery unit 23 that recovers the grain with branches and the like leaking from the rear side of the swing sorting means 20 as the second item are arranged in order in that order. Configured.

In the threshing unit 3A, the handling chamber 15 includes a receiving net 16 that covers the handling cylinder 17 from below, and an upper cover 26 that covers the upper part of the handling cylinder 17 from above so as to be openable and closable. Further, a front vertical plate member 27 that rotatably supports the front end portion of the barrel 18, a rear vertical plate member 28 that rotatably supports the rear end of the barrel 18, and the harvested cereal from the feeder 12. It is divided by a grain culm guide plate 29 provided with a guide surface 29A in a rearwardly inclined posture for guiding the culm to the receiving net 16, and the like.
A supply port 15 </ b> A is formed between the front vertical plate member 27 and the culm guide plate 29 to enable the supply of the harvested cereal that has been scraped and conveyed by the feeder 12 to the handling chamber 15. Further, between the rear end of the receiving net 16 and the rear vertical plate member 28, a discharge port for allowing discharge from the handling chamber 15, such as waste straw, which is a cereal cereal after processing. 15B is formed.

As shown in FIG. 3, the swing sorting means 20 includes a sheave case 40 that swings up and down and back and forth by the operation of an eccentric cam type swing drive mechanism 30 provided at the lower portion thereof.
On the upper part of the sheave case 40, a rough sorting grain pan 41, a chaff sheave 42 and a stroller 43 are arranged in that order from the front end of the sheave case 40 to the rear, and at the lower part of the sheave case 40, A Glen pan 44 and a Glen sheave 45 are connected to each other in that order, and a Chaff sheave 46 for selecting a second item is arranged behind the Glen sheave 45 so as to be connected to the Glen sheave 45.

  The red pepper 21 is arranged at the front lower side of the swing sorting means 20, and generates a sorting wind by rotating counterclockwise when viewed from the left side about the left-right-direction hot shaft (corresponding to the output shaft) 51. This sorting wind is configured to be supplied for fine sorting that blows through the rear and upper Glen sheave 45 and the first collecting unit 22, the entire area of the Glen sheave 45, and between the Glen sheave 45 and the chaff sheave 46. .

  As a result, the sorting air from the Karatsu 21 is allowed to act from the front and lower side on the processed material that leaks from the grain sieve 45 and flows down to the first collecting unit 22 and the processed material that is being screened by the grain sieve 45. It is possible to perform wind power sorting in which dust such as sawdust having a small specific gravity is blown from the processed material and then wind-carrying upward. By this wind sorting, the first recovery process for recovering the single-grained grains leaking from the grain sieve 45 to the first recovery unit 22 while preventing dust such as sawdust from entering the first recovery unit 22 It can be performed with high accuracy.

At the bottom of the No. 1 recovery unit 22, a No. 1 transport screw 22a that conveys the No. 1 item dropped from the Glen Sheave 45 to the right is provided. At the bottom of the No. 2 recovery unit 23, the No. 1 recovery unit 22 falls from the Chaff sheave 46. The 2nd conveyance screw 23a which conveys the 2nd thing to the right side is arranged.
A screw-type transporting conveyor 24 (see FIG. 5) is connected to the right end of the first transporting screw 22a to transport the first product transported by the first transporting screw 22a to the upper part of the bagging device 4. is there. A screw-type second reduction screw 25 that continuously reduces and conveys the second item conveyed by the second conveyance screw 23a to the rough sorting grain pan 41 is connected to the right end of the second conveyance screw 23a.

  The chopper 19 disposed at the lower rear end of the threshing device 3 is provided with a plurality of rotary blades 19b aligned and arranged at predetermined intervals in the circumferential direction and the left-right direction on a left-right chopper shaft 19a. With respect to the plurality of fixed blades 19c arranged and arranged at regular intervals in the direction, the threshing cereal and the like are shredded by rotating counterclockwise as viewed from the left side.

[Swing drive mechanism]
The swing drive mechanism 30 that swings the sheave case 40 is configured as follows.
As shown in FIG. 3, the front end side of the sheave case 40 is supported by a support portion 47 that is supported so as to be slidable back and forth within a predetermined small range. The rear end side of 40 is configured to be driven to swing in the vertical direction including the front-rear direction by the swing drive mechanism 30.

The swing drive mechanism 30 gives the output of the drive shaft 31 pivotally supported by the side wall portion 3a of the threshing device 3 to the rear end side of the sheave case 40 as an operating force for swing drive. However, the output transmission location that provides the operating force is located eccentric to the axis x1 of the drive shaft 31.
That is, as shown in FIG. 3, FIG. 6, and FIG. 7, an eccentric cam 32 provided to rotate integrally with the drive shaft 31 to which the driving force of the engine 70 is transmitted via the input pulley 31A, and A swing drive mechanism is provided by an eccentric drive mechanism that includes a drive transmission member 33 that is externally fitted to the eccentric cam 32 and a swing link 34 that is rotatably coupled to the drive transmission member 33. 30 is configured. Therefore, the eccentric cam 32 that moves eccentrically with respect to the axis x1 of the drive shaft 31 serves as an output transmission location to the rear end side of the sheave case 40.

The drive transmission member 33 includes a ring portion 33A that is externally fitted to the eccentric cam 32 via a ball bearing 32a, and an arm that extends radially outward from the outer peripheral side of the ring portion 33A. A pivotal support portion 33C that supports the connecting shaft 35 fixed to the bottom surface side of the sheave case 40 is provided at the distal end portion of the arm portion 33B.
One end side of the swing link 34 is pivotally supported by a lateral support shaft 3b provided on the side wall 3a of the threshing device 3, and the other end side is pivotably supported around the axis x2 of the lateral support shaft 3b. The pivot portion 34A provided on the other end side pivotally supports the connecting shaft 35 together with the pivot portion 33C provided on the arm portion 33B of the drive transmission member 33, thereby swinging the sheave case 40 in the vertical direction including the front-rear direction. It is configured to be driven dynamically.

The eccentric cam 32 is formed in a disc shape having an arc center p1 at a position eccentric with respect to the axis x1 of the drive shaft 31, and the axis of the drive shaft 31 is rotated with the rotation of the drive shaft 31. It is driven to rotate around x1. Along with this, the drive transmission member 33 rotates relative to the eccentric cam 32, and the vertical direction includes the front-rear direction from the highest position U indicated by the solid line to the lowest position D indicated by the phantom line in FIG. Driven by.
At this time, the pivot 33C provided on the arm 33B of the drive transmission member 33 pivotally supports the connecting shaft 35 fixed to the bottom surface side of the sheave case 40 together with the pivot 34A of the swing link 34. The connecting shaft 35 swings in the vertical direction including the front-rear direction around the axis x2 of the lateral support shaft 3b of the swing link 34, and the rear end portion of the sheave case 40 swings in the vertical direction including the front-rear direction. It is configured to be.

  A balance weight 36 is detachably attached to the eccentric cam 32 on one side of the lateral side surface 32b via a mounting bolt 36a, and an annular flywheel portion 37 is provided on the other lateral side surface 32b. These are detachably mounted via mounting bolts 37a.

As shown in FIG. 7, the balance weight 36 attached to the lateral side surface 32 b on one side has the center of the eccentric cam 32 of the drive shaft 31 so that the arm portion 33 </ b> B of the drive transmission member 33 exists at the highest position U. It is attached so as to be located on the lower front side of the eccentric cam 32 in a state of being located on the upper rear side with respect to the shaft center x1.
That is, the drive shaft 31 is placed on the straight line L connecting the axis x3 of the connecting shaft 35 supported by the arm portion 33B at the highest position U, the center p1 of the eccentric cam 32, and the axis x1 of the drive shaft 31. The balance weight 36 is mounted so that the center of gravity G of the balance weight 36 exists on the opposite side to the center p1 of the eccentric cam 32.
Therefore, when the eccentric cam 32 rotates and the shaft center x3 of the connecting shaft 35 supported by the arm portion 33B reaches the lowest lowered position D, the balance weight 36 is moved to the drive shaft 31 as shown by the phantom line in FIG. It is comprised so that it may move above the shaft center x1.

As shown in FIGS. 6 and 7, the flywheel portion 37 attached to the other side surface 32 b is formed in a thick annular shape on the outermost periphery side, and the center of the annular shape is the center of the drive shaft 31. It is detachably mounted on the eccentric cam 32 via a mounting bolt 37a so as to coincide with the shaft center x1.
Therefore, even if the eccentric cam 32 performs an eccentric motion, the flywheel portion 37 is configured to perform a rotational motion around the axis x1 of the drive shaft 31.

[Transmission structure]
As shown in FIGS. 2 and 5, in this combine, an engine 70 is provided below the driver seat 71 in the boarding operation unit 7, and the power from the engine 70 extends leftward from the engine 70. The output shaft 72 is branched for traveling and working.

  As shown in FIG. 5, the driving power is transmitted from the output shaft 72 of the engine 70 to the left and right crawler type driving devices 6 via the driving transmission means A. The driving transmission means A includes a belt transmission type transmission mechanism 73, a hydrostatic continuously variable transmission 74, a gear type transmission mechanism (not shown) built in the transmission case 75, and the like.

  The working power is transmitted from the output shaft 72 of the engine 70 to the cutting and conveying device 2 and the threshing device 3 via the working transmission means B. The cutting and conveying apparatus 2 includes a rotating reel 9 that is driven by power from the engine 70, a cutting mechanism 10, an auger 11, and a feeder 12. The threshing device 3 includes a handling cylinder 17 driven by power from the engine 70, a swing sorting means 20, a tang 21, a first conveying screw 22a, a second conveying screw 23a, a lifting conveyor 24, and a second reducing screw 25. , And a chopper 19.

The working transmission means B transmits the power from the engine 70 from the output shaft 72 of the engine 70 to the right end portion of the tang shaft 51 through the belt transmission type transmission mechanism 50.
The rotational power of the rotary shaft 51 starts from the left end, which is the lower end of the transmission shaft 51 in the transmission direction, through the first belt transmission mechanism 52 and the left end of the first screw 22a and the left end of the second screw 23a. And a drive shaft 31 (corresponding to a sheave case swinging input shaft) for the swing drive mechanism 30 of the swing sorting means 20 so as to be transmitted to the left end portion.
The drive shaft 31 is transmitted through a branch belt transmission mechanism 53 that branches via a relay shaft 54 provided in the first belt transmission mechanism 52.

Further, the second shaft transmission mechanism 55 is provided with another second belt transmission mechanism 55 on the left end side from the position where the first belt transmission mechanism 52 is installed. To the left end of the chopper shaft 19a.
The second belt transmission mechanism 55 is provided with an intermediate pulley 56 so that the rotational power of the red shaft 51 can be transmitted at an increased speed.

The third shaft transmission mechanism 57 is provided with another third belt transmission mechanism 57 further on the left end side than the position where the second belt transmission mechanism 55 is installed. Thus, it is configured to be transmitted to the handling cylinder shaft 18 through a bevel gear type transmission mechanism 59 incorporated in the transmission case 58 as an input shaft for the handling cylinder.
That is, the rotational power of the rotary shaft 51 is transmitted to the left end portion of the left and right transmission shaft 58a provided in the transmission case 58 via the third belt transmission mechanism 57, and the bevel gear type transmission is transmitted from the right end portion of the transmission shaft 58a. It is configured to transmit to the handling cylinder shaft 18 via the mechanism 59.

  The transmission shaft 58a is provided with a belt transmission mechanism 60 for cutting and conveying, and the power from the engine 70 via the rod shaft 51 is transmitted from the transmission shaft 58 to the left end of the cutting input shaft 14 via the belt transmission mechanism 60. It is comprised so that it may transmit to a part.

  The right half of the transmission case 58 has a left and right reverse rotation shaft 58b that rotates integrally with a bevel gear 59a for taking out the reverse rotation power provided in the bevel gear type transmission mechanism 59, and the right end portion of the reverse rotation shaft 58b is the transmission case. Equipped to extend laterally outward from the right end of 58. Then, a belt transmission mechanism 61 for reverse rotation that allows transmission of reverse rotational power from the reverse rotation shaft 58b to the cutting input shaft 14 is installed over the right end portion of the reverse rotation shaft 58b and the right end portion of the cutting input shaft 14. It is.

  The power transmitted to the cutting input shaft 14 is transmitted to the rotating reel 9, the cutting mechanism 10, the auger 11, and the feeder 12 of the cutting and conveying device 2.

[Other Embodiment 1]
In the embodiment, the swing drive mechanism 30 has a structure in which the balance weight 36 and the flywheel portion 37 are arranged and arranged on both lateral side surfaces 32b of the eccentric cam 32. However, the present invention is not limited to this. You may comprise as shown in FIG.

In other words, a disc-shaped plate 38 having a boss portion 38a that fits outside the drive shaft 31 and formed in a circle centered on the same position as the axis x1 of the drive shaft 31 is arranged around the axis x1 of the drive shaft 31. The annular rib 38c constituting the eccentric cam 32 is integrally provided on the lateral side surface 38b of the disc-shaped plate 38, and the lateral side 38b of the disk-shaped plate 38 is integrally provided. An annular convex portion 38d constituting the flywheel portion 37 is integrally provided on the side surface 38b.
A drive transmission member 33 is fitted on the outer peripheral side of the annular rib 38c via a ball bearing 32a so as to be relatively rotatable, and a balance weight 36 is attached to a part of the lateral side surface 38b on the other side. It is detachably mounted via.

An annular rib 38c that is formed on one side surface 38b of the disk-shaped plate 38 and that forms the eccentric cam 32 is eccentric with respect to the axis x1 of the drive shaft 31, as shown in FIG. It is formed in an annular shape having an arc center p1 at the position, and is driven to rotate about the axis x1 of the drive shaft 31 as the drive shaft 31 rotates. Along with this, the drive transmission member 33 rotates relative to the eccentric cam 32 and extends from the highest position U to the lowest position D indicated by the phantom line as in the structure shown in FIG. It is driven in the vertical direction including the front-rear direction.
At this time, the pivot 33C provided on the arm 33B of the drive transmission member 33 pivotally supports the connecting shaft 35 fixed to the bottom surface side of the sheave case 40 together with the pivot 34A of the swing link 34. The connecting shaft 35 swings in the vertical direction including the front-rear direction around the axis x2 of the lateral support shaft 3b of the swing link 34, and the rear end portion of the sheave case 40 swings in the vertical direction including the front-rear direction. It is configured to be.

As shown in FIG. 8, the flywheel portion 37 provided on the other side surface 38b of the side surface 38b of the disk-shaped plate 38 is formed in a thick annular shape on the outermost peripheral side, and the center of the annular shape is formed. Is configured to coincide with the axis x1 of the drive shaft 31.
Therefore, even if the annular rib 38c constituting the eccentric cam 32 performs an eccentric motion, the flywheel portion 37 is configured to perform a rotational motion around the axis x1 of the drive shaft 31.

The balance weight 36 is driven by the center p1 of the annular rib 38c constituting the eccentric cam 32 so that the arm portion 33B of the drive transmission member 33 exists at the highest position U as in the structure shown in FIG. It is attached so as to be located on the lower front side of the annular rib 38c in a state of being located on the upper rear side with respect to the axis x1 of the shaft 31.
That is, the drive shaft 31 is placed on the straight line L connecting the axis x3 of the connecting shaft 35 supported by the arm portion 33B at the highest position U, the center p1 of the annular rib 38c, and the axis x1 of the drive shaft 31. The balance weight 36 is mounted so that the center of gravity G of the balance weight 36 exists on the opposite side to the center p1 of the annular rib 38c.
Therefore, when the annular rib 38c constituting the eccentric cam 32 rotates and the axial center x3 of the connecting shaft 35 supported by the arm portion 33B reaches the lowest lowered position D, as shown by the phantom line in FIG. The weight 36 is configured to move above the axis x1 of the drive shaft 31.

The annular rib 38c and the flywheel portion 37 may be integrated with the disk-shaped plate 38 by welding or integral molding with a casting, or may be integrated by bolting together with another member. May be. Further, the balance weight 36 may be integrally formed.
Other configurations may be configured similarly to the above-described embodiment.

[Second embodiment]
In the embodiment, the oscillating drive mechanism 30 has a structure using the eccentric cam 32 that rotates integrally with the rotation of the drive shaft 31, but is not limited thereto, for example, as shown in FIG. 9. You may comprise as follows.

  That is, as shown in FIG. 9A, the swing drive mechanism 30 constituted by a combination of an eccentric cam 32 and a drive transmission member 33 similar to the structure shown in FIG. 6 or FIG. A balance weight 36 attached to a part of 31B in the circumferential direction is used. Then, the eccentric cam 32 is mounted on the drive shaft 31 so as to rotate integrally, and the disk-like member 31B is fitted on the drive shaft 31 and is driven to rotate in the direction opposite to the rotation direction of the drive shaft 31. It is mounted so as to rotate integrally with the cylinder shaft 31C.

Power transmission from the drive shaft 31 to the drive cylinder shaft 31 </ b> C and the disk-shaped member 31 </ b> B is performed via the reverse rotation mechanism 39.
The reversing mechanism 39 meshes a bevel gear 39b pivotally supported at a fixed position on the fuselage with a bevel gear 39a mounted to rotate integrally with the drive shaft 31, and is driven with respect to the bevel gear 39b. A bevel gear 39c provided on the cylindrical shaft 31C is engaged with each other. As a result, the disk-like member 31B fixed to the drive cylinder shaft 31C is driven to rotate in synchronization with the eccentric cam 32 mounted so as to rotate integrally with the drive shaft 31 at the same speed in the opposite direction. It is configured to be.

Since the eccentric cam 32 and the disk-shaped member 31B configured in this way are driven in the reverse direction, they are mounted so as to rotate together with the eccentric cam 32 and the disk-shaped member 31B. The balance weight 36 rotates as shown in the conceptual diagram of FIG.
That is, at the position shown in (1) of FIG. 9B, the balance weights 36 (positions shown by diagonal lines in the figure) mounted on the left and right eccentric cams 32 and the disc-like member 31B are both eccentric cam 32 and It is located in the lower part of the disk-shaped member 31B. In this state, the acting directions of the inertial forces of the left and right balance weights 36 both act downward, and are configured to act in the direction opposite to the swinging direction of the sheave case 40 that swings upward and swinging upward.
From this state, the right disk-shaped member 31B rotates counterclockwise, and the left eccentric cam 32 rotates counterclockwise.

In the position shown in (2) of FIG. 9B, the balance weight 36 of the right disk-shaped member 31B is on the right side in the figure, and the balance weight 36 of the left eccentric cam 32 is on the left side in the figure. To do. As a result, the direction of action of the inertia force of the balance weight 36 is directed in the opposite direction to each other and acts to cancel each other.
In the position shown in (3) of FIG. 9B, both the eccentric cam 32 and the balance weight 36 attached to the disk-like member 31B are located above the eccentric cam 32 and the disk-like member 31B. In this state, the acting direction of the inertia force of the left and right balance weights 36 acts upward, and is configured to act in the direction opposite to the swinging direction of the sheave case 40 swinging downward.
9 (b), the balance weight 36 of the right disk-shaped member 31B is on the left side in the figure, and the balance weight 36 of the left eccentric cam 32 is on the right side in the figure. To do. As a result, the direction of action of the inertia force of the balance weight 36 is directed in the opposite direction to each other and acts to cancel each other.
Other configurations may be configured similarly to the above-described embodiment.

[3 of another embodiment]
In the embodiment, an example in which the oscillating drive mechanism 30 is configured using the eccentric cam 32 is illustrated, but the configuration is not limited thereto, and for example, a configuration as illustrated in FIG. 10 may be used.
That is, the drive shaft 31 to which engine power is transmitted is constituted by a crankshaft, and the flywheel portion 37 is mounted to rotate integrally with a central shaft portion 31D that rotates concentrically with the shaft center x1 that is the rotation center of the drive shaft 31. To do.
Then, the balance weight 36 is attached to the eccentric shaft portion 31D that rotates at a position eccentric with respect to the shaft center x1 as the rotation center of the drive shaft 31 so as to rotate integrally, and the bearing portion 40A of the eccentric shaft portion 31E is mounted. The sheave case 40 may be provided on the bottom side of the sheave case 40 so that the sheave case 40 is swung up and down.
Other configurations may be the same as those in the above-described embodiment.

[4 of another embodiment]
In the embodiment, only the input pulley 31A has a function for power transmission, but is not limited thereto. For example, as shown by a virtual line in FIG. 9, the outer peripheral portion of the input pulley 31A. In the vicinity, a thick portion 31Aa having a thickness sufficiently thicker than the thickness for securing the strength necessary for the flywheel portion 37 is provided, and the inertia required to make the input pulley 31A as the flywheel portion 37 is obtained. You may comprise in such a structure.
Other configurations may be configured similarly to the above-described embodiment.

[5 of another embodiment]
In the embodiment, the flywheel portion 37 is formed in a continuous annular shape. However, the present invention is not limited thereto, and the drive shaft 31 is formed by, for example, forming a discontinuous thick portion in the same arc shape. The flywheel portion 37 may be configured such that the weight is evenly or substantially evenly distributed over the entire area in the circumferential direction around the same axis as the axis x1.
Other configurations may be configured similarly to the above-described embodiment.

  The present invention can also be used for a self-removing combine machine equipped with a glen tank instead of a bagging device.

DESCRIPTION OF SYMBOLS 3 Threshing apparatus 3a Side wall part 30 Oscillation drive mechanism 31 Drive shaft 31A Input pulley 32 Eccentric cam 36 Balance weight 37 Flywheel part 40 Sheave case x1 axis

Claims (6)

A sheave case configured to select a specific gravity of a workpiece by swinging the other end side up and down with the one end side as a swing fulcrum, and a swing drive mechanism that swings the other end side of the sheave case Prepared,
The swing drive mechanism is configured by an eccentric drive mechanism in which an output transmission location to the other end side of the sheave case is eccentric with respect to an axis of a drive shaft pivotally supported on a side wall portion of the threshing apparatus. ,
The eccentric drive mechanism is provided with a balance weight for vibration suppression that imparts a motion inertia in the direction opposite to the up-and-down swing direction on the other end side of the sheave case, and is the same as the axis of the drive shaft. A sorting apparatus provided with a flywheel portion having a weight distributed evenly or substantially uniformly over the entire region in the circumferential direction around an axis.   The sorting apparatus according to claim 1, wherein the flywheel unit is provided so as to be driven integrally with the drive shaft.   The sorting apparatus according to claim 1 or 2, wherein the flywheel unit is provided so as to be driven integrally with an eccentric cam constituting the eccentric drive mechanism.   The sorting apparatus according to claim 3, wherein the flywheel unit is configured integrally with an eccentric cam constituting the eccentric drive mechanism.   The sorting apparatus according to claim 3 or 4, wherein the flywheel portion is disposed on the opposite side of the balance weight with the eccentric cam interposed therebetween.   The sorting apparatus according to claim 1 or 2, wherein the flywheel portion is configured integrally with an input pulley provided on the drive shaft that extends outward from a side wall portion of the threshing device.

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