JPS6137886B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an agricultural binding machine used for binding waste straw after threshing in a combine harvester, or for binding grain culms after reaping in a binder.

This kind of agricultural tying machine, which is widely used, winds the string around the grain bundle after the tying clutch is activated, and supplies the string to the knotting building and the holder for holding the string end. The string is passed through the needle provided on the opposite side of the holder, that is, the string insertion hole formed at the tip, and the string is constantly grasped, and when the binding clutch is activated, the string is passed across the convergence path and the above-mentioned string winding and string supply are carried out. The needle is arranged to cross the focusing path and return to the original position after the focusing is completed.

On the other hand, the applicant of the present application has previously determined that the winding of the string, whose end is held in the holder, around the grain culm bundle and the supply to the bill and the holder are performed at the nodule point based on the convergence path of the grain culm bundle. A cord supplying arm provided on the same side as the cord, which is reciprocated from the standby position only when the binding is activated, engages the cord midway through the engagement metal at the tip on the opposite side of the knot when viewed from the above-mentioned focusing path, and An agricultural tying machine has been developed which is configured to move the string to wrap the grain bundle around the grain culm bundle, and to wrap the string around the grain culm bundle, using a string supply arm that detaches from the string after being supplied to the building and the holder.

This new agricultural binding machine uses the above-mentioned string supply arm to wind the string around the grain culm bundle and supply the string to the building and holder, instead of the needle in the conventional one. The agricultural binding machine of 1999 had a structure in which the needle, its related mechanism, and the knot part were placed opposite each other with a convergence passageway in between, but the string winding and supply mechanism was provided on the knot part side, and therefore the binding Related mechanisms such as clutches can also be provided on the knotting section side, and as a result, the entire tying mechanism can be installed on one side of the convergence path, thereby reducing the size of the tying case and making the entire tying machine extremely compact. It becomes lightweight.

The object of the present invention is to provide a novel agricultural binding machine as described above, which is designed to ensure its operation, and in particular, to improve the flow rate of grain culms sent into the concentrating passage. Even when the string feeding arm is large in size, the engaging alloy at the tip of the string supply arm can reliably pass through the grain culm flow, cross the convergence path, and reach the engagement position with the string, and the engaging alloy can be moved against the string. To provide an agricultural tying machine designed to ensure reliable engagement and to ensure that strings are removed from the engaging metal in preparation for the next tying operation.

Regarding the illustrated embodiment, the configuration of the agricultural binding machine according to the present invention will be explained. As shown in FIG. In a waste straw processing case 2 to which waste straw after threshing is supplied, a waste straw cutter C is installed, with the waste straw cutter C disposed below and the binding machine B disposed above. The binding machine B has U-shaped rails 3a with open lower ends provided at both ends of the upper part of the support frame 3 attached to the upper surface of the binding machine B.
Front and back 1 spanned between both side walls of waste straw processing case 2
By placing it on the pair of support pipes 4, it is supported in a suspended manner, and by tilting it backward and downward at an appropriate angle, the lower surface thereof becomes a focusing passage 5, and the waste straw processing case 2
is installed inside. The straw cutter C is a disk cutter in which cutter disks 8 and 9 for handling multiple sheets are equipped on a pair of parallel cutter shafts 6 and 7.
It is composed of cutters. Inside the waste straw processing case 2, there is a straw supply port 10 to the waste straw cutter C.
a first shutter 11 that selectively opens and closes the straw, and a straw supply port 12 to the tying machine B or its concentrating passage 5;
a second shutter 13 that selectively opens and closes the
It is supported rotatably around each fulcrum shaft 11a, 13a. The fulcrum shaft 11a to which the first shutter 11 is attached is supported by a fixed support cylinder 14, and is also fixed to an arm 16 that is rotatably displaced by an operating cable 15 operated from the combine operator's seat. Further, the arm 16 and the arm 13b vertically disposed on the second shutter 13 are interlocked and connected by an interlocking rod 17 having a long hole at one end. As described above, when the arm 16 is placed in the position shown in the figure, each shutter 11, 13 is in the position shown by the solid line, the straw supply port 10 is closed, the straw supply port 12 is opened, and the straw is sent to the binding machine B. After the supplied bundling is performed, the arm 16 is rotated to the position shown by the chain line, and each shutter 11, 13 is then rotated to the position shown by the chain line, so that the straw supply port 10 is opened and the straw supply port 10 is opened. 12 is closed, and the waste straw is supplied to the waste straw cutter C, so that the waste straw is shredded.
It is planned. The bundling machine B is capable of adjusting its displacement left and right by moving the rail 3a on the support pipe 4, thereby making it possible to change and adjust the bundling position according to the length of the waste straw.

Hereinafter, the specific structure of the illustrated binding machine B, only the outline of which is shown in FIG. 1, will be explained with reference to FIG. 2 and subsequent figures.

As shown in Figures 2-5, the illustrated binding machine B is
A binding case is provided only on one side (the upper side in FIG. 1) of the above-mentioned focusing passage 5, and the binding case is
It is composed of a case body 21 and a case lid 22 which is fixed to the case body 21 and closes an opening on one side of the body 21. A deck 23 is fixedly attached. Binding cases 21, 22
Inside, there is an input shaft 24 with one end facing outside the case body 21, a pusher shaft 25 with one end facing outside the case lid 22, and an input shaft 25 with one end facing outside the case body 21 and the other end facing outside the case body 21. The clutch shaft 26 facing outside the case lid 23 and the door shaft 27 having one end facing outside the case lid 22 are parallel to each other, and the clutch shaft 26 is parallel to the input shaft 24 as shown in FIG. axis 2
5 and the clutch shaft 26 are arranged at approximately equal intervals and are rotatably provided.

In order to push the grain culms (waste straw) into the collecting passage 5, a packer is provided as in a conventional binding machine, but in the case shown, the packer is a main packer disposed on the outer surface of the case lid 22. 27A and the auxiliary pack car 27 placed on the outer surface of the case body 21
It is also composed of B. Main police car 27
A is provided with one end pivoted 30 on a rotation support arm 29 whose pivot shaft 28 is one of the connecting rods connecting the case body 21 and the case lid 22, and fixed to the packer shaft 25. Pats car crank 3
1 through a pivot connection 32. The auxiliary packer 27B is fixed 34 at its base end to a bracket 33 (FIG. 2) provided on the main packer 27A. By meshing the packer shaft 25 and the gear 35 fitted therewith with the gear 36 fitted to the input shaft 24, the main packer 27A is constantly driven by the input shaft 24. It is constantly driven so as to rotate and displace along the trajectory _C1 shown in FIG. Also, auxiliary police car 27
Since B is fixed to the main packer 27A, it is driven in the same way as the main packer 27A.

A door 38 is provided on the outer surface of the case lid 22 in order to receive grain culms (waste straw) at the end of the collecting passage 5. In the case shown, this door 38 is
7, which is provided with a plurality of insertion holes 39a for fixing devices 40 so that the amount of door protrusion in the direction of the focusing passage 5 can be changed. On the clutch shaft 26, a clutch gear 41 meshed with the gear 36 on the input shaft 24 is loosely fitted. A sense actuated tie-down clutch 42 is conventionally provided. The specific structure of the illustrated binding clutch 42 will be explained later, but in any case, the clutch shaft 26 is connected to the binding clutch 42 in the same manner as in the conventional binding machine.
It is intermittently driven one rotation by the operation of .

A bill 43 for tying a tying cord and a holder 44 for holding the end of the cord are arranged such that the bill 43 is placed on the upstream side in the grain culm flow direction and the holder 44 is placed on the downstream side in the same direction, as in the conventional binding machine. They are arranged and arranged side by side, respectively. As shown in FIG. 3 for the building 43, these buildings 43 and holders 44 are supported by a support provided on the deck 23, and small diameter bevel gears 43a, 44a are connected to the base end as in the conventional binding machine. The drive shaft 43b, 44b (the drive shaft 43b is integrated with the building body, and the drive shaft 44b is spline-fitted to the holder body), etc. , a large-diameter drive bevel gear 45 provided with teeth 45a only in a certain angular range, which meshes with the small-diameter bevel gears 43a and 44a in the middle of one rotation of the clutch shaft 26 to drive the building 43 and holder 44. A driving bevel gear 45 is fixedly mounted directly on the clutch shaft 26. The building 4 is driven in the middle of one rotation of the clutch shaft 26.
3 and the holder 44 are the same as conventional ones.

In order to discharge the bundled grain culm (waste straw) bundle, a discharge arm is provided as in the conventional binding machine. In the case shown in the figure, two ejection arms 46 are arranged on both sides of the fuselage case part 21-23.
A, 46B are provided, and the release arms 4 on both sides
A connecting pipe 47 connecting 6A and 46B is supported by the deck 23 via a connecting frame 49 having pivot points 49a and 49b at both ends. A release crank 50 is loosely fitted onto the clutch shaft 26 outside the case body 21, and the release arm 46 on one side
A is pivotally connected 51 to the discharge crank 50, and is connected to a rotary cylinder 52 at the proximal end of the discharge arm 46A.
A connecting pipe 47 end is attached. A crank plate 53 is provided fixed to the clutch shaft 26, and this crank plate 53 and the discharge crank 50 are connected to each other.
The rotation of the clutch shaft 26 is transmitted to the discharge crank 50 by connecting the clutch shaft 26 with a pin 53a. As described above, the ejection crank 50 is driven by the clutch shaft 26 during one rotation of the clutch shaft 26, and causes the ejection arms 46A, 46B to move along the rotational trajectory shown in FIG.
The bundle is released and rotated so that it is displaced along C ₂ .

As mentioned above, the illustrated binding machine B includes packers 27A and 27B, a door 38, a building 4
3. Holder 44 and release arms 46A, 46B
Also, a tying clutch 42 is provided, but the needle provided in the conventional tying machine is
It is no longer set up. In place of the conventional needle, a string supply arm 55 as described below is provided.

That is, the supply arm fulcrum shaft 5 is rotatably supported by the deck 23 and protrudes outside the deck 23.
The rotation support arm 57 whose base end is attached to 6,
The string supply arm 55, which is provided on the outer surface of the deck 23, has a cylindrical body 55a fixed to its base end.
Support cylinder 57 fixed to the tip of rotation support arm 57
A is fitted and fixed to a pin 58 which is rotatably supported on the supply arm fulcrum shaft 56, and is rotatable around the supply arm fulcrum shaft 56 together with the rotation support arm 57, and relative to the rotation support arm 57 around the pin 58. It is rotatably supported and provided along the outer surface of the deck 23 outside the outer surface. A string supply crank 59 is fitted to the end of the clutch shaft 26, and the other end of a drive arm 61 whose one end is pivoted 60 to the string supply crank 59 is connected to a pin 6 midway through the rotation support arm 57.
2, so that the lace supply arm 55 can be driven when the clutch shaft 26 rotates.

An engaging metal 64 is provided at the tip of the string supply arm 55 in the following manner. That is, as clearly shown in FIGS. 6 and 7, a boss 55a is welded and fixed to the tip of the string supply arm 55.
A fulcrum shaft 65a is rotatably inserted and supported in the hole of the string supply arm 55 and is prevented from coming out with a retaining ring.
A pedestal 65 equipped with a pedestal 65 is rotatably supported by the string supply arm 55 around a fulcrum shaft 65a. This pedestal 65 is formed into an L-shaped cross section having a horizontal plate part 65b and a vertical plate part 65c, as seen in FIGS.
A boss 65d is fixed on the opposite side to the extending direction of b, and a hole 65e of the same diameter is bored concentrically with the hole of the boss 65d. And the above-mentioned engagement alloy 6
4 is attached with a support shaft 67 by inserting the end into the hole of the metal fitting 64 and fixing it with a pin 66. With the engaging metal 64 facing onto the pedestal 65, the support shaft 67 is inserted into the hole 65e and the boss 65d. The engagement alloy 64 can be rotated around the support shaft 67 by inserting it into the pedestal 6 so that it can be rotated.
5 is supported. That is, the engagement alloy 64 is
It is supported by the string supply arm 55 so as to be rotatable along with the pedestal 65 around the fulcrum shaft 65a, and also supported by the pedestal 65 so as to be rotatable around the fulcrum shaft 67.

The string supply arm 55 supported as described above and driven as described above is connected to each arm 55, 57, 61.
By appropriately setting the length etc., the clutch shaft 26
During one rotation, the fulcrum shaft 65a of the pedestal 65 on which the engaging alloy 64 is placed as described above first moves from the standby position _P0 to the focusing passage ₅ along the trajectory C3 shown in FIG.
cross in the other direction to reach the first dead center position _P1 , then cross the focusing passage 5 in the opposite direction, and then cross the building 4.
3 and the holder 44 position, and the holder 4
It reaches the other dead center position _P2 , which is slightly past the 4th position,
It is then driven to return to the standby position _P0 again. The above trajectory C ₃ is the movement trajectory of the fulcrum shaft 65a at the tip of the string supply arm 55.
is set at a trajectory such that the angle formed by the string supply arm 55 with respect to the focusing path 5 is always kept constant, and for this purpose, the following mechanism is provided. That is, as clearly shown in Figure 3,
A sprocket wheel 69 is provided on the supply arm fulcrum shaft 56, and is fixedly connected to the deck 23 by a connector 68 and restrained from rotating.
Further, another sprocket wheel 70 is fixedly installed on the pin 58 at the base end of the string supply arm 55, and both of these sprocket wheels 69, 7
0, the chain 7 has a length adjustment part 71a.
1 is turned over. Therefore, the drive arm 6
1, the rotation support arm 57 and the string supply arm 5
When 5 is rotated, the rotation support arm 5
7 drives the chain 71 and rotates the pin 58 together with the sprocket wheel 70, so that the string supply arm 55, whose base end is fixed to the pin 58, is moved relative to the rotation support arm 57. The angle between the rotation support arm 57 and the string supply arm 55 is changed, and the string supply arm 55 is designed to always form a constant angle with respect to the focusing path 5. be.

A knot cover 72 is provided on the focusing passage 5 side of the knot section including the bill 43 and the holder 44, as in the conventional binding machine, and a knot cover 72 is provided on the inner surface side of the knot cover 72 in front of the bill 43. Similarly to the conventional binding machine, a string guide 73 (FIG. 5) is provided for directing the tip of the string R toward the building 43 and the holder 44. On the other hand, in the case shown, the second shutter 1
3 (FIG. 1), the following string guide means is provided. That is, as shown in FIG. 5, the string guide means has a first string guide 74 located on the upstream side in the flow direction of grain culms (excluded straw) and a second string guide 75 located on the downstream side. , and as shown in FIG. 9, the first string guide 74
is equipped with a guide portion 74a such that the portion of the string R on the proximal end side of the first string guide 74, which the string R comes into contact with from the opposite side of the focusing path 5, is always made substantially parallel to the focusing path 5. Furthermore, when the string R comes into contact with the second string guide 75 from the focusing path 5 side, the string R portion between the first and second string guides 74 and 75 is made to be approximately parallel to the focusing path 5. The guide portion 75a is provided with a guide portion 75a.
It is provided with two leg portions 75b extending in a widening shape toward the focusing passage 5 from both ends of the a. The first and second string guides 74, 75 are arranged so that when viewed in the direction along the focusing path 5, the two guides 74, 75 form a closed string guiding channel C _h as shown in FIG. 9b. It is provided on the shutter 13 in a suitable arrangement.

Engagement alloy 64 at the tip of the string supply arm 55 described above
While being moved along the trajectory _C3 shown in FIG. 2, the string R guided by the guide means as described above crosses the focusing path 5 and reaches the first dead center position _P1. It engages when it is about to return in the opposite direction again, and continues along the trajectory C ₃ to reach the other dead center position P ₂ . During that time, the grain culm bundles that are converged in the convergence passage 5 on the front side of the door 38 At the same time as winding the string R, the string R is supplied to the building 43 and the holder 44, and on the way back from the dead center position _P2 to the standby position _P0 , the engagement with the string R is released and the string R is It is configured to remove the For this purpose, the engaging alloy 64 is _particularly
The posture is changed from the position Y ₁ where it has almost crossed the focusing path 5 to the engagement posture in which it reliably engages with the string R,
At a point _Y2 in the middle of the return stroke from the other dead center position _P2 , when the string knotting operation by the knotter is completed, the engaging metal 64 is maintained in the same engaged posture until the position _Y2 . , in the latter position to ensure that the string R is removed.
It is designed to be moved from Y ₂ to the disengaged position with the string R.

Therefore, first, the above-mentioned engagement posture and disengagement posture of the engagement alloy 64 will be explained with reference to FIGS. By being moved, the posture can be changed between the above two postures, and FIGS. 7a and 8a show the above engagement posture,
FIG. 7b and FIG. 8b show the above-mentioned disengaged posture. That is, the engagement alloy 64 is formed into a tapered end shape as shown in FIGS. 6-8, and is oriented laterally and outward in the engagement posture shown in FIGS. 7a and 8a. As shown in FIG.
4 is configured such that string guide grooves 64a, 64b, which engage the string R in a relatively slidable manner at the grooves 64a, 64b, are continuously provided over one side and the back surface. The surface 64c located on the upper side in the engaged position as seen in FIG. 7a is inclined downward toward the tip end, and the string guide groove 64 on one side
4a is inclined in this direction, and the string guide groove 64b on the back side runs approximately horizontally from the rear end of the former groove 64a. Furthermore, when the engaging alloy 64 moves from the standby position P ₀ to the first dead center position P ₁ in the direction of the focusing passage 5, it moves along the axial direction of the support shaft 67 as described later in FIGS. 7b and 8. Although it is moved toward the distal end as shown by the arrow A in Figure b, it is shaped so that its width is particularly small in the disengaged position shown in the figure. The engagement alloy 64 is moved 90 degrees in the direction of arrow B in FIG. 7b on the pedestal 65.
When the engaging metal 64 is rotated once, it is moved to the engaged position shown in FIG. 7a.
A stopper surface 64d that comes into contact with the horizontal plate portion 65b of the pedestal 65 to restrict further rotation of the engaging metal 64 in the direction of arrow B when the engaging metal 64 is rotated by 90 degrees 64.

In order to rotationally displace the engagement alloy 64 between the above-mentioned positions, the following driving means is provided. That is, first, as shown in FIGS. 2, 3, and 5, the tip of the rotary support arm 57 is bent from the position of the pin 58, and a plate having an L-shaped cross section is welded and fixed to the bent tip. A drive frame 76 that rotates integrally with the rotation support arm 57 is formed. A plate-shaped drive arm 78 is connected to the drive frame 76 by a pin 77 and is provided along the string supply arm 55. The tip of the drive arm 78 is a curved arm part 78a that is stepped from the main body of the drive arm 78, and is connected to the pin 7.
A curved arm portion 78 is connected to the drive arm 78 body at 9 and is welded to the drive arm 78 body.
It is composed of a.

As shown in FIGS. 6 and 7, a pair of through holes 80 and 81 are bored in the curved arm portion 78a at the tip of the drive arm 78 at a mid-curving point position and at a tip position protruding in the direction of the string supply arm 55. A pin 82 is inserted into the through hole 80 and prevented from coming out with a retaining ring.
A drive cam 83 is rotatably supported by a curved arm portion 78a at the tip of the drive arm 78. It is provided. The holder hardware 82 is provided with a through hole 82b through which the base end of the support shaft 67 described above is inserted.
The support shaft 67 has its proximal end inserted into the through hole 82b and a retaining ring for preventing removal is attached to the proximal end, so that the distal end is supported by the pedestal 65 and the proximal end is supported by the holder. It is supported by hardware 82. As shown in FIG. 5, the center of the pin 58 at the base end of the string supply arm 55 is S ₁ , the center of the pin 77 at the base end of the drive arm 78 is S ₂ , and the center of the fulcrum shaft 65 a at the tip of the string supply arm 55 is S 1 . Center S ₃ , drive arm 78
If the center of the pin 82a at the tip is _S4 , then the length is
S ₁ S ₂ and length S ₃ S ₄ are equal, length S ₁ S ₃ and length S ₂ S ₄ are equal, and quadrilateral S ₁ S ₂ S ₃ S ₄ forms a parallelogram. A connecting plate 86 connected to pins 84 and 85 is provided near the tip of the string supply arm 55 and near the tip of the drive arm 78, and between the centers S ₅ and S ₆ of the pins 84 and 85. The length S ₅ S ₆ of the four-point parallel link S ₁ S is set equal to the above-mentioned lengths S ₁ S ₂ and S ₃ S ₄ , and the shape changes as the rotation support arm 57 rotates. ₂ S ₃ S ₄ is formed. This four-point parallel link S ₁ S ₂ S ₃ S ₄ is set such that points S ₃ and S ₄ are always located on the trajectory C ₃ .

By configuring the four-point parallel link S ₁ S ₂ S ₃ S ₄ in this way, the support shaft 67 constituting one side of the four-point parallel link S 1 S 2 S 3 S 4
The relative posture with respect to the string supply arm 55 and the drive arm 78 is changed when the rotation support arm 57 is rotated, and the support shaft 67 is provided with a through hole 87a as shown in FIGS. 6 and 7. The driven cam 87 inserts the support shaft 67 into the through hole 87a and attaches the pin 88 to the support shaft 67.
By fixing it, it is fixedly installed. This driven cam 87 cooperates with the driving cam 83 to control the attitude change of the engaging metal 64, and both cams 87
3 and 87 are related as follows. That is, first, the drive cam 83 is formed with an integrally protruding engaging portion 83b which is adapted to engage with the pin 82a of the holder hardware 82, and one end is inserted into a through hole 83c formed in the cam 83. is inserted, and the other end is pressed against the pin 82a of the aforementioned holder metal fitting 82.
b is rotationally biased in the direction in which it engages with the pin 82a. On the other hand, the driven cam 87 is formed with an integrally protruding engaging portion 87b that engages with the driving cam 83, and on the support shaft 67, between the driven cam 87 and the holder metal fitting 82, one end of the engaging portion 87b is formed. Holder hardware 82
A torque spring 90 is provided, the other end of which is received by the spring receiving step 82c formed in the spring support step 82c, and whose other end is in contact with the driven cam 87. The engagement alloy 64 is rotated and biased in the direction of arrow B.
In the support shaft 67 phase when the cam is placed in the disengaged position, the driven cam 87 is moved by the biasing force of the torque spring 90.
is designed to engage with the drive cam 83 as shown in FIGS. 7b and 10a. Therefore, the engagement alloy 64 fixed to the tip of the support shaft 67
is constantly rotated and biased by the torque spring 90 in the direction of changing the attitude from the above-mentioned disengaged attitude to the engaged attitude, and the driven cam 8 changes the disengaged attitude to the engaged attitude.
7 is maintained by engagement with the drive cam 83.

By changing the shape of the four-point parallel link S ₁ S ₂ S ₃ S ₄ , the above-mentioned cams 83, 87 and spring 89,
90, the attitude of the engagement alloy 64 can be changed as follows. That is, this is connected to the engagement alloy 64 and both torque springs 8.
10, which depicts changes in the relative posture between the string supply arm 55 and the drive arm 78, with illustrations 9 and 90 omitted and some parts exaggerated, will be explained as follows. FIG. 10a corresponds to FIG. 7b and shows a state in which the string supply arm 55 and the engaging metal 64 are in the standby position, and at this time, the driven cam 87 is in the engaging portion 87b as described above. 10a, the drive cam 83 is inserted from the upper side as seen in FIG.
The drive cam 83 is engaged with the torque spring 89
The engaging portion 83b is also tightly engaged with the pin 82a by force, and rotation of the support shaft 67 is prevented.
When the string supply arm 55 is moved from such a standby position, the engaging metal 64 moves into the focusing passage 5.
Until the fulcrum shaft 65a of the pedestal 65 reaches the first dead center position _P1 (FIG. 2), the drive arm 78 remains relative to the string supply arm 55 as indicated by the arrow shown in FIG. 10a. A four-point parallel link S ₁ S ₂ S ₃ S ₄ is set so as to move in the proximal direction.
Therefore, while the fulcrum shaft 65a is moved from the standby position _P0 to the first dead center position _P1 , the drive arm 7
The drive cam 83, which is supported by the drive arm 87 and whose relative position with the drive arm 78 is kept constant by engagement with the pin 82a, moves in a direction away from the engagement portion 87b of the driven cam 87. However, the driving cam 83 is disengaged from the driven cam 87 at the position Y ₁ (FIG. 2), where the engaging metal 64 has almost crossed the focusing passage 5. 87 shapes are set. When the driving cam 83 is disengaged from the driven cam 87, the support shaft 67, which is biased by the torque spring 90 in the direction of arrow B in FIG. 10a, is rotated by the force of the spring 90. As described above, the rotation of the support shaft 67 is such that the stopper surface 64d of the engagement alloy 64, which rotates integrally with the support shaft 67, is attached to the base 65.
The engagement metal member 64 is rotated by 90 degrees and moved from the disengaged attitude to the engaged attitude. FIG. 10b shows the state when the fulcrum shaft 65a is moved to the first dead center position _P1 , and the driving cam 83 is disengaged from the driven cam 87, and the engaging portion 87b of the driven cam 87 is shown in FIG. is pointing downward.

The four-point parallel link S ₁ S ₂ S ₃ S ₄ is connected to the fulcrum shaft 65a of the pedestal 65 from the first dead center position P ₁ to the other dead center position P ₂ shown in FIG. The drive arm 78 is set to move toward the distal end relative to the string supply arm 55 as shown by the arrow shown in _FIG . When the driving cam 83 is turned downward, the driving cam 83 comes into contact with the engaging portion 87b of the driven cam 87 which is in a downward position. However, since the contact direction at this time is the direction in which the drive cam 83 rotates the support shaft 67 in the direction of the arrow B, and the engagement alloy 64 is in an engagement posture, the stopper surface 64d and the pedestal are horizontal. Since the engagement alloy 64 and the support shaft 67 are prevented from rotating in the direction of arrow B by the contact between the plate portions 65b, the drive cam 83 resists the force of the torque spring 89 as shown in FIG. 10c. death,
The engaging portion 83b is disengaged from the pin 82a and rotated, and the driving cam 83 quickly escapes from the driven cam 87. When the driving cam 83 escapes from the driven cam 87 and leaves the position of the driven cam 87 in this way, the driving cam 83 is moved again by the torque spring 89.
As a result, the engaging portion 83b is rotated to its original position in which it engages with the pin 82a. FIG. 10d depicts the state when the fulcrum shaft 65a reaches the other dead center position P ₂ (FIG. 2), and the drive cam 83 is engaged with the pin 82a with its engaging portion 83b. The driven cam 87 has been returned to its original position, and the driven cam 87 is maintained in a downward position that places the engaging metal 64 in the engaging position.

From the dead center position P ₂ to the standby position P ₀ shown in Fig. 10d
While the fulcrum shaft 65a is being moved in the direction,
The drive arm 78 is displaced in the proximal direction relative to the string supply arm 55 as indicated by the arrow in FIG. 10d. Therefore, the drive arm 78 is supported by the drive arm 78 and is engaged with the pin 82a.
Drive cam 8 whose relative position between
3 is moved in the direction of the driven cam 87 and the first
As shown in Figure 0e, the engaging portion 87b of the driven cam 87
However, this contact occurs at the position Y ₂ shown in FIG.
cam 8 so that position Y ₂ taken by 5a is carried out.
3,87 shapes are set. When the drive cam 83 is further moved in the direction of the driven cam 87 due to the relative displacement of the drive arm 78 while the drive cam 83 is in contact with the driven cam 87, the driven cam is pushed by the drive cam 83 and 87 along with the support shaft 67 in the opposite direction to the arrow B (Fig. 10e)
(in the direction of arrow E shown in the figure). In this way, while the engaging alloy 64 is returned to the standby position, the engaging alloy 64 is rotated by 90 degrees along with the support shaft 67, and the engaging alloy 64 changes from the above-mentioned engaged attitude to the disengaged attitude. It is designed to be transferred to

As shown in FIG. 6, a regulating plate 92 is fixed to one side of the tip of the string supply arm 55. This regulation plate 9
2 is a string supply arm 5 as illustrated in FIG.
The engaging portion 8 of the driven cam 87 on the support shaft 67 is moved so as to constantly change its relative attitude with respect to the shaft 67.
7b, the engaging metal 64 unexpectedly rotates the support shaft 67 in the opposite direction of the arrow B due to the force applied to the string R from the building 43 or the holder 44 side during the knotting operation by the knotting part. This is to restrict the rotation while moving, and is arranged so as to engage with the driven cam 87 almost only during the knotting operation.

Other consideration given to the string supply mechanism will be explained later along with its operation.

The above-mentioned binding clutch 42 is constructed in the same manner as well-known ones and operates in the same manner, so only an outline thereof will be explained. In FIGS. 3 and 4, 94 is
The clutch actuating arm is supported by a loose fit on the packer shaft 25, and has one end that engages with a pin 95a on the actuating arm 95 on the door shaft 27 through a long hole 94a, and a regulating protrusion 94b at the other end. In addition, a pin 9 is installed in a disk 96 that is fixed to the clutch shaft 26.
7 includes a claw 98a that engages with the regulating protrusion 94b.
A clutch arm 98 is supported, and the arm 98 has a clutch pin 98 that can be engaged with an engaging portion 41b formed in a part of the circumferential direction of the clutch gear 41 by the action of a spring 99.
b is attached. A rotary arm 100 loosely fitted and supported on the clutch shaft 25 has a roller 102 that slides in sliding contact with a cam plate 101 fixed to the clutch shaft 26 . A spring 105 is provided. The illustrated binding clutch 42 is connected to the focusing passage 5
When a set amount of grain culm (waste straw) is collected and the door 38 senses the pressure, the clutch actuating arm 94 is rotated by a certain amount and the regulating protrusion 94b disengages the claw 98a. The clutch pin 98b is moved to the engaging portion 4 by the action of the spring 99.
1b is engaged with the clutch gear 41, thereby causing the clutch shaft 26 to rotate.
Then, as the rotation of the clutch shaft 26 progresses and the roller 102 falls into the cam groove 101a formed on the cam plate 101 thereon, the rotating arm 100
Then, the clutch actuating arm 94 is rotated in the door 38 opening direction, and then the roller 102 is moved into the cam groove 101.
When pulling out from a, both arms 100, 94 are rotated in the door 38 closing direction, and then the pawl 98a engages with the regulating protrusion 94b, and the binding clutch 42 is disengaged. In FIG. 4, 107 is the case lid 2.
A reverse rotation prevention plate is pivotally supported 109 on a bracket 108 on the inner surface of the clutch 2, and engages with the engagement step of the disk 96 by the action of a spring 110, thereby preventing the clutch shaft 26 from reversing.

5 and 11, the operation of the illustrated tying machine B, especially the operation of its string supply mechanism, will be explained below when tying waste straw is performed with the shutters 11 and 13 in the position shown by the solid line in FIG. 1. I will explain it while adding some explanations of the structure.

At the start of work and after one cycle of tying operation is completed, the tying string R is guided by the first string guide 74 on the shutter 13 and the string guide 73 at the knot, as shown in FIG. 43 and the end of the cord is held in the holder 44.
In addition, the string supply arm 55 has an engagement alloy 6 at its tip.
The fulcrum shaft 65a of the pedestal 65 on which 4 is placed is at the position P ₀
The door 38 is in a standby position located at , and the door 38 is in a position to close the end of the focusing passage 5 .

As the straw is fed into the collecting passage 5 from the state shown in FIG. 5 with the help of the police cars 27A and 27B, the string R portion crossing the collecting passage 5 moves toward the door 38. As shown in Fig. 11a, the R part of the string has a loop shape, and the door
The straw is collected in front of the shutter 13.
On the side, the string R is moved in a direction along the surface of the shutter 13, and the string R comes into contact with the second string guide 75 on the downstream side of the first string guide 74, and as described above, both strings are moved. Between the guides 74 and 75, the string R is kept substantially parallel to the focusing path 5. As shown in FIG.
can be entered.

As a result of this operation of the binding clutch 42, the string supply arm 55 is moved to the fulcrum shaft 6 of the pedestal 65, as described above.
The focusing passage 5 is moved in the direction of the shutter 13 from the standby position in FIG. 11a where the fulcrum shaft 65a is at position _{P 0 to} the first dead center position in FIG. , an engaging object 64 between
When the fulcrum shaft 65a assumes a position _Y1 such that Y1 substantially crosses the focusing path 5, the engaging alloy 64 moves from the disengaged position shown in FIGS. 7b and 8b to the seventh position as described above. The posture is changed to the engaged posture shown in FIGS. a and 8a. Therefore, the interlocking alloy 64
The grain crosses the convergence passage 5 in a disengaged position with a narrow tip and a narrow cloth while pushing through the grain culm flow. The above-mentioned first dead center position P ₁ is set at a position where the engagement alloy 64 slightly passes the guides 74 and 75 between the two string guides 74 and 75 on the shutter 13, and the engagement alloy 64 The relative positional relationship between the string R between the string guides 74 and 75 in the direction perpendicular to the plane of the paper in FIG.
When passing between the two, the string R between the two
It is set so that it relatively climbs up on the slope 64c of No. 4, crosses over the engagement alloy 64, and reaches behind it.

Therefore, as described above, the string supply arm 55
crosses the focusing passage 5 in the opposite direction, and the engagement alloy 64
11b to the position shown in FIG. 11c, when the engaging metal 64 passes between both string guides 74 and 75, the middle of the string R moves to the above-mentioned position of the metal fitting 64. The string R enters from the string guide groove 64b to the string guide groove 64a, and the string R
Then, the string R is grasped in a state where it can freely slide in the length direction, and the string supply arm 55 engages with the string R with the engaging metal 64 at its tip. Therefore, as shown in FIG. 11c, the middle part of the string R is disengaged from the second string guide 75 and brought to the knot side across the convergence passage 5, and then the string supply arm 55 further rotates. While the engagement alloy 64 moves toward the building 43 and the holder 44 and reaches the position shown in FIG. 11d, the string R is wound around the focused bundle. Said track C ₃ (second
In Figure 11(d), the engaging alloy 64 passes through the lower surface of the building 43 and the string R is guided doubly by the string guide 73 as shown in Figure 11d.
is supplied, and then, as shown in FIG. 11e, the engagement alloy 64 passes through the lower surface of the holder 44 and the string R is attached to the holder 44 until the fulcrum shaft 65a reaches the other dead center position _P2 . is set so that it is supplied.

When the state shown in FIG.
3a, 44a is reached, and the building 43 is driven to tie the string R in the same manner as in the conventional binding machine.
As the knotting is performed, the holder 4
4 is driven to hold the string R and cut the string R between the node and the holding point using the knife 44d (FIG. 5). The string supply arm 55 is shown in FIG.
The engagement metal 64 returns from the dead center position to the standby position shown in FIG.
The engagement position described above is maintained until the position Y2 in FIG. ₂ , which is the position of the fulcrum shaft 65a when the knotting operation is almost completed.

Thereafter, the string supply arm 55 returns to the standby position shown in FIG. 5 and is stopped when the clutch shaft 26 stops rotating.
are moved to the disengaged position as described above, and after completion of tying, the bundled bundle is pushed out and released by rotating the release arms 46A, 46B while rotating the door 38. In addition, in the case of illustration, the second
The open position of the door 38 is set at a position where the door 38 sinks into the knot cover 72, as shown by the chain line in the figure, so that the bundle can be released smoothly.

The surface S ₁ of the case body 21 and the surface S ₂ of the knot cover 72 facing the focusing passage 5 are configured as guide surfaces that guide the grain culms (husks) in the focusing passage 5 together with the shutter 13 on the other side. and the guide surface
S ₁ and S ₂ provide a grain culm guide surface having a large width in the grain culm (hull) length direction.

Note that, unlike the above embodiment, the string supply arm 5
It is also possible to make modifications such as installing a cam on the shutter 13 and on the binding case for changing the attitude of the engaging metal member 64 at the tip of the 5 between two positions.

As is clear from the above explanation, the agricultural tying machine of this invention connects the end of the string to the holder 4.
Winding the string R held at 4 around the grain culm bundle and supplying it to the building 43 and the holder 44 are carried out by a string supply provided on the same side as the knot, with reference to the concentrating passage 5 of the grain culm bundle. The arm 55 is reciprocated from the standby position only when the binding is activated, and engages the string midway through the engaging metal 64 at the tip on the opposite side of the knotted portion with respect to the focusing passage 5, and moves the string R. As mentioned at the beginning, this is done by the string supply arm 55 which is detached from the string R after wrapping the string R around the grain bundle and supplying it to the building 43 and the holder 44. Since the string winding and supply mechanism is provided on the same side as the knot, as shown in the example, related mechanisms such as the tying clutch can also be provided on the same side as the knot, making it possible to complete the entire tying mechanism. It can be installed on one side of the convergence passage 5, and the binding case is made small, making the entire binding machine extremely compact and lightweight.

In particular, the agricultural binding machine of the present invention is capable of changing the attitude of the above-described engaging metal 64 at the tip of the string supply arm 55 between an engagement attitude and a disengagement attitude with respect to the string R. In conjunction with the movement of the string supply arm 55, the engagement alloy 64 is moved approximately from the standby position to the opposite side of the knotting section from the time when the focusing passage 5 is crossed until the time when the knotting operation is completed. Since the posture changing driving means for placing the engagement posture in the above-mentioned engagement posture is provided only during this period, the engagement alloy 64 at the tip of the string supply arm 55 moves from the standby position to the opposite side of the knot portion in the focusing passage 5. The posture of the engagement metal 64 when it crosses the ridge becomes the above-mentioned disengagement posture, and the disengagement posture in which the binding string R is not grabbed can be set almost freely. By setting the posture of the engaging alloy 64 in the shape of a tip and having a small width when viewed in the direction of movement of the engaging alloy 64, even when the flow rate of the grain culm sent into the convergence passage 5 is large, the engaging alloy 64 is It is possible to reliably move through the grain culm flow, cross the focusing passage 5, and reach the engagement position with the string R, and also change the posture of the engagement alloy 64 to the engagement posture with the string R. Since the engagement alloy 64 is made to take the engagement attitude with the string R only at the time necessary for the required operation, the engagement alloy 64 can be reliably engaged with the string R. At the same time, the string R is reliably removed from the engagement alloy 64 in preparation for the next binding operation, resulting in a binding machine that operates reliably as expected.

[Brief explanation of the drawing]

Fig. 1 is a partially cutaway schematic side view showing the main parts of a combine harvester equipped with an embodiment of the present invention, Fig. 2 is a plan view of the embodiment, and Fig. 3 is a partially expanded longitudinal section of the embodiment. 4 is a cross-sectional view of the same embodiment, and Fig. 5 is a cross-sectional view of the same embodiment.
The figure is a plan view of only the main parts of the same embodiment, FIG. 6 is an exploded perspective view of the main parts of the same embodiment, and FIGS. 7a and b show the main parts of the same embodiment in different states. 8A and 8B are perspective views showing the main parts of the same embodiment in different postures, and FIGS. 9A and 9B are perspective views of only the main parts of the same embodiment. 10a, b, c, d, and e are partially omitted perspective views showing the main parts of the embodiment in different states with some exaggerations, and FIGS. 11a and 11a,
b, c, d, and e are plan views of only the main parts of the same embodiment, respectively, and are for explaining the action;
FIG. 2 is a perspective view of only the main parts of the same embodiment for explaining the operation. B... Binding machine, R... String, 5... Focusing passage, 1
3...Shutter, 26...Clutch shaft, 27
A, 27B... Police car, 38... Door, 42...
... Binding clutch, 43 ... Bill, 44 ... Holder, 46A, 46B ... Release arm, 55 ... Strap supply arm, 56 ... Arm fulcrum shaft, 57 ... Rotation support arm, 58 ... Pin, 59 ... String supply crank, 61 ... Drive arm, 64 ... Engagement alloy, 64a, 64b ... String guide groove, 64d ...
Stopper surface, 65... Pedestal, 65a... Fulcrum shaft, 65b... Horizontal plate portion, 67... Support shaft, 73...
... String guide, 74, 75... String guide, 76...
Drive frame, 77... Pin, 78... Drive arm, 78a... Curved arm portion, 82... Holder hardware, 82a... Pin, 83... Drive cam, 83
a... Pin, 86... Connection plate, 87... Followed cam, 89... Torque spring, 90... Torque spring.

Claims (1)

[Claims] 1. A string supply arm provided on the same side as the knot, with the string end held in the holder, wrapping the string around the grain bundle and supplying it to the building and the holder, with reference to the convergence path of the grain bundle. The cord is reciprocated from the standby position only when the binding is activated, and when viewed from the above-mentioned focusing path, the cord is engaged halfway by the engaging metal at the tip on the opposite side of the knot, and the cord is moved to form a grain culm bundle of the cord. The agricultural tying machine is configured to perform this by a string supply arm that is detached from the string after winding it around the building and supplying it to the building and the holder. The engaging alloy is supported so as to be changeable between an engaged position and a disengaged position, and the engaging alloy is moved along the focusing path from the standby position to the opposite side of the knot in relation to the movement of the string supply arm. An agricultural tying machine characterized by being provided with an attitude change drive means that maintains the engagement attitude only from the time of crossing until the time of completion of the tying operation.