JPS6119627Y2 - - Google Patents

Description

[Detailed description of the invention] In a conventional binding machine, both the knot and the needle were directly connected to the one-turn clutch and were started at the same time as the one-turn clutch was engaged, so the impact when starting the one-turn clutch mechanism was large; As a result, various parts of the transmission mechanism were damaged, and vibration and noise were extremely large.

The present invention aims to improve the above-mentioned drawbacks, and includes a one-turn clutch mechanism that operates upon sensing that a certain amount of grain culm has been collected, and a nodule driven by the one-turn clutch mechanism. In the tying machine equipped with a part and a needle, a delay drive device is interposed between the needle and the one-turn clutch mechanism to delay the start time of the needle than the start time of the one-turn clutch. The invention is characterized in that the activation timing of the one-turn clutch mechanism is delayed by the operation of the delay drive device.

The embodiments shown in the drawings and related matters will be described below.

The needle drive device in this binding machine can be applied to both a combine knotter and a binder, and 5 is a receiving part, 6 is a supply part, 7 is a collection part, and 14 is a string supply port.

Transmission device The input pulley, which is driven by an appropriate shaft of the combine main body, is fixed to the spline shaft supported by the bearing and constantly rotates.The spline shaft is spline-fitted to the cylindrical shaft 21, so When the device is moved and adjusted in the direction of the culm as described later, it expands and contracts while transmitting rotation.

In Figs. 2 to 5, the transmission mechanism is housed in one transmission case 22 having a case cover 23, and an input shaft 24 is connected to a cylindrical shaft 21 by a pin 24'. The gear 25 rotates together with the input shaft 24 via a torque limiter.

However, if a torque limiter is not used, the gear 25 is fixed to the input shaft 24.

A gear 27 that meshes with the gear 25 and has a tapered pawl 27a on the side surface is spline-fitted to the crankshaft 26 having a crank pin 26 and an arm cam 26a, and a one-turn clutch boss 28
is rotatably fitted. The one-turn clutch boss 28 has a crescent-shaped convex shape 28b and a pin 28 at one end.
The cam plate 28a is provided with a cam plate 28a having a diameter c, and the small diameter portion of this cam plate 28a is formed into an arc centered on the shaft center, and when the clutch is disengaged once, the roller 3
7 are in sliding contact with each other, and a partially toothed gear 30 is spline-fitted on the other side with a loosely fitted clutch plate 29 sandwiched therebetween. The clutch plate 29 is biased in the rotational direction (counterclockwise in FIG. 5) by a torsion spring 32c that is engaged with the clutch plate 29 and 30d.

A clutch pin 31 has tapered portions 31a and 31b at both ends, and is loosely fitted into a hole 28a protruding from the cam plate 28a.
has a protrusion 29c, a tapered hole 29b into which the tapered portion 31b of the clutch pin 31 fits, and a recessed portion 29a in which the pin 28c engages to regulate the rotation angle of the clutch plate 29 relative to the cam plate 28a. As shown in FIG. 4C, the gear 30 is integrally provided with a flange-shaped cam 30a with a part (wide tooth 30b portion) cut out, and the teeth have five wide teeth 30b.
It is composed of three narrow teeth 30c and seven teeth missing.

The forward/reverse shaft 33 has one end that meshes with the wide teeth 30b and the narrow teeth 30c of the partially toothed gear 30, and has tapered holes 34a, 34b, 34c, 34 spaced at 90° intervals.
d has a bored intermediate gear 34 (24 teeth), and a swing link 35 is loosely fitted on the other side, and the swing link 35 has tapered portions 36 on both sides.
a and 36b, a mounting seat 35d having a projection 35a that pivotally supports a sliding roller 37 on the cam plate 28a and engages with the projection 29c, and a stopper cam. Boss part 3 in which 38 is rotatably fitted
5c, the stopper cam 38 has a tapered hole 38b provided at a portion corresponding to the hole 35' of the swing link 35, a recess 38a into which the mounting seat 35d fits, and a convex portion of the cam plate 28a. Two protrusions 38 that can come into contact with the arcuate portion of the portion 28b
d, 38e, and this stopper cam 3
8 is biased by a torsion spring 39 whose both ends are engaged with the small holes 38c and 35b so that the tapered hole 38b is displaced relative to the clutch pin 36, as shown in FIG. 4A.

Further, the intermediate gear 34 has a gear 4 of a multi-use shaft 40.
1 are in mesh with each other, and a needle 42 and a door 49, which will be described later, are attached to the multi-use shaft 40, and the multi-use shaft 40 serves both as a door shaft and a needle shaft.

Nodule drive mechanism The drive gear 50 consists of 10 teeth in this example,
These teeth are designed to mesh only with the wide tooth 30b of the partially toothed gear 30, and the two teeth, which are out of phase by 180 degrees, have about half of the tooth width cut out to form the partially cut teeth 50a, 50a. ', the drive gear 50 rotates 180 degrees and the cam 30a of the partially toothed gear 30 rotates to the partially partially toothed gear 50a.
Or, when the cam 50b enters the cutout, the front and rear long teeth 50b, 50b' slide into contact with the outer periphery of the cam 30a and are locked, and when the cam 30a passes through the cutout,
The cutout tooth 50a meshes with the wide tooth 30b and is driven. Also, at the same time as the last wide tooth 30b passes the long tooth 50b, the cam 30a enters the cutout tooth 50a',
Drive gear 50 rotates 1/2 turn and locks again.

In other words, the toothless gear 30 has 15 teeth, including seven toothless parts, and five of them, 5 wide teeth 30b, rotate the driving gear 50 by 1/2 rotation, and the following gear Since the speed is increased by
During the 15 rotations, the bill and holder complete one rotation and perform the knotting action.

Further, the drive gear 50 integrally includes a bevel gear 51 having 18 teeth and is rotatably supported by a shaft 52, which has a small diameter portion at one end and a pin 52c at the other end. At the same time, a mounting seat 52b screwed onto the transmission case 22 with a mounting bolt is fixed, and a reversal prevention pawl 53 set on the pin 52c is fixed.
The distal end 53a is pressed against the periphery of the cam plate 28a, the proximal end is pulled by a tension spring 54 whose one end is fixed to the transmission case 22, and the back is attached to the mounting bolt 55.
It is in contact with the end 55a of. However, the protrusion 35a
is engaged with 28c and is acting as a stopper, as shown in FIGS. 3 and 4 A, the reversal prevention pawl 5
3 is apart from the end 55a of the mounting bolt 55.

The speed increasing gear 60 (16 teeth) includes a bevel gear 61 that meshes with the bevel gear 51, and is rotatably supported by a shaft 62, with one end of the shaft 62 connected to the transmission case 22.
The other end is supported by inserting the small diameter portion of the shaft 52 into the hole 62a.

The three-point meshing gear 70 (the number of teeth has no meaning, but it is set to 26) always meshes with the speed increasing gear 60, the holder gear 80 (12 teeth), and the building gear 90 (12 teeth). The shaft 71 is fixed to the transmission case 22 with a nut 72, and a building pressing plate 73 is attached to the outer end of the shaft 71.

Further, the holder gear 80 is attached to a holder shaft 81 that transmits rotation but slides in the axial direction, and the holder shaft 81 is supported by the transmission case 22 via a bush 85 and is also inserted into the cam metal 82. Only the holder 84 fixed to the outer end of the holder 84 protrudes outside the case, and the holder spring 83 and the holder gear 80 are housed inside the transmission case 22.

Further, since a holder spring 83 is interposed between the holder gear 80 and a spring receiver 86 adjusted by a nut 88, the tapered surface of the holder 84 is pressed against the tapered surface of the cam metal 82, and the tapered surface 87 for holding the string is pressed against the tapered surface of the cam metal 82. The spring receiver 8
When adjusting the string clamping pressure by turning a hexagonal nut 88 formed in a hexagonal pyramid-shaped tapered groove on the outer end surface of
The nut 88 matches the tapered groove of the spring receiver 86 every 1/6 rotation, and the holder spring 88
3 constantly presses the spring receiver 86 to prevent the nut 88 from returning.

The building 91 itself is exactly the same as the conventional one, but the shaft hole of the building gear 90 is oval-shaped with two parallel surfaces, and the gear bearing portion of the building shaft 91a has a width of the two parallel surfaces as described above. It is formed into an oval shape that is slightly narrower than the shaft hole. In other words, a certain play is formed between the bill gear 90 and the bill shaft 91a.

Further, as shown in FIG. 2, the building pressing plate 73 is pressed against the building 91 by being pulled by a tension spring 92 whose tension can be adjusted by a nut, thereby applying cord clamping pressure to the building 91 and applying braking force. Therefore, the bill 91 rotates with an angle deviated in the counter-driving direction by the amount of the play, and when the knot is removed, it is pulled by the tied string and reaches the position shown by the solid line without depending on the rotation of the bill gear 90 and the bill gear 90 and the bill shaft. The spring 91a rotates by the amount of play caused by the fitting of the spring 91a, etc., but at the same time as the knot is removed, the spring 9
2 and the press plate 73 to return to the original state.

The knot guide 94 has its base fixed to the transmission case 22, and is connected to one side of the grain culm binding processing passage A in which the receiving section 5, the supply path 6, the culm gathering section 7, etc. are connected as a series, as shown in FIG. and prevents grain culms from coming into contact with the building 91 and the holder 84, and the lower end of the string guide groove 94c provided diagonally downward from the top of the end surface 94d of the nodule guide 94 is a dead end. The entrance portion is a needle passage path 94a, and one side edge is a string guide surface 94b.

Packer and star wheel drive mechanism Arm 10 protruding from the end of packer shaft 100
A pin 100b is fixed to 0a, and this pin 100
b is connected by a rod 101 to a pin 26b that rotates integrally with the crankshaft 26, so that the arm 100a is constantly oscillated;
02 swings, and its tip 102a moves in an arc.

The cam link 110 that is in contact with the arm cam 26a that rotates together with the crankshaft 26 is attached to the case cover 2.
The pin 110a provided at the end of the arm cam 26a swings as the arm cam 26a rotates.

Also, the bracket 1 that holds the transmission case 22
The intermediate shaft 11 is attached to the bearing pipe 112a provided in the bearing pipe 12.
3 is rotatably inserted through the intermediate shaft 113.
The tip pin 11 of the arm 113a fixed at one end
3b is a pin 110a of the cam link 110;
are connected by links.

The star wheel 114 has a support pin 112 attached to the upper part of the arm 112b which is erected on the bearing pipe 112a.
The pin 115a at the other end of the link 115, which is rotatably supported by the arm 113c and whose one end is rotatably supported by the boss 114a of the star wheel 114, is connected to the pin 113 of the arm 113c by the rod 116.
d.

Further, a torsion spring 117 is interposed between the arms 112b and 113c so that the cam link 110 is constantly pressed against the arm cam 26a, and the link 115 is biased downward, and is held by the boss portion of the link 115. The stopper pin 119 is attached to the star foil 11 via the spring 118 as shown in FIG.
4, the inclined groove 11 is provided on the plate surface of the star foil 114 and is gradually shallower on the rear side in the direction of rotation.
A one-way rotating clutch is formed by press-fitting the head of the stopper pin 119 into the base arm 112b, and the torsion spring 11 is pivotally supported on the base arm 112b.
Since the stopper 120 biased by 7 receives the tip of the scraping protrusion of the star wheel 114 in a press-contact state, the star wheel 114 does not rotate in the opposite direction and the stopper pin 119 of the one-way rotation clutch
escapes from the inclined groove 114b and enters the next inclined groove 1.
14b, and eventually the star wheel 114 is driven intermittently by 1/3 rotation in synchronization with the pack car 102.

Needle and Door Drive Mechanism In Figures 1 and 2, the boss 42 of the needle 42
A is a boss multi-use shaft 40 that is attached to the tip of the multi-use shaft 40 so as to rotate integrally therewith, and has culm guides 43a, 43a and stopper arms 43b, 43b protruding therefrom.
It is freely rotatably fitted. A torsion spring 44 is set between the small hole of the boss 42a, and a stopper 43b protruding from the boss 42a of the needle 42 toward the base side is located between the culm guides 43a and 43a. The needle 42 comes into contact with the culm guide 43a, and the needle 42 is in an arcuate state 42r, 42r' bundle release action 42s, 42s, string hooking recess 42t, 42
t' and one claw 42w is made long and curved to cover the other short claw to form a crab claw shape, and string receiving portions 42v, 42v are formed between the two.

Further, the main part of the door 49 has a hole in the middle part that fits into the stepped part of the boss, and one side and the other of the main part are formed with L-shaped receiving parts. The door 49 is fixed to the stopper arm 43b by screwing bolts inserted into arc-shaped long holes 49a and 49a' drilled near both ends of the door into a screw hole located in the middle of the stopper arm 43b. The mounting angle is adjusted within the range of the elongated holes 49a and 49a'.

Operation timing The crankshaft 26 constantly rotates, and as the arm cam 26a rotates, the cam link 110 rotates.
Turn star foil 114 1/3 turn. During this time, the tip of the packer 102 returns, and thereafter descends along the side of the scraping protrusion of the star foil 114.
When rising, the cam link 110 is in sliding contact with the arc-shaped portion at the base of the arm cam 26a, so the star foil 1
14 is not rotationally driven.

During grain culm raking by the packer 102, while the concentrated grain culm on the door 49 does not reach a predetermined amount, the amount by which the cushion bar 48, which is pressed upward by the constant pressure spring 47 and supports the stopper 43c, descends, that is, the constant pressure Since the amount of compression of the spring 47 has not reached the predetermined amount, the one-turn clutch does not engage, and as shown in FIG. 40 frequently used axes reach a fixed quantity
(rotation from point O to direction A in FIG. 4A), the swing link 35 moves to the intermediate gear 34
and rotate in the C direction (15 degrees in this example),
The protrusion 35a is removed from the protrusion 29c of the clutch plate 29.

At this time, the clutch plate 29 rotates because it is biased counterclockwise in FIG.
Press 1. Next, when the police car 102 moves backward, the door 49 and the needle 42 are pushed up by the constant pressure spring 47 and return to their original positions.
2 has descended to the position shown by the solid line in FIG. 1, the taper pawl 27a of the constantly rotating gear 27 comes into contact with the clutch pin 31, and the one-turn clutch is engaged.

In this way, while the cam plate 28a rotates 15 degrees after the one-turn clutch is engaged, the periphery of the cam plate 28a does not press the roller 37, which is in an arc shape centered on the axis, but after that, the roller 37 is not pressed. 37 is rotated counterclockwise by the cam plate 28a to the position shown in FIG. 4C. That is, the arcuate portion of the cam plate 28a constitutes a delay drive device that prevents the needle 42 from starting while the cam plate 28a rotates about 15 degrees when the one-turn clutch engages in relation to the roller 37. When the cam plate 28a further rotates, the needle 42 passes through the back side of the wide part at the tip of the packer 102 and winds the string around the straw bundle.

In this example, when the cam plate 28a is rotating 80 degrees, the drive gear 50 is rotated by the wide tooth 30b of the partially toothed gear 30.
, and drives the building 91 and the holder 84 at the same time.

At this time, the needle 42 is 5 degrees before the completion of string winding (Fig. 4 C), the packer 102 is 21 degrees before the maximum compression, and 123 degrees after the cam plate 28a has rotated 85 degrees.
Since the guide surface of the cam plate 28a is an arc centered on the axis during the 38° angle to 38°, the needle 42 is inserted the most and reaches the state shown in Fig. 4 O with the holder 84 provided with a hold and a string. The police car 102 continues to compress, while building 91 has been stopped until approximately
Driven at 63°.

That is, by stringing the grain culm while compressing it with the packer 102, it is possible to firmly bind the grain culm.

Furthermore, even after the maximum compression point, the packer 102 is still being driven by the clutch movement of the cam arm 26a and is near the bottom dead center, so the amount of return of the packer 102 is extremely small.

That is, while maintaining the compressed state, the building 91
The cord rotates 130 degrees and finishes pulling the cord, so it does not loosen and is tightly tightened.

Then, when the stop period of the needle 42 ends, the needle 42 begins to return due to the rotation of the cam plate 28a (after rotating 120 degrees) (Fig. 4 O), and at this time, the cam plate 28a
The protrusion 28b of a is the protrusion 3 of the stopper cam 38.
8d, the roller 37 starts to descend, so the relative positions of the teeth of the partially toothed gear 30 and the intermediate gear 34 are regulated, and the teeth begin to mesh smoothly without colliding with each other (see Fig. 4). (just before the occlusion).

When the cam plate 28a rotates 130 degrees, the protrusion 28b of the cam plate 28a comes into contact with the protrusion 38e of the stopper cam 38, as shown in FIG. Since the narrow teeth 30c and the intermediate gear 34 mesh,
The torsion spring 39 is further twisted to the state shown in FIG.
a is pushed out by the tapered hole 34a of the intermediate gear 34, and its end surface rides on the plate surface of the intermediate gear 34, and the other tapered portion 36b
Since it fits into the tapered hole 38b of No. 8, the intermediate gear 3
4 and the swing link 35 are in a free position with respect to each other (the state shown in FIG. 4G).

At this time, the cam plate 28a has been rotated 195 degrees,
The needle 42 returns to the O point, and thereafter the intermediate gear 34
is driven by the partially toothed gear 30, so the needle 4
2 starts to release the bundled grain culm from point O by the release action part 42s of the needle 42 which has the bundled grain culm below it, which will be described later.

During that time, when the cam plate 28a rotates 165 degrees, that is, during the clutch switching action by the clutch pin 36, the bill 91 catches the string in its beak, and the knife of the holder 84 immediately after that cuts the string, and the cam plate When the rotation angle of 28a reaches 205 degrees, the building 91 and holder 84 rotate once, and the cutout tooth 5
0a' is locked and stopped by the cam 30a of the partially toothed gear 30, and when the rotation angle of the cam plate 28a becomes approximately 212 degrees inward or outward, the rear needle 42 moves into the discharge action section 4.
Knotting is performed by pushing out the bundled grain culm with 2s', and then the rotation angle of the cam plate 28a is
When the angle reaches 240°, the star foil 114 is activated.

The needle 42 continues to rotate further and stops when the rotation angle of the cam plate 28a reaches 345 degrees. At that time, the protrusion 35a of the swing link 35, which was rotating together with the intermediate gear 34, receives the protrusion 29c of the clutch plate 29 and rotates the clutch plate 29 in the opposite direction relative to the cam plate 28a, thereby shifting the taper pawl 27.
Clutch pin 31 which was under pressure by a
is fitted into the tapered hole 29 of the clutch plate 29, and the one-turn clutch is disengaged.

Next, the operation of each part will be further described below.

String pinching and cutting When the cam plate 28a rotates 165 degrees, the building 91 pinches the string, and when the clutch plate 28a rotates 170 degrees, the previously pinched string is separated from the holder 84, and the new string is held in the holder 84. It will be cut off along with.

The relationship between the return of the needle 42 and the trouser car 102 is shown in Fig. 4K. After the needle 42 rotates toward the building 91 to wrap the string, it returns to the standby position (the position indicated by the solid line in Fig. 1) at point O. This shows the moment when the cam plate 28a has rotated 195 degrees, and the needle 42 is integrated with the culm guide 43a, door 49, etc.
During this time, the door 49 and the discharge portion 42s' of the needle 42 perform the cutting and discharge operations.

When the needle 42 returns to point O, the timing is such that the needle 42 passes through the back of the packer 102, and there is no disturbance of the grain culm due to the intersection between the needle 42 and the packer 102.

Further, as shown in FIG. 6, the police car 102 has returned by the time the star wheel 114 is started, and from this point on, the rotation of the star wheel 114 begins as described above, so the police car 102 is returned even in the return stroke.
The tip of the star foil 114 wraps within the width of the scratching protrusion.

Relationship between the return of the needle and the puller In Figures 4 and 6, when the rotation angle of the cam plate 28a reaches 205 degrees, the building 91 and the holder 84
stops, the discharge action section 42s of the needle 42 and the door 49 begin to push out the bundle, and then the bundle is jumped out of the collection culm part 7 and enters the discharge state, and only at this time is the star wheel 114 driven.

Needle stop and one-turn clutch intermittent timing The needle 42 is connected to the wide tooth 3 at the end of the partially toothed gear 30.
When 0b finishes driving the intermediate gear 34, the cam plate 2
8a has rotated 345 degrees (15 degrees before returning to point O) as described above, and at this time, the protrusion 35 of the swing link 35
a comes into contact with the protrusion 29c of the clutch plate 29, so when the cam plate 28a further rotates 15 degrees with respect to the clutch plate 29, the clutch pin 31 moves into the tapered hole 29b.
The clutch disengages one turn.

In other words, when the clutch is engaged once, the cam plate 28 rotates 15 degrees after the clutch engages, and then the cam plate 28a
The needle 42 is activated by the circumferential shape of the cam plate 28a, and after the needle 42 stops when the one-turn clutch is disengaged, the cam plate 28a is rotated by 15 degrees and cut, so that when the one-turn clutch is disengaged, it is in a no-load state and is extremely light. In addition, the clutch can be engaged and engaged accurately, and it is also advantageous in terms of strength and can be made lightweight and compact.

Culm guide, door, and constant pressure spring Culm guides 43a, 43a' and door 49 are door 49
The stopper arm 43c is screwed onto the stopper arm 43b so that the stopper arm 43c is integrated with the stopper arm 43b.
Alternatively, it is supported by a cushion bar 46 which is supported by a constant pressure spring 47 via 43c'.

In addition to operating the one-turn clutch, the door 49 also has the function of holding the bundle against packer pressure via a constant pressure spring 47 to improve the tightness of the bundle. 42
The collecting culm 7 is held while the bundle ends and returns to point O shown by the solid line, but when the bundle is released thereafter, the needle 42 and the door 49 rotate together to open the release path. do.

Immediately before the needle 42 rotates 180 degrees from point O and stops, the stopper 43c or 43c' rides on the head while tilting the cushion bar 46 and stops.

Drive and connection of bill and holder Bill 91 and holder 84 are three-point mesh gear 70
The needles 42 are simultaneously driven by the needles 42 and eject the bundle in the retracting direction.

String supply to the needle Needle 42 rising from the bottom when releasing the bundle
The annular string supply port 14 is located on the opposite side of the shaft of the needle 42 across the passage and the string holder of the needle 42, as described above, in order to supply the string to the grain culm and to receive the grain culm supplied after release with the string. A string is attached to the boss 15a of the guide 15 so as to diagonally cross the rotation locus of the portion 42v, and is stretched around the needle arc-shaped portion 42r' while the needle 42 located below rotates toward the standby position. and finally enter the string receiving section.

Furthermore, when the string is wound by the needle 42, the needle 42 guides the string pulled out from the string supply port 14 away from the bill 91 and the holder 84, so that the string on the string supply port 14 side is attached to the bill. You will not be caught by 91 mag.

In addition, in the drawing, 9 is a frame, 9c is a pipe,
10a is a base, 10b is a support metal, 10c is a pin, 15b is a mounting bracket, 29a is a recess, 45 is a bracket, 62a is a hole, 127 is a brake pin that operates a torque limiter, 128 is a fixed part,
128c is a pressing part, 128d and 128e are nuts, 129 is a threaded handle, 130 and 133 are bolts, 131 is a compression spring, 132 is a double nut, and 134 is a lock nut.

As mentioned above, the present invention includes a one-turn clutch mechanism that operates upon sensing that a certain amount of grain culm has been focused;
In the tying machine equipped with a knotter and a needle driven by the one-turn clutch mechanism, the needle activation timing is set between the needle and the one-turn clutch mechanism to be earlier than the activation timing of the one-turn clutch. Since a delay drive device is installed to delay the activation timing, the activation of the needle is delayed from the one-turn clutch activation timing, which is earlier than the nodule activation timing, and the activation timing of the one-turn clutch mechanism is delayed. An excessive starting load is not generated, and damage to the complex one-turn clutch and the transmission mechanism that transmits power thereto can be prevented.

Moreover, when the one-turn clutch mechanism is engaged, there is no load due to the needle and its accompanying members.
The one-turn clutch mechanism, which normally causes many troubles, can be started smoothly.

[Brief explanation of the drawing]

The drawings show an example of the embodiment, and FIG. 1 is a side view of the binding machine, FIG. 2 is an exploded sectional view of the transmission part, FIG. 3 is a right side view with the case cover removed, and FIG. 4 is a side view of the binding machine. 5 is a drawing showing the operating sequence of the transmission part.
The figure is an exploded perspective view of the transmission part, FIG. 6 is a timing diagram of the same as above, and FIG. 7 is a side view of the one-turn clutch and interlocking mechanism. 26...Crankshaft, 28a...Cam plate, 37
...Roller, 42...Needle, 47...Constant pressure spring, 70...Three point mesh gear, 100...Patzker shaft, 102...Patsuker.

Claims (1)

[Scope of utility model registration request] A tying machine comprising a one-turn clutch mechanism that operates upon sensing that a certain amount of grain culm has been collected, and a knotter and a needle driven by the one-turn clutch mechanism, wherein the needle and the one-turn clutch mechanism are 1. A needle drive device for a tying machine, characterized in that a delay drive device is interposed between the steps to start the needle earlier than the start time of the knot portion but later than the start time of the one-turn clutch.