WO2016155364A1 - 一种双齿盘驱动打结器 - Google Patents

一种双齿盘驱动打结器 Download PDF

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Publication number
WO2016155364A1
WO2016155364A1 PCT/CN2015/097646 CN2015097646W WO2016155364A1 WO 2016155364 A1 WO2016155364 A1 WO 2016155364A1 CN 2015097646 W CN2015097646 W CN 2015097646W WO 2016155364 A1 WO2016155364 A1 WO 2016155364A1
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WIPO (PCT)
Prior art keywords
knotter
shaft hole
arm
axis
disc
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2015/097646
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English (en)
French (fr)
Inventor
尹建军
张万庆
陈亚明
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Jiangsu University
Original Assignee
Jiangsu University
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN201510161254.6A external-priority patent/CN104823607B/zh
Priority claimed from CN201510890000.8A external-priority patent/CN105638119A/zh
Application filed by Jiangsu University filed Critical Jiangsu University
Publication of WO2016155364A1 publication Critical patent/WO2016155364A1/zh
Priority to US15/719,593 priority Critical patent/US10667466B2/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01F—PROCESSING OF HARVESTED PRODUCE; HAY OR STRAW PRESSES; DEVICES FOR STORING AGRICULTURAL OR HORTICULTURAL PRODUCE
    • A01F15/00—Baling presses for straw, hay or the like
    • A01F15/08—Details
    • A01F15/14—Tying devices specially adapted for baling presses
    • A01F15/145—Twine knotters
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01F—PROCESSING OF HARVESTED PRODUCE; HAY OR STRAW PRESSES; DEVICES FOR STORING AGRICULTURAL OR HORTICULTURAL PRODUCE
    • A01F15/00—Baling presses for straw, hay or the like
    • A01F15/08—Details
    • A01F15/0841—Drives for balers
    • A01F15/0858—Drives for balers for the tying devices or needles

Definitions

  • the invention relates to the field of straw or forage harvesting and bundling technology, in particular to a double-toothed disk drive knotter.
  • the square bale baler is widely used for the collection and bundling of rice straw and dried green grass in rural and pasture.
  • the knotter is the core component of the square bale baler.
  • the main function is to send the rope feeding mechanism.
  • the bundled rope is clamped, and the buckles, the tongs, the tying ropes, the tying ropes, and the tripping knots required for the tying of the tying are completed, and the two rope ends are knotted to prevent the loosened bales from being loosened.
  • the bundled and tied bales have high density and are easy to transport and store, which is very beneficial to the utilization of biomass energy such as straw.
  • knotters are all integrated knotters, which have the disadvantages of complicated space structure, high manufacturing difficulty and high assembly precision requirements. And the multiple structures are concentrated on one part, which increases the load of the strength of the part, and there is a shortage of structure and the need to replace the whole part.
  • Chinese invention patent 201110001685.8 designed a humanoid double-finger knotter, which is installed on the knotter spindle at the end of the baler, which can simulate the clamping of the rope sent by the rope-feeding mechanism by the two fingers of the hand and complete Bundling the ropes, ropes, ropes, biting ropes, cutting ropes and tripping actions required for knotting, realizing automatic bundling and knotting of the compacted bales, and improving the inconvenience of the knotter bracket manufacturing, which Compared with foreign knotters, the invention has a relatively simple spatial structure and reduces manufacturing costs.
  • the composite toothed disc is provided with a knotted drive incomplete bevel gear and a gripper driven incomplete bevel gear on one side, the force is not uniform, and the space structure is complicated, the manufacturing is difficult, and the assembly precision is high;
  • the rope feeding mechanism can not directly feed the rope into the rope slot, and when the rope is cut, the position of the rope head is close to the upper part of the blade, which is not conducive to cutting the rope head;
  • the spherical knife arm roller is in point contact with the cylindrical cam, and the medium stress is used.
  • the shock wave is large, and the long-term use of cylindrical cam wear is large, which affects the service life of the knotter.
  • the present invention proposes an automatic knotting device for bundling crop straw or pasture into a rectangular bale with a rope, and has a double-toothed disc drive with reasonable structure, convenient processing and assembly, low manufacturing cost and reliable formation.
  • the knot device solves the problem that the domestic enterprise production side bale baler is subject to the imported knotter.
  • the technical problem to be solved by the invention is that the uneven force of the composite toothed disc leads to complicated space structure of the knotter, high manufacturing difficulty and high assembly precision; when the rope feeding mechanism cuts the rope, the position of the rope head is close to the upper part of the blade, which is not conducive to cutting.
  • the invention provides a double-toothed disc drive knotter with novel structure and low manufacturing cost, which overcomes the defects of complicated space structure, high manufacturing difficulty and high assembly precision of the foreign knotter, and has reasonable structure, convenient processing, assembly and manufacture. Low cost and reliable reliability.
  • the technical solution of the invention is that the composite toothed disc of the double-toothed disc drive knotter is divided into two parts: a small toothed disc and a large toothed disc, the small toothed disc drive gripper drives the incomplete bevel gear, and the large toothed disc drives the knotted knot. Drive the incomplete bevel gear and drive the arm to move.
  • the invention comprises a small toothed disc, a knotter bracket, a large toothed disc, a cutter arm mounted on the knotter bracket, a buckle jaw biting mechanism R and a rope gripper drive mechanism Q; the small chainring and the large a toothed disc is coaxially fixed to both ends of the knotter spindle shaft hole on the knotter bracket; the buckle jaw biting mechanism R and the rope gripper drive mechanism Q are respectively mounted on the knotter bracket Both sides of the large toothed disc are provided with a knotted drive incomplete bevel gear, and the cutter arm roller at the top end of the cutter arm cooperates with the groove cam on the inner side of the large toothed disc to knot the driven bevel gear and the joint
  • the knotting drive is incomplete bevel gear meshing; the circumference of the small toothed disc is provided with a clamping rope driving the incomplete bevel gear, and the clamping rope driven bevel gear meshes with the clamping rope driving the incomplete bevel gear.
  • the rope gripper drive mechanism Q drives the gripper J, and the outer edges of the gripping discs of the gripper J are evenly distributed with three gripping slots, and the driven bevel gears are passed through the worm shaft.
  • the number of the involute worms of the knot is 2, and the number of teeth of the helical gear engaged with the involute worm is 6.
  • the knife arm roller is cylindrical, the cam surface of the groove cam is a space contour curved surface, the cylindrical surface of the knife arm roller is in line contact with the space contour curved surface of the cam surface, and the blade arm is along the space contour Surface scrolling. Both ends of the knife arm are arcuate chamfers.
  • the cylindrical cam profile on the knotter bracket that mates with the buckle jaw biting mechanism R is an Archimedes spiral cam.
  • the space contour surface is established as follows: the center of the upper surface of the roller on the over-cutting knife arm is perpendicular to the center axis of the swing, and the intersection point is the center O1 of the moving coordinate system, and the vertical line of the roller is used as the rotation center axis.
  • the X-axis of the moving coordinate system and the rotating axis are used as the Y-axis.
  • the coordinate system is established according to the right-hand rule; the O1 point is perpendicular to the central axis of the toothed disc, and the intersection is made.
  • the X axis is parallel to the direction of the moving coordinate system X1
  • the Y axis is parallel to the direction of Y1.
  • the static coordinate system is established according to the right hand rule; while the moving coordinate system rotates clockwise around the static coordinate system.
  • the angle is ⁇ ; the initial position, the moving coordinate system is equivalent to the static coordinate system shifting m unit length in the negative direction of the Z axis, and the n unit length is translated by n unit length in the negative direction of the Y axis; setting the clip arm in the initial position and the moving coordinate system
  • the angle is ⁇ 0, the angle rotated when oscillating is ⁇ , the center point of the upper surface of the knife arm is P, the center point of the lower surface is Q, and the length of the arm is set to l, and the distance between PQ is set to f; therefore,
  • the coordinates of P and Q points in the moving coordinate system are respectively P(lcos( ⁇ + ⁇ 0), -lsin( ⁇ + ⁇ 0), 0), Q((lf)cos( ⁇ + ⁇ 0), -(lf)sin ( ⁇ + ⁇ 0), 0);
  • x1, y1, and z1 are coordinate points in the moving coordinate system, respectively.
  • One end of the involute worm is provided with a nut-shaped boss B.
  • the knotter bracket further includes a worm shaft hole, a knot nozzle shaft hole and a yoke disk shaft hole; the knot nozzle shaft hole and the knotter spindle shaft hole are arranged at a non-orthogonal intersecting axis, the worm
  • the shaft hole is arranged perpendicular to the shaft hole of the knotter spindle, and the shaft hole of the cutter arm and the shaft hole of the knot nozzle are arranged perpendicular to each other, the shaft hole of the clamping disc and the spindle of the knotter
  • the shaft holes are arranged perpendicularly to each other in space, and the shaft holes of the knotter shaft and the shaft holes of the clamping rope are arranged in a space perpendicular to each other.
  • the knotter bracket further includes a worm shaft shaft hole, a knot nozzle shaft hole and a clamp, and a rope shaft hole; the knot nozzle shaft hole and the knotter spindle shaft hole are arranged at a non-orthogonal intersection axis, The worm shaft hole is arranged perpendicular to the shaft hole of the knotter spindle, and the shaft hole of the cutter arm and the shaft hole of the knot nozzle are arranged perpendicular to each other, the arm shaft hole and the cable shaft The hole and the knotter spindle shaft holes are spatially arranged perpendicular to each other.
  • the angle axis d of the knot nozzle shaft hole is at an angle of 98° with the shaft axis of the knot shaft of the knotter spindle, and the shaft axis d of the knot shaft shaft and the shaft line of the worm shaft hole
  • the c-space stagger angle is 30°, and the angle between the axis line e of the clamping disk shaft hole and the axis line c of the worm shaft hole is 72°.
  • the arm is hinged to the arm shaft hole through a blade arm shaft, and the arm arm is supported by a pair of symmetrically mounted pair of sliding bearings and a pair of first thrust ball bearings on the knotter bracket In the shaft hole, both ends of the arm shaft are fixed by bolts.
  • the transmission ratio of the involute worm to the helical gear is 3, and three clamping slots are evenly distributed on the outer edge of the clamping disc; the number of the involute worms is 2, The number of teeth of the helical gear is 6.
  • a boss is disposed between the end surface of the clamping disc, the end surface of the helical gear, and the end surface of the shaft hole of the clamping disc on the knotter bracket.
  • a second thrust ball bearing is mounted between the helical gear and the end face of the shaft hole of the clamping disc.
  • the composite toothed disc of the double-toothed disc drive knotter is divided into a small toothed disc and a large toothed disc, and the small toothed disc and the large toothed disc are coaxially fixed on both ends of the shaft hole of the knotter spindle, so that the knotter spindle is subjected to The balance of force improves the working stability of the knotter.
  • the knife arm roller rolls along the surface contour surface and is in line contact with the space contour surface of the cam surface, so that the bearing capacity is greater and the wear is reduced.
  • the setting of the space contour curve makes the arm move with sinusoidal acceleration, theoretically eliminating the stress shock of the blade arm and the cam surface.
  • the axial line arrangement of the shaft hole on the knotter bracket reduces the manufacturing difficulty of the shaft hole of the knotter bracket, and is beneficial to ensure the machining precision between the shaft hole angles.
  • One end of the involute worm is provided with a nut-shaped boss, which greatly facilitates the assembly and disassembly of the involute worm.
  • the end surface of the clamping reel, the end surface of the spiral gear and the end face of the shaft hole of the clamping disc on the knotter bracket are provided with a boss to reduce the friction during the working process of the knotter, which is beneficial to the transmission.
  • a thrust bearing may be installed between the helical gear and the end face of the shaft hole of the clamping disc to replace the boss, so as to reduce the end face of the helical gear and the shaft hole of the clamping disc during the operation of the knotter. The friction between them is good for the transmission.
  • Figure 1 is a front perspective view of a dual-disc drive knotter assembly of one embodiment.
  • Fig. 2 is a structural view of a small toothed disc of an embodiment.
  • Fig. 3 is a structural view of a large chainring of an embodiment.
  • Figure 4 is a schematic view showing the structure of the arm of an embodiment.
  • Figure 5 is a two dimensional cross-sectional view of the arm shaft assembly of one embodiment.
  • Fig. 6 is a schematic view showing the structure of the buckle jaw biting mechanism R of one embodiment.
  • Figure 7 is a side view of the construction of the rope gripper of one embodiment.
  • Figure 8 is a side elevational view of the configuration of the cable gripper drive mechanism of one embodiment.
  • Figure 9 is an assembled view of a double-toothed disk drive knotter of one embodiment.
  • Figure 10 is a schematic view of a boss shaft hole boss of an embodiment.
  • Figure 11 is a side cross-sectional view of F-F of Figure 9.
  • Figure 12 is a schematic view of the shaft hole of the knotter holder of one embodiment.
  • Figure 13 is a schematic view of a shaft hole of a knotter holder of an embodiment.
  • Figure 14 is a perspective view of the shaft hole angle of the knotter bracket of one embodiment.
  • Figure 15 is a perspective view of the angle of the shaft of the knotter bracket of one embodiment.
  • Figure 16 is a perspective view of the angle of the shaft of the knotter bracket of one embodiment.
  • Figure 17 is a schematic view of the knife arm roller.
  • Figure 18 is a schematic front view of a prior art German D-type knotter.
  • Figure 19 is a schematic rear view of a prior art German D-type knotter.
  • first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated.
  • features defining “first” and “second” may include one or more of the features either explicitly or implicitly.
  • the meaning of "a plurality” is two or more unless specifically and specifically defined otherwise.
  • the terms “installation”, “connected”, “connected”, “fixed” and the like shall be understood broadly, and may be either a fixed connection or a detachable connection, unless explicitly stated and defined otherwise. , or connected integrally; may be mechanical connection or electrical connection; may be directly connected, or may be indirectly connected through an intermediate medium, and may be internal communication between the two elements.
  • installation shall be understood broadly, and may be either a fixed connection or a detachable connection, unless explicitly stated and defined otherwise.
  • , or connected integrally may be mechanical connection or electrical connection; may be directly connected, or may be indirectly connected through an intermediate medium, and may be internal communication between the two elements.
  • the specific meanings of the above terms in the present invention can be understood on a case-by-case basis.
  • the first feature may be "on” or “below” the second feature unless otherwise specifically defined and defined. Direct contact with the first and second features may also include that the first and second features are not in direct contact but are contacted by additional features between them.
  • the first feature "above”, “above” and “above” the second feature includes the first feature directly above and above the second feature, or merely indicating that the first feature level is higher than the second feature.
  • the first feature “below”, “below” and “below” the second feature includes the first feature directly below and below the second feature, or merely the first feature level being less than the second feature.
  • a double-toothed disc drive knotter includes a small toothed disc 1, a knotter bracket 2, a large toothed disc 3, and a cutter arm 7 assembled on the knotter bracket 2, and a buckle jaw biting mechanism R, the rope gripper J and its drive mechanism Q.
  • the small toothed disc 1 and the large toothed disc 3 are coaxially fixed to both ends of the knotter spindle shaft hole 201 on the knotter holder 2.
  • the cutter arm 7 is hinged to the arm shaft shaft hole 202 of the knotter holder 2 via a pin shaft, and a groove cam 4 is disposed inside the large toothed disc 3, and the arm is provided. The upper end of 7 bears against the grooved cam 4.
  • the buckle jaw biting mechanism R and the rope gripper drive mechanism Q are respectively mounted on both sides of the knotter bracket 2.
  • the large toothed disc 3 is provided with a knotted drive incomplete bevel gear 5 on the circumference thereof, the buckle jaw biting mechanism R is fixedly coupled to the knotted driven bevel gear 9, and the knotted driven bevel gear 9 is The knotted drive is incompletely meshed by the bevel gear 5.
  • the large toothed disc 3 is mounted with a knotted drive incomplete bevel gear 5 (the buckle clamp biting mechanism R and the knotted driven bevel gear 9 are fixed, the knotted driven cone
  • the gear 9 is meshed with the knotted drive incomplete bevel gear 5) and is provided with a grooved cam 4 having a spatial contour curved surface, and the spatial contour curved surface is established as follows: the overcutting rope arm is rolled up The center of the upper surface of the sub is perpendicular to the center axis of the oscillation, the intersection point is the center O1 of the moving coordinate system, the vertical line made by the roller to the central axis of rotation is taken as the X axis of the moving coordinate system, and the rotating axis is taken as the Y axis, according to the right hand.
  • the coordinate system is established; the O1 point is perpendicular to the central axis of the toothed disc rotation, the intersection point is used as the center O of the static coordinate system, the X axis is parallel to the direction of the moving coordinate system X1, and the Y axis is parallel to the direction of the Y1, according to the right hand.
  • the rule establishes a static coordinate system; at the same time, the dynamic coordinate system rotates clockwise around the static coordinate system; the initial position, the dynamic coordinate system also corresponds to the static coordinate system shifting 22 unit lengths in the negative direction of the Z axis, and 58 translations in the negative direction of the Y axis.
  • the unit length is obtained; the arm is in the initial position and the moving coordinate system
  • the angle is 5 ⁇ /36, the angle rotated when oscillating is ⁇ , the center point of the upper surface of the knife arm is P, the center point of the lower surface is Q, and the length of the arm is 64, and the distance between PQ is set to 17;
  • the coordinates of P and Q points in the moving coordinate system are P(64cos( ⁇ +5 ⁇ /36), -64sin( ⁇ +5 ⁇ /36), 0), Q(47cos( ⁇ +5 ⁇ /36),- 47 sin ( ⁇ + 5 ⁇ / 36), 0).
  • the tool arm rotates the angle at the cam thrust [0, ⁇ /3] and return [ ⁇ /3, 2 ⁇ /3] phases respectively:
  • the circumference of the small toothed disc 1 is provided with a rope driving incomplete bevel gear 20 (the rope gripping drive mechanism Q and the clamp driven bevel gear 19 are fixed, the gripping rope is The bevel gear 19 meshes with the gripper drive incomplete bevel gear 20, and the gripper drive mechanism Q includes a helical gear 26 that is fixed to the gripper J by a gripping disc shaft 27. .
  • the arm 7 is mounted on the arm shaft hole 202 through a blade arm shaft 8, and the groove cam 4 causes the arm 7 to be wound by driving the arm roller 6.
  • the axis of the arm shaft 8 reciprocates.
  • the blade roller 6 is cylindrical, and the cylindrical surface of the blade roller is in line contact with the spatial contour surface of the cam surface. As shown in FIG. 17, the two ends of the blade roller 6 are arcuately chamfered, which is advantageous for reducing the assembly requirements between the blade roller 6 and the grooved cam 4 and reducing wear.
  • the arm shaft 8 is supported by a pair of symmetrical bearing pairs 29 and a pair of first thrust ball bearings 28 in the stepped arm shaft hole 202 of the knotter holder 2.
  • the both ends of the arm shaft 8 are fixed by bolting.
  • the end surface of the shaft hole 102 of the cutter arm is not rubbed against the end face of the shaft hole of the arm 7, so that the arm axis 8 is convenient.
  • the bolts of the ends are tightly tightened, and the position of the cutter arms 7 is strictly ensured while the rotation thereof is flexible.
  • the buckle jaw biting mechanism R includes a knotting nozzle 13, a hooking pliers 14, a cylindrical cam 12 on the knotter holder 2, and a hook clamp plate 10, the top end of which is passed through
  • the cam 12 is fixed to the knotted driven bevel gear 9
  • the hook clamp 14 is hinged to the knotting nozzle 13 via a pin shaft, and the top end of the hook clamp 14 is pressed by the hook clamp plate 10 , the hook clamp
  • the pressure plate 10 is hinged on the hook clamp plate shaft hole 207 of the knotter bracket 2 through a pin shaft, and the compression spring 11 is sleeved on the hook clamp plate shaft 1001 and fixed by screws for adjusting the hook clamp plate 10 Pressure
  • the cylindrical cam 12 is an Archimedes spiral cam. During the rotation of the knotting nozzle 13, the hook-and-roller roller on the hook clamp is controlled by the Archimedes spiral cam. Zhanghe movement.
  • the rope gripper J includes a gripping disc 16, a gripping piece 17, a gripper 21, and a gripper platen 22.
  • the clip piece 17 is caught on the fixed tab 210 of the knotter holder 2, and the gripper 21 is hinged to the knotter holder 2 via a gripper swing shaft 23.
  • the clipper slides on the shaft shaft hole 206, one side of the gripper stator 17 is pressed by the gripper moving plate pressing plate 22, and the gripper moving plate pressing plate 22 is hinged to the knotter bracket through the pin shaft.
  • the rope gripper drive mechanism Q includes a further involute worm 25 and a helical gear 26, and the clamp driven bevel gear 19 and the involute worm 25 are fixed to the worm shaft 18, respectively.
  • the helical gear 26 is fixed to the clamping disc 16 by a clamping disc shaft 27, and the involute worm 25 meshes with the helical gear 26.
  • One end of the involute worm 25 is provided with a nut-shaped boss 2501 to facilitate the attachment and detachment of the involute worm 25.
  • a boss 209 is disposed between the end surface of the clamping reel 16 and the end surface of the helical gear 26 and the end surface of the clamping disc shaft hole 205 of the knotter bracket to reduce the impact.
  • the friction during the working process of the knot is beneficial to the transmission.
  • a second thrust ball bearing 31 may be mounted between the helical gear 26 and the end surface of the clamping disc shaft hole 205.
  • the boss instead of the boss, as shown in Figure 11.
  • the knotting drive incomplete bevel gear 5 meshes with the knotted driven bevel gear 9 to drive the knotting nozzle 13 to rotate the buckle, and the cylindrical cam 12 controls the Hook clamp 14 piece clamps bite the rope.
  • the incomplete bevel gear 20 is meshed with the gripper driven bevel gear 19 by the gripper to cause the involute worm 25 to drive the helical gear 26 to rotate, and the gripping disc 16 is rotated.
  • the number of the involute worms 25 is two, and the number of teeth of the helical gears 26 is six.
  • 3 clip slots 24 are evenly distributed on the outer edge of the clamping disc 16, and the pinion 1 rotates once in each knotting cycle, and the clip is driven by the gripper drive mechanism Q
  • the three rope slots 24 on the rope tray 16 are rotated through 120°, and the rope tray 16 holds the rope from the initial position to the end position of the rope, so that the rope reaches the middle position of the cutting blade 15 and adds The length of the blade is cut and the length of the rope is cut, so that the knotter cutting rope is reliable.
  • the knotter holder 2 includes a knotter spindle shaft hole 201, a knife arm shaft hole 202, a worm shaft shaft hole 203, a knot nozzle shaft hole 204, and a gripping disk shaft hole 205.
  • the shaft axis d of the knot nozzle shaft hole 204 and the shaft shaft hole 201 of the knotter spindle The axis line a is arranged in a non-orthogonal intersecting axis, and the axis line c of the worm shaft hole 203 is arranged perpendicularly to the axis line a of the knotter spindle shaft hole 201, and the arm shaft hole of the arm shaft.
  • the axis line b of the 202 is arranged perpendicular to the axis d of the shaft hole 204 of the knotting nozzle, and the axis line b of the shaft hole 202 of the arm, the axis line e of the shaft hole 205 of the clamping disc, and
  • the axis line a of the knotter spindle shaft hole 201 is spatially arranged perpendicular to each other.
  • the end face of the knotter spindle shaft hole 201 is used as a front view projection surface, and the angular relationship of each shaft hole is designed as shown in Figs. 14, 15, and 16.
  • the worm shaft hole 203 is disposed on one side of the knotter bracket 2, and the worm shaft 18 is disposed in the worm shaft hole 203, so that the rivet driven bevel gear 19 consolidated with the worm shaft 18 is not driven by the yoke
  • the complete bevel gear 20 meshes.
  • the axis line d of the knot nozzle shaft hole 204 and the axis line a of the knotter spindle shaft hole 201 are at an angle of 98°, the shaft axis c of the worm shaft hole 203 and the knotter spindle
  • the axial hole a-axis intersection angle of the shaft hole 201 is 90°
  • the shaft axis d of the knot nozzle shaft hole 204 and the axial center line c of the worm shaft hole 203 are spatially staggered by 30°
  • the angle between the axis eo of the 205 and the axis c of the worm shaft hole 203 is 72°
  • the axis line b of the arm shaft hole 202 and the axis line d of the shaft hole 204 of the knotting nozzle The angle is 90°.
  • the bale is first fed by the cord to the gripper slot 24, which is controlled on the pinion 1
  • the rope driving incomplete rope bevel gear 20 of the rope gripper J meshes with the rope driven bevel gear 19 fixed to one end of the worm shaft 18, and is fixed to the other end of the worm shaft 18
  • the wire worm 25 meshes with the helical gear 26 to drive the clamping disk 16 to rotate, and the clamping piece 21 cooperates with the clamping disk 16 to clamp the rope while tying the rope Said to knot the mouth 13 .
  • the knotted driving incomplete bevel gear 5 on the large toothed disc 3 controlling the rotation of the knotting nozzle 13 is fixed to the end of the knotting nozzle 13
  • the knotted driven bevel gear 9 meshes, and the knotting nozzle 13 is rotated to wind the bundle around the surface of the knotting nozzle 13 in an annular shape.
  • the hook and tongs 14 are closed by the opening of the tongs under the action of the cylindrical cam 12, and then closed, and the tying rope is bitten between the hook tongs 14 and the knotting nozzle 13.
  • the groove cam 4 controls the blade arm 7 to swing, and the cutting blade 15 on the blade arm 7 cuts the rope under the holder J And the rope buckle on the knotting nozzle 13 is forcibly pushed off by the blade arm notch 30 on the blade arm 7, and finally a knot is formed.
  • the blade arm 7 swings back to the initial position to complete a knotting process.

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  • Life Sciences & Earth Sciences (AREA)
  • Environmental Sciences (AREA)
  • Braiding, Manufacturing Of Bobbin-Net Or Lace, And Manufacturing Of Nets By Knotting (AREA)
  • Scissors And Nippers (AREA)

Abstract

一种双齿盘驱动打结器，包括小齿盘（1）、打结器支架（2）、大齿盘（3）、装配在打结器支架上的刀臂（7）、绕扣钳咬机构R和夹绳器驱动机构Q；将双齿盘驱动打结器的复合齿盘分成小齿盘（1）和大齿盘（3），小齿盘（1）和大齿盘（3）同轴固定在打结器主轴轴孔（201）的两端，使打结器主轴受力平衡，提高了打结器的工作稳定性；夹绳盘（16）上设置3个夹绳槽口（24），加大了割绳刀片（15）滑切捆绳的长度，使打结器割绳动作可靠；刀臂滚子（6）沿空间轮廓曲面滚动，与凸轮表面的空间轮廓曲面呈线接触，使得承载能力更大，减小磨损。双齿盘打结器具有结构合理、便于加工和装配、制造成本低、成结可靠的特点。

Description

一种双齿盘驱动打结器 技术领域
本发明涉及秸秆或牧草收获打捆技术领域，具体涉及一种双齿盘驱动打结器。
背景技术
方草捆打捆机广泛用于农村和牧场的稻麦秸秆和干青牧草的收集和打捆，打结器是方草捆打捆机的核心部件，主要功能是将送绳机构送上的捆绳夹持，完成捆扎打结所需的绕扣、钳咬捆绳、割断捆绳和脱扣成结动作，将两个绳端打成死结，防止压缩后的草捆松散。经过捆扎打结的草捆密度高，便于运输和存放，非常有利于秸秆等生物质能源的利用。
目前，使用最广泛的C、D型打结器，国外的方草捆打捆机制造商拥有较为成熟的打结器设计制造技术和打结器发明专利，比如德国CLAAS公司、Rasspe Systemtechnik公司，美国的John Deer公司等。如欧洲EP1532859(A1)专利，RotoleDavid Vincent设计的D型单结式打结器，被Deere公司买断专利权；欧洲EP1745691(A1)专利，Schumacher Friedrich-Wilhelm等改进后的C型打结器。国内方草捆打捆机制造商长期依赖进口国外打结器来生产打捆机，打结器价格居高不下，垄断国内方草捆打捆机市场。此外，这些打结器皆属于集成式打结器，存在空间结构复杂，制造难度大、装配精度要求高的缺点。且将多个结构集中在一个零件上，增加了零件强度的负荷，存在一个结构的破坏而需更换整个零件的不足。
中国发明专利201110001685.8设计了一款仿人双指打结器，，该装置安装在压捆机尾部的打结器主轴上，能够模拟人手双指将送绳机构送上的绳子夹持，并完成捆扎打结所需的搭绳、夹绳、绕绳、咬绳、割绳和脱扣动作，实现对压实草捆的自动捆扎和打结，改善了打结器支架不便制造的缺陷，该发明与国外打结器相比空间结构相对简单，降低了制造成本。
但是，现有技术中，复合齿盘将打结驱动不完全锥齿轮和夹绳驱动不完全锥齿轮设于一侧，受力不均匀，而且空间结构复杂，制造难度大、装配精度要求高；送绳机构不可以将捆绳直接送入夹绳槽口，且割绳时，绳头位置接近刀锋上部，不利于割断绳头；球面刀臂滚子与圆柱凸轮呈点接触配合，使用中应力冲击波大，长期使用圆柱凸轮磨损大，影响打结器的使用寿命。
为此，本发明提出了一种用绳将农作物秸秆或牧草捆扎为长方形草捆的自动打结装置，具有结构合理、便于加工和装配、制造成本低、成结可靠特点的双齿盘驱动打结器，解决国内企业生产方草捆打捆机受制于进口打结器的问题。
发明内容
本发明所要解决的技术问题是复合齿盘受力不均匀导致打结器空间结构复杂，制造难度大、装配精度要求高；送绳机构在割绳时，绳头位置接近刀锋上部，不利于割断绳头；圆柱凸轮磨损大，影响打结器的使用寿命。本发明提供一种结构新颖、制造成本低的双齿盘驱动打结器，克服国外打结器空间结构复杂、制造难度大、装配精度要求高的缺点，具有结构合理、便于加工和装配、制造成本低、成结可靠的特点。
本发明的技术方案是：将双齿盘驱动打结器的复合齿盘分成小齿盘和大齿盘两个部件设置，小齿盘驱动夹绳驱动不完全锥齿轮，大齿盘驱动打结驱动不完全锥齿轮并带动刀臂动作。本发明包括小齿盘、打结器支架、大齿盘、装配在打结器支架上的刀臂、绕扣钳咬机构R和夹绳器驱动机构Q；所述小齿盘和所述大齿盘同轴固定在所述打结器支架上的打结器主轴轴孔的两端；所述绕扣钳咬机构R和所述夹绳器驱动机构Q分别安装在所述打结器支架的两侧；所述大齿盘圆周上设置有打结驱动不完全锥齿轮，所述刀臂顶端的刀臂滚子与大齿盘内侧的沟槽凸轮配合，打结从动锥齿轮与所述打结驱动不完全锥齿轮啮合；所述小齿盘的圆周上设置有夹绳驱动不完全锥齿轮，夹绳从动锥齿轮与所述夹绳驱动不完全锥齿轮啮合。
所述夹绳器驱动机构Q驱动夹绳器J，所述夹绳器J的夹绳盘的外缘上均布3个夹绳槽口，与所述夹绳从动锥齿轮通过蜗杆轴固结的渐开线蜗杆的头数是2，与所述渐开线蜗杆啮合的螺旋齿轮的齿数是6。
所述刀臂滚子为圆柱状，所述沟槽凸轮的凸轮表面为空间轮廓曲面，所述刀臂滚子的圆柱面与凸轮表面的空间轮廓曲面呈线接触，刀臂滚子沿空间轮廓曲面滚动。刀臂滚子的两端为圆弧状倒角。
与所述绕扣钳咬机构R配合的所述打结器支架上的圆柱凸轮轮廓为阿基米德螺旋线凸轮。
所述空间轮廓曲面建立过程如下：过割绳刀臂上滚子的上表面中心向摆动中心轴作垂线，交点作为动坐标系的中心O1，以滚子向旋转中心轴作的垂线作为动坐标系的X轴，旋转轴作为Y轴，根据右手定则建立坐标系；过O1点向齿盘旋转中心轴作垂线，交点作 为建立静坐标系的中心O，平行于动坐标系X1的方向作X轴，平行Y1的方向作Y轴，根据右手定则建立静坐标系；同时动坐标系绕着静坐标系顺时针旋转角度为β；初始位置，动坐标系也相当于静坐标系在Z轴负方向平移m个单位长度，Y轴负方向平移n个单位长度得到；设刀臂在初始位置时与动坐标系的夹角为θ0,摆动时转过的角度为θ，刀臂滚子上表面中心点为P，下表面中心点为Q，同时刀臂长度设为l，PQ之间的距离设为f；因此，P、Q点在动坐标系中的坐标分别为P(lcos(θ+θ0),-lsin(θ+θ0),0),Q((l-f)cos(θ+θ0),-(l-f)sin(θ+θ0),0)；
Figure PCTCN2015097646-appb-000001
其中，x1、y1、z1分别为动坐标系中的坐标点。
带入P、Q连点坐标为
Figure PCTCN2015097646-appb-000002
Figure PCTCN2015097646-appb-000003
另；刀臂在凸轮推程和回程阶段分别转过角度：
推程转过角度
Figure PCTCN2015097646-appb-000004
回程转过角度
Figure PCTCN2015097646-appb-000005
其中：
θ1—割绳刀臂摆动角度；
Figure PCTCN2015097646-appb-000006
—推程起始相位；
Φ—推程结束相位；
ω—回程结束相位。
所述渐开线蜗杆的一端设置有螺母状凸台B。
所述打结器支架还包括蜗杆轴轴孔、打结嘴轴孔和夹绳盘轴孔；所述打结嘴轴孔与所述打结器主轴轴孔呈非正交相交轴布置，所述蜗杆轴轴孔与所述打结器主轴轴孔呈垂直相交轴布置，所述刀臂轴轴孔与所述打结嘴轴孔空间相互垂直布置，所述夹绳盘轴孔和打结器主轴轴孔呈空间相互垂直布置，实施打结器主轴轴孔和夹绳盘轴孔呈空间相互垂直布置。
所述打结器支架还包括蜗杆轴轴孔、打结嘴轴孔和夹、绳盘轴孔；所述打结嘴轴孔与所述打结器主轴轴孔呈非正交相交轴布置，所述蜗杆轴轴孔与所述打结器主轴轴孔呈垂直相交轴布置，所述刀臂轴轴孔与所述打结嘴轴孔空间相互垂直布置，所述臂轴轴孔、夹绳盘轴孔和打结器主轴轴孔呈空间相互垂直布置。
所述打结嘴轴孔轴心线d与所述打结器主轴轴孔轴心线a轴交角为98°，所述打结嘴轴孔轴心线d与所述蜗杆轴孔轴心线c空间交错角为30°，所述夹绳盘轴孔轴心线e与所述蜗杆轴孔轴心线c之间的夹角为72°。
所述刀臂通过刀臂轴铰接在所述刀臂轴轴孔上，所述刀臂轴由对称安装的一对滑动轴承和一对第一推力球轴承支撑在打结器支架上的刀臂轴孔内，刀臂轴两端通过螺栓连接固定。
所述渐开线蜗杆与所述螺旋齿轮的传动比为3，在所述夹绳盘的外缘上均布3个夹绳槽口；所述渐开线蜗杆的头数是2，所述螺旋齿轮的齿数是6。
所述夹绳盘端面、所述螺旋齿轮端面与所述打结器支架上的夹绳盘轴孔端面之间均设置凸台。或者所述螺旋齿轮与所述夹绳盘轴孔端面之间安装第二推力球轴承。
本发明的有益效果是：
1、将双齿盘驱动打结器的复合齿盘分成小齿盘和大齿盘，小齿盘和大齿盘同轴固定在打结器主轴轴孔的两端，使打结器主轴受力平衡，提高了打结器的工作稳定性。
2、通过将夹绳器驱动机构Q和绕扣钳咬机构R安装在打结器支架上的不同侧，充分利用了打结器支架空间，使打结器空间参数匹配更加灵活、合理。
3、夹绳盘上设置3个夹绳槽口，当夹绳盘从初始位置夹持捆绳转到夹绳结束位置，使捆绳到达割绳刀片的刀刃中间位置，加大了割绳刀片滑切捆绳的长度，使打结器割绳动作可靠。
4、刀臂滚子沿空间轮廓曲面滚动，与凸轮表面的空间轮廓曲面呈线接触，使得承载能力更大，减小磨损。同时空间轮廓曲的设置使刀臂呈正弦加速度运动，理论上消除刀臂滚子与凸轮表面的应力冲击。
5、打结器支架上所述轴孔轴心线布置降低了打结器支架轴孔的制造难度，有利于保证各轴孔角度之间的加工精度。
6、通过采用滑动轴承和推力球轴承组合结构，使打结器支架上的刀臂轴孔端面不与刀臂轴孔端面发生摩擦，便于刀臂轴两端的螺栓紧固，严格保证刀臂安装位置的同时使其转动灵活。
7、渐开线蜗杆的一端设置有螺母状凸台，大大方便了所述渐开线蜗杆的装拆。
8、夹绳盘端面、所述螺旋齿轮端面与所述打结器支架上的夹绳盘轴孔端面之间均设置凸台，减小打结器工作过程中的摩擦，利于传动。
9、所述螺旋齿轮与所述夹绳盘轴孔端面之间也可以安装推力轴承来代替凸台，以便减小打结器工作过程中，所述螺旋齿轮与所述夹绳盘轴孔端面之间的摩擦，利于传动。
附图说明
图1是一个实施例的双齿盘驱动打结器装配正向轴测图。
图2是一个实施例的小齿盘结构布置图。
图3是一个实施例的大齿盘结构布置图。
图4是一个实施例的刀臂结构示意图。
图5是一个实施例的刀臂轴装配二维剖视图。
图6是一个实施例的绕扣钳咬机构R的结构示意图。
图7是一个实施例的夹绳器构造轴侧图。
图8是一个实施例的夹绳器驱动机构配置轴侧图。
图9是一个实施例的双齿盘驱动打结器装配图。
图10是一个实施例的夹绳盘轴孔凸台示意图。
图11是图9中F-F的侧剖图。
图12是一个实施例的打结器支架轴孔示意图a。
图13是一个实施例的打结器支架轴孔示意图b。
图14是一个实施例的打结器支架轴孔角度关系图a。
图15是一个实施例的打结器支架轴孔角度关系图b。
图16是一个实施例的打结器支架轴孔角度关系图c。
图17是刀臂滚子示意图。
图18是现有技术的德国D型打结器正向示意图。
图19是现有技术的德国D型打结器背面示意图。
图中，1、小齿盘；2、打结器支架；201、打结器主轴轴孔；202、刀臂轴轴孔；203、蜗杆轴轴孔；204、打结嘴轴孔；205夹绳盘轴孔；206、夹绳动片摆轴轴孔；207、钩钳压板轴轴孔；208、夹绳动片压板轴轴孔；209、凸台；2010、定片卡口；3、大齿盘；4、沟槽凸轮；5、打结驱动不完全锥齿轮；6、刀臂滚子；7、刀臂；8、刀臂轴；9、打结从动锥齿轮；10、钩钳压板；1001、钩钳压板轴；11、压缩弹簧；12、圆柱凸轮；13、打结嘴；14、钩钳；15、割绳刀片；16、夹绳盘；17、夹绳定片；18、蜗杆轴；19、夹绳从动锥齿轮；20、夹绳驱动不完全锥齿轮；21、夹绳动片；22、夹绳动片压板；23、夹绳动片摆轴；24、夹绳槽口；25、渐开线蜗杆；2501、螺母状凸台；26、螺旋齿轮；27、夹绳盘轴；28、第一推力球轴承；29、滑动轴承；30、刀臂缺口；31、第二推力球轴承：32、复合齿盘。
具体实施方式
在本发明的描述中，需要理解的是，术语“上”、“下”、“前”、“后”、“左”、“右”、“顶”、“底”“内”、“外”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括一个或者更多个该特征。在本实用新型的描述中，“多个”的含义是两个或两个以上，除非另有明确具体的限定。
在本发明中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或一体地连接；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本发明中的具体含义。
在本发明中，除非另有明确的规定和限定，第一特征在第二特征之“上”或之“下”可 以包括第一和第二特征直接接触，也可以包括第一和第二特征不是直接接触而是通过它们之间的另外的特征接触。而且，第一特征在第二特征“之上”、“上方”和“上面”包括第一特征在第二特征正上方和斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”包括第一特征在第二特征正下方和斜下方，或仅仅表示第一特征水平高度小于第二特征。
下面结合附图具体实施方式对本发明作进一步详细说明，但本发明的保护范围并不限于此。
如图1所示，一种双齿盘驱动打结器包括小齿盘1、打结器支架2、大齿盘3和装配在打结器支架2上的刀臂7、绕扣钳咬机构R、夹绳器J及其驱动机构Q。
所述小齿盘1和所述大齿盘3同轴固定在所述打结器支架2上的打结器主轴轴孔201的两端。
如图3所示，所述刀臂7通过销轴铰接在所述打结器支架2的刀臂轴轴孔202上，所述大齿盘3内侧设置有沟槽凸轮4，所述刀臂7的上端顶住所述沟槽凸轮4。
所述绕扣钳咬机构R和所述夹绳器驱动机构Q分别安装在所述打结器支架2的两侧。
所述大齿盘3圆周上设置有打结驱动不完全锥齿轮5，所述绕扣钳咬机构R与打结从动锥齿轮9固接，所述打结从动锥齿轮9与所述打结驱动不完全锥齿轮5啮合。
如图3所示，所述大齿盘3上安装有打结驱动不完全锥齿轮5(所述绕扣钳咬机构R与打结从动锥齿轮9固接，所述打结从动锥齿轮9与所述打结驱动不完全锥齿轮5啮合)和设有沟槽凸轮4，所述沟槽凸轮4具有空间轮廓曲面，所述空间轮廓曲面建立过程如下：过割绳刀臂上滚子的上表面中心向摆动中心轴作垂线，交点作为动坐标系的中心O1，以滚子向旋转中心轴作的垂线作为动坐标系的X轴，旋转轴作为Y轴，根据右手定则建立坐标系；过O1点向齿盘旋转中心轴作垂线，交点作为建立静坐标系的中心O，平行于动坐标系X1的方向作X轴，平行Y1的方向作Y轴，根据右手定则建立静坐标系；同时动坐标系绕着静坐标系顺时针旋转一周；初始位置，动坐标系也相当于静坐标系在Z轴负方向平移22个单位长度，Y轴负方向平移58个单位长度得到；设刀臂在初始位置时与动坐标系的夹角为5π/36,摆动时转过的角度为θ，刀臂滚子上表面中心点为P，下表面中心点为Q，同时刀臂长度为64，PQ之间的距离设为17；因此，P、Q点在动坐标系中的坐标分别为P(64cos(θ+5π/36),-64sin(θ+5π/36),0),Q(47cos(θ+5π/36),-47sin(θ+5π/36),0)。
Figure PCTCN2015097646-appb-000007
带入P、Q两点坐标为
Figure PCTCN2015097646-appb-000008
Figure PCTCN2015097646-appb-000009
刀臂在凸轮推程[0,π/3]和回程[π/3,2π/3]阶段分别转过角度：
推程转过角度
Figure PCTCN2015097646-appb-000010
回程转过角度
Figure PCTCN2015097646-appb-000011
其中：
θ1—割绳刀臂摆动角度；
Figure PCTCN2015097646-appb-000012
—推程起始相位；
Φ—推程结束相位；
ω—回程结束相位。
如图2所示，所述小齿盘1的圆周上设置有夹绳驱动不完全锥齿轮20(所述夹绳器驱动机构Q与夹绳从动锥齿轮19固接，所述夹绳从动锥齿轮19与所述夹绳驱动不完全锥齿轮20啮合，所述夹绳器驱动机构Q包括螺旋齿轮26，所述螺旋齿轮26通过夹绳盘轴27与所述夹绳器J固接。
如图4所示，所述刀臂7通过刀臂轴8装配在所述刀臂轴轴孔202上，所述沟槽凸轮4通过驱动刀臂滚子6使所述刀臂7绕所述刀臂轴8的轴心往复摆动。
如图4所示，刀臂滚子6为圆柱状，刀臂滚子的圆柱面与凸轮表面的空间轮廓曲面呈线接触。如图17所示，刀臂滚子6的两端为圆弧状倒角，有利于降低刀臂滚子6与沟槽凸轮4之间的装配要求、减少磨损。
如图5所示，所述刀臂轴8由对称安装的一对滑动轴承29和一对第一推力球轴承28支撑在所述打结器支架2上的阶梯型刀臂轴轴孔202内，所述刀臂轴8两端通过螺栓连接固定。通过采用所述滑动轴承29和所述第一推力球轴承28组合结构，使所述刀臂轴轴孔202端面不与所述刀臂7轴孔端面发生摩擦，便于所述刀臂轴8两端的螺栓紧固，严格保证所述刀臂7安装位置的同时使其转动灵活。
如图6所示，所述绕扣钳咬机构R包括打结嘴13、勾钳14、打结器支架2上的圆柱凸轮12和钩钳压板10，所述打结嘴13的顶端穿过所述凸轮12与打结从动锥齿轮9固接，勾钳14通过销轴铰接在打结嘴13上，所述勾钳14的顶端被所述钩钳压板10压住，所述钩钳压板10通过销轴铰接在所述打结器支架2的钩钳压板轴轴孔207上，压缩弹簧11套在钩钳压板轴1001上通过螺丝固定，用于调节对所述钩钳压板10的压力，所述圆柱凸轮12轮廓为阿基米德螺旋线凸轮，所述打结嘴13转动过程中，所述钩钳上的钩钳滚子在阿基米德螺旋线凸轮的控制下，完成张合运动。
如图7所示，所述的夹绳器J包括夹绳盘16、夹绳定片17、夹绳动片21和夹绳动片压板22。所述夹绳定片17卡在所述打结器支架2上的定片卡口210上，所述夹绳动片21通过夹绳动片摆轴23铰接在所述打结器支架2的夹绳动片摆轴轴孔206上，所述夹绳定片17的一侧被夹绳动片压板22压住，所述夹绳动片压板22通过销轴铰接在所述打结器支架2的夹绳动片压轴轴孔208上，在打结器夹绳过程中，随所述夹绳盘16的转动带动所述夹绳动片21绕所述夹绳动片摆轴23的轴心摆动。
如图8所示，所述夹绳器驱动机构Q包括还渐开线蜗杆25和螺旋齿轮26，所述夹绳从动锥齿轮19和所述渐开线蜗杆25分别固接在蜗杆轴18的两端，所述螺旋齿轮26与所述夹绳盘16通过夹绳盘轴27固接，所述渐开线蜗杆25与所述螺旋齿轮26啮合。
所述渐开线蜗杆25的一端设置有螺母状凸台2501，方便了所述渐开线蜗杆25的装拆。
如图9、10所示，所述夹绳盘16端面、所述螺旋齿轮26端面与所述打结器支架上的夹绳盘轴孔205端面之间均设置凸台209，以减小打结器工作过程中的摩擦，利于传动。所述螺旋齿轮26与所述夹绳盘轴孔205端面之间也可以安装第二推力球轴承31来 代替凸台，如图11所示。
如图1和图8所示，通过所述打结驱动不完全锥齿轮5与所述打结从动锥齿轮9啮合带动所述打结嘴13旋转绕扣，所述圆柱凸轮12控制所述钩钳14张合钳咬捆绳。通过所述夹绳驱动不完全锥齿轮20与所述夹绳从动锥齿轮19啮合使所述渐开线蜗杆25驱动所述螺旋齿轮26转动，带动所述夹绳盘16转动。通过将所述夹绳器驱动机构Q和所述绕扣钳咬机构R分别安装在所述打结器支架2上的两侧，充分利用了所述打结器支架2空间，使打结器空间参数匹配更加灵活。所述渐开线蜗杆25与所述螺旋齿轮26传动比为3，优选的所述渐开线蜗杆25的头数是2，所述螺旋齿轮26的齿数是6。在所述夹绳盘16的外缘上均布3个夹绳槽口24，在每个打结周期，所述小齿盘1旋转一周，通过所述夹绳器驱动机构Q使所述夹绳盘16上的3个夹绳槽口24转过120°，所述夹绳盘16从初始位置夹持捆绳到达夹绳结束位置，使捆绳到达割绳刀片15的刀刃中间位置，加大了刀片滑切捆绳的长度，使打结器割绳动作可靠。
如图12和13所示，所述打结器支架2包括打结器主轴轴孔201、刀臂轴轴孔202、蜗杆轴轴孔203、打结嘴轴孔204和夹绳盘轴孔205；为了降低所述打结器支架2上轴孔的制造难度，保证各轴孔角度之间的加工精度，所述打结嘴轴孔204轴心线d与所述打结器主轴轴孔201轴心线a呈非正交相交轴布置，所述蜗杆轴轴孔203轴心线c与所述打结器主轴轴孔201轴心线a呈垂直相交轴布置，所述刀臂轴轴孔202轴心线b与所述打结嘴轴孔204轴心线d呈空间相互垂直布置，所述刀臂轴轴孔202轴心线b、所述夹绳盘轴孔205轴心线e和所述打结器主轴轴孔201轴心线a呈空间相互垂直布置。将所述打结器主轴轴孔201端面作为主视图投影面，各轴孔角度关系设计如图14、15、和16所示。蜗杆轴轴孔203设于打结器支架2的一侧，蜗杆轴18设于蜗杆轴轴孔203内，使与蜗杆轴18固结的夹绳从动锥齿轮19与所述夹绳驱动不完全锥齿轮20啮合。
所述打结嘴轴孔204轴心线d与所述打结器主轴轴孔201轴心线a轴交角为98°，所述蜗杆轴轴孔203轴心线c与所述打结器主轴轴孔201轴心线a轴交角为90°，所述打结嘴轴孔204轴心线d与所述蜗杆轴孔203轴心线c空间交错角为30°，所述夹绳盘轴孔205轴心线e与所述蜗杆轴孔203轴心线c之间的夹角为72°，所述刀臂轴轴孔202轴心线b与所述打结嘴轴孔204轴心线d的夹角为90°。通过将所述打结器支架2的各轴孔轴心线角度呈上述的优选布置，既实现了夹绳、绕扣和割绳脱扣动作的动力传动，又充分利用了打结器支架空间，使打结器空间结构参数匹配更加合理，方便所述打结器支架2上各轴孔加工。
当本发明工作时，捆绳首先被绳针送到所述夹绳槽口24处，所述小齿盘1上控制 所述夹绳器J动作的夹绳驱动不完全锥齿轮20与固接在所述蜗杆轴18一端的夹绳从动锥齿轮19啮合，固接在所述蜗杆轴18另一端的所述渐开线蜗杆25与所述螺旋齿轮26啮合，带动所述夹绳盘16转动，所述夹绳动片21与所述夹绳盘16配合将捆绳夹持的同时将捆绳搭接在所述打结嘴13上。当所述小齿盘1转过一个相位后，所述大齿盘3上控制所述打结嘴13转动的所述打结驱动不完全锥齿轮5与固接在所述打结嘴13一端的所述打结从动锥齿轮9啮合，带动所述打结嘴13旋转使捆绳呈环状地缠绕在所述打结嘴13的表面上。与此同时，所述钩钳14在打所述圆柱凸轮12作用下先张开钳咬住捆绳之后再闭合，将捆绳咬在所述钩钳14和所述打结嘴13之间。当所述大齿盘3继续转动一个相位后，所述沟槽凸轮4控制所述刀臂7摆动，所述刀臂7上的割绳刀片15将所述夹持器J下方的捆绳割断，并借助所述刀臂7上的刀臂缺口30将所述打结嘴13上的绳扣强制推脱，最后形成绳结。当所述大齿盘3转回到初始位置时，所述刀臂7反向摆回到初始位置，完成一个打结过程。
所述实施例为本发明的优选的实施方式，但本发明并不限于上述实施方式，在不背离本发明的实质内容的情况下，本领域技术人员能够做出的任何显而易见的改进、替换或变型均属于本发明的保护范围。

Claims (12)

  1. 一种双齿盘驱动打结器，其特征在于，包括小齿盘(1)、打结器支架(2)、大齿盘(3)、装配在打结器支架(2)上的刀臂(7)、绕扣钳咬机构R和夹绳器驱动机构Q；
    所述小齿盘(1)和所述大齿盘(3)同轴固定在所述打结器支架(2)上的打结器主轴轴孔(201)的两端；所述绕扣钳咬机构R和所述夹绳器驱动机构Q分别安装在所述打结器支架(2)的两侧；
    所述大齿盘(3)圆周上设置有打结驱动不完全锥齿轮(5)，所述刀臂(7)顶端的刀臂滚子(6)与大齿盘(3)内侧的沟槽凸轮(4)配合，打结从动锥齿轮(9)与所述打结驱动不完全锥齿轮(5)啮合；所述小齿盘(1)的圆周上设置有夹绳驱动不完全锥齿轮(20)，夹绳从动锥齿轮(19)与所述夹绳驱动不完全锥齿轮(20)啮合。
  2. 根据权利要求1所述的双齿盘驱动打结器，其特征在于，所述夹绳器驱动机构Q驱动夹绳器J，所述夹绳器J的夹绳盘(16)的外缘上均布3个夹绳槽口(24)，与所述夹绳从动锥齿轮(19)通过蜗杆轴(18)固结的渐开线蜗杆(25)的头数是2，与所述渐开线蜗杆(25)啮合的螺旋齿轮(26)的齿数是6。
  3. 根据权利要求1所述的双齿盘驱动打结器，其特征在于，所述刀臂滚子(6)为圆柱状，所述沟槽凸轮(4)的凸轮表面为空间轮廓曲面，所述刀臂滚子(6)的圆柱面与凸轮表面的空间轮廓曲面呈线接触，刀臂滚子(6)沿空间轮廓曲面滚动。
  4. 根据权利要求1、2或3所述的双齿盘驱动打结器，其特征在于，与所述绕扣钳咬机构R配合的所述打结器支架(2)上的圆柱凸轮(12)轮廓为阿基米德螺旋线凸轮。
  5. 根据权利要求3所述的双齿盘驱动打结器，其特征在于，所述凸轮表面的空间轮廓曲面为：过割绳刀臂上滚子的上表面中心向摆动中心轴作垂线，交点作为动坐标系的中心O1，以滚子向旋转中心轴作的垂线作为动坐标系的X轴，旋转轴作为Y轴，根据右手定则建立坐标系；过O1点向齿盘旋转中心轴作垂线，交点作为建立静坐标系的中心O，平行于动坐标系X1的方向作X轴，平行Y1的方向作Y轴，根据右手定则建立静坐标系；同时动坐标系绕着静坐标系顺时针旋转角度为β；初始位置，动坐标系也相当于静坐标系在Z轴负方向平移m个单位长度，Y轴负方向平移n个单位长度得到；设刀臂在初始位置时与动坐标系的夹角为θ0,摆动时转过的角度为θ，刀臂滚子上表面中心点为P，下表面中心点为Q，同时刀臂长度设为l，PQ之间的距离设为f；因此，P、Q点在动坐标系中的坐标分别为P(lcos(θ+θ0),-lsin(θ+θ0),0),Q((l-f)cos(θ+θ0),-(l-f)sin(θ+θ0),0)；
    Figure PCTCN2015097646-appb-100001
    带入P、Q连点坐标为
    Figure PCTCN2015097646-appb-100002
    Figure PCTCN2015097646-appb-100003
    刀臂在凸轮推程和回程阶段分别转过角度：
    推程转过角度
    Figure PCTCN2015097646-appb-100004
    回程转过角度
    Figure PCTCN2015097646-appb-100005
    其中：
    θ1—割绳刀臂摆动角度；
    Figure PCTCN2015097646-appb-100006
    —推程起始相位；
    Φ—推程结束相位；
    ω—回程结束相位。
  6. 根据权利要求3或5所述的双齿盘驱动打结器，其特征在于，所述刀臂滚子(6)的两端为圆弧状倒角。
  7. 根据权利要求1、2或3所述的双齿盘驱动打结器，其特征在于，所述渐开线蜗杆(25)的一端设置有螺母状凸台B(2501)。
  8. 根据权利要求1、2或3所述的双齿盘驱动打结器，其特征在于，所述打结器支架(2)还包括蜗杆轴轴孔(203)、打结嘴轴孔(204)和夹绳盘轴孔(205)；所述打结嘴轴孔(204)与所述打结器主轴轴孔(201)呈非正交相交轴布置，所述蜗杆轴轴孔(203)与所述打结器主轴轴孔(201)呈垂直相交轴布置，所述刀臂轴轴孔(202)与所述打结嘴轴孔(204)空间相互垂直布置，所述夹绳盘轴孔(205)和打结器主轴轴孔(201)呈空间相互垂直布置，实施打结器主轴轴孔(201)和夹绳盘轴孔(205)呈空间相互垂直布置。
  9. 根据权利要求7所述的双齿盘驱动打结器，其特征在于，所述打结嘴轴孔(204)轴心线d与所述打结器主轴轴孔(201)轴心线a轴交角为98°，所述打结嘴轴孔(204)轴心线d与所述蜗杆轴孔(203)轴心线c空间交错角为30°，所述夹绳盘轴孔(205)轴心线e与所述蜗杆轴孔(203)轴心线c之间的夹角为72°。
  10. 根据权利要求1、2或3所述的双齿盘驱动打结器，其特征在于，所述刀臂(7)通过刀臂轴(8)铰接在所述刀臂轴轴孔(202)上，所述刀臂轴(8)由对称安装的一对滑动轴承(29)和第一推力球轴承(28)支撑在打结器支架(2)上的刀臂轴(8)孔内，刀臂轴(8)两端通过螺栓连接固定。
  11. 根据权利要求1、2或3所述的双齿盘驱动打结器，其特征在于，所述夹绳盘(16)端面、所述螺旋齿轮(26)端面与所述打结器支架上的夹绳盘轴孔(205)端面之间均设置凸台(209)。
  12. 根据权利要求1、2或3所述的双齿盘驱动打结器，其特征在于，所述螺旋齿轮(26)与所述夹绳盘轴孔(205)端面之间安装第二推力球轴承(31)。
PCT/CN2015/097646 2015-04-03 2015-12-17 一种双齿盘驱动打结器 Ceased WO2016155364A1 (zh)

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