CN205510981U - Bidentate dish drive knotter - Google Patents
Bidentate dish drive knotter Download PDFInfo
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- CN205510981U CN205510981U CN201521001639.8U CN201521001639U CN205510981U CN 205510981 U CN205510981 U CN 205510981U CN 201521001639 U CN201521001639 U CN 201521001639U CN 205510981 U CN205510981 U CN 205510981U
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- wire twister
- tool arm
- axis hole
- rope
- folder
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Abstract
The utility model discloses a bidentate dish drive knotter relates to straw or grass harvesting and beats a bundle technical field, the utility model discloses a tool arm on the knotter support of little fluted disc, knotter support, big fluted disc, assembly, sting R of mechanism and rope clamping device actuating mechanism Q around buckleing to clamp, divide into little fluted disc and big fluted disc with bidentate dish drive knotter's composite tooth dish, little fluted disc makes knotter main shaft the force balance with big the fluted disc is coaxial fixes at the both ends in knotter main shaft shaft hole, has improved the job stabilization nature of knotter, setting up 3 double -layered grooving mouths on pressing from both sides the cheese, having increaseed the length of twine knife piece sliding cutting bundle rope, it is reliable that messenger's knotter cuts the rope action, the tool arm roller rolls along the spatial outline curved surface, is the line contact with cam surface's spatial outline curved surface for bearing capacity is bigger, reduces wearing and tearing. This life buddha has rational in infrastructure, handling ease and assembly, low in manufacturing cost, the reliable characteristics of one -tenth knot.
Description
Technical field
This utility model relates to straw or herbage harvesting bundling technical field, is specifically related to a kind of two gear disk and drives knotting
Device.
Background technology
Medulla Tetrapanacis bundle baler is widely used in the rice wheat straw in rural area and pasture and does collection and bundling, the wire twister of blue or green herbage
Being the core component of Medulla Tetrapanacis bundle baler, major function is that bundle rope clamp Song Sheng mechanism served is held, and completes to tie up knotting required
Around button, pincers sting bundle rope, cut off bundle rope and thread off into knot action, two ends are broken into fast knot, prevent compression after bale pine
Dissipate.High through tying up the bale tension of knotting, it is simple to transport and deposit, be very beneficial for the utilization of the biomass energies such as straw.
At present, most popular C, D type wire twister, external Medulla Tetrapanacis is tied baler manufacturer and is had more ripe beating
Knot device design and manufacturing technology and wire twister patent of invention, such as CLAAS company of Germany, Rasspe Systemtechnik company,
John Deer company of the U.S. etc..Such as Europe EP1532859 (A1) patent, the D type list of RotoleDavid Vincent design
Eliminant wire twister, is bought out patent right by Deere company；Europe EP1745691 (A1) patent, Schumacher Friedrich-
C-type wire twister after the improvement such as Wilhelm.Domestic Medulla Tetrapanacis is tied the baler manufacturer external wire twister of long-term dependence on import and is produced
Baler, wire twister holds at high price, and monopolizes domestic Medulla Tetrapanacis bundle baler market.Additionally, these wire twisters come under integrated
Formula wire twister, Existential Space structure is complicated, and manufacture difficulty is big, assembly precision requires high shortcoming.And multiple structures are concentrated on
On one part, add the load of part strength, there is a structural damage and the deficiency of whole part need to be changed.
Chinese invention patent 201110001685.8 devises a humanoid two-finger knotter, this device is arranged on baling
On the wire twister main shaft of drive end unit, it is possible to the double rope clamping referring to serve Song Sheng mechanism of simulation staff, and complete to tie up knotting
Required take rope, folder rope, wiring, sting rope, cut and restrict and trip action, it is achieved to being compacted automatically tying up and tiing a knot of bale, improvement
The defect that wire twister support inconvenience manufactures, this invention space structure compared with external wire twister is relatively easy, reduce manufacture
Cost.
But, in prior art, knotting is driven incomplete bevel gear and folder rope to drive incomplete bevel gear by compound fluted disc
Being located at side, discontinuity, and space structure is complicated, manufacture difficulty is big, assembly precision requires height；Song Sheng mechanism cannot
Bundle rope is sent directly into folder grooving mouth, and when cutting rope, fag end is closely located to knife edge top, is unfavorable for cutting off fag end；Sphere tool arm
Roller is that point cantact coordinates with cylindrical cam, uses middle stress shock wave big, and the abrasion of life-time service cylindrical cam is big, impact knotting
The service life of device.
To this end, the utility model proposes that agricultural crop straw or herbage tied up as rectangle bale by a kind of rope is automatic
Knotting device, have rational in infrastructure, be easy to process with assembling, low cost of manufacture, become knot certain features two gear disk drive tie a knot
Device, solves the problem that domestic enterprise's producer bale baler is limited by import wire twister.
Summary of the invention
Technical problem to be solved in the utility model is that compound fluted disc discontinuity causes wire twister space structure multiple
Miscellaneous, manufacture difficulty is big, assembly precision requires height；Song Sheng mechanism is when cutting rope, and fag end is closely located to knife edge top, is unfavorable for cutting off
Fag end；Cylindrical cam abrasion is big, affects the service life of wire twister.This utility model provides a kind of novel structure, manufacturing cost
Low two gear disk drives wire twister, overcomes that external wire twister space structure is complicated, manufacture difficulty is big, assembly precision requirement is high lacks
Point, have rational in infrastructure, be easy to process with assembling, low cost of manufacture, become knot reliable feature.
The technical solution of the utility model is: two gear disk drives the compound fluted disc of wire twister be divided into small tooth plate and large fluted disc
Two parts are arranged, and small tooth plate drives folder rope to drive incomplete bevel gear, and large fluted disc drives knotting to drive incomplete bevel gear also
Drive tool arm action.This utility model include small tooth plate, wire twister support, large fluted disc, the tool arm being assemblied on wire twister support,
Mechanism R and rope brake drive mechanism Q is stung around clasp forceps；Described small tooth plate and described large fluted disc are coaxially fixed on described wire twister support
On the two ends of wire twister spindle hole of main；Described sting mechanism R around clasp forceps and described rope brake drive mechanism Q is separately mounted to described
The both sides of wire twister support；Described large fluted disc is provided circumferentially about has knotting to drive incomplete bevel gear, the cutter on described tool arm top
Arm roller coordinates with the grooved cam inside large fluted disc, and knotting driven wheel of differential drives incomplete bevel gear to nibble with described knotting
Close；The provided circumferentially about of described small tooth plate has folder rope to drive incomplete bevel gear, folder rope driven wheel of differential to drive with described folder rope
Not exclusively bevel gear engagement.
Described rope brake drive mechanism Q drives uniform 3 folder ropes in the outer rim of the folder cheese of rope brake J, described rope brake J
Notch, is 2 with the described head number pressing from both sides the involute helicoid worm that rope driven wheel of differential is consolidated by worm shaft, with described involute helicoid worm
The number of teeth of the helical gear of engagement is 6.
Described tool arm roller is cylindric, and the cam face of described grooved cam is space profiles curved surface, and described tool arm rolls
The face of cylinder of son is linear contact lay with the space profiles curved surface of cam face, and tool arm roller rolls along space profiles curved surface.Tool arm rolls
The two ends of son are arc-shaped chamfering.
It is Archimedian screw with the described cylindrical cam profile stung on the described wire twister support that mechanism R coordinates around clasp forceps
Line cam.
It is as follows that described space profiles curved surface sets up process: on mistake twine knife arm, the upper surface center of roller is to oscillation center axle
Make vertical line, intersection point as the center O1 of moving coordinate system, the vertical line made to center of rotation axle using roller as the X-axis of moving coordinate system,
Rotary shaft, as Y-axis, sets up coordinate system according to the right-hand rule；Crossing O1 point and make vertical line to fluted disc center of rotation axle, intersection point is as building
Founding the center O of quiet coordinate system, X-axis is made in the direction being parallel to moving coordinate system X1, and Y-axis is made in the direction of parallel Y1, according to the right-hand rule
Set up quiet coordinate system；Moving coordinate system is β around quiet coordinate system dextrorotation gyration simultaneously；Initial position, moving coordinate system also phase
When tying up to Z axis negative direction m unit length of translation in mark of sitting quietly, n unit length of Y-axis negative direction translation obtains；If tool arm exists
During initial position, the angle with moving coordinate system is θ 0, and the angle turned over during swing is θ, and tool arm roller upper surface central point is P, under
Centre of surface point is Q, and tool arm length is set to l simultaneously, and the distance between PQ is set to f；Therefore, P, Q point seat in moving coordinate system
Mark is respectively P (lcos (θ+θ0),-lsin(θ+θ0),0),
Q((l-f)cos(θ+θ0),-(l-f)sin(θ+θ0),0)；
Wherein, the coordinate points during x1, y1, z1 are respectively moving coordinate system.
Bring P, Q into and connect point coordinates and be
Tool arm turns over angle respectively at cam rise and backhaul stage:
Rise turns over angle
Backhaul turns over angle
Wherein:
θ1Twine knife arm swing angle；
Rise start-phase；
Φ rise terminates phase place；
ω backhaul terminates phase place.
One end of described involute helicoid worm is provided with nut type boss B.
Described wire twister support also includes worm shaft axis hole, knotter jaw axis hole and folder cheese axis hole；Described knotter jaw axis hole
Being that nonopiate concurrent aces is arranged with described wire twister spindle hole of main, described worm shaft axis hole and described wire twister spindle hole of main are in hanging down
Straight concurrent aces is arranged, described tool arm axle axis hole and described knotter jaw axis hole space are mutually perpendicular to arrange, described folder cheese axis hole and
Wire twister spindle hole of main is that space is mutually perpendicular to arrange, implements wire twister spindle hole of main and folder cheese axis hole is that space is mutually perpendicular to
Arrange.
Described wire twister support also includes worm shaft axis hole, knotter jaw axis hole and folder, cheese axis hole；Described knotter jaw axis hole
Being that nonopiate concurrent aces is arranged with described wire twister spindle hole of main, described worm shaft axis hole and described wire twister spindle hole of main are in hanging down
Straight concurrent aces is arranged, described tool arm axle axis hole and described knotter jaw axis hole space are mutually perpendicular to arrange, described arm axle axis hole, folder rope
Dish axis hole and wire twister spindle hole of main are that space is mutually perpendicular to arrange.
Described knotter jaw axis hole axial line d and described wire twister spindle hole of main axial line a crossed axis angle are 98 °,
Described knotter jaw axis hole axial line d and described worm screw axis hole axial line c spatial intersecting angle are 30 °, described folder cheese
Angle between axis hole axial line e and described worm screw axis hole axial line c is 72 °.
Described tool arm is hinged on described tool arm axle axis hole by tool arm axle, and described tool arm axle is by a pair cunning being symmetrically installed
Dynamic bearing and a pair first thrust ball bearings are supported in the tool arm axis hole on wire twister support, and tool arm axle two ends are by bolt even
Connect fixing.
Described involute helicoid worm is 3 with the gear ratio of described helical gear, uniform 3 folders in the outer rim of described folder cheese
Grooving mouth；The head number of described involute helicoid worm is 2, and the number of teeth of described helical gear is 6.
Between folder cheese axis hole end face on described folder cheese end face, described helical gear end face and described wire twister support
It is respectively provided with boss.Or between described helical gear and described folder cheese axis hole end face, the second thrust ball bearing is installed.
The beneficial effects of the utility model are:
1, two gear disk drive the compound fluted disc of wire twister be divided into small tooth plate and large fluted disc, small tooth plate and large fluted disc coaxially solid
It is scheduled on the two ends of wire twister spindle hole of main, makes wire twister main shaft stress balance, improve the job stability of wire twister.
2, by stinging the not homonymy that mechanism R is arranged on wire twister support, fully by rope brake drive mechanism Q with around clasp forceps
Make use of wire twister rack space, make wire twister spatial parameter coupling more flexibly, rationally.
3,3 folder grooving mouths are set on folder cheese, when folder cheese forwards folder rope end position to from initial position clamping bundle rope,
Make bundle rope arrive the blade centre position of twine knife sheet, increase the length of twine knife sheet sliding cutting bundle rope, make wire twister cut rope dynamic
Make reliable.
4, tool arm roller rolls along space profiles curved surface, is linear contact lay with the space profiles curved surface of cam face so that hold
Loading capability is bigger, reduces abrasion.The setting that space profiles is bent simultaneously makes tool arm be sinusoidal acceleration motion, eliminates tool arm in theory
Roller and the stress impact of cam face.
5, on wire twister support, the manufacture difficulty reducing wire twister rack shaft hole arranged by described axis hole axial line, is conducive to
Ensure the machining accuracy between each axis hole angle.
6, by using sliding bearing and thrust ball bearing combinative structure, the tool arm axis hole end face on wire twister support is made not
Rub with tool arm axis hole end face, it is simple to the bolt fastening at tool arm axle two ends, make while strict guarantee tool arm installation site
It rotates flexibly.
7, one end of involute helicoid worm is provided with nut type boss, greatly facilitates the mounting or dismounting of described involute helicoid worm.
8, between the folder cheese axis hole end face on folder cheese end face, described helical gear end face and described wire twister support all
Boss is set, reduces the friction in wire twister work process, beneficially transmission.
9, boss can also be replaced by installed thrust bearing between described helical gear and described folder cheese axis hole end face, with
Just reduce in wire twister work process, the friction between described helical gear and described folder cheese axis hole end face, beneficially transmission.
Accompanying drawing explanation
Fig. 1 is that the two gear disk of an embodiment drives wire twister assembling forward axonometric drawing.
Fig. 2 is the small tooth plate structural plan of an embodiment.
Fig. 3 is the large fluted disc structural plan of an embodiment.
Fig. 4 is the tool arm structural representation of an embodiment.
Fig. 5 is the tool arm axle assembling two dimension sectional view of an embodiment.
Fig. 6 is the structural representation stinging mechanism R around clasp forceps of an embodiment.
Fig. 7 is the rope brake structure shaft side figure of an embodiment.
Fig. 8 is the rope brake actuator configuration shaft side figure of an embodiment.
Fig. 9 is that the two gear disk of an embodiment drives wire twister installation diagram.
Figure 10 is the folder cheese axis hole boss schematic diagram of an embodiment.
Figure 11 is the sectional side view of F-F in Fig. 9.
Figure 12 is the wire twister rack shaft hole schematic diagram a of an embodiment.
Figure 13 is the wire twister rack shaft hole schematic diagram b of an embodiment.
Figure 14 is the wire twister rack shaft hole angular relationship figure a of an embodiment.
Figure 15 is the wire twister rack shaft hole angular relationship figure b of an embodiment.
Figure 16 is the wire twister rack shaft hole angular relationship figure c of an embodiment.
Figure 17 is tool arm roller schematic diagram.
Figure 18 is the German D type wire twister forward schematic diagram of prior art.
Figure 19 is the German D type wire twister schematic rear view of prior art.
In figure, 1, small tooth plate；2, wire twister support；201, wire twister spindle hole of main；202, tool arm axle axis hole；203, worm screw
Axle axis hole；204, knotter jaw axis hole；205 folder cheese axis holes；206, folder rope moving plate balance staff axis hole；207, hook pincers pressing plate shaft axis hole；
208, folder rope moving plate pressing plate shaft axis hole；209, boss；2010, stator bayonet socket；3, large fluted disc；4, grooved cam；5, knotting drives
Not exclusively bevel gear；6, tool arm roller；7, tool arm；8, tool arm axle；9, knotting driven wheel of differential；10, hook pincers pressing plate；1001, hook
Pincers pressing plate shaft；11, compression spring；12, cylindrical cam；13, knotter jaw；14, hook pincers；15, twine knife sheet；16, folder cheese；17、
Folder rope stator；18, worm shaft；19, folder rope driven wheel of differential；20, folder rope drives incomplete bevel gear；21, folder rope moving plate；22、
Folder rope moving plate pressing plate；23, folder rope moving plate balance staff；24, folder grooving mouth；25, involute helicoid worm；2501, nut type boss；26, spiral shell
Rotation gear；27, folder cheese axle；28, the first thrust ball bearing；29, sliding bearing；30, tool arm breach；31, the second thrust ball axle
Hold: 32, compound fluted disc.
Detailed description of the invention
In description of the present utility model, it is to be understood that term " on ", D score, "front", "rear", "left", "right",
" push up ", " end " " interior ", the orientation of the instruction such as " outward " or position relationship are based on orientation shown in the drawings or position relationship, be only for
It is easy to describe this utility model and simplifying describe rather than instruction or the device of hint indication or element must have specifically
Orientation, with specific azimuth configuration and operation, therefore it is not intended that to restriction of the present utility model.
Additionally, term " first ", " second " are only used for describing purpose, and it is not intended that instruction or hint relative importance
Or the implicit quantity indicating indicated technical characteristic.Thus, define " first ", the feature of " second " can express or
Implicitly include one or more this feature.In description of the present utility model, " multiple " are meant that two or two
Above, unless otherwise expressly limited specifically.
In this utility model, unless otherwise clearly defined and limited, term " install ", " being connected ", " connection ", " Gu
Fixed " etc. term should be interpreted broadly, connect for example, it may be fixing, it is also possible to be to removably connect, or be integrally connected；Can
To be mechanical connection, it is also possible to be electrical connection；Can be to be joined directly together, it is also possible to be indirectly connected to by intermediary, Ke Yishi
The connection of two element internals.For the ordinary skill in the art, above-mentioned term can be understood as the case may be
Concrete meaning in this utility model.
In this utility model, unless otherwise clearly defined and limited, fisrt feature second feature it " on " or it
D score can include that the first and second features directly contact, it is also possible to includes that the first and second features are not directly contact but logical
Cross the other characterisation contact between them.And, fisrt feature second feature " on ", " top " and " above " include
One feature is directly over second feature and oblique upper, or is merely representative of fisrt feature level height higher than second feature.First is special
Levy second feature " under ", " lower section " and " below " include fisrt feature immediately below second feature and obliquely downward, or only
Represent that fisrt feature level height is less than second feature.
This utility model is described in further detail by detailed description of the invention below in conjunction with the accompanying drawings, but guarantor of the present utility model
The scope of protecting is not limited to this.
As it is shown in figure 1, a kind of two gear disk drives wire twister include small tooth plate 1, wire twister support 2, large fluted disc 3 and be assemblied in
Tool arm 7 on wire twister support 2, sting mechanism R, rope brake J and drive mechanism Q thereof around clasp forceps.
Described small tooth plate 1 and described large fluted disc 3 are coaxially fixed on the wire twister spindle hole of main on described wire twister support 2
The two ends of 201.
As it is shown on figure 3, described tool arm 7 by hinge on the tool arm axle axis hole 202 of described wire twister support 2, institute
Stating and be provided with grooved cam 4 inside large fluted disc 3, described grooved cam 4 is withstood in the upper end of described tool arm 7.
Described sting mechanism R around clasp forceps and described rope brake drive mechanism Q is separately mounted to the two of described wire twister support 2
Side.
Described large fluted disc 3 is provided circumferentially about has knotting to drive incomplete bevel gear 5, described stings mechanism R and knotting around clasp forceps
Driven wheel of differential 9 is affixed, and described knotting driven wheel of differential 9 drives incomplete bevel gear 5 to engage with described knotting.
Incomplete bevel gear 5 is driven (described to sting mechanism R around clasp forceps as it is shown on figure 3, be provided with knotting on described large fluted disc 3
Affixed with knotting driven wheel of differential 9, described knotting driven wheel of differential 9 drives incomplete bevel gear 5 to engage with described knotting) and set
Having grooved cam 4, described grooved cam 4 to have space profiles curved surface, it is as follows that described space profiles curved surface sets up process: crosses and cuts rope
On tool arm, vertical line is made to oscillation center axle in the upper surface center of roller, and intersection point is as the center O1 of moving coordinate system, with roller to rotation
Turning the vertical line X-axis as moving coordinate system of central shaft work, rotary shaft, as Y-axis, sets up coordinate system according to the right-hand rule；Cross O1 point
Making vertical line to fluted disc center of rotation axle, intersection point is as setting up the center O of quiet coordinate system, and X is made in the direction being parallel to moving coordinate system X1
Axle, the direction of parallel Y1 is made Y-axis, is set up quiet coordinate system according to the right-hand rule；Moving coordinate system is clockwise around quiet coordinate system simultaneously
Rotate a circle；Initial position, the moving coordinate system mark that also corresponds to sit quietly ties up to Z axis negative direction 22 unit lengths of translation, Y-axis losing side
Obtain to 58 unit lengths of translation；If tool arm is 5 π/36 when initial position with the angle of moving coordinate system, turn over during swing
Angle is θ, and tool arm roller upper surface central point is P, and lower surface central point is Q, simultaneously tool arm a length of 64, the distance between PQ
It is set to 17；Therefore, P, Q point coordinate in moving coordinate system is respectively P (64cos (θ+5 π/36) ,-64sin (θ+5 π/36), 0),
Q(47cos(θ+5π/36),-47sin(θ+5π/36),0)；
Bring into P, Q two point coordinates be
Separately；Tool arm turns over angle respectively at cam rise [0, π/3] and backhaul [π/3, π/3,2] stage:
Rise turns over angle
Backhaul turns over angle
Wherein:
θ1Twine knife arm swing angle；
Rise start-phase；
Φ rise terminates phase place；
ω backhaul terminates phase place
As in figure 2 it is shown, the provided circumferentially about of described small tooth plate 1 has folder rope to drive incomplete bevel gear 20 (described rope brake
Drive mechanism Q is affixed with folder rope driven wheel of differential 19, and described folder rope driven wheel of differential 19 drives with described folder rope and not exclusively bores tooth
Wheel 20 engagement, described rope brake drive mechanism Q includes helical gear 26, and described helical gear 26 is by pressing from both sides cheese axle 27 with described
Rope brake J is affixed.
As shown in Figure 4, described tool arm 7 is assemblied on described tool arm axle axis hole 202 by tool arm axle 8, described grooved cam 4
By driving tool arm roller 6 to make described tool arm 7 around the axle center reciprocally swinging of described tool arm axle 8.
As shown in Figure 4, tool arm roller 6 is cylindric, the face of cylinder of tool arm roller and the space profiles curved surface of cam face
In linear contact lay.As shown in figure 17, the two ends of tool arm roller 6 are arc-shaped chamfering, advantageously reduce tool arm roller 6 and grooved cam
Matching requirements between 4, minimizing abrasion.
As it is shown in figure 5, described tool arm axle 8 is by the pair of sliding bearing 29 being symmetrically installed and a pair first thrust ball bearings 28
In the notch cuttype tool arm axle axis hole 202 being supported on described wire twister support 2, described tool arm axle 8 two ends are bolted solid
Fixed.By using described sliding bearing 29 and described first thrust ball bearing 28 combinative structure, make described tool arm axle axis hole 202 end
Face does not rubs with described tool arm 7 axis hole end face, it is simple to the bolt fastening at described tool arm axle 8 two ends, cutter described in strict guarantee
It is made to rotate flexibly while arm 7 installation site.
As shown in Figure 6, described sting mechanism R around clasp forceps and include that knotter jaw 13, the cylinder hooked on pincers 14, wire twister support 2 are convex
Wheel 12 and hook pincers pressing plate 10, the top of described knotter jaw 13 is affixed with knotting driven wheel of differential 9 through described cam 12, hooks pincers 14
By hinge on knotter jaw 13, the described top hooking pincers 14 is pushed down by described hook pincers pressing plate 10, described hook pincers pressing plate 10
Clamping on pressing plate shaft axis hole 207 by hinge at the hook of described wire twister support 2, compression spring 11 is enclosed within hook pincers pressing plate shaft
Being screwed on 1001, for the regulation pressure to described hook pincers pressing plate 10, described cylindrical cam 12 profile is A Ji meter
Moral helix cam, in described knotter jaw 13 rotation process, the hook pincers roller on described hook pincers is at spiral of Archimedes cam
Control under, complete opening and closing campaign.
As it is shown in fig. 7, described rope brake J includes pressing from both sides cheese 16, folder rope stator 17, folder rope moving plate 21 and folder rope moving plate pressure
Plate 22.Described folder rope stator 17 is stuck on the stator bayonet socket 210 on described wire twister support 2, and described folder rope moving plate 21 is by folder
Rope moving plate balance staff 23 is hinged on the folder rope moving plate balance staff axis hole 206 of described wire twister support 2, the side of described folder rope stator 17
Being pushed down by folder rope moving plate pressing plate 22, described folder rope moving plate pressing plate 22 is moved at the folder rope of described wire twister support 2 by hinge
On sheet last item axis hole 208, during wire twister folder rope, drive described folder rope moving plate 21 around institute with the rotation of described folder cheese 16
State the axis swing of folder rope moving plate balance staff 23.
As shown in Figure 8, described rope brake drive mechanism Q includes going back involute helicoid worm 25 and helical gear 26, described folder rope
Driven wheel of differential 19 and described involute helicoid worm 25 are respectively and fixedly connected to the two ends of worm shaft 18, described helical gear 26 and described folder
Cheese 16 is affixed by folder cheese axle 27, and described involute helicoid worm 25 engages with described helical gear 26.
One end of described involute helicoid worm 25 is provided with nut type boss 2501, facilitates the dress of described involute helicoid worm 25
Tear open.
Such as Fig. 9, shown in 10, described folder cheese 16 end face, described helical gear 26 end face with on described wire twister support
It is respectively provided with boss 209, to reduce the friction in wire twister work process, beneficially transmission between folder cheese axis hole 205 end face.Described
Second thrust ball bearing 31 can also be installed to replace boss between helical gear 26 and described folder cheese axis hole 205 end face, as
Shown in Figure 11.
As illustrated in figures 1 and 8, incomplete bevel gear 5 is driven to engage with described knotting driven wheel of differential 9 by described knotting
Drive described knotter jaw 13 to rotate around button, described cylindrical cam 12 control described hook clamp 14 opening and closing pincers sting bundle rope.By described folder
The rope incomplete bevel gear 20 of driving engages with described folder rope driven wheel of differential 19 and makes described involute helicoid worm 25 drive described spiral
Gear 26 rotates, and drives described folder cheese 16 to rotate.By by described rope brake drive mechanism Q with described sting mechanism R around clasp forceps
It is separately mounted to the both sides on described wire twister support 2, takes full advantage of described wire twister support 2 space, make wire twister space
Parameter coupling is more flexible.Described involute helicoid worm 25 is 3 with described helical gear 26 gear ratio, preferred described involute snail
The head number of bar 25 is 2, and the number of teeth of described helical gear 26 is 6.Uniform 3 folder grooving mouths in the outer rim of described folder cheese 16
24, in each knotting cycle, described small tooth plate 1 rotates a circle, and is made on described folder cheese 16 by described rope brake drive mechanism Q
3 folder grooving mouths 24 turn over 120 °, described folder cheese 16 from initial position clamping bundle rope arrive folder rope end position, make bundle rope
Arrive the blade centre position of twine knife sheet 15, increase the length of blade sliding cutting bundle rope, make wire twister cut rope reliable in action.
As shown in Figures 12 and 13, described wire twister support 2 includes wire twister spindle hole of main 201, tool arm axle axis hole 202, snail
Bar axle axis hole 203, knotter jaw axis hole 204 and folder cheese axis hole 205；In order to reduce the manufacture of described wire twister support 2 upper shaft hole
Difficulty, it is ensured that the machining accuracy between each axis hole angle, described knotter jaw axis hole 204 axial line d and described wire twister spindle shaft
Hole 201 axial line a is that nonopiate concurrent aces is arranged, described worm shaft axis hole 203 axial line c and described wire twister spindle hole of main
The 201 perpendicular concurrent aceses of axial line a are arranged, described tool arm axle axis hole 202 axial line b and described knotter jaw axis hole 204 axial line d
It is mutually perpendicular in space arrange, described tool arm axle axis hole 202 axial line b, described folder cheese axis hole 205 axial line e and described beat
Knot device spindle hole of main 201 axial line a is that space is mutually perpendicular to arrange.Described wire twister spindle hole of main 201 end face is regarded as main
Figure perspective plane, the design of each axis hole angular relationship is such as Figure 14, shown in 15 and 16.Worm shaft axis hole 203 is located at wire twister support 2
Side, worm shaft 18 is located in worm shaft axis hole 203, makes and the folder rope driven wheel of differential 19 of worm shaft 18 consolidation and described folder rope
Incomplete bevel gear 20 is driven to engage.
Described knotter jaw axis hole 204 axial line d and described wire twister spindle hole of main 201 axial line a crossed axis angle are 98 °, institute
Stating worm shaft axis hole 203 axial line c with described wire twister spindle hole of main 201 axial line a crossed axis angle is 90 °, described knotter jaw axle
Hole 204 axial line d and described worm screw axis hole 203 axial line c spatial intersecting angle are 30 °, described folder cheese axis hole 205 axial line e
And the angle between described worm screw axis hole 203 axial line c is 72 °, described tool arm axle axis hole 202 axial line b and described knotter jaw
The angle of axis hole 204 axial line d is 90 °.By being above-mentioned preferred by each axis hole axial line angle of described wire twister support 2
Arrange, both achieved folder rope, around button and cut rope trip action power transmission, take full advantage of again wire twister rack space, make
Wire twister forest spatial structure parameters coupling is more reasonable, facilitates each axis hole processing on described wire twister support 2.
When utility model works, first bundle rope is delivered at described folder grooving mouth 24 by toggle, and described small tooth plate 1 is controlled
The folder rope making described rope brake J action drives incomplete bevel gear 20 and is fixed in the folder rope of described worm shaft 18 one end from mantle
Gear 19 engages, and the described involute helicoid worm 25 being fixed in described worm shaft 18 other end engages with described helical gear 26, band
Dynamic described folder cheese 16 rotates, described folder rope moving plate 21 coordinate with described folder cheese 16 bundle rope clamp is held while bundle restricted overlap
On described knotter jaw 13.After described small tooth plate 1 turns over a phase place, described large fluted disc 3 controls described knotter jaw 13 turns
Dynamic described knotting drives incomplete bevel gear 5 to nibble with the described knotting driven wheel of differential 9 being fixed in described knotter jaw 13 one end
Close, drive described knotter jaw 13 to rotate and make bundle rope annularly be wrapped on the surface of described knotter jaw 13.Meanwhile, described
Hook pincers 14 first opening clamp under playing the effect of described cylindrical cam 12 is closed again after biting bundle rope, is stung by bundle rope and clamps 14 at described hook
And between described knotter jaw 13.After described large fluted disc 3 is rotated further a phase place, described grooved cam 4 controls described tool arm 7
Swinging, the bundle rope below described clamper J is cut off by the twine knife sheet 15 on described tool arm 7, and by the cutter on described tool arm 7
Sling on described knotter jaw 13 is forced to evade by arm breach 30, eventually forms knot.When described large fluted disc 3 rotates back into initial bit
When putting, described tool arm 7 reversely swings back into initial position, completes a knotting process.
Described embodiment be of the present utility model preferred embodiment, but this utility model is not limited to above-mentioned embodiment party
Formula, in the case of without departing substantially from flesh and blood of the present utility model, those skilled in the art can make any obviously
Improvement, replacement or modification belong to protection domain of the present utility model.
Claims (12)
1. a two gear disk drives wire twister, it is characterised in that include small tooth plate (1), wire twister support (2), large fluted disc (3),
The tool arm (7) that is assemblied on wire twister support (2), sting mechanism R and rope brake drive mechanism Q around clasp forceps；
Described small tooth plate (1) and described large fluted disc (3) are coaxially fixed on the wire twister spindle hole of main on described wire twister support (2)
(201) two ends；Described sting mechanism R around clasp forceps and described rope brake drive mechanism Q is separately mounted to described wire twister support (2)
Both sides；
Described large fluted disc (3) is provided circumferentially about has knotting to drive incomplete bevel gear (5), the tool arm rolling on described tool arm (7) top
Son (6) coordinates with the grooved cam (4) of large fluted disc (3) inner side, and knotting driven wheel of differential (9) drives not exclusively cone with described knotting
Gear (5) engages；The provided circumferentially about of described small tooth plate (1) has folder rope to drive incomplete bevel gear (20), and folder rope is from mantle tooth
Wheel (19) drives incomplete bevel gear (20) to engage with described folder rope.
Two gear disk the most according to claim 1 drives wire twister, it is characterised in that described rope brake drive mechanism Q drives
Uniform 3 folders grooving mouth (24) in the outer rim of the folder cheese (16) of rope brake J, described rope brake J, with described folder rope from mantle tooth
Wheel (19) is 2 by the head number of the involute helicoid worm (25) that worm shaft (18) consolidates, and engages with described involute helicoid worm (25)
The number of teeth of helical gear (26) is 6.
Two gear disk the most according to claim 1 drives wire twister, it is characterised in that described tool arm roller (6) is cylindric,
The cam face of described grooved cam (4) is space profiles curved surface, the face of cylinder of described tool arm roller (6) and the sky of cam face
Between contour surface be linear contact lay, tool arm roller (6) along space profiles curved surface roll.
4. drive wire twister according to the two gear disk described in claim 1,2 or 3, it is characterised in that sting mechanism R with described around clasp forceps
Cylindrical cam (12) profile on described wire twister support (2) coordinated is spiral of Archimedes cam.
Two gear disk the most according to claim 3 drives wire twister, it is characterised in that described space profiles curved surface sets up process
As follows: vertical line is made to oscillation center axle in the upper surface center of roller on twine knife arm of crossing, intersection point as the center O1 of moving coordinate system,
The vertical line made to center of rotation axle using roller is as the X-axis of moving coordinate system, and rotary shaft, as Y-axis, is set up according to the right-hand rule and sat
Mark system；Crossing O1 point and make vertical line to fluted disc center of rotation axle, intersection point, as setting up the center O of quiet coordinate system, is parallel to moving coordinate system
X-axis is made in the direction of X1, and Y-axis is made in the direction of parallel Y1, sets up quiet coordinate system according to the right-hand rule;Moving coordinate system is around sitting quietly simultaneously
Mark system dextrorotation gyration is β；Initial position, the moving coordinate system mark that also corresponds to sit quietly ties up to Z axis negative direction m unit of translation
Length, n unit length of Y-axis negative direction translation obtains；If tool arm is θ 0 when initial position with the angle of moving coordinate system, during swing
The angle turned over is θ, and tool arm roller upper surface central point is P, and lower surface central point is Q, and tool arm length is set to l simultaneously, between PQ
Distance be set to f；Therefore, P, Q point coordinate in moving coordinate system is respectively,；
Wherein, the coordinate points during x1, y1, z1 are respectively moving coordinate system；
Bring P, Q into and connect point coordinates and be
Tool arm turns over angle respectively at cam rise and backhaul stage:
Rise turns over angle
Backhaul turns over angle
Wherein:
θ1Twine knife arm swing angle；
φ rise start-phase；
Φ rise terminates phase place；
ω backhaul terminates phase place.
6. drive wire twister according to the two gear disk described in claim 3 or 5, it is characterised in that the two ends of described tool arm roller (6)
For arc-shaped chamfering.
Two gear disk the most according to claim 2 drives wire twister, it is characterised in that one end of described involute helicoid worm (25)
It is provided with nut type boss B(2501).
8. drive wire twister according to the two gear disk described in claim 1,2 or 3, it is characterised in that described wire twister support (2) is also
Including worm shaft axis hole (203), knotter jaw axis hole (204) and folder cheese axis hole (205)；Described knotter jaw axis hole (204) and institute
State wire twister spindle hole of main (201) to arrange in nonopiate concurrent aces, described worm shaft axis hole (203) and described wire twister spindle shaft
Hole (201) perpendicular concurrent aces is arranged, described tool arm axle axis hole (202) is mutually perpendicular to described knotter jaw axis hole (204) space
Arranging, described folder cheese axis hole (205) and wire twister spindle hole of main (201) are mutually perpendicular in space arrange, implement wire twister master
Axle axis hole (201) and folder cheese axis hole (205) are mutually perpendicular in space arrange.
Two gear disk the most according to claim 7 drives wire twister, it is characterised in that described knotter jaw axis hole (204) axle center
Line d and described wire twister spindle hole of main (201) axial line a crossed axis angle are 98 °, described knotter jaw axis hole (204) axial line d and institute
Stating worm screw axis hole (203) axial line c spatial intersecting angle is 30 °, described folder cheese axis hole (205) axial line e and described worm shaft
Angle between hole (203) axial line c is 72 °.
10. drive wire twister according to the two gear disk described in claim 1,2 or 3, it is characterised in that described tool arm (7) passes through cutter
Arm axle (8) is hinged on described tool arm axle axis hole (202), and described tool arm axle (8) is by the pair of sliding bearing (29) being symmetrically installed
Being supported in tool arm axle (8) hole on wire twister support (2) with the first thrust ball bearing (28), spiral shell is passed through at tool arm axle (8) two ends
Tether connect fixing.
11. two gear disks according to claim 2 drive wire twisters, it is characterised in that described folder cheese (16) end face, described
It is respectively provided with boss (209) between folder cheese axis hole (205) end face on helical gear (26) end face and described wire twister support.
12. two gear disks according to claim 2 drive wire twister, it is characterised in that described helical gear (26) is with described
Between folder cheese axis hole (205) end face, the second thrust ball bearing (31) is installed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201521001639.8U CN205510981U (en) | 2015-12-07 | 2015-12-07 | Bidentate dish drive knotter |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201521001639.8U CN205510981U (en) | 2015-12-07 | 2015-12-07 | Bidentate dish drive knotter |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205510981U true CN205510981U (en) | 2016-08-31 |
Family
ID=56762716
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201521001639.8U Expired - Fee Related CN205510981U (en) | 2015-12-07 | 2015-12-07 | Bidentate dish drive knotter |
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| Country | Link |
|---|---|
| CN (1) | CN205510981U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105638119A (en) * | 2015-12-07 | 2016-06-08 | 江苏大学 | Double-fluted disc driving knotter |
| CN110234221A (en) * | 2017-05-02 | 2019-09-13 | 凯斯纽荷兰(中国)管理有限公司 | The improvement of knotter system for baler |
| CN113455202A (en) * | 2021-06-04 | 2021-10-01 | 江苏大学 | Identical-tooth-direction double-fluted-disc driving knotter and bundling machine provided with same |
| CN113853956A (en) * | 2021-11-01 | 2021-12-31 | 泰州市力鼎机械设备有限公司 | Double-fluted disc drive knotter based on D type knotter principle |
-
2015
- 2015-12-07 CN CN201521001639.8U patent/CN205510981U/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105638119A (en) * | 2015-12-07 | 2016-06-08 | 江苏大学 | Double-fluted disc driving knotter |
| CN110234221A (en) * | 2017-05-02 | 2019-09-13 | 凯斯纽荷兰(中国)管理有限公司 | The improvement of knotter system for baler |
| CN110234221B (en) * | 2017-05-02 | 2022-07-05 | 凯斯纽荷兰(中国)管理有限公司 | Improvements in knotter systems for banders |
| CN113455202A (en) * | 2021-06-04 | 2021-10-01 | 江苏大学 | Identical-tooth-direction double-fluted-disc driving knotter and bundling machine provided with same |
| CN113853956A (en) * | 2021-11-01 | 2021-12-31 | 泰州市力鼎机械设备有限公司 | Double-fluted disc drive knotter based on D type knotter principle |
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Legal Events
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|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20170531 Address after: 225321, Jinma East Street, Baima Town, high port area, Jiangsu, Taizhou Patentee after: Taizhou Xiangsheng Tools Co., Ltd. Address before: Zhenjiang City, Jiangsu Province, 212013 Jingkou District Road No. 301 Patentee before: Jiangsu University |
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| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20160831 Termination date: 20171207 |
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| CF01 | Termination of patent right due to non-payment of annual fee |