CN103387838B - Horizontal braking torque self-increased few tooth difference-gear rack coke-pushing device - Google Patents

Horizontal braking torque self-increased few tooth difference-gear rack coke-pushing device Download PDF

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CN103387838B
CN103387838B CN201210141272.4A CN201210141272A CN103387838B CN 103387838 B CN103387838 B CN 103387838B CN 201210141272 A CN201210141272 A CN 201210141272A CN 103387838 B CN103387838 B CN 103387838B
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coke
pushing
gear
type
slotted disk
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CN103387838A (en
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吴声震
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Zhou Fenlan
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吴小杰
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Abstract

The invention relates to the technical field of coke-pushing devices, and particularly relates to a horizontal braking torque self-increased few tooth difference-gear rack coke-pushing device. The horizontal braking torque self-increased few tooth difference-gear rack coke-pushing device comprises a coke-pushing support, a supporting roll, a coke-pushing rod, a braking torque self-increased transmission device, wherein the transmission device comprises a rotor shaft, eccentric bearings, a planet wheel, an inner ring gear and an output mechanism. The horizontal braking torque self-increased few tooth difference-gear rack coke-pushing device is characterized in that the output shaft is supported into inner holes of a front frame and a rear frame; a cross section of a long rack engaged with a driving gear presents a convex shape; the long rack is put in a coke-pushing rod long slot; the upper surface at two sides of the long slot limit two shoulders of the convex shape; the coke-pushing rod moves forward when the driving gear rotates clockwise and moves backward when the driving gear rotates anticlockwise; phase difference between two side wheels and a middle wheel is 180 degrees; the widths of the two side wheels is half that of the middle wheel; and a braking component comprises two V-shaped groove disc mechanisms, a friction pair and a reset spring. The horizontal braking torque self-increased few tooth difference-gear rack coke-pushing device has the beneficial effects that the gear and the rack have good meshing accuracy; the weight is reduced by 45-60%, the price is reduced by 50%-65%; the braking torque increases with the increasing of a resisting torque; and the output shaft is in static and dynamic balance.

Description

Horizontal braking moment is from increasing few teeth difference-tooth bar coke pusher
[technical field]
The present invention relates to coke pusher technical field, a kind of horizontal braking moment is from increasing few teeth difference-tooth bar coke pusher.
[background technology]
The research > > of the paper < < 6m of coke oven factory of Baogang vibration of pushing rod of coke oven points out: during the reciprocal work done of pushing ram in coke pusher, can produce vibration, its major cause is after pushing ram is heated, progressively to have the collapse distortion of waist > > trend of < <, pushing ram distortion makes gear-tooth bar sideshake and bottom clearance substantial deviation theoretical value (sideshake 3.5-5, bottom clearance 8-12): the anterior tooth bar sideshake 6.8-7.2 of place of actual measurement pushing ram, bottom clearance 14.8, middle part sideshake 7.5-7.8, bottom clearance 18, rear portion sideshake 7.6-8, bottom clearance 17.2 (units: mm).
Vibrating in various degree all appears in the 6m coke oven coke-pusher bar of domestic Baosteel, Wuhan Iron and Steel Plant, Handan Iron and Steel Co, elder brother's steel, Shan Jiaoji Baogang etc., when serious, produce resonance and cause that bottom brick becomes flexible, cracks, the positive displacement of jamb brick and combustion chamber string leak etc. (6m coke oven principal dimension: the long 15140mm of coking chamber, high 5650mm, average wide 450mm);
Coke pusher comprises pushing ram, coke pushing bearing and transmission mechanism: motor YZR355L110kW, n 1=582rpm, n 2=14.6rpm, pushing ram (comprising coke pushing head, crawler shoe) is bearing on support roll, in support roll, have three groups with side roller to prevent pushing ram sideslip, coke pushing leverage body structure, tooth bar is located at the top of bar, in pushing ram enters stove after, in order to support pushing ram, be provided with crawler shoe, its bottom height is adjustable.Adopt magnetic eddy-current brake WZ355L and hydraulic pressure block brake YWZ-400/90-10 to carry out the speed setting of coke pushing whole process, to realize without impacting coke pushing.For pushing ram in the incinerator that prevents from having a power failure suddenly, be provided with hand gear.
Transmission mechanism is that three grades of slowing-down structure: i=2.045 * 3.962 * 4.923=39.9, driving gear (Z=15, a m=40) tooth bar of one-level cone tooth+secondary parallel-axes gears realized pushing ram forward and back, coke pushing speed 27.4m/min, stroke 25774mm.
[summary of the invention]
The horizontal braking moment that when the object of the invention provides a kind of work done, gear-tooth bar stable drive, pushing ram do not vibrate and the single-stage few teeth difference low by price, efficiency is identical replaces background technology is from increasing few teeth difference-rack drives coke pusher.
Technical scheme:
(A) driving gear and output shaft are with spending strong being slidably connected, make driving gear there is certain amount of floating in order to sideshake and the bottom clearance of compensation and tooth bar, long tooth bar is placed in the corresponding elongated slot of pushing ram, running fit, tooth bar bottom supporting is in slide roller, slide roller is connected in pushing ram, therefore in the reciprocal work done of pushing ram, when there is " waist collapses " distortion in pushing ram, because tooth bar is not to be fixed on pushing ram to make tooth bar can not produce moderate finite deformation, the sideshake of gear-tooth bar and bottom clearance are still in theoretical value, the steady transmission of gear-tooth bar, greatly reduce gear-tooth bar surging force and pushing ram vibration,
(B) with single-stage involute less tooth difference, slow down and replace: the calculated example of 7-126 page on < < gear handbook > >: efficiency eta=0.944 (two teeth difference Z d=2), contriver is according to 100 examples, tooth difference Z d=2,3,4, calculation result draws: efficiency eta=0.934,0.96,0.97., thereby single-stage involute less tooth difference can replace background technology < < cone tooth+secondary reducer with hardened tooth surface > >;
(C) two groups of steel ball V-type slot devices in brake component are steel ball V-type groove automatic pressurizing device improved (seeing 90 pages of the < < of Ruan Zhong Tang mechanical stepless transmission > >): first group is comprised of the steel ball between active V-type slotted disk, the telophragma driven V-type slotted disk of one side and two V-type groove faces, and telophragma connects with cone dish; Second group is comprised of the steel ball in the middle of telophragma opposite side active V-type slotted disk, the second driven V-type slotted disk and two V-type groove faces.Principle of work: during energising, first group of active V-type groove face produces positive pressure to steel ball, and its axial component promotes the driven V-type slotted disk of telophragma makes friction pair separated, and braking moment disappears, and its circumferential component drives the output shaft work done connecting with second group of driven V-type slotted disk; During power-off, input shaft stop, moment of resistance makes the second driven V-type groove face produce positive pressure to steel ball, and its axial component compresses friction pair, and braking moment will muchly have much.
[beneficial effect], according to background technology, its creativeness is embodied in:
(1) in the reciprocal work done of pushing ram, guarantee the gear-tooth bar accuracy of mesh, greatly reduce surging force and pushing ram vibration;
(2) background technology < < cone tooth+secondary reducer with hardened tooth surface > > (bearing capacity 72000Nm) is suitable with DCY-500 type reducer with hardened tooth surface (seeing JB/T9002-1999), 113930 yuan of the heavy 4340kg of machine, prices; Weight saving 45-60% of the present invention, price can reduce 50-65%.Theoretical Calculation data are as follows: center circle radius R z=275, contact coefficient Y 1max=1.43, B=21/42
Contact stress σ jmax=(8914/R z) { Y 1maxt 2/ B} 0.5=1605 (MPa)
Allowable contact stress [σ h]=1617 (MPa) (HB600-600) (see Xu Hao < < mechanical design handbook > > volume 1.4-289 page);
(3) Involute Small Teeth Difference Planetary Gearing advantage: few, the soft flank of tooth technique of simple in structure, another part is simple, cost is low;
(4) braking moment increases with moment of resistance and automatically increases, and therefore can replace magnetic eddy-current brake WZ355L with hydraulic pressure block brake YWZ-400/90-10 carries out the speed setting of coke pushing whole process, to realize without impact coke pushing.
[accompanying drawing explanation] Fig. 1. embodiment of the present invention structural representation
Force principle figure when Fig. 2,3 is respectively steel ball and V-type groove power-off (braking), energising (work done)
[embodiment] encyclopaedizes the present invention below in conjunction with accompanying drawing:
With reference to Fig. 1., 2 and 3. a kind of horizontal braking moment from increasing few teeth difference-tooth bar coke pusher, comprise coke pushing bearing 1, support roll 2, pushing ram 3 and braking moment are from increasing transmission mechanism, described pushing ram 3 comprises coke pushing head, crawler shoe, described pushing ram 3 is bearing on support roll 2 for body structure, in support roll 2, have three groups with side roller to prevent pushing ram 3 sideslips, support roll 2 is connected in the bottom of coke pushing bearing 1, described braking moment comprises driving member and brake component from increasing transmission mechanism, described driving member comprises input shaft 21 and is contained in first on input shaft 21, two capacity eccentric bearings 20, 19, satellite gear, ring gear 34 and output mechanism, output mechanism comprises output shaft 11, pin 14 and column sleeve, it is characterized in that:
(A) described output shaft 11 two ends use respectively first, two bearings 10, 12 be bearing in before, afer bay 9, 13 endoporus, device is first, two bearings 10, driving gear 8 between 12 is slidably connected with output shaft 11 use splines, make driving gear 8 there is certain amount of floating in order to sideshake and bottom clearance between compensation and long tooth bar 5, driving gear 8 and long tooth bar 5 engagements, the driving gear of background technology cantilever arrangement 8 is improved to freely supported structure and has improved the accuracy of mesh of gear-tooth bar, long tooth bar 5 transverse section are " protruding " shape, be placed in the corresponding elongated slot of pushing ram 3, running fit, two shoulders that long tooth bar 5 " protruding " shape is faced on the upper edge of dependence elongated slot two sides carry out spacing, upper along gapped between face and " protruding " shape two shoulders, long tooth bar 5 bottom supportings are in slide roller 4, slide roller 4 is connected in pushing ram 3, principle of work is: when driving gear 8 turns clockwise, long tooth bar 5 drives pushing ram 3 to move forward, otherwise, when driving gear 8 turns counterclockwise, long tooth bar 5 drives pushing ram 3 to move backward, because long tooth bar 5 is not to be fixed on pushing ram 3, therefore when there is " waist collapses " in pushing ram 3, the sideshake of gear-tooth bar and bottom clearance are still in theoretical value, before, afer bay 9, 13 are fastened on step-down gear base plate 7, described step-down gear base plate 7, footing 6 and coke pushing bearing 1 are integrally togather in turn, in described satellite gear, both sides satellite gear 16 is identical, described both sides satellite gear 16 is taken turns 180 ° of 17 phase differential with middle planetary, described both sides satellite gear 16 is taken turns wide half of middle planetary wheel 17 of equaling, column sleeve 15, 18 minutes separately corresponding to satellite gear 16, 17, described ring gear 34 is connected in afer bay 13 endoporus,
(B) described brake component comprise be connected in afer bay 13 end faces middle cylinder 22, with middle 22 plackets that connect 31 and in, Liang ZuVXing slotted disk mechanism, friction pair and the return spring of placket endoluminal means, wherein:
Described friction pair comprises inner cone 33 and cone dish 32, and wherein inner cone 33 is connected in placket 31 endoporus, and cone dish 32 connects with telophragma 27, and the axial theoretical value of friction pair separation is x;
In described Liang ZuVXing slotted disk mechanism, first group of active V-type slotted disk 29 is connected on rotor axis of electric 30, telophragma 27 1 sides are the first driven V-type slotted disk, between master and slave two V-type grooves, there is steel ball 28, the second driven V-type slotted disk 25 is slidably connected with the male spline shaft extension end of input shaft 21, telophragma 27 opposite sides are to have steel ball 26 between the second active V-type slotted disk, two V-type grooves, and uniform steel ball number equates with V-type groove number;
Described return spring 24 one end are close to a glass interior end of type spring support 23, the other end is close to the second driven V-type slotted disk 25 end faces, return spring 24 compresses cone dish 32 and inner cone 33 friction pairs, the outer face of described cup type spring support 23 is near input shaft 21 shaft shoulders and opening end equals the separated axial theoretical value x of friction pair with the gap between the second driven V-type slotted disk 25, and described input shaft 21 use bearings are bearing in middle cylinder 22 endoporus.
Braking principle: during energising, the V-type groove face of the first group of active V-type slotted disk 29 connecting with rotor axis of electric 30 produces positive pressures to steel ball 28: the driven V-type slotted disk that axial component promotes telophragma 27 makes friction pair separated (axial distance x), and braking moment disappears; Circumferentially component drives with the input shaft 19 of the second driven V-type slotted disk 25 splined and rotates work done.Obvious first group of steel ball V-type slot device function is clutch coupling, and second group of steel ball V-type slot device function is shaft coupling; When power-off, rotor axis of electric 30 stops, moment of resistance makes the V-type groove face of the second driven V-type slotted disk 25 produce positive pressure to steel ball 26, and its axial component compresses friction pair, thereby braking moment will muchly have much.

Claims (1)

1. a horizontal braking moment is from increasing few teeth difference-tooth bar coke pusher, comprise that coke pushing bearing (1), support roll (2), pushing ram (3) and braking moment are from increasing transmission mechanism, described pushing ram (3) comprises coke pushing head, crawler shoe, and described pushing ram (3) is body structure be bearing on support roll (2), in support roll (2), have three groups with side roller to prevent pushing ram (3) sideslip, support roll (2) is connected in the bottom of coke pushing bearing (1), described braking moment comprises driving member and brake component from increasing transmission mechanism, described driving member comprises input shaft (21) and is contained in first and second capacity eccentric bearing (20,19), satellite gear, ring gear (34) and the output mechanism on input shaft (21), output mechanism comprises output shaft (11), pin (14) and column sleeve, it is characterized in that:
(A) described output shaft (11) two ends use respectively first, two bearings (10, 12) before being bearing in, afer bay (9, 13) endoporus, device is first, two bearings (10, 12) driving gear between (8) is slidably connected with spline with output shaft (11), driving gear (8) and long tooth bar (5) engagement, described long tooth bar (5) transverse section is " protruding " shape, be placed in the corresponding elongated slot of pushing ram (3), running fit, two shoulders that long tooth bar (5) " protruding " shape is faced on the upper edge of dependence elongated slot two sides carry out spacing, upper along gapped between face and " protruding " shape two shoulders, long tooth bar (5) bottom supporting is in slide roller (4), slide roller (4) is connected in pushing ram (3), before, afer bay (9, 13) be fastened on step-down gear base plate (7), described step-down gear base plate (7), footing (6) and coke pushing bearing (1) are integrally togather in turn, in described satellite gear, both sides satellite gear (16) is identical, described both sides satellite gears (16) and 180 ° of middle planetary wheel (17) phase differential, described both sides satellite gears (16) are taken turns wide half that equals middle planetary and take turns (17), column sleeve (15, 18) correspond respectively to satellite gear (16, 17), described ring gear (34) is connected in afer bay (13) endoporus,
(B) described brake component comprise be connected in the middle cylinder (22) of afer bay (13) end face, the placket (31) connecting with middle (22) and in, Liang ZuVXing slotted disk mechanism, friction pair and the return spring of placket endoluminal means, wherein:
Described friction pair comprises inner cone (33) and cone dish (32), and wherein inner cone (33) is connected in placket (31) endoporus, and cone dish (32) connects with telophragma (27), and the axial theoretical value of friction pair separation is x;
In described Liang ZuVXing slotted disk mechanism, first group of active V-type slotted disk (29) is connected on rotor axis of electric (30), telophragma (27) one sides are the first driven V-type slotted disk, between master and slave two V-type grooves, there is steel ball (28), the second driven V-type slotted disk (25) is slidably connected with the male spline shaft extension end of input shaft (21), telophragma (27) opposite side is to have steel ball (26) between the second active V-type slotted disk, two V-type grooves, and uniform steel ball number equates with V-type groove number;
Described return spring (24) one end is close to a glass interior end of type spring support (23), the other end is close to the second driven V-type slotted disk (25) end face, return spring (24) compresses cone dish (32) and inner cone (33) friction pair, the outer face of described cup type spring support (23) is near input shaft (21) shaft shoulder and opening end equals the separated axial theoretical value x of friction pair with the gap between the second driven V-type slotted disk (25), and described input shaft (21) is bearing in middle (22) endoporus with bearing.
CN201210141272.4A 2012-05-08 2012-05-08 Horizontal braking torque self-increased few tooth difference-gear rack coke-pushing device Active CN103387838B (en)

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2250357Y (en) * 1996-02-08 1997-03-26 史正高 Horizontal coke pushing machine
CN2861158Y (en) * 2005-09-14 2007-01-24 大连华锐股份有限公司 Coke pusher slot type collecting device for two ends coke
CN201801487U (en) * 2010-09-09 2011-04-20 江苏泰隆减速机股份有限公司 Transmission device for coke pusher
CN201818748U (en) * 2010-09-19 2011-05-04 杜明乾 Anti-backlash transmission case for linear motion on rack

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH034784B2 (en) * 1987-06-08 1991-01-23 Tooru Hirano

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2250357Y (en) * 1996-02-08 1997-03-26 史正高 Horizontal coke pushing machine
CN2861158Y (en) * 2005-09-14 2007-01-24 大连华锐股份有限公司 Coke pusher slot type collecting device for two ends coke
CN201801487U (en) * 2010-09-09 2011-04-20 江苏泰隆减速机股份有限公司 Transmission device for coke pusher
CN201818748U (en) * 2010-09-19 2011-05-04 杜明乾 Anti-backlash transmission case for linear motion on rack

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
JP昭63-308262A 1988.12.15

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