CN1232146A - Multifunctional planetary speed reducer - Google Patents
Multifunctional planetary speed reducer Download PDFInfo
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- CN1232146A CN1232146A CN 98112433 CN98112433A CN1232146A CN 1232146 A CN1232146 A CN 1232146A CN 98112433 CN98112433 CN 98112433 CN 98112433 A CN98112433 A CN 98112433A CN 1232146 A CN1232146 A CN 1232146A
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Abstract
A multifunctional sprocket-wheel speed reducer is composed of sprocket-wheel drive assembly, planetary gear mechanism and bevel gear pair. After n control axles drive bevel gear pair and sprocket-wheel drive assembly to reduce speed, the inner gear is driven. The main power axle is linearly connected to central gear. The rotary arm is closely connected to output axle to form a single-stage speed reducer. The control axle can be perpendicular to, or parallel with, or 180-deg symmetrical with the main power axle. Its output axle can serially connected to various speeding-up, speed-reducing and speed-varying mechanisms. Its advantages are high load capability, compact structure, long service life and saving energy and material.
Description
The present invention relates to gear drive, (the present invention both can the permanent torque transmission of permanent power for the multifunctional planetary speed reducer that is specifically related to be formed by combining as the star-wheel transmitting assemblies and the planetary gears of rotation transfer mechanism with multicrank rolling star-wheel, also can realize becoming the permanent torque transmission of power, so all right speedup after the speed change is the general designation multifunctional planetary speed reducer).
Universal speed reducer had only a velocity ratio, a kind of output speed, exists function singleness, can not change the shortcoming of technical parameter by the main frame working conditions change present age, thereby the power of motor of retarder coupling often is more than 1.5～2 times of actual loading power, cause the energy and material to be not fully utilized, also be not easy to realize the production automation, especially outstanding at high-power transmission field; The various mechanical stepless transmissions of prior art, the stepless speed regulation of direct current generator controllable silicon, alternating current machine pole-changing or frequency control of motor speed, Hydraulic Adjustable Speed etc. have overcome the shortcoming of retarder function singleness partially, but are used for specific smaller power transmission field more; The transmission example that adopts special-purpose differential planetary retarder is arranged on lifting, metallurgical equipment, but structure huge, do not have a versatility; At coal pulverizer, cement grinding mill the transmission scheme that adopts two retarder exchange series connection to use is arranged, but shortcomings such as Utilization ratio is low, floor space big, operation inconvenience are arranged; The blower fan coupling heavy-duty motor that power industry is used, working condition requirement can change working speed, the factory that has adopts the high-power pole-changing transmission of double winding, but is difficult to satisfy the optimum Working requirement, adopts frequency control of motor speed to exist again that technical difficulty is big, shortcoming such as cost an arm and a leg.The inventor is in 96118189.3 patent documentations at application number, has narrated a kind of star-wheel speed changer of new structure and can realize that permanent power becomes the torque transmission, but existed the shortcoming that needs to shut down speed change.
The present invention is intended to overcome above-mentioned deficiency, can be by working conditions change thereby provide, do not shut down multifunctional planetary speed reducer various types, general that changes technical parameter, is transferred to high-power transmission from small-power.
The object of the present invention is achieved like this: with the star-wheel transmitting assemblies is the basic element of character, assembly goes out end string dress planetary gears, speed end string dress bevel gear pair, its bevel pinion is contained on the n root Control Shaft, Control Shaft drives bevel gear pair and star-wheel transmitting assemblies deceleration back drives the planetary gears internal gear, a main power input shaft passes the sun gear (central pinion) of star-wheel transmitting assemblies center direct connection planetary gears, so just becoming, planetary gears has two differential planetary mechanisms freely, the planetary mechanism pivoted arm is contained on the output shaft, just be combined into the multi-functional star energy retarder of main power single-stage driving, by the operation Control Shaft, the transmission that realization and main frame working conditions change adapt under non-stop-machine state; One commonly used of Control Shaft can be 2,3 or 4; Control Shaft both can be arranged vertically, also can cancel the parallel or symmetrical 180 ° of layouts of bevel gear pair with main power input shaft; Output terminal both can connect all kinds of reducing gears, gear, the also all kinds of speed increasing mechanisms of can connecting; The multifunctional planetary speed reducer of one-tenth various uses below just capable of being combined and pattern.
Below in conjunction with example structure principle accompanying drawing in detail the present invention is described in detail:
Fig. 1: the multifunctional planetary speed reducer structure principle chart that adopts star-wheel transmission modification assembly and planetary gears, bevel gear pair to form;
Fig. 2: the multifunctional planetary speed reducer structure principle chart that adopts star-wheel transmission modification assembly and star-wheel transmission general purpose module, bevel gear pair to form;
Fig. 3: the modification multifunctional planetary speed reducer structure principle chart that Control Shaft and main power input shaft are arranged in parallel;
Fig. 4: the modification multifunctional planetary speed reducer structure principle chart of Control Shaft and 180 ° of layouts of main power input shaft symmetry;
Fig. 5: Control Shaft and main power input shaft symmetry are arranged vertically for 180 °, the multifunctional planetary speed reducer structure principle chart of low speed end series connection twin-stage star-wheel transmitting assemblies;
Fig. 6: the multifunctional planetary speed reducer structure principle chart that the low speed end is connected with combined type star wheel reducer structure;
Fig. 7: the multifunctional planetary speed reducer structure principle chart that the low speed end is connected with double star-wheel transmission speed reducer structure;
Fig. 8: output terminal increases the multifunctional planetary speed reducer structure principle chart of planetary pinion speed increasing mechanism.
Embodiment 1:(is referring to accompanying drawing 1)
Multifunctional planetary speed reducer shown in Figure 1 mainly partly is made up of planetary gears, star-wheel transmission modification assembly, bevel gear pair three.Star-wheel transmission modification assembly is mainly by 1 internal gear, two planetary pinions, n rolling star-wheel, 1 hollow double-crank eccentric bushing, compositions such as 1 planet carrier and rolling bearing, internal gear [6] and front-end bearing pedestal [2], rear bearing block [10] also uses bolton on casing by internal gear cylindrical place screw for whole admittedly, two planetary structures are identical with technical parameter, and staggered 180 ° of whiles mesh with internal gear [6], planetary pinion [5] distribution circle DZ goes up a uniform n bearing hole, rolling bearing [7] on spider gear shaft [4] double-crank is inserted in this bearing hole, the center hole of planetary pinion [5] is sleeved on the cylindrical of bearing [21], the inner hole sleeve of two bearings [21] is contained on the double-crank of hollow eccentric bushing [18], uniform n perforation dx on the planetary pinion distribution circle Dx circumference, and hand over file to arrange with n bearing hole, pass perforation dx with n supporting axle [20], and with preceding supporting disk [3], back supporting disk [8] connects and is tightened to a whole planet carrier, whole planet carrier is supported in the endoporus of antero posterior axis bearing [2] and [10] by bearing [9], n root spider gear shaft [4] two ends shaft extension is inserted in (spider gear shaft [4] and top part are referred to as the rolling star-wheel) in the planet carrier n bearing hole by rolling bearing [7], the double-crank of the double-crank of hollow eccentric bushing [18] and spider gear shaft [4] should guarantee that throw of eccentric a value is consistent, eccentric bushing bearings at both ends [15] pack into before and after supporting disks [3] and [8] endoporus in; Star-wheel transmission modification assembly can make planetary gears (NGW transmission) into: with the double-crank on the hollow eccentric bushing [18] is a hollow sun gear (central gear) instead, it is fastening to change n root spider gear shaft [4] into n root cylinder d-axis, two ends and planet carrier, n planetary pinion is installed in the middle of d-axis, the center planetary gear hole is installed bearing [7] and is made it to be contained in rotationally on the d-axis intermediate cylindrical, and n planetary pinion just makes star-wheel transmission modification assembly into the planetary gear mechanism (not shown) with sun gear and internal gear [6] engagement simultaneously; Planetary gears is made up of sun gear, a n planetary pinion, rotating shaft, pivoted arm and bearing, internal gear [1] is by fastening connection of supporting disk [3] before spline and bolt and the planet carrier, sun gear [24] and n planetary pinion [32] engagement, n planetary pinion meshes with internal gear [1] simultaneously, planetary pinion is contained on force transmission shaft [30] cylinder rotationally by bearing [31], n root force transmission shaft [30] is distributed on pivoted arm [29] distribution map Da and upward and with pivoted arm is fastening connects, pivoted arm and fastening connection of shaft [27], bearing [28] is for going out shaft support bearing; Bevel gear pair is made up of bevel gear [19], [13], and bevel gear [19] connects with hollow eccentric bushing is fastening, and bevel pinion is installed on the Control Shaft [11], and Control Shaft is supported in the hole of rear bearing block [10] by bearing [12]; Main power input shaft [17] (hereinafter to be referred as main power shaft) is supported in the bearing hole of end seat [14] by bearing [16], and main power shaft passes star-wheel transmission modification assembly center hole, by spline housing [23] and sun gear [24] rotating shaft [25] direct connection; Retarder drives with two motors (or other power plant), a called after M
KThe control motor, its rated power is P
K(secondary power), rated speed are n
K, M
KDirect by coupling and Control Shaft [11], the break (not shown) is installed at coupling cylindrical place; Another motor called after master power motor M, its rated power are that P (main power), rated speed are n, and M is by coupling and the direct (not shown) of main power shaft [17], control motor rated power P
KBe generally 0.05～0.35 times of main motor current P, require to decide on condition.The transmission principle of retarder is: when the main power shaft of braking [17], and the control motor M
KDrive Control Shaft [11] rotation, bevel pinion on the Control Shaft drives bevel gear wheel [19] and rotates, because bevel gear [19] and fastening connection of hollow eccentric bushing [18], so part [19] drivening piece [18] rotation, two planetary pinions [5] are made nominal and spinning motion under the acting in conjunction of two cranks of eccentric bushing and fixed annulus [6], because the bearing housing on the n root rolling star-wheel crank is contained in the planetary pinion n bearing hole, thereby planetary pinion promotes rolling star-wheel work revolution and spinning motion synchronously, rolling star-wheel bearings at both ends is sleeved in the bearing hole of planet carrier, so promote end of line frame spinning motion by the rolling star-wheel.And then drive internal gear [1] by planet carrier and rotate at a slow speed, because sun gear [24] maintains static, internal gear [1] drives planetary pinion [32] and centers on sun crop rotation revolution and spinning motion, also does the automatic motion after the deceleration by bearing [31], force transmission shaft [30] drive pivoted arm [29], pivoted arm and fastening connection of shaft [27], thereby will move output, by after three grades of decelerations, retarder obtains a control rotation speed n like this
dWhen braking Control Shaft [11], main power motor drive main power shaft [17] rotation, part [17] drives sun gear [24] rotation, because internal gear this moment [1] maintains static, so sun gear drives planetary pinion [32] and makes revolution and spinning motion around internal gear [1], in like manner by bearing [31], force transmission shaft [30], pivoted arm [29], shaft [27] with the output that rotatablely moves behind the retarder, at this moment, obtain a working speed n by one-level deceleration back shaft
HDrive main power shaft [17] rotation when starting main power motor, restart the control motor M
KDrive Control Shaft [11] rotation, make internal gear [1] and sun gear [24] when rotating in the same way behind double reduction, output shaft [27] obtains high workload rotation speed n
g, obtain an optimum start-up rotation speed n during counterrotating
f, more than the relation of each technical parameter be: n
g=n
H+ n
d, n
f=n
H-n
d, n
H=(n
g+ n
f)/2, n
d=n
g-n
H, n
d=n
k/ i
k, n
H=n/i, i
kThe resultant gear ratio of retarder when braking main power shaft [17], i is the retarder resultant gear ratio during for braking Control Shaft [11]; If output speed is n
dThe time the output torque be T
d, output speed is n
HThe time the output torque be T
H, then should satisfy T
d=T
HThe requirement of torque balance, and with this as definite p
kAnd the foundation of numerical relation between the P.
Retarder is work like this: start M simultaneously
KWith the M motor and make it opposite direction rotation, use the optimum start-up rotation speed n
fTo start main frame; And then motor is controlled in braking, main power motor continues rotation, makes the retarder output speed from n
fRise to n
HRestart the control motor and make it and main power motor equidirectional rotation, make retarder shaft rotating speed from n
HRise to high workload rotation speed n
gStepless speed regulation if desired then adopts variable frequency regulating speed control motor (or other stepless speed regulation) to make rotating speed from n by said procedure operation control motor
fStepless raising speed is to n
H, again from n
HStepless raising speed is to n
g, or inverse process, because the control motor M
KPower P
KMuch smaller than main motor current P, therefore reach the purpose of high-power transmission stepless speed regulation, or adopt other control program by the main frame operating mode by the stepless speed regulation of smaller power motor.This multifunctional planetary speed reducer structural feature mainly contains:
1, structurally, is the synthetic complete parts of core group from piece number [1] to [23] with star-wheel transmission modification assembly, is synthetic another the complete parts of core group from piece number [24] to [32] with planetary pinion and sun gear, two parts be loaded in the casing simultaneously make [1] and part [32] correct engagement, spline housing [23] link just with [25] assembly is the multifunctional planetary speed reducer of the main power single-stage driving of various installation patterns, it is very convenient to install and remove.
2, in a specific diameter is effective circle of D, the area shared to the major part of two parts carries out the most rational distribution, bearing capacity of the present invention is big, transmission efficiency is high to reach, the life-span is long, and two parts reach or near the technical requirements of equal strength and equivalent-load ability, to realize the purpose of the mutual balance of torque that double power flow produces.
3, the vertical input of secondary power (power is little), through three grades of decelerations output of will moving, main power passes the coaxial direct input planet gear structure of hollow eccentric bushing, not only met bevel gear transmitted power features of limited, but also made large diameter internal gear [1] be in low speed smooth operation state, both satisfied the compact structure requirement, made the efficient transmission of high-power realization again.
4, with respect to the star-wheel transmission modification assembly of a specific effective circular diameter D, six aspect opposite any one velocity ratios such as the rolling bearing of its bearing capacity, input speed allowable, design of part size, employing, working life, production technology all are identical, the change because of velocity ratio does not change, the change of velocity ratio only need change tooth portion parameter and eccentric huge a, thereby component have very high generalization and standardization level.
5, Control Shaft (comprising bevel pinion [13], bearing [12]) can be 2,3,4 and is beneficial to secondary power dividing transmission or a plurality of control motor (not shown)s are used in exchange.
6, the present invention has designed effective circular diameter D from φ 250～1600mm, divide 31 effectively product lines of circle by the R40 preferred numbers, transmit peak torque 382.2KN.m, transmit maximum main power 4000kw, the highest input speed 1500r/min, from Control Shaft [11] to velocity ratio ik=31.5～125 that go out end, from main power shaft to velocity ratio i=4～10 that go out end.
Embodiment 2:(is referring to accompanying drawing 2)
Difference shown in Figure 2 and shown in Figure 1 is to adopt star-wheel transmission general purpose module to replace planetary gears, main power shaft is by spline housing [23] direct connection double-crank eccentric shaft [43], when braking Control Shaft [11], internal gear [1] maintains static, when main power shaft drives [43] rotation, because internal gear [1] is fixing, so planetary pinion [35] is made revolution and spinning motion under the acting in conjunction of part [43] double-crank and internal gear, and promotion rolling star-wheel [34] is made revolution and spinning motion synchronously, rolling star-wheel bearings at both ends [33] is sleeved on by part [41], [37], [38] in the planet carrier bearing hole of Zu Chenging, planet carrier and fastening connection of shaft [44], shaft is supported in the casing endoporus by bearing [45], so the spinning motion by after the deceleration of rolling star-wheel promotion shaft [44] do obtains a rotation speed n
HIn like manner, brake main power shaft [17], drive controlling axle [11] rotation, behind double reduction, promote internal gear [1] and rotate at a slow speed, because double crank shaft [43] is fixing, planetary pinion [35] and internal gear [1] engagement, when [1] rotates, drive planetary pinion [35] and make nominal and spinning motion around part [43], and promote revolution of rolling star-wheel [34] do and spinning motion, and the rolling star-wheel promotes planet carrier by bearings at both ends and shaft is made spinning motion, and shaft obtains a control rotation speed n
dStart-up control axle and main power shaft [17] rotate internal gear [1] and [43] in the same way and obtain an optimum start-up commentaries on classics n simultaneously
f, counterrotating obtains high workload rotation speed n
g, the present invention is to have enlarged velocity ratio in function aspects and the described difference of Fig. 1: the velocity ratio i from Control Shaft [11] to shaft [44]
k=63～250, realize by increasing the bevel gear pair velocity ratio; Velocity ratio i=18～71 of [44] from main power shaft to shaft, all the other as described in Figure 1.
Embodiment 3:(is referring to accompanying drawing 3)
Modification multifunctional planetary speed reducer shown in Figure 3 is by a planetary gears and star-wheel transmission modification assembly, forms by carrier gear [61] connection.Star-wheel transmission deformed component by an endoporus and cylindrical all have involute tooth unsteady gear ring, planetary pinion [73], double-crank Control Shaft [66], connect the planet carrier that forms and bearing cap [65] and rolling bearing by front and back supporting disk [75], [69], supporting axle [77] and combine, planet carrier is fixed, and gear ring is contained in the planet carrier end rotationally by bearing [70]; Planetary gears is by main power shaft 49], sun gear [48], planetary pinion [55], force transmission shaft [53], inside and outside all have the gear ring main parts such as [58] of gradually opening uncinus to combine, gear ring is by in bearing cap [56] and bearing [57] the rotatably support ground casing endoporus, main power shaft is bearing in cover endoporus and the planet carrier endoporus by bearing [50] and [63], planet carrier is formed by part [64] and [47] and the fastening connection of supporting axle [62], and be bearing in the chassis hole by bearing [52], the fastening connection of planet carrier and shaft [46], shaft is bearing in the casing endoporus with bearing [51] and [52]; Carrier gear [61] is installed in rotation on the stationary axle [59] by bearing [60], and meshes with gear ring [58] and [74] simultaneously.Its transmission principle is: when the main power shaft of braking [49], control motor M K drives Control Shaft [66] rotation, double-crank on the Control Shaft promotes planetary pinion [73] motion by bearing [68], because planet carrier is fixed, so planetary pinion is done the revolution translation under planet carrier and double-crank acting in conjunction, and promotion rolling star-wheel [71] is made spinning motion, planetary pinion and the engagement of gear ring internal gear, thereby promotion gear ring [74] is made spinning motion, driving gear ring [58] by carrier gear [61] simultaneously rotates at a slow speed, because main power shaft [49] is fixing, so the internal tooth of gear ring [58] drives planetary pinion [55] around sun crop rotation revolution and spinning motion, and by the spinning motion after force transmission shaft [53] and the deceleration of planet carrier drive shaft [46] do, shaft obtains a control commentaries on classics n
dWhen braking Control Shaft [66], main power motor M drives main power shaft rotation, because gear ring [58] is fixed, so main power shaft drives sun gear [48] rotation, after planetary mechanism slows down, makes shaft obtain a working speed n
HIn like manner, drive controlling axle and main power shaft rotation simultaneously, when gear ring [58] and sun gear counterrotating, shaft obtains an optimum start-up rotation speed n
f, rotation obtains high workload rotation speed n in the same way
gVelocity ratio i=4 of the present invention～10, i
k=18～71, when needs enlarge velocity ratio and torque, shaft [46] but all kinds of reducing gears of direct connection, when needs are exported at a high speed, then shaft [46] but all kinds of speed increasers of direct connection, all the other are as described in Figure 1.
Embodiment 4:(is referring to accompanying drawing 4)
Modification multifunctional planetary speed reducer shown in Figure 4 is to be combined by star-wheel transmitting assemblies and planetary gears, with difference shown in Figure 3 be main power shaft [107] and 180 ° of layouts of secondary power Control Shaft [94] symmetry.Planet carrier that the star-wheel transmitting assemblies constitutes by multicrank Control Shaft [94], planetary pinion [88], rolling star-wheel [90] with by part [91], [96], [97] fastening connection and rolling bearing [93], [92], [95], [89] combine, and planet carrier is fixed on casing [86] end; Planetary gears is formed by combining by sun gear [100], rotating shaft [103], planetary pinion [78], force transmission shaft [80], pivoted arm [79], supporting disk [82] and bearing [81], [83], [101], [102], [98]; Internal gear [84] and internal gear [87] be fastening to be connected and is supported in the endoporus of casing [86] with bearing [85]; Main power shaft [107] is by spline housing [104] and rotating shaft [103] direct connection, and main power shaft [107] is bearing on the support [109] by bearing [108] and output cover [105] end bearing; Output cover one end bearing is on support [109], and the other end is bearing in pivoted arm [79] and goes up and fastening connection, and output puts can install rotating cylinder [106], also driving components such as gear, sprocket wheel can be installed; In like manner exchange main power shaft of braking and Control Shaft output cover can obtain n
dAnd n
HTwo kinds of rotating speeds start main power shaft, control Control Shaft sense of rotation can obtain n
HAnd n
fTwo kinds of rotating speeds, all the other as described in Figure 1.
Embodiment 5 (referring to accompanying drawing 5)
Shown in Figure 5, main power shaft [141] is vertical to be installed, axle head bevel pinion [143] and bevel gear [151] engagement, and part [151] is fastening to be installed on the cylinder shaft extension of internal gear [138] end, and internal gear is supported in the casing by bearing [144]; Secondary power Control Shaft [147] is also vertically installed, axle head bevel pinion and bevel gear [149] engagement, bevel gear [149] be bearing in the cover bearing hole by bearing [150] and with fastening connection of rotating shaft [152], rotating shaft links by sun gear [156] rotating shaft [154] of spline housing [153] with planetary mechanism, rotating shaft [152], [154] and spline housing [153] all are loaded in the endoporus of internal gear [138] end, rotating shaft [154] is supported in the endoporus of [138] end with two bearings [155], and rotating shaft [152] is supported in the cover endoporus with bearing [145]; Sun gear [156] and planetary pinion [140] engagement, planetary pinion is contained on the force transmission shaft [137] rotationally by bearing [139], part [137] and fastening connection of pivoted arm [157]; In like manner, by the sense of rotation of the exchange main power shaft of braking and Control Shaft and change Control Shaft, pivoted arm [157] can obtain n
g, n
f, n
H, n
dFour specific output speeds, if Control Shaft [147] and frequency control motor link, n then
dFor stepless, because n
dBe stepless, thereby can realize complete machine stepless speed regulation, all the other as described in Figure 1.This is a concrete instance that is used for the ladle rotation, require the retarder velocity ratio big, so go out to hold pivoted arm [157] back series connection twin-stage star-wheel transmitting assemblies, double crank shaft [125] end and fastening connection of pivoted arm [157] of the star-wheel transmitting assemblies of middling speed level, when pivoted arm drives the double-crank rotation, promote planetary pinion [127] motion by bearing [136], planetary pinion and internal gear [128] engagement, because [128] are fixed on the support, so planetary pinion is under the acting in conjunction of internal gear and double-crank, make revolution and spinning motion, promote rolling star-wheel [126] simultaneously and make revolution and spinning motion, and promote planet carrier by rolling star-wheel bearings at both ends and make spinning motion, planet carrier is by preceding supporting disk [110] and fastening connection of slow speed turbine stage star-wheel transmitting assemblies double crank shaft [116].Therefore drive the rotation of slow speed turbine stage double crank shaft, in like manner planetary pinion [123] is made revolution and spinning motion, is promoted rolling star-wheel [122] simultaneously and make revolution and spinning motion under the acting in conjunction of double-crank and internal gear [124], promote planet carrier by rolling star-wheel bearings at both ends [121] equally and make spinning motion, supporting disk [114] and fastening connection of shaft [118] before the planet carrier, thus planet carrier drives the motion output after shaft will slow down.Part among the figure [119], [117], [111], [120], [134] etc. are rolling bearing.
Instance graph 6:(is referring to Fig. 6)
Shown in Figure 6 the velocity ratio expansion that can make multifunctional planetary speed reducer is more than 16～400 times in the one-level combined type star-wheel gearing speed-reducer mechanism that goes out to hold to connect shown in Figure 1, and its output torque also increases along with the expansion of velocity ratio.Combined type star-wheel transmission speed reducer structure mainly is made of two pairs of internal gear pairs.The technical parameter of two planetary pinions [169] is identical, and the number of teeth is Z
2, and hand over 180 ° of whiles of file to mesh with internal gear [170], the internal gear number of teeth is Z
1, the module of gear pair is m
12, eccentric bushing [160] is housed in rotating shaft [159], the center planetary gear hole is contained on the double-crank of eccentric bushing rotationally by bearing [165], and its throw of eccentric is a
12(being the Gear center distance) is at distribution circle DZ
2Uniform n rolling star-wheel [167] on the circumference, the rolling bearing on the rolling star-wheel double-crank is sleeved in the planetary bearing hole, and bearings at both ends is packed in the planet carrier bearing hole; Another is made up of staggered 180 ° of whiles of two identical planetary pinions of technical parameter [176] and internal gear [173] engagement internal gear pair, and the planetary pinion number of teeth is Z
3, the internal gear number of teeth is Z
4, the module of gear pair is m
34, internal gear is fixed in the casing end, and eccentric bushing [178] is housed in same rotating shaft [159], and planetary pinion [176] center hole is contained in rotationally by bearing on the double-crank of eccentric bushing, and its throw of eccentric is a
34, at same distribution circle DZ
2Uniform n rolling star-wheel [172] on the circumference, its double-crank upper bearing sleeve is contained in the planetary bearing hole, and bearings at both ends is packed in the bearing hole of planet carrier; Whole planet carrier is made up of preceding supporting disk [166], back supporting disk [175], n root supporting axle [158], middle supporting disk [179], n root supporting axle [158] and the fastening connection of three dishes, and the supporting disk end has bearing [174] to be supported in the casing endoporus behind planet carrier.Its working principle is: when pivoted arm [29] drives rotating shaft [159] rotation, two planetary pinions [176] entry into service under the effect of eccentric bushing double-crank [178], because of planetary pinion and fixed annulus [173] engagement, so planetary pinion is made revolution and spinning motion under the acting in conjunction of double-crank and internal gear, and promotion rolling star-wheel [172] is made revolution and spinning motion synchronously, the rolling star-wheel promotes planet carrier by bearings at both ends and makes spinning motion, and the rotating speed of planetary pinion [176] is passed to planetary pinion [169] with the relation of 1:1; Rotating shaft [169] rotation drives eccentric bushing [160] rotation simultaneously, because planet carrier rotates with planet gear [176], rolling star-wheel [167] bearings at both ends is contained in again in the endoporus of planet carrier, so planetary pinion [169] is made revolution and spinning motion under the acting in conjunction of eccentric bushing [160] double-crank and planet carrier, planetary pinion [169] is meshed with internal gear [170], internal gear again with fastening connection of shaft [163], thereby the motion that planetary pinion will promote after internal gear will slow down with shaft is exported.All the other is characterized in that as described in Figure 1:
1, the bearing capacity of two pairs of internal gear pairs, rotating speed allowable, standard piece, structural dimensions, working life are identical, and the change because of velocity ratio does not change; And with a planet carrier, thereby standardization of the present invention, generalization degree height.
2, have identical bearing capacity and life-span for satisfying two pairs of gear pairs, tooth of the present invention portion parameter satisfies Z
2* m
12≈ Z
3* m
34Requirement.
3, for satisfying efficient transmission requirement, internal gear of the present invention [l70] is realized rotation in the same way with rotating shaft [159], and with respect to any one velocity ratio in the reducing gear velocity ratio series, tooth portion parameter satisfies Z
1-Z
2〉=Z
4-Z
3, a
12〉=a
34, velocity ratio i=+Z
1Z
3/ (Z
1Z
3-Z
2Z
4) requirement.
4, the present invention is by Z
1, Z
2, Z
3, Z
4But 4 parameter permutation and combination become a large amount of velocity ratios, and velocity ratio preferably commonly used is more than 16～400, and maximum transmission ratio can reach more than 10000.
5, the present invention has realized that by 4 planetary reasonable Arrangement driving component self is bidirectional balanced, phoresys very steady.
The multifunctional planetary speed reducer of the main power twin-stage transmission of connecting with combinations thereof formula reducing gear is applicable to wants that cube is little, the king-sized low speed transmission field of velocity ratio, and all the other as described in Figure 1.
Embodiment 7:(is referring to accompanying drawing 7)
The multifunctional planetary speed reducer slow speed turbine stage shown in Figure 7 double star-wheel transmission speed reducer structure of connecting, be to mesh with internal gear [191] by staggered 180 ° of whiles of four identical planetary pinions of technical parameter [190], by bearing [182], planetary pinion is contained on the double-crank rotationally, and rotating shaft [180] is by bearing [28] and [186] supporting.By front and back supporting disk [187], [193], middle supporting disk [196], the whole planet carrier end of the fastening connection of n root supporting axle [195] is supported in the casing endoporus by bearing [192] and [183], when pivoted arm drives rotating shaft [180] rotation, two identical double-crank eccentric bushings [181] of physical dimension promote four planetary pinion motions simultaneously, planetary pinion and fixed annulus engagement, so four planetary pinions are made revolution and spinning motion under the acting in conjunction of internal gear and double-crank, and n rolling star-wheel of promotion [188] made revolution and spinning motion synchronously, promoting planet carrier by rolling star-wheel bearings at both ends rotates, because planet carrier and fastening connection of shaft [185], thereby the motion behind the retarder is exported.Output shaft is supported in the casing endoporus by bearing [184] and [186].The characteristics of this reducing gear are that bearing capacity is higher 0.75～1 times than single star-wheel transmitting assemblies, and driving component is realized two-way self balance, connect multifunctional planetary speed reducer velocity ratio i=50～800, the i of main power twin-stage transmission of this kind reducing gear of slow speed turbine stage
k=125～10000, all the other as described in Figure 1.
Embodiment 8:(is referring to accompanying drawing 8)
Multifunctional planetary speed reducer shown in Figure 8 is 1 planetary pinion speed increasing mechanism in parallel in differential planet gear mechanism, by sun gear [199], planetary pinion [212], internal gear [213] is formed differential planet gear mechanism, by sun gear [203], planetary pinion [209], the internal gear [211] that is fixed on the casing is formed the planetary pinion speed increasing mechanism, by front and back supporting disk [202], [198], n root supporting axle [201] and force transmission shaft [204] be fastening to be coupled to shared whole planet carrier, and be supported in casing endoporus and internal gear [213] bearing hole by bearing [197], planetary pinion all is installed in rotation on the force transmission shaft [204] by bearing [210], the shaft [208] that connects sun gear [203] is by bearing [206], [207] supporting, the rotating shaft [205] that connects sun gear [199] is supported by bearing [200], and by Hua Jiantao [23] and main power shaft [17] direct connection.Working principle of the present invention is: as described in Figure 1 after planet gear differential mechanism makes planet carrier (part among Fig. 1 [29]) obtain four specific rotation speeds, because planetary pinion [209] and [212] all are contained on the force transmission shaft [204] rotationally, so planet carrier forces planetary pinion [209] to make revolution and spinning motion around internal gear [211] by force transmission shaft [204], planetary pinion drives sun gear [203] and shaft [208] is done the speedup motion, and establishing internal gear [211] number of teeth is ZB
1, sun gear [203] number of teeth is ZA
1, planet carrier rotating speed speedup (ZA then
1+ ZB
1)/ZA
1Doubly, through sun gear [203] and output shaft [208] output, so that the present invention reaches the purpose of speedup output.All the other as described in Figure 1.
Characteristics of the present invention are to realize that the heavy-duty motor of the couplings such as blower fan, water pump is at a high speed defeated Go out the requirement with gear, for reaching this specification requirement, except increasing above-mentioned speed increasing mechanism, Also can set up parallel axes or the in-line gears transmission increases at the output of Fig. 1 and the described decelerator of Fig. 3 Speed mechanism, narration is omitted.
Adopt the technology of the present invention to design the series of products that transmitting torque 2646KN.m is following, transmitted power 4000kw is following, gearratio 4～25000 scopes are interior, systematically overcome the in the past shortcoming of universal speed reducer function singleness, advantage of the present invention is that significantly major advantage is:
1, transmission efficiency height, main power single-stage driving efficient 98%, single-stage speedup transmission efficiency Can reach more than 96%.
2, energy-saving material-saving is effective, owing to can change technical parameter with the operating mode load variations, be used for the coal pulverizer transmission and can reduce power of motor 25～45%, reduce weight more than 30%, be used for cement grinding mill, heavy rubber mixing machine transmission can reduce power of motor more than 23%, weight reduces more than 30%.
3, can be by lower-powered control motor stepless or step speed regulation reach the purpose that the stepless or step speed regulation in ground is not shut down in high-power transmission, overcome the shortcoming of heavy-duty motor speed governing difficulty, for improve host performance, the production automation provides advantage.
4, output terminal of the present invention can be realized the transmission of high speed output variable speed by speed increasing mechanism, realizes not shutting down the stepless or step speed regulation in ground for blower fans such as power industry, pump motor advantage is provided.
5, product structure adopts blocking assembly, fabricated structure, thereby product component generalization and standardization level height, is beneficial to large-scale production.
Claims (8)
1, multifunctional planetary speed reducer is to adopt star-wheel transmitting assemblies and planetary gears and bevel gear pair tandem compound with two degrees of freedom to form: the star-wheel transmitting assemblies is by the hollow eccentric bushing of double-crank [18], two identical and staggered 180 ° of whiles of technical parameter and internal gear [6] planet gear meshed [5], by preceding supporting disk [3], back supporting disk [8], planet carrier and bearing that the fastening connection of n root supporting axle [20] forms combine, uniform n rolling star-wheel on planetary pinion distribution circle DZ circumference, bearing housing on the rolling star-wheel double-crank is contained in the planetary gear bearing hole, and bearings at both ends is sleeved in the bearing hole of planet carrier; On distribution circle Dx circumference uniform n perforation dx, n root supporting axle pass hole dx and with rolling star-wheel interlaced arrangement, rolling star-wheel double-crank has identical throw of eccentric a with the eccentric bushing double-crank, two planetary pinions are contained on the double-crank of eccentric bushing rotationally by bearing [21], eccentric bushing [18] is contained in the planet carrier bearing hole by bearing [22] and [15], planet carrier is contained in the endoporus of bearing support [2] and [10] by bearing [9], bearing support [2], [10] are 1 body with internal gear [6] with bolton, and are installed on the support by internal gear cylindrical end face screw; The gearwheel of bevel gear pair and eccentric bushing be fastening to be connected, small gear is contained in Control Shaft [11] end, Control Shaft is loaded in the bearing hole of bearing support [10] with bearing [12]; Planetary gears is made up of solar energy [24], a n planetary pinion [32], internal gear [1], planetary pinion is installed in rotation on the force transmission shaft [30] by bearing [31], n root force transmission shaft be distributed on the circumference of distribution map Da and with fastening connection of pivoted arm [29], pivoted arm [29] and fastening connection of shaft [27]; Main power shaft [17] passes the eccentric bushing endoporus, an end is supported in the bearing hole of end cap [14] by bearing [16], and the other end is by coupling [23] and sun gear rotating shaft [25] direct connection, and rotating shaft [25] is packed into bearing [26] in the pivoted arm endoporus; Control Shaft drives the internal gear of bevel gear pair and star-wheel transmitting assemblies deceleration back drive planetary gears; 1 main power input shaft passes the sun gear of star-wheel transmitting assemblies center direct connection planetary gears; so planetary gears just becomes the differential planetary mechanism with two degrees of freedom; the planetary gears pivoted arm is contained on the output shaft; just be combined into multifunctional planetary speed reducer, by the operation Control Shaft, under non-stop-machine state, realize the transmission that adapts with the main frame working conditions change.
It is characterized in that:
A, structurally, is the synthetic complete parts of core group from piece number [1] to [23] with star-wheel transmission modification assembly, is synthetic another the complete parts of core group from piece number [24] to [32] with planetary pinion and sun gear, two parts be loaded in the casing simultaneously make [1] and part [32] correct engagement, spline housing [23] link just with [25] assembly is the multifunctional planetary speed reducer of various installation patterns.
B, in a specific diameter is effective circle of D, the area shared to the major part of two parts carries out the most rational distribution, bearing capacity of the present invention is big, transmission efficiency is high to reach, the life-span is long, and two parts reach or near the technical requirements of equal strength and equivalent-load ability, to realize the purpose of the mutual balance of torque that double power flow produces.
C, the vertical input of secondary power (power is little), through three grades of decelerations output of will moving, main power passes the direct input planet gear structure of hollow eccentric bushing, both met bevel gear transmitted power features of limited, make large diameter internal gear [1] be in low speed smooth operation state again, both satisfied the compact structure requirement, made the efficient transmission of high-power realization again.
D, the double-crank eccentric bushing in star-wheel transmission modification assembly are an integral body and have the special eccentric bushing of endoporus, be beneficial to main power shaft and pass the center.
E, star-wheel transmission modification assembly also can change planetary gear mechanism (NGW transmission) into: with the double-crank on the hollow eccentric bushing [18] is a hollow sun gear (central gear) instead, change n root spider gear shaft [4] into n root cylinder d-axis, two ends and planet carrier are fastening, n planetary pinion is installed in the middle of d-axis, planetary pinion is installed in rotation on the d-axis intermediate cylindrical, and n planetary pinion just makes to be star-wheel transmission modification assembly into planetary gear mechanism with sun gear and internal gear [6] engagement simultaneously.
One commonly used of the Control Shaft of f, multifunctional planetary speed reducer [11] (containing bevel pinion [13], bearing [12]) can be 2,3 and 4.
G, multifunctional planetary speed reducer output terminal can connect all kinds of reducing gears, gear, all kinds of speed increasing mechanisms of also can connecting.
2, multifunctional planetary speed reducer according to claim 1, it is characterized in that replacing planetary gears with the star-wheel transmitting assemblies, main power shaft and double-crank eccentric shaft [43] are direct, two identical planetary pinions of technical parameter interlock 180 °, mesh with internal gear [1] simultaneously, because of internal gear [1] is rotating, thereby form a kind of star wheels transport mechanism with two degrees of freedom, to enlarge the velocity ratio i of retarder, enlarge velocity ratio i matchingly by the velocity ratio that increases bevel gear pair simultaneously
k
3, multifunctional planetary speed reducer according to claim 1, it is characterized in that a kind of main power shaft and Control Shaft are that the modification multifunctional planetary speed reducer that is arranged in parallel is to be combined with differential planet gear mechanism is in parallel by carrier gear [61] by star-wheel transmission modification assembly, internal gear [58] and [74] existing internal tooth have external tooth again.
4, multifunctional planetary speed reducer according to claim 1, the modification multifunctional planetary speed reducer that it is characterized in that 180 ° of layouts of a kind of main power shaft and Control Shaft symmetry is to be combined by star-wheel transmission general purpose module and differential planet gear mechanism, the fastening connection of the internal gear of two parts, and be supported in the casing with bearing [85], drive controlling axle [94], planetary pinion [88] is done plane motion and is promoted internal gear [87] and [84] execute commentaries on classics at a slow speed, the sun gear of planetary mechanism is driven by the main power shaft [107] with 180 ° of layouts of Control Shaft symmetry, and the output cover [105] that moves through after the deceleration is exported between main power motor and secondary power motor.
5, multifunctional planetary speed reducer according to claim 1, it is characterized in that a kind of main power shaft and Control Shaft all is arranged vertically, the modification multifunctional planetary speed reducer of slow speed turbine stage series connection twin-stage star-wheel transmission speed reducer structure, its main power shaft by bevel-gear sett pair ([143] and [151]) deceleration rear driving internal gear [138], Control Shaft by another to bevel gear pair ([149] and [148]) and planetary gear reducing mechanism driving internal gear [138], import star-wheel transmission speed reducer structure by the motion after with differential speed change of force transmission shaft [137], pivoted arm [157].
6, multifunctional planetary speed reducer according to claim 1, it is characterized in that multifunctional planetary speed reducer in the main power twin-stage transmission that goes out end series connection one-level combined type star-wheel transmission speed reducer structure, its combined type star-wheel transmission speed reducer structure combines (each is to being meshed with an internal gear by two identical staggered 180 ° of whiles of planetary pinion of technical parameter) different shared planet carrier of internal gear pair of technical parameter by two, and its velocity ratio is by the different tooth number Z of two pairs of gear pairs
1, Z
2, Z
3, Z
4Be arranged in a combination, two pairs of gear pairs have identical bearing capacity, satisfy Z
2Xm
12≈ Z
3Xm
34, Z
1-Z
2〉=Z
4-Z
3, a
12〉=a
34Requirement, reach the bidirectional balanced purpose of driving component by two pairs of 4 planetary reasonable Arrangement.
7, multifunctional planetary speed reducer according to claim 1, it is characterized in that the connect multifunctional planetary speed reducer of main power twin-stage transmission of double star-wheel transmission speed reducer structure of slow speed turbine stage, its double star-wheel transmission speed reducer structure, be to be meshed with an internal gear [191] and a shared planet carrier combines by staggered 180 ° of whiles of two pairs four the identical planetary pinions of technical parameter [190], in two pairs of planetary gear bearing holes identical rolling star-wheel is housed, identical double-crank eccentric bushing and bearing reach the bidirectional balanced purpose of driving component by two pairs of four planetary reasonable Arrangement.
8, multifunctional planetary speed reducer according to claim 1, the multifunctional planetary speed reducer that it is characterized in that differential planet gear mechanism 1 planetary pinion speed increasing mechanism in parallel, its differential planet gear mechanism and planetary pinion speed increasing mechanism altogether same planet carrier, planetary pinion [212] and [209] all are contained on same (n root) force transmission shaft [204] rotationally, and internal gear [211] number of teeth is Z
B1, sun gear [203] number of teeth is Z
A1, then make four specific outputs of multifunctional planetary speed reducer change n
g, n
H, n
f, n
dEqual speedup (Z
A1+ Z
B1)/Z
A1Doubly output realizes the purpose of output at a high speed to reach the present invention.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN98112433A CN1089150C (en) | 1998-04-14 | 1998-04-14 | Multifunctional planetary speed reducer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN98112433A CN1089150C (en) | 1998-04-14 | 1998-04-14 | Multifunctional planetary speed reducer |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1232146A true CN1232146A (en) | 1999-10-20 |
| CN1089150C CN1089150C (en) | 2002-08-14 |
Family
ID=5222284
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN98112433A Expired - Fee Related CN1089150C (en) | 1998-04-14 | 1998-04-14 | Multifunctional planetary speed reducer |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1089150C (en) |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2003006845A1 (en) * | 2001-07-09 | 2003-01-23 | Ganxu Zhou | A type of speed reducer or speed-varying device with sprocket-wheel drive assembly |
| CN101842611A (en) * | 2007-11-26 | 2010-09-22 | 池田昌幸 | Transmission device |
| CN101949439A (en) * | 2010-09-09 | 2011-01-19 | 江苏泰隆减速机股份有限公司 | Vertical star-wheel differential speed regulation device |
| CN101994785A (en) * | 2010-11-15 | 2011-03-30 | 南京高特齿轮箱制造有限公司 | Gear box with two drive converting mechanisms |
| CN103089940A (en) * | 2011-11-04 | 2013-05-08 | 吴小杰 | Large involute star wheel speed regulator |
| CN103089938A (en) * | 2011-11-04 | 2013-05-08 | 吴小杰 | Large planet differential motion-cycloid speed regulator |
| CN103802601A (en) * | 2012-11-13 | 2014-05-21 | 中国重汽集团济南动力有限公司 | Single-stage speed-reducing driving axle assembly |
| CN103912637A (en) * | 2014-04-28 | 2014-07-09 | 江苏泰隆减速机股份有限公司 | Special vertical star wheel reducer for ladle turret |
| CN106015474A (en) * | 2016-07-29 | 2016-10-12 | 洛阳理工学院 | Solar tracking gear assembly |
| CN107415320A (en) * | 2017-06-08 | 2017-12-01 | 深圳市科发机械制造有限公司 | It is die cut roller apparatus and printing and die-cutting apparatus |
| CN108007686A (en) * | 2017-10-23 | 2018-05-08 | 华南理工大学 | A kind of robot harmonic wave speed reducing machine test platform precision analysis test method |
| CN113070902A (en) * | 2021-04-08 | 2021-07-06 | 合肥工业大学 | Three-axis rotating robot joint |
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- 1998-04-14 CN CN98112433A patent/CN1089150C/en not_active Expired - Fee Related
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2003006845A1 (en) * | 2001-07-09 | 2003-01-23 | Ganxu Zhou | A type of speed reducer or speed-varying device with sprocket-wheel drive assembly |
| CN101842611A (en) * | 2007-11-26 | 2010-09-22 | 池田昌幸 | Transmission device |
| CN101842611B (en) * | 2007-11-26 | 2013-04-24 | 池田昌幸 | Transmission device |
| CN101949439A (en) * | 2010-09-09 | 2011-01-19 | 江苏泰隆减速机股份有限公司 | Vertical star-wheel differential speed regulation device |
| CN101949439B (en) * | 2010-09-09 | 2013-01-09 | 江苏泰隆减速机股份有限公司 | Vertical star-wheel differential speed regulation device |
| CN101994785A (en) * | 2010-11-15 | 2011-03-30 | 南京高特齿轮箱制造有限公司 | Gear box with two drive converting mechanisms |
| CN101994785B (en) * | 2010-11-15 | 2013-01-02 | 南京高特齿轮箱制造有限公司 | Gear box with two drive converting mechanisms |
| CN103089938A (en) * | 2011-11-04 | 2013-05-08 | 吴小杰 | Large planet differential motion-cycloid speed regulator |
| CN103089940A (en) * | 2011-11-04 | 2013-05-08 | 吴小杰 | Large involute star wheel speed regulator |
| CN103089940B (en) * | 2011-11-04 | 2015-07-15 | 陈伟 | Large involute star wheel speed regulator |
| CN103089938B (en) * | 2011-11-04 | 2016-04-13 | 吴小杰 | Large planetary is differential-cycloid speed regulator |
| CN103802601A (en) * | 2012-11-13 | 2014-05-21 | 中国重汽集团济南动力有限公司 | Single-stage speed-reducing driving axle assembly |
| CN103912637A (en) * | 2014-04-28 | 2014-07-09 | 江苏泰隆减速机股份有限公司 | Special vertical star wheel reducer for ladle turret |
| CN106015474A (en) * | 2016-07-29 | 2016-10-12 | 洛阳理工学院 | Solar tracking gear assembly |
| CN106015474B (en) * | 2016-07-29 | 2018-06-29 | 洛阳理工学院 | Solar tracking gear assembly |
| CN107415320A (en) * | 2017-06-08 | 2017-12-01 | 深圳市科发机械制造有限公司 | It is die cut roller apparatus and printing and die-cutting apparatus |
| CN108007686A (en) * | 2017-10-23 | 2018-05-08 | 华南理工大学 | A kind of robot harmonic wave speed reducing machine test platform precision analysis test method |
| CN113070902A (en) * | 2021-04-08 | 2021-07-06 | 合肥工业大学 | Three-axis rotating robot joint |
| CN113070902B (en) * | 2021-04-08 | 2022-09-16 | 合肥工业大学 | Three-axis rotating robot joint |
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Address after: 410007 Hunan Machinery Research Institute, No. 277 Zi Road, Hunan, Changsha Co-patentee after: Zhou Ganxu Patentee after: Hunan Provincial Machinery Institute Address before: 410007, 24, Zi Lu Road, Changsha, Hunan Patentee before: Zhou Ganxu |
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Assignee: Changsha Xinglun Transmission Equipment Co.,Ltd. Assignor: Hunan Provincial Machinery Institute|Zhou Ganxu Contract fulfillment period: 2006.2.9 to 2016.2.9 contract change Contract record no.: 2008430000041 Denomination of invention: Multifunctional planetary speed reducer Granted publication date: 20080814 License type: Exclusive license Record date: 20081128 |
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Free format text: EXCLUSIVE LICENSE; TIME LIMIT OF IMPLEMENTING CONTACT: 2006.2.9 TO 2016.2.9; CHANGE OF CONTRACT Name of requester: CHANGSHA XINGLUN DRIVING EQUIPMENT CO., LTD. Effective date: 20081128 |
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Granted publication date: 20020814 Termination date: 20130414 |