CN102371276B - Planet gear and double sliding block transmission device of high-speed and energy-saving pipe cold rolling mill - Google Patents

Planet gear and double sliding block transmission device of high-speed and energy-saving pipe cold rolling mill Download PDF

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CN102371276B
CN102371276B CN201010259015.1A CN201010259015A CN102371276B CN 102371276 B CN102371276 B CN 102371276B CN 201010259015 A CN201010259015 A CN 201010259015A CN 102371276 B CN102371276 B CN 102371276B
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planetary gear
tie
rod
balancing
balance
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CN102371276A (en
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岑乐庆
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岑乐庆
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Abstract

The invention relates to a scheme of a device of a planet gear transmission balancing box for balancing the inertia force of a working base of a reciprocating pipe cold rolling mill and the inertia moment on a main shaft and a scheme of a double sliding block mechanism transmission balancing box. When a tie rod (8) in a main shaft (6) rotates to each position angle, the inertia force of a working frame can be nearly completely balanced in the horizontal direction, the inertia force of a component consisting of a balance connector (3), the tie rod (8) and a planet gear (10) can be nearly completely balanced in the vertical direction, and most inertia moment on the main shaft can also be balanced, so that the defect that the common crank-link mechanism is used as a main transmission mechanism is overcome. A motor of relatively low power can be selected when the pipe cold rolling mill rotates at a high speed with low vibration and low no-load power consumption, so that the requirement for the civil foundation of equipment is low, and the whole working frame made of steel can be driven to do linear reciprocating motion; and the structural schemes can be applied to various extra large, large, medium and small high-speed and energy-saving Pilger mills.

Description

The planetary gear of high-speed and energy-saving type cold tube-rolling mill and double-slider transmission device
Technical field
The invention belongs to the main transmission driven equilibrium mechanism of reciprocating cold tube-rolling mill.
Background technology
The main transmission driven equilibrium mechanism of Chinese Patent Application No. 200810017629.1 described cold tube-rolling mills installs balance weight to come the one order inertia power of balance work housing to reach the object of main shaft high speed rotating on the basis of toggle on the axle of two identical switched in opposite of rotating speed, also the inertia force of remainder work housing not yet can be balanced and act on foundation of civil work, and balance weight acts on foundation of civil work producing a pair of very large alternation moment each other.The main transmission driven equilibrium mechanism of the described cold tube-rolling mill of Chinese patent ZL200920074011.9 is also identical at three rotating speeds on the basis of toggle, on three fulcrums of a middle fulcrum and other two fulcrums switched in opposite, balance weight being installed respectively comes the one order inertia power of balance work housing to reach the object of main shaft high speed rotating, the inertia force of equally also remainder work housing not yet can be balanced and act on foundation of civil work, no matter balance weight is subject to the less object of small machine vibration of wind tunnel by not producing a pair of alternation moment while running up to reach each other on foundation of civil work. but be that the main transmission two spindle balance mechanisms of Chinese Patent Application No. 200810017629.1 described cold tube-rolling mills or three spindle balance mechanisms of the main transmission of the described cold tube-rolling mill of Chinese patent ZL200920074011.9 add that on the basis of toggle balance weight reaches the object of main shaft high speed rotating. and moment of inertia during this class cold tube-rolling mill main shaft high speed rotating on crank spindle is large especially, thereby the no-load power consumption when crank spindle high speed rotating is also large especially. even numerically surpassed required power. Chinese patent ZL00222220.5 " main engine of high speed cooling pipe mill " although in used 4 pairs of planet pinions as the main transmission drive unit of milling train, but this device, the connector and the fan-shaped balance weight that in design, structurally without the special shape through mathematics Mechanics Calculation, design, that is to say the balance that there is no the wind tunnel of taking into account system in design, both do not considered that frame inertia equilibrium of forces do not consider the balance of the moment of inertia in drive shaft yet, and machine is stressed also unreasonable, frame inertia force acts on planetary gear and gear ring rather than acts on bearing, thereby this type of main transmission driving mechanism can not reach and can not reach at a high speed the object that moment of inertia reducing in drive shaft reduces to overcome the no-load power consumption of moment of inertia. and driving mechanism only drives the roll retainer assembly that weight is lighter, and can not drive the integrated steel work housing assembly that weight is larger, the VE transmission cold tube-rolling mill that Germany SMS.Meer company produces is as KPW100VMR (K) KPW125VMR (K) KPW150VMR (K) type cold tube-rolling mill, although this class milling train also can reduce the moment of inertia on crank spindle to a certain extent greatly, reduce to overcome the required no-load power consumption of moment of inertia on crank spindle, improving the utilization rate of electric energy. but this class milling train still belongs to the mechanism that adds balance weight on slider-crank mechanism basis, also can only balance one order inertia power, also has the not existence of balanced larger residual inertia force, and this class milling train needs very dark expensive foundation of civil work.
The horizontal equilibrium Gear Planet Transmission cold tube-rolling mill that Germany SMS.Meer company produces is horizontal, and is only only applicable to Minitype pipe cold-rolling mill as KPW18HMR (K) and KPW25HMR (K) type cold tube-rolling mill.
Summary of the invention
Object of the present invention (technical problem that will solve): the cold tube-rolling mill driving with toggle exists two main shortcomings:
1) the one order inertia power that the balanced controls of toggle can only balance work housing, thereby the larger remaining frame inertia force that total existence is not balanced after balance.
2) when turning round, the cold tube-rolling mill that toggle drives there is larger moment of inertia on crank axle, especially when crank axle runs up, the moment of inertia on crank axle increases greatly, thereby the no-load power consumption that overcomes moment of inertia also increases greatly, and the no-load power consumption that especially overcomes moment of inertia when crank axle runs up is large especially.
For overcoming above two shortcomings, hereby adopted through the balancing connector of special shape design of mathematics Mechanics Calculation and the main drive gear of the planet tooth opinion transmission of fan-shaped balance weight, this main transmission driven equilibrium mechanism can be when running up almost complete equipilibrium fall the inertia force of work housing, the remaining frame inertia force not being balanced existing after balance is especially little, the moment of inertia that exists on crank axle when running crank axle especially little especially when crank axle runs up the moment of inertia on crank axle also very little and be less than the moment of inertia producing on VE transmission cold tube-rolling mill crank axle, thereby the no-load power consumption that overcomes moment of inertia while running up is also very little, and be less than on VE transmission cold tube-rolling mill main shaft and overcome the required no-load power consumption of moment of inertia.
Thereby the reciprocating cold tube-rolling mill that adopts this main transmission driven equilibrium mechanism can reach the object of high-speed and energy-saving.
Main transmission driven equilibrium of the present invention mechanism can directly drive whole steel work housing assembly to do to move back and forth at a high speed.
Structure of the present invention and principle:
1) structure
In the ring gear 9 that the planetary gear 10 that structure of the present invention is Rx for employing pitch radius is 2Rx in pitch radius, make pure rolling, planetary gear 10 is fitted together with tie-rod 8 use key connecting, tie-rod 8 is contained in a cylindrical hole in slave spindle 6, two bearings 4 are housed in cylindrical hole, on tie-rod, by key connecting, respectively fill a balancing connector 3 on one side, tie-rod 8 is installed the connecting rod connecting pin 18 of connection frame through planetary gear 10. of balancing connector on one side 3 use key connecting assemblings on the balancing connector 3 of another side by key connecting, bearing 2 is installed on connecting rod connecting pin 18, balancing connector 3 is designed on one side for rectangle another side is designed to semicircle (or other shape). the direction of a fan-shaped balance weight 11 and fan-shaped balance weight 11 installations of gear wheel 5. is installed at direction (Fig. 1 of the extended line of the line of the center O of tie-rod 8 and the center A of slave spindle 6 on slave spindle 6, 2, 3, 4, 5), power is passed on gear wheel 5 and slave spindle 6 by shaft coupling 16 driving shaft 14 pinions 13, by frame connecting pin 18 drivening rods 1 on balancing connector 3, do reciprocating linear motion with frame 17.
The technical scheme of Planetary Gear Transmission tandem-driving bogie shown in Fig. 6 and Fig. 7 one single planetary gear transmission tandem-driving bogie device option A, its design feature is the side that planetary gear 10 and large ring gear 9 are placed in transmission tandem-driving bogie.
The tandem-driving bogie of Planetary Gear Transmission shown in Fig. 8 technical scheme one single planetary gear transmission tandem-driving bogie device option b, the difference of its design feature and option A is that planetary gear 10 and large ring gear 9 are placed in the centre of transmission tandem-driving bogie. in the middle of slave spindle 6, fluting is installed planetary gear 10 to pass, the maximum gauge of slave spindle 6 must be less than the tip diameter of large ring gear 9 so that pass while installing, casing is divided into two spaces, left and right, lays balance weight 11 another lays gear wheel 5 and pinion 13 for one.
The tandem-driving bogie of Planetary Gear Transmission shown in Fig. 9 technical scheme one single planetary gear transmission case apparatus scheme C that partly weighs, its design feature is to be that with the difference of option A planetary gear 10 and large ring gear 9 are placed in the centre of transmission tandem-driving bogie. slave spindle 6 is slotted on one side, to pass, planetary gear 10 is installed, the maximum gauge on the left side of slave spindle 6 must be less than the tip diameter of large ring gear 9 so that pass while installing, be in casing that with the difference of option b, regardless of space, two of left and right, balance weight 11 gear wheels 5 are all arranged in a casing with pinion 13.
The tandem-driving bogie of Planetary Gear Transmission shown in Figure 10 technical scheme two dual planetary gear transmission tandem-driving bogie device option As, its design feature is to drag work housing 17 by two of left and right Planetary Gear Transmission tandem-driving bogie and two stand connecting rod 1, due to two Planetary Gear Transmission tandem-driving bogies thereby can drag greater weight work housing 17, the running speed of slave spindle 6 also can be higher.
The transmission of double-slider mechanism shown in Figure 12 tandem-driving bogie technical scheme two double-slider mechanism transmission tandem-driving bogie device option bs, are that with the difference of the technical scheme of Planetary Gear Transmission tandem-driving bogie shown in figure ten two dual planetary gear transmission tandem-driving bogie device option As in this device, not having planetary gear 10 and large ring gear 9 the substitute is increases wear-resistant slide plate 19 slide block 20 slipper bearings 21 and slide block bearing pin 22.
2) principle
Fig. 1, 2, 3, 4, in Planetary Gear Transmission in 5, 2 B on balance connector 3 (stand connecting rod pin center) are Rx with each distance apart from the center O of tie-rod 8 of C (centers of gravity of planetary gear 10 tie-rods 8 and balancing connector 3 assemblies), 180 ° of the center O phase phasic differences of B point and C point and tie-rod 8, stand connecting rod pin center B makes horizontal rectilinear motion and seesaws by connecting rod 1 frame 17 that pushes the work forward, and another C makes the rectilinear motion that vertical line motion .B point and C point are made quadrature, when B point moves to the extreme position of stroke, C point is just in time at the mid point of stroke, when otherwise C point moves to the extreme position of stroke, B point is just in time at the mid point of stroke, balancing connector 3 is also done the rotation reverse with slave spindle around C point, the instantaneous angular velocity that its instantaneous angular velocity and crank spindle rotate just in time equates. the motion of balancing connector 3 is the rectilinear motion of the C vertical direction of ordering and the compound motion rotatablely moving of ordering around C.
While doing the configuration design of balancing connector 3 for single planetary driving device, make two of left and right balancing connector 3 add that tie-rod 8 and the center of gravity of total parts of planetary gear 10 just in time drop on C point, and make the weight of its total parts slightly surpass frame weight and single connecting rod weight sum.
When work housing 17 moves to the extreme position of stroke, kinetic energy equals another, and balancing connector 3 adds that parts total when the center of gravity C point of tie-rod 8 and total parts of planetary gear 10 moves to the extreme position of stroke are also around the center of gravity C point work of parts and the reverse rotation of slave spindle, the instantaneous angular velocity of the slave spindle when instantaneous angular velocity that when therefore work housing 17 moves to the extreme position of stroke, slave spindle rotates is just larger than center of gravity C point that balancing connector 3 adds tie-rod 8 and total parts of planetary gear 10 and moves to the extreme position of stroke, thereby be that the remaining connecting rod that is not balanced of the horizontal direction that makes to exist after balance and the inertia force of frame and the balancing connector of vertical direction 3 add that tie-rod 8 is as much as possible little with the Remnant inertia force not being balanced of total parts of planetary gear 10 for single-drive tandem-driving bogie device, two balance connectors 3 add that tie-rod 8 and the gross weight outline of total parts of planetary gear 10 are slightly larger than the weight sum of connecting rod 1 and work housing 17. for dual transmission, be to make the remaining connecting rod not being balanced of horizontal direction existence after balance and inertia force and the vertical direction balancing connector 3 of frame, tie-rod 8 is as much as possible little with the Remnant inertia force not fallen by half weighing apparatus of total parts of planetary gear 10, four balance connectors 3 add two tie-rods 8 and two planetary gears 10 two total parts gross weight outline be slightly larger than the weight sum of connecting rod 1 and work housing 17.
Because C point is the center of gravity that balancing connector 3 adds total parts of tie-rod 8 and planetary gear 10, thereby balancing connector 3 total parts of adding tie-rod 8 and planetary gear 10 are made around C point the centrifugal force that the rotation reverse with slave spindle produce and are equaled another. centrifugal force when slave spindle 6 rotates on slave spindle 6 be tie-rod 8 be arranged on that the centrifugal force of hole on slave spindle 6 and middle groove (as Fig. 8 and Fig. 9) generation of opening of slave spindle 6 and fan-shaped balance weight 11 produced centrifugal force sum, this centrifugal force minute dynamic balance work housing 17 in the horizontal direction and total inertia force of stand connecting rod 1 generation when slave spindle 6 rotates, minute dynamic balance balancing connector 3 in the vertical direction adds total inertia force that total parts of tie-rod 8 and planetary gear 10 produce.
Because B point and C point are done moving both vertically of quadrature, the weight of frame can be regarded as and concentrates on B point, and C point to be balancing connector 3 add that tie-rod 8 can be regarded as a double-slider mechanism with center of gravity thereby the mechanism of total parts of planetary gear 10, and the kinetic energy sum of two slide blocks each position angle in motion process will remain constant in double-slider mechanism, the instantaneous angular velocity of slave spindle remains constant, the instantaneous moment of inertia of each position angle is equal to separately. and in fact because two rolls in frame also rotate, balancing connector 3 add tie-rod 8 with the center of gravity C of total parts of planetary gear 10 except also rotating around center of gravity C point moving linearly in the vertical direction, thereby be not that in simple double-slider mechanism, the motion of two slide blocks thereby the instantaneous angular velocity of slave spindle are not to remain constant, the instantaneous moment of inertia of each position angle is not to be equal to separately, only very little, the no-load power consumption that overcomes instantaneous moment of inertia is also very little, thereby the characteristics of motion of said structure and another part has greatly reduced the fluctuation of the kinetic energy sum of total another part of motion in whole system, thereby greatly reduced the fluctuation of the instantaneous angular velocity of slave spindle 6, greatly reduced the upper instantaneous moment of inertia of slave spindle 6, also greatly reduced to overcome the no-load power consumption of instantaneous moment of inertia simultaneously.
Accompanying drawing explanation
Fig. 1 is the tie-rod angle setting f=30 that rotate in place 0time balancing connector 3 and the mutual alignment figure of fan-shaped balance weight 11 and ring gear 9 and planetary gear 10 and stand connecting rod 1.
Fig. 2 is the tie-rod angle setting f=90 that rotate in place 0time balancing connector 3 and the mutual alignment figure of fan-shaped balance weight 11 and ring gear 9 and planetary gear 10 and stand connecting rod 1.
Fig. 3 is the tie-rod angle setting f=120 that rotate in place 0time balancing connector 3 and the mutual alignment figure of fan-shaped balance weight 11 and ring gear 9 and planetary gear 10 and stand connecting rod 1.
Fig. 4 is the tie-rod angle setting f=150 that rotate in place 0time balancing connector 3 and the mutual alignment figure of fan-shaped balance weight 11 and ring gear 9 and planetary gear 10 and stand connecting rod 1.
Fig. 5 is the tie-rod angle setting f=180 that rotate in place 0time balancing connector 3 and the mutual alignment figure of fan-shaped balance weight 11 and ring gear 9 and planetary gear 10 and stand connecting rod 1.
Fig. 6 is the plane structure chart of Planetary Gear Transmission tandem-driving bogie technical scheme 1 single planetary gear transmission case device option A, is also the main plane structure chart of the present invention.
Fig. 7 is the Planetary Gear Transmission tandem-driving bogie technical scheme 1 single planetary gear transmission case device option A tie-rod angle setting f=0 that rotate in place 0time facade structures figure.
Fig. 8 is the plane structure chart of Planetary Gear Transmission tandem-driving bogie technical scheme 1 single planetary gear transmission case device option b.
Fig. 9 is the plane structure chart of Planetary Gear Transmission tandem-driving bogie technical scheme 1 single planetary gear transmission case device scheme C.
Figure 10 is the plane structure chart of Planetary Gear Transmission tandem-driving bogie technical scheme 2 dual planetary gear transmission case device option As.
Figure 11 is double-slider mechanism transmission principle figure
Figure 12 is the plane structure chart of the double-slider mechanism transmission tandem-driving bogie device being comprised of 2 double-slider mechanisms corresponding to transmission tandem-driving bogie technical scheme 2 transmission case device option bs.
In Fig. 1-12:
1-stand connecting rod; 2-stand connecting rod bearing; 3-balancing connector; 4-tie-rod bearing; 5-gear wheel; 6-slave spindle;
7-slave spindle bearing; 8-tie-rod axle; 9-ring gear; 10-planetary gear; The fan-shaped balance weight of 11-; 12-block; 13-pinion;
14-driving shaft; 15-drive shaft bearing; 16-shaft coupling; 17-work housing; 18-connecting rod connecting pin; 19-wear-resistant slide plate;
20-slide block; 21-slipper bearing; 22-slipper bearing bearing pin.
Specific embodiments of the invention are:
1) the one single planetary gear transmission case device option A of the technical scheme shown in Fig. 6 and 7.
2) the one single planetary gear transmission case device option b of the technical scheme shown in Fig. 8.
3) the one single planetary gear transmission case device scheme C of the technical scheme shown in Fig. 9.
4) the two dual planetary gear transmission case device option As of the technical scheme shown in Figure 10.
5) the two double-slider mechanism transmission tandem-driving bogie device option bs of the technical scheme shown in Figure 12.
The specific embodiment
For middle-size and small-size cold tube-rolling mill, for saving manufacturing cost, can adopt the technical scheme one single planetary gear transmission case device option A as shown in Fig. 6 and 7 as the main drive of φ 25 cold tube-rolling mills and φ 60 cold tube-rolling mills, or the one single planetary gear transmission case device option b of the technical scheme shown in employing Fig. 8, or the one single planetary gear transmission case device scheme C of the technical scheme shown in employing Fig. 9, by a connecting rod, drag whole work housing, although this kind of scheme inertia force almost can the overwhelming majority be balanced, the Remnant inertia force not being balanced existing after balance is very little, moment of inertia on slave spindle 6 is very little, thereby it is less to overcome the required no-load power consumption of instantaneous moment of inertia, utilization rate of electrical is very high, but because the center line of fan-shaped balance weight 11 and the center line of work housing 17 exist larger mistake distance, also there is wrong distance in the center line of the parts that in fan-shaped balance weight 11 center lines and transmission case, balance connector 3 tie-rods 8 and planetary gear 10 form, so will produce larger alternation moment in the Equipment Foundations of single file star transmission case device when slave spindle 6 rotates, Remnant inertia force and the minimum of the Remnant inertia force square on slave spindle for making not to be balanced in the situation of employing single assembly, the gross weight outline of the assembly that 2 balancing connectors 3 and tie-rod 8 and the planetary gear 10 on two limits forms is slightly larger than the gross weight of work housing 17 and 1 addition of single connecting rod.
For big-and-middle-sized cold tube-rolling mill as φ 60 with the main drive of cold tube-rolling mill can adopt the technical scheme two dual planetary gear transmission case device option As shown in Figure 10, by two connecting rods, drag whole work housing, this kind of scheme not only inertia force almost can the overwhelming majority be balanced, the Remnant inertia force not being balanced existing after balance is very little, the larger mistake distance of center line existence due to fan-shaped balance weight 11 center lines and work housing 17, also there is wrong distance with the center line of the parts that planetary gear 10 forms in balance connector 3 tie-rods 8 in fan-shaped balance weight 11 center lines and Planetary Gear Transmission case, so larger alternation moment producing in the Equipment Foundations of single planetary gear transmission case device when slave spindle 6 rotates. but when adopting dual planetary gear transmission case device, the alternation moment producing on two the Planetary Gear Transmission case apparatus in left and right is opposite sign but equal magnitude just in time, cancel out each other on the base plate of two the Planetary Gear Transmission case apparatus in left and right, thereby equipment is very low to basic requirement, can save a civil engineering costs, adopting the situation of two transmission tandem-driving bogie devices to divide into timing is to make the Remnant inertia force and the minimum of the Remnant inertia force square on slave spindle that are not balanced, the gross weight outline of the assembly that four balancing connectors 3 on two limits and two tie-rods 8 and two planetary gears 10 form is slightly larger than work housing 17 and two gross weights that connecting rod 1 is added.
For super-huge cold tube-rolling mill, can adopt the technical scheme two double-slider mechanism transmission tandem-driving bogie device option bs as shown in Figure 12 as the main drive of φ 280 cold tube-rolling mills, while dragging the design of whole very heavy work housing by two connecting rods, make the center of gravity of the assembly that balancing connector 3 tie-rods 8 and slide block bearing pin form still drop on C point, during design, be make the Remnant inertia force that is not balanced and the Remnant inertia force square on slave spindle minimum, the gross weight outline of four balancing connectors 3 on two limits and two tie-rods 8 and two slide blocks 21 and two slide block bearing pins 11 is slightly larger than work housing 17 and two gross weights that connecting rod 1 is added.
Beneficial effect
1) almost can complete equipilibrium work housing 17 with the inertia force of connecting rod 1 and the parts that formed by balance connector 3 tie-rods 8 and planetary gear 10, therefore machine vibration skinny device basic stress is very little, the reciprocating motion number of times per minute of the work housing of cold pilger mill is very high, the technical scheme that adopts said structure is installed the inertia force that centrifugal force sum that the hole of tie-rod axle produces not only can balance the weight generation of work housing 17 and connecting rod 1 in the horizontal direction when planetary gear 10 tie-rods 8 go to each position angle in fan-shaped balance weight 11 and slave spindle, and can balance in the vertical direction the inertia force of the parts that formed by balance connector 3 tie-rods 8 and planetary gear 10, as adopt dual planetary gear transmission tandem-driving bogie scheme, the larger mistake distance of center line existence due to fan-shaped balance weight 11 center lines and work housing 17, also there is wrong distance in the center line of the parts that in fan-shaped balance weight 11 center lines and transmission case, balance connector 3 tie-rods 8 and planetary gear 10 form, so the alternation moment producing on two Gear Planet Transmission case apparatus about when slave spindle 6 rotates is opposite sign but equal magnitude just in time, the Equipment Foundations of can cancelling out each other on base plate are stressed hardly, thereby the main drive gear of this Planetary Gear Transmission is very low to the requirement of Equipment Foundations, can greatly save the expense of foundation of civil work. as compared with the VE transmission cold tube-rolling mill that is all high-speed and energy-saving type cold tube-rolling mill, more can save a very dark expensive foundation of civil work expense.
2) adopt main drive gear of the present invention as the main drive gear of cold tube-rolling mill, the moment of inertia producing on slave spindle 6 is minimum, thereby it is very little to overcome the required no-load power consumption of moment of inertia, even also like this under high speed. under equal conditions, the moment of inertia producing on slave spindle 6 with overcome the required no-load power consumption of moment of inertia and be even less than general low speed cold tube-rolling mill and also belong to the VE cold tube-rolling mill of high-speed and energy-saving type, utilization rate of electrical is high, the motor of smaller power can be adopted, and many electricity charge spendings can be saved every year.
Example for two φ 60 cold pilger mills illustrates:
A crank linkage for driving with a two-or three-axis balanced φ60 cold rolling mill n = 140rpm instantaneous moment of inertia of the spindle between +113043- ---- 110166NM hourly fluctuations need to overcome this moment of inertia energy consumed about 235.3 kilowatts hour / hour, while for vertical balanced φ60 cold rolling mill for n = 140rpm instantaneous moment of inertia of the spindle between +29687- ---- 49475.6NM hourly fluctuations overcome this moment of inertia consumption of electricity required approximately 65.2 kWh / h, while for the use of cold rolling mill shown φ60 work double planetary gear rack box device reciprocating balance per minute up to 140 beats / min X. when n = 140rpm instantaneous moment of inertia when the spindle between +2938.4 ----- 2938 .4 NM hourly fluctuations in the moment of inertia to overcome this consumes power (no load power consumption) approximately 13.7 kWh / hour.
The φ 60 cold pilger mill design the highest reciprocating stroke number of times per minute that B produces is at present that 83 beats/min of no-load power consumptions are about 49.6 kilowatt-hours/hour, adopt 200 kilowatts of main motors, if adopt φ 60 cold pilger mills to add that on the basis of toggle balance weight reaches the technical scheme of main shaft high speed rotating, if no-load power consumption is about 149.9 kilowatt-hours/hour when the highest reciprocating stroke number of times per minute is 120 beats/min. adopt the technical scheme of the single planetary gear transmission tandem-driving bogie device shown in figure six figure seven, φ 60 cold pilger mill design the highest reciprocating stroke number of times per minute also can reach 120 beats/min of no-load power consumptions now and only be about 8.73 kilowatt-hours/hour, still can adopt 200 kilowatts of main motors.

Claims (4)

1. the transmission system for Pilger cold pilger mill, this transmission system has: a rolling-mill housing that can move back and forth back and forth (17), at least one planetary gear mechanism, move back and forth the inertia force of working stand by fan-shaped balance weight (11) balance on the main shaft (6) of Planetary Gear Transmission, this class milling train is characterised in that structure is that employing pitch radius is R xplanetary gear (10) in pitch radius, be 2R xring gear (9) in make pure rolling, together with planetary gear (10) is installed on key with tie-rod (8), tie-rod (8) is contained in a cylindrical hole in main shaft, 2 bearings (4) are housed in cylindrical hole, tie-rod (8) is upper respectively fills a balancing connector (3) on one side by key connecting, tie-rod (8) is through a key connecting assembling planetary gear (10) for balancing connector (3) on one side, the upper connecting rod connecting pin (18) that links frame of installing by key connecting of balancing connector (3) at another side, the upper bearing (2) of installing of connecting rod connecting pin (18), balancing connector (3) is designed on one side for rectangle another side is designed to semicircle, a upper fan-shaped balance weight (11) and the gear wheel (5) installed of slave spindle (6), the direction that fan-shaped balance weight (11) is installed is in the direction of the extended line of the center A line of tie-rod (8) center O and slave spindle (6), the centrifugal force of the hole that tie-rod axle is installed on fan-shaped balance weight (11) and slave spindle generation during with the rotation of the groove on the main shaft inertia force that the gross weight of balance work housing and stand connecting rod produces in the horizontal direction, the inertia force that the weight of balance tie-rod planetary gear and balancing connector assembly produces in the vertical direction.
2. the transmission system for Pilger cold pilger mill as claimed in claim 1, it is characterized in that: for the remaining inertia force not being balanced that makes to exist after balance is less than as much as possible as making the upper remaining moment of inertia not being balanced existing of slave spindle after balance (6) as much as possible little, for two balancing connectors of single planetary gear transmission device (3), add that the gross weight outline of total parts that a tie-rod (8) and a planetary gear (10) form is slightly larger than the weight sum of a connecting rod (1) and a work housing (17), for dual planetary gear transmission tandem-driving bogie device, be make two connecting rods (1) that are not balanced that exist of horizontal direction and the Remnant inertia force of a work housing (17) and vertical direction after balance as much as possible little with the total Remnant inertia force not being balanced of two parts of two planetary gears (10) by (3) two tie-rods of four balancing connectors (8), four balancing connectors (3) add two tie-rods (8) and two planetary gears (10) two total parts gross weight outline be slightly larger than the weight sum of two connecting rods (1) and a work housing (17).
3. the transmission system for Pilger cold pilger mill as claimed in claim 1 or 2, it is characterized in that: for the remaining inertia force not being balanced that makes to exist after balance as much as possible little with for making the remaining moment of inertia not being balanced of existence slave spindle after balance (6) on as much as possible little, for single planetary gear transmission tandem-driving bogie device when doing the configuration design of balancing connector (3), make two balancing connectors in left and right (3) add that the center of gravity of the parts that tie-rod (8) and planetary gear (10) form just in time drops on C point, be that C point is the center of gravity that balancing connector (3) adds the parts that tie-rod (8) and planetary gear (10) form, each distance apart from the center O of tie-rod 8 of C point and stand connecting rod pin center B is R x180 ° of the center O phase phasic differences of B point and C point and tie-rod 8, while doing the configuration design of balancing connector (3) for double-planetary transmission device, for each single planetary gear transmission device, make two balancing connectors in left and right (3) add that the center of gravity of the parts that tie-rod (8) and planetary gear (10) form also just in time drops on C point, C point is the center of gravity that balancing connector (3) adds the parts of tie-rod (8) and planetary gear (10).
4. the transmission system for Pilger cold pilger mill as claimed in claim 1, is characterized in that: slave spindle (6) is done horizontally disposed, and balancing connector (3) rotates on the vertical plane being parallel to each other with fan-shaped balance weight (11).
CN201010259015.1A 2010-08-20 2010-08-20 Planet gear and double sliding block transmission device of high-speed and energy-saving pipe cold rolling mill Active CN102371276B (en)

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CN103234016A (en) * 2013-05-06 2013-08-07 扬州大学 Long-range hypocycloid mechanism
CN112178143B (en) * 2020-09-22 2021-08-10 青岛理工大学(临沂)管理委员会办公室 Crank block mechanism capable of controlling balance inertia force

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