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Drive system for cold rolling pilger mill

IPC classes for russian patent Drive system for cold rolling pilger mill (RU 2247613):

B21B21 - Pilgrim-step tube-rolling

Another patents in same IPC classes:

Method for making hot deformed and conversion mean- and large-diameter tubes of corrosion resistant hard-to-form steels and alloys in tube rolling aggregate with pilger mills / 2247612
Method comprises steps of drilling electroslag-refining ingots or billets with diameter 380-500 mm; holding them on grates of furnace at temperature 500-550°C for 70-95 min depending upon diameter of blank; heating up to temperature 1120 - 1140°C at rate 1.4 - 1.5 °C/min; piercing billets for forming sleeves at revolution number of rolling rolls 25 - 40 rev/min on mandrel with diameter providing reduction degree in pilger mill no less than 25 mm; realizing first piercing of electroslag-refining ingots or billets with diameter 460-600 mm in piercing mill at elongation degree 1.2 -1.4 and at revolution number of rolling rolls 15 -25 rev/min; realizing second and next (if necessary) piercing or expanding processes at diameter fit no more than 5.0%, elongation degree 1.4 -1,75 and revolution number of rolls 25 - 50 rev/min; seasoning cold sleeves after their first piercing with diameter 460-600 mm at relation D/S = 3.0 -4.5 on grates at temperature 400-500°C for 50 - 70 min depending upon sleeve diameter and wall thickness; heating sleeves until yielding temperature 1100 - 1260°C at rate 1.6 - 1.8°C/min depending upon kind of steel; uniformly heating sleeves with temperature 600 - 800 C after piercing mill until yielding temperature 1100 - 1260°C at rate 1.7 - 2.0°C/min; before discharging sleeves out of furnace keeping them for 45 -60 min at plasticity temperature while tilting sleeves in 10-15 min by angle 180є. Process of piercing sleeves that begins from gripping ingots or billets until their complete fitting onto mandrel is realized at decreased revolution number of rolling rolls from 25 until 15 rev/min. Stable piercing process is performed is realized at 15 -20 rev/min. At outlet of sleeve revolution number of rolls is increased up to 35 -40 rev/min. Piercing (expanding) process beginning from gripping sleeve until complete fitting of it onto mandrel is realized at decreased revolution number of rolling rolls from 50 until 20 rev/min. Stable expanding process is realized 20-25 rev/min. At outlet of sleeve revolution number of rolls is increased up to 45 - 50. Tubes are rolled in pilger mill at elongation degree μ = 3.0 - 5.0. Invention provides possibility for making high quality hot deformed tubes of large and mean diameters from corrosion resistant hard-to-form steels and alloys in tube rolling aggregates with pilger mills.

Method for preparing rolls of pilger mills for hot rolling of tubes / 2246364
Method comprises steps of mechanically working portion of roll in roll-turning machine tool with use of contour follower for surfacing it with overlap 5 - 10° to side of cold portion from zero point and from angle of lengthwise outlet; under-flux surfacing working portion with wear-resistant refractory steel layer having allowance for mechanical working; mechanically working rolls with use of contour follower until their ready size and grinding working surface. Mechanical working of rolling portion of roll after surfacing is performed along portion from 0.25 - 0.30 of striker length until end of angle of lengthwise outlet adjoined to polishing portion. Grinding of polishing portion and of 0.25 - 0.30 of angle of lengthwise outlet adjoined to polishing portion is realized. Mechanical working of rolling portion of roll for surfacing from zero point until 0.25 -0.30 of striker portion is performed while taking into account allowance of surfaced layer for finish working.

Method for making hot-deformed seamless large-diameter tubes / 2243837
Method comprises steps of heating ingots and billets until yielding temperature; piercing them to hollow thick-wall sleeves in first skew rolling mill for further expanding to thin-wall sleeves in second skew rolling mill and rolling to large-diameter tubes in plants provided with automatic or pilger mills; piercing ingots and billets to thick-wall sleeves in first piercing mill with working rolls driven to rotation in one side and expanding billets to thin-wall sleeves in second piercing mill with working rolls driven to rotation in opposite side.

Drive system for cold rolling pilger mill / 2247613
Drive system includes rolling stand that may perform reciprocation motion; at least one crank and connecting rod mechanism operated by means of drive unit and having crank arm with balancing weight at least for partially balancing inertia forces created by rolling stand; connecting rod jointly connecting rolling stand and crank arm; at least one arranged eccentrically and driven to rotation counter-balance for balancing inertia forces and (or) moments of inertia. Motion of crank and connecting rod mechanism and counter-balance is synchronized by means of gearing. At least one crank and connecting rod mechanism is provided with single counter-balance. Motion plane of balancing weight of crank and connecting rod mechanism driven to rotation coincides with motion plane of counter-balance driven to rotation. Crank and connecting rod mechanism, counter-balance and drive unit are mutually joined through gearing. Drive unit through said gearing drives shaft joined with counter-balance. Mounted on shaft pinion of said gearing through other gearing drives shaft joined with crank and connecting rod mechanism. Balancing weight or counter-balance is in the form of eccentrically arranged mass of one gear wheel of gearing.

Drive system of rolling mill / 2247614
Drive system includes at least one rolling stand mounted with possibility of reciprocation motion; at least one crank and connecting rod mechanism having crank arm with balancing weight at least for partially compensating inertia forces of rolling stand; drive unit and connecting rod jointly connecting rolling stand and crank arm; at least one counter-balance mounted with possibility of eccentric rotation in order to compensate inertia forces and (or) moments of inertia. In order to provide effective compensation of inertia forces in simplified drive system, at least one counter-balance is mounted with possibility of driving it to rotation by means of autonomous drive unit isolated from drive unit of crank and connecting rod mechanism. Said autonomous drive unit of counter-balance acts in rotation direction opposite to rotation direction of crank arm. Mass values of mass of rolling stand, balancing weight, counter-balance are selected in such a way that to compensate as possible first-order components of inertia forces of rolling stand at operation of drive system. System is provided with unit for controlling or regulating autonomous drive unit depending upon angle ϕ₆ and (or) revolution number of crank arm. Rotation center of counter-balance is selected in such a way that including inertia forces of rolling stand and (or) balancing weight moments of inertia of all masses of drive system are at least significantly compensated.

Method for making conversion tubes of low-ductility boron-containing steel / 2255820
Method comprises steps of drilling ingots of electroslag refining, heating them till ductility temperature, piercing in piercing mill for making sleeves; rolling sleeves in pilger mill to tube-blanks, cooling, repairing, cutting tube-blanks by two blanks, heating them up to ductility temperature, piercing-rolling in piercing mill and rolling conversion tubes in pilger mill. Ingots of electroslag refining with diameter 460 - 480 mm are drilled from their bottom end along length L = H - B, where H - height of ingot, mm; B - under-drilled part of ingot equal to 100 - 120 mm. Then ingots are soaked at temperature 450 - 500°C on grates of heating furnace without tilting for 90 - 120 min; heated till 800 - 850° C at rate 1.8 - 2.0°C/min; then heated up to ductility temperature 1050 - 1090°C at rate 2.1 - 2.2°C/min at tilting in 15 - 20 min and soaked at such temperature for 70 - 80 min at tilting by angle about 180° in 10 -15 min.

Roll for die rolling of cone elongated hollow metallic articles / 2255821
Roll for die rolling includes along circle of its barrel round cross section groove with outlets. Length of said groove includes successively arranged striker formed by radius of roll ridge of increased length, having constant angles of cross outlet in one third of striker length and smoothly lowered in its remaining part till outlets of polishing portion ( radius of roll ridge in end of portion with constant value of cross outlet consists 1.3 of radius of roll ridge in the beginning of said portion), polishing portion with constant radius of roll ridge, transition portion and idle portion. Round variable groove pass with cross outlets is arranged along helical line on cylindrical surface of roll with ideal diameter. Number of pitches of helical line is determined as n = (L sin α)/(2πR_r) + B + B_{1 ,} where L - length of cone article, mm; R_r - rolling radius of roll, mm; α -inclination angle of axis of roll grooved pass relative to axis of roll, °; B - length of idle portion at inlet equal to (0.20 - 0.25)n; B₁ -length of idle portion at outlet equal to (0.10 -0.15)n. Semipass of upper roll has left-hand and semipass of lower roll has right-hand direction of helical line or vice versa. Groove of roll is half round one with cross tangential or oval outlets with angles 30 - 32°. Values of said angles are constant ones, they are equal to 30 -35° for central angle and they are smoothly decreased to outlet cross section to 20 - 18°.

Method for making elongated conversion large- and mean- diameter tubes of centrifugally cast hollow billets and electroslag refining ingots of steels for telescopic systems (periscopes of submarines) / 2257271
Method comprises steps of producing centrifugally cast billets, heating them till ductile temperature, rolling in pilger mill to thick-wall tubes with allowance for mechanical working, subjecting tubes to heat treatment. In pilger mill conversion hot rolled tubes are rolled while taking into account 1 - 3 rerolling procedures in cold rolling mills depending upon type of billet and dimension of ready product (length, diameter, wall thickness). Conversion hot rolled tubes are rolled to intermediate and final sizes in cold rolling mills at elongation value μ = 1.2 - 1.55. Centrifugally cast hollow billets and drilled ingots of electroslag refining are soaked on grates of furnace without tilting them at 950 -1000°C for 180 - 300 min of homogenization depending upon diameter and wall thickness. Then centrifugally cast billets are uniformly heated up to 1150 -1200°C at heating rate 2.3 - 2.5° C/min at tilting in periods of 15 - 20 min at total period of heating 8 - 11 hours. Ingots of electroslag refining are heated up to 1200 -1250°C at heating rate 1.8 - 2.0°C/min while tilting them in 20 - 25 min for total heating period 9.5 - 12.5 hours. Large-size billets and ingots are heated for more long periods. Centrifugally cast hollow billets are rolled in pilger mill to hot rolled conversion tubes while taking into account 2 - 3 next rerolling of them in cold rolling mills. Sleeves pierced of ingots are rolled in pilger mill to conversion hot rolled conversion tubes while taking into account 1 - 2 rerolling processes in cold rolling mills. Ingots with diameter up to 500 mm are pierced in skew rolling mill to sleeve at one piercing operation with elongation value μ = 1.2 - 1.4. Ingots with diameter 540 mm and more are pierced at two piercing operations with elongation value μ₁ = 1.2 -1.4 and μ₂ = 1.1 - 1.3 respectively. Conversion elongated cold rolled tubes after rolling them to intermediate size are subjected to austenitization in mode providing temperature of furnace space at time moment of charging in range 1000 - 1100°C, heating according to power of furnace up to 1050 ± 15°C, soaking at such temperature for 1 min per 1 mm of tube wall thickness and cooling in air. Conversion elongated cold rolled tubes of ready size after rolling and austenitization are subjected to heat treatment - tempering in mode providing charging at 700 - 730°C; heating according to power of furnace; soaking at temperature 685 ± 15°C for 5 - 5.5 h; cooling in air.

Method for balancing crank-gear drive motor torque / 2260898
Proposed method that can be used to control systems incorporating frequency converter with off-line voltage inverter and induction motor operating into mechanisms handling alternating cyclic load (deep-well pimps, crank gear drive mechanisms, and the like) involves automatic correction of motor speed as function of voltage deviation in dc current section from maximal permissible value which makes it possible to dispense with energy dissipating and rectifying devices affording recuperation mode.

FIELD: drive systems of cold rolling pilger mills.

SUBSTANCE: drive system includes rolling stand that may perform reciprocation motion; at least one crank and connecting rod mechanism operated by means of drive unit and having crank arm with balancing weight at least for partially balancing inertia forces created by rolling stand; connecting rod jointly connecting rolling stand and crank arm; at least one arranged eccentrically and driven to rotation counter-balance for balancing inertia forces and (or) moments of inertia. Motion of crank and connecting rod mechanism and counter-balance is synchronized by means of gearing. At least one crank and connecting rod mechanism is provided with single counter-balance. Motion plane of balancing weight of crank and connecting rod mechanism driven to rotation coincides with motion plane of counter-balance driven to rotation. Crank and connecting rod mechanism, counter-balance and drive unit are mutually joined through gearing. Drive unit through said gearing drives shaft joined with counter-balance. Mounted on shaft pinion of said gearing through other gearing drives shaft joined with crank and connecting rod mechanism. Balancing weight or counter-balance is in the form of eccentrically arranged mass of one gear wheel of gearing.

EFFECT: lowered cost for maintaining simplified -design rolling mill, reduced investment cost.

11 cl, 10 dwg

The invention concerns a drive system for cold mill Pilerne rolling with reciprocating roaming rolling stand, at least one powered by a drive crank mechanism having a crank arm with balanced load for at least partial balancing of inertia forces that occur during operation of the mill, and rod that pivotally connects with each other the rolling mill and the crank arm, and at least one eccentrically seated, rotate the counterweight to balance the forces and/or moments of inertia, due to gearbox movement of the crank mechanism and counterweight is synchronized.

This type of drive for the mill cold Pilerne rolling is known from DE 4336422 C2. For cold polerowanie necessary rolling mill equipped with a pair of rolls for cold polerowanie, which is driven in an oscillatory motion. It uses a crank mechanism, which is driven by a motor. A crank mechanism is equipped with balanced load to align the forces of inertia of the rolling stands.

The output of the mill cold Pilerne rolling depends on the number of passes of the rolling stands per unit of time, so from economicallycompetent strive to make the maximum number of passes per minute. It also means large inertial forces that impinge on the drive system, in particular its bearings, and the Foundation, and thereby surrounding structures.

In the known patent DE 4336422 C2 provides that a crank mechanism due to the gearing results in the movement of these shafts are eccentric relative to the center of gravity is located balances. These balances are spinning during the rotation of the crank mechanism in the forward and backward directions and can create a balancing inertial forces or moments of inertia so that we achieve the complete balancing of inertia forces in the entire drive system.

A shortcoming of this implementation is that the design of the entire system drive get expensive due to the need for a large number of machine elements, connected by toothed gearing. Due to this increased the cost of the drive system and the whole mill cold Pilerne rolling, you should take into account not only the installation costs, but also the cost of Foundation installation, replacement of worn and spare parts, the cost of maintenance and repairs.

From DE-PS 962062 known drive system for cold mill Pilerne rolling, in which the crankshaft of the drive rolling stands is with centrifugal loads is oscillating in the vertical direction load balancing to balance the inertia forces of the first order, and moments of inertia in the drive.

The disadvantage of this solution is that the Foundation of the rolling mill is very costly and expensive, because it must be possible to dive balancing load to the Foundation. This requires a large and deep space, causing a corresponding increase in the cost of rolling mill.

In the patent DE 3613036 C1 describes a drive for a rolling mill stand the cold Pilerne rolling, in which a planetary crank mechanism to drive and balance of forces and moments of inertia.

Although, with this solution, can be achieved optimal balancing of masses, this drive is only applicable for small mills cold Pilerne rolling, as in the case of large installations, the size of the drive system disproportionately increases, which causes a corresponding increase in value.

All known drive system for cold-pilgern rolling have the significant disadvantage that relatively high costs required for the reduction of forces or moments of inertia, which leads to high investment costs and the cost of the Foundation and/or expensive operations in the construction, repair and maintenance of rolling mill.

It should be noted that the known is s earlier partly quite expensive in the performance of the system for balancing forces and moments of inertia are sometimes absolutely unnecessary, if they are used modern, high-quality machine elements that can perceive relatively high load.

The basis of the invention lies in the task of creating a possible simple and appropriate for the cost of construction of the drive system for this type of cold-pilgern rolling, which may limit to a reasonable level of forces and moments of inertia.

This problem is solved according to the invention in such a way that at least one of the crank mechanism works only one opposed, with the plane in which the rotation of the moving load balancing of the crank mechanism, and the plane in which it moves during the rotation of opposed, identical.

This implementation achieves a very simple design of drive system for cold mill Pilerne rolling. Despite this, it is sufficient balancing forces and moments of inertia that creates an acceptable operating condition of the mill.

According to the first improvement provides that the crank mechanism, the counterweight and the drive are connected to each other via a gear, the drive che is ez gear rotates the shaft, which is connected to the counterweight, and the pinion gear located on the shaft through the other gear rotates the shaft, which is connected to a crank mechanism.

Predominantly provided that the shaft of the crank mechanism, the counterweight shaft and the drive shaft lie in the same plane, thus, can be implemented in a particularly simple and easily mounted design.

According to the first constructive implementation of the drive system of rolling mill and a single crank mechanism can be connected through a single connecting rod. It is recommended particularly simple structure, when the connecting rod is mounted on the crank mechanism of the console.

When the alternate form of the rolling mill and a single crank mechanism may be interconnected by two connecting rods, which are installed the console on both sides of the crank mechanism. It mostly can be provided that the median plane (plane of symmetry) rolling stands and the median plane (plane of symmetry) of the crank mechanism are identical. Next, mainly that of the median plane (plane of symmetry) of the crank mechanism and the median plane (plane of symmetry) counterweight Eden is icny.

Further alternative implementation provides that the rolling mill and two located on either side symmetrically to the median plane of the rolling stands of the crank mechanisms are interconnected by two connecting rods. This further can be provided that the drive connects via gears both of the crank mechanism and both the counterweight, while the gears are located laterally next to one of the crank mechanism.

For all forms of execution advantage was that balancing the load and/or the counterweight installed as eccentric mass located in one of the pinion gears.

The shaft of the crank mechanism, the counterweight and the drive can be positioned vertically or horizontally.

Attaches great importance to efficient and effective automatic distribution of bearings connecting rod bearings or work rolls in the rolling mill stand. Therefore according to a further improvement provides that the connecting rod is installed on the supporting neck, with at least one supporting the neck is provided with a hole for grease in the bearing seat between the rod and the root neck.

For optimal functioning of the drive system is proposed that wt is s rolling stands, balancing load (or loads) and counterweight (or balances) were chosen so that the force of inertia of the cage of the first order during operation of the drive system, at least mostly balanced.

The proposed drive system for cold mill Pilerne rolling is characterized by a simple design, which enables cost-effective construction and operation of the rolling mill. The quality of trim masses at the same time quite good, allowing you to get high quality pipes. The drive system operates with a relatively small vibrations, thus, the Foundation and other surrounding structures work in a sparing mode. The drive system is reliable and has a long service life, cost of repairs and maintenance is low.

Construction costs for the drive system is low due to the proposed design. In the same way, there are no special requirements to the Foundation.

The drawings depict examples of carrying out the invention. Shown:

On figa - schematic side view of a pair of rolls for cold Pilerne rolling during a forward pass of the process of cold Pilerne rolling;

On fig.1b - appropriate type according figa during the backward pass;

On figa - side view and

On fig.2b - sootvetstvujushij top view of the first form of execution of drive system for cold mill Pilerne rolling;

On figa - side view and

On fig.3b is the corresponding top view of a second form of execution of the drive system;

On figa - side view and

On fig.4b is the corresponding top view of the third form of execution of the drive system;

On figa - side view and

On fig.5b is the corresponding top view of the fourth form of implementation of the drive system.

On figa and 1b schematically depict the process of cold Pilerne rolling. It is used for fabrication or deformation of the pipe 22 with 23 pairs of rolls for cold Pilerne rolling, which is not shown here rolling stands. Processed tube 22 is fed to the mandrel 24. Rolling mill performs during the rolling process of the vibrational motion, the frequency of passages (oscillations) can be up to 300 per minute and more.

Tube 22 during the rolling process moves in the direction R feed. During the forward pass, the diagram of which is depicted in figa, a pair of rolls 23 for cold Pilerne rolling rotates in the direction R of the feed pipe 22, during the backward pass, the diagram of which is depicted in fig.1b, is the rotation of the 23 pairs of rolls for cold Pilerne rolling through the pipe 22 in the direction opposite to the direction R of filing (see directional arrow and move).

On figa and 2b schematically shows a system 1 drive for rolling tile is 2, in which is fixed a pair of rolls 23, depicted in figa and 1b, respectively, a side view and a top.

For cold Pilerne rolling mill stand 2 must perform an oscillatory motion, namely reciprocating motion. For this purpose, provided a crank mechanism 4, which has a shoulder 5 of the crank, at least one knee and eccentric located relative to the fulcrum balancing the load 6. A crank mechanism 4 and rolling whip 2 are connected by a connecting rod 7, which is hinged on the shoulder 5 of the crank, and on the rolling stands 2.

The oscillating actuator of the rolling mill stand 2 is organized as follows: in one common plane 25 adjacent to each other are installed on the three bearings of the shaft 12, 13 and 14. The shaft 14 is connected to the actuator 3, which is not illustrated, it may be the motor. The shaft 12 is installed in the eccentric located the counterweight 8. Finally, the shaft 13 is the backbone of the crank mechanism 4, as above. On each of the three shafts 12, 13 and 14 rigidly (non-rotation) are installed respectively on the cylindrical gear 9, 10 or 11. Gear 9 and gear 10 form a first gear, the gear 10 with the gear 11 to form the second gear. As can be seen from fig.2b, all gears 9, 10 and 11 without excluding the CDs are in engagement, so that the actuator 3 rotates with the shaft 14 causes the rotation of the shaft 13 and its associated counterweight 8. The shaft 12 drives through gears 9 and 10, the shaft 13 and thus crank mechanism 4.

When the system 1 of the drive shaft 12 and with it the counterweight 8 are rotated in the opposite direction to the crank mechanism 4 with the number of revolutions of the crank, this is the balancing masses.

It is important that the crank mechanism 4 corresponds to only one counterweight 8, and the rotation of the counterweight 8 is carried out synchronously with the rotation of the crank mechanism 4. Further, the plane 26 (fig.2b), which moves with the rotation of the load balancing 6 of the crank mechanism 4, and the plane 27 (fig.2b), which moves during the rotation of the counterweight 8, identical.

The simple design of the actuator is achieved by a crank mechanism 4, the counterweight 8 and the actuator 3 through gears 9, 10, 11 are interconnected. As already mentioned, the actuator 3 through gears 10, 11 rotates the shaft 12, which is connected to the counterweight 8, on the other hand, located on the shaft 12 of the gear 10, part of the gear 10, 11, rotates through the gear 9, the shaft 13, which is connected to a crank mechanism 4. The shaft 13 of the crank mechanism 4, the shaft 12 of the counterweight 8 and the shaft 14 of the drive 3 races is orogeny mainly in a common plane 25 (figa).

Balancing the load 6 and the counterweight 8 is designed in such a way that the inertial forces of the first order for a system consisting of rolling stands 2, balancing load 6 and the counterweight 8, are balanced when driving system 1 of the drive. Inertial forces of the second and higher order terms arising from the vibrational movement of the rolling stands 2 are not balanced. Also not taken any precautions to compensate for the torque arising under the action of centrifugal components of the gravity loads acting perpendicular to the direction of the thrust stand. This is also true for issues that arise because the resultant force of the inertia balancing cargo does not lie on the same line of action as equalizing the force of inertia of rolling stands.

The proposed drive concept has several lesser quality adjustment weights, than is the case in the prior art. This disadvantage, however, no effect on small plants, because the amplitude of the forces and moments that appear through the Foundation, are fairly minor. Only in the case of locations with particularly sensitive to fluctuations in soil may impact on surrounding structures. In this case also required with the known solutions in the analysis of fluctuations and the corresponding updat is a comparative measure.

In a particularly preferred embodiment of the design shown on figa or 2b, works with a single connecting rod 7, which is set console on a crank mechanism 4. Schematic location of the rod in the median plane 15 rolling stands provides or deep location of the system consisting of the crank mechanism 4, the counterweight 8 and the actuator 3 or the necessary deviation of manufactured pipe from the middle of the cage.

For economical operation of the mill cold Pilerne rolling, it is important to place the lubricant in the automatic mode bearings connecting rod bearings and the work rolls in the rolling mill stand. For this purpose, fig.2b very schematically, that the two holes 20 and 21 pass through the crank of the crank mechanism 4. Through these holes 20, 21 may be supplied grease in place the supports that connect the bearings 18 or 19 on rolling stands 2 or crank mechanism 4 with the connecting rod 7.

Thanks to the supply of lubricating oil through the holes 20, 21, is almost possible to avoid stopping production for lubricating the bearings, as this can be done many times during operation of the drive system. A special advantage that is achieved by using similar designs, that you can achieve reliable section is placed lubricating oil and cooling lubricant.

On figa and 3b shows an alternative implementation of the system 1 of the drive. Here the rolling stands 2 side are two of the connecting rod 7 and 7’, which in turn is attached to the side and console on a crank mechanism 4. The median plane 15 of the rolling stand 2, the median plane 16 of the crank mechanism 4 and the median plane 17 of the counterweight 8 are identical. This ensures that there are no unbalanced moments of inertia, when the mass of the rolling stands 2 or mass balancing load 6 and the counterweight 8 are moved relative to each other.

As you can see in figa, gears 9, 10, 11 are located below the Central plane of the cage. Balancing the load 6 in the depicted case is in the form of an eccentric located on the pinion gear 9 masses, balancing the load 6 is thus integrated into the gear 9. In the same way, the counterweight 8 is in the form of an eccentric mass located in the gear 10.

As you can see in figa and 4b, there departed from the principle of cantilever mounted on the crank mechanism 4 rods 7 or 7’: the connecting rods 7, 7’ are connected here with two crank mechanisms 4 and 4’. One of the crank mechanism 4 is located riparian unit consisting of gears 9, 10 and 10, 11, and the actuator 3. Each crank mechanism 4 S4’ balanced load 6 or 6’ corresponds to the counterweight 8 or 8’, which with the gear 9, 10, 11 is driven synchronously to balance the masses.

The resulting centrifugal forces are all balanced cargo 6, 6’ or counterweights 8, 8’ operates in the median plane 15 rolling stands due to the symmetrical design so that also lying in the median plane 15 by the force of inertia of the rolling stand 2 can be optimally balanced.

An alternative implementation according figa or 5b shows that can be implemented in the design in which the shafts 12, 13 and 14 are arranged vertically, in the solution shown in figure 2, 3 and 4, these shafts are located horizontally opposite.

The proposed system 1 drive has a very simple design that requires little investment. Further, relatively low and operating costs. On the other hand, perhaps a good balancing of inertia forces and moments of inertia that allows you to operate the mill cold Pilerne rolling almost without any hesitation and without additional high costs to achieve this. The mill has high reliability. Ensures the production of pipes of high quality at low cost.

List of used symbols

1 drive System

2 Rolling mill

3 Drive

4 Crank mechanism

4’ Cree is osobno-connecting rod mechanism

5, the crank arm

6 load Balancing

6’ load Balancing

7 Rod

7’ Rod

8 Contrast

8’ Contrast

9, 10 gears/Gearbox

10, 11 gears/Gearbox

9 Gear

10 Gear

11 Gear

12 Shaft

13 Shaft

14 Shaft

15 the Median plane (plane of symmetry) rolling stands

16 the Median plane (plane of symmetry) of the crank mechanism

17 the Median plane (plane of symmetry) counterweight

18 Supporting the neck

19 Supporting the neck

20 Hole

21 Hole

22 Pipe

23 Pair of rolls for cold Pilerne rolling

24 Arbor

25 Plane

26 Plane

27 Plane

R Direction of feed

1. The system (1) drive for mill cold Pilerne rolling, containing a reciprocating roaming rolling mill (2)at least one powered actuator (3) a crank mechanism (4), which has a shoulder (5) of the crank balanced load (6) for at least partial balancing of inertia forces generated by rolling stand (2)and the rod (7)which pivotally connects the rolling stand (2) and the shoulder (5) of the connecting rod, at least one eccentrically located rotate the counterweight (8) to balance the inertia forces and/or moments of the trade the AI, and the gear (9, 10), synchronizing the movement of the crank mechanism (4) and the counterweight (8), characterized in that a crank mechanism (4) given a single counterweight (8), with the plane in which moves during the rotation balancing weight (6) of the crank mechanism (4), and the plane in which moves during the rotation of the counterweight (8), are identical.

2. The drive system according to claim 1, characterized in that a crank mechanism (4), the counterweight (8) and the actuator (3) are connected through gears (9, 10, 11), the actuator (3) through the transmission gear (10, 11) actuates a shaft (12), which is connected to the counterweight (8), and located on the shaft (12) gear (10) gear (10,11) through a gear (9) actuates a shaft (13), which is connected to a crank mechanism (4).

3. The drive system according to claim 2, characterized in that the shaft (13) of the crank mechanism (4), the shaft (12) of the counterweight (8) and shaft (14) of the actuator (3) are located in one plane.

4. The drive system according to claim 2, characterized in that the plane (15) of symmetry of the rolling stands (2) and the plane (16) symmetry of the crank mechanism (4) are identical.

5. The drive system according to claim 4, characterized in that the plane (16) symmetry of the crank mechanism (4) and the plane (17) of symmetry of the counterweight (8) are identical.

6. With the stem of the actuator according to any one of claims 1 to 3, characterized in that the rolling stand (2) and two located on the sides symmetrically relative to the plane (15) of symmetry of the rolling stands (2) of the crank mechanism (4, 4') are connected to each other by means of two connecting rods (7, 7').

7. The drive system according to claim 6, characterized in that the actuator (3) through gears (9, 10, 11) connects both of the crank mechanism (4, 4') and both the corresponding counterweight (8, 8')with gears (9, 10, 11) are arranged laterally next to a crank mechanism (4).

8. The drive system according to any one of claim 2 to 7, characterized in that balancing the load (6) and/or the counterweight (8) is in the form of an eccentrically located mass of one of the gears (9, 10) gears(9, 10, 11).

9. The drive system according to any one of p-8, characterized in that the shafts (12, 13, 14) of the crank mechanism (4, 4'), counterweight (8, 8') and the actuator (3) are arranged horizontally.

10. The drive system according to any one of p-9, characterized in that the shafts (12, 13, 14) of the crank mechanism (4, 4'), counterweight (8, 8') and the actuator (3) are arranged vertically.

11. The drive system according to any one of claims 1 to 10, characterized in that the rod (7, 7') is installed on the supporting neck (18, 19), with at least one support collar (18, 19) is provided with at least one aperture (20, 21) for supplying lubricating oil in place of raspologaetsya between the connecting rod (7, 7') and the bearing neck (18, 19).