EP3544750A1

EP3544750A1 - Adjusting cylinder quick adjustment in edging stands

Info

Publication number: EP3544750A1
Application number: EP17821463.1A
Authority: EP
Inventors: Stefan Wendt; Martin Schmidt; Michael Zielenbach
Original assignee: SMS Group GmbH
Current assignee: SMS Group GmbH
Priority date: 2016-11-22
Filing date: 2017-11-10
Publication date: 2019-10-02
Anticipated expiration: 2037-11-10
Also published as: US11117173B2; TW201825206A; CN110114154A; EP3544750B1; DE102016122521A1; CN110114154B; US20210170459A1; JP2020513322A; WO2018095465A1

Abstract

The invention relates to an adjusting cylinder quick adjustment (9) for long, fast stroke movements in edging stands, at least consisting of edging stands (20), adjusting system, balancing system, and edging roll sets, comprising at least one piston each, which operates via edging roll chocks (32, 33) of at least one edging roll (31) on both sides for adjusting against the rolled material (11) and wherein the adjustment of the edging roll (31) can be actuated on each side hydraulically by means of a fluid and the adjusting cylinder quick adjustment (9) is fastened in the edging stand (20) and applies the force required for the edging process. According to the invention, the adjusting cylinder quick adjustment (9) on each side of the edging stand (20) consists of at least one double cylinder (50), wherein the double cylinder (50) consists of two separately controllable cylinders, coupled to each other, and is designed first of all for quick adjustment and second of all for control adjustment of the edging roll (31).

Description

Anstellzylinderschnellverstellung

in compression frameworks

description

The invention relates to a Anstellzylinderschnellverstellung for long, fast strokes in edger stands, at least consisting of Staucherständer, Anstellsystem, Ausbalancierungssystem and compression roll sets, comprising at least one piston which acts on the upsetting roll chocks at least one upsetting roller on both sides for hiring against the rolling and the employment of the compression roll depending Hydraulically actuated side by means of a fluid and the Anstellzylinderschnellverstellung is mounted in the Staucherständer and applies the force required for the upsetting process.

The Anzustelleinrichtung in edger stands has the task to set the required roll gap, to hold and regulate if necessary. Here, the terms quick start and regular employment are used. The quick adjustment is used for quick opening or closing of the roll gap. The standard setting is the job in which ultimately the rolling force is transferred to the rolling stock with the roll gap previously set by the quick setting. The standard setting keeps the roll gap constant within a predefined value range. The system is only controlled by a compression roll balan- No clearance between the compression roller chock, cylinder head and the cylinder piston occurs.

In upsetting rigs, actuators are known as purely mechanical, purely hydraulic or as a combination of mechanical and hydraulic adjustment. Technically possible and useful is the arrangement of one or two jobs per page.

For example, a purely hydraulic adjusting device is known in edger stands at the roughing stamper of a hot strip mill. This is designed as a classic differential cylinder consisting of piston, cylinder cover and cylinder bottom.

This version has limits both in the required fluid requirement and thus in the traversing speed as well as in the transverse force sensitivity when the piston rod is fully extended.

From the document EP 1 687 104 B1 it is known to equip the adjusting cylinder with a second piston rod, so that each adjusting cylinder has a piston which is equipped with two piston rods facing in opposite directions, and the piston in each case a recess in the cylinder bottom or Cylinder cover is used, which have coaxially arranged bores for the passage of the piston rods. However, this solution has the disadvantage that for the required working speeds a very high

Pump power is needed.

From EP 2 41 1 165 B1 a device for edge rolling of metal plates is known. This device comprises a roller mounted on a block, comprising at least one edge-working hydraulic cylinder with a relatively large working surface, at least one further hydraulic cylinder being provided, having a relatively small working surface and each cylinder having an associated piston the pistons mechanically are coupled such that a movement of the one causes a movement of the other. The device requires a positive, possibly detachable for maintenance, connection between employment, Balancierzylinder and Balanciertraverse. This can lead to leaks at the joints again and again. Furthermore, inadmissibly high transverse forces can act on the cylinder piston, which can lead to damage of the piston rod and other guide elements. Which in turn leads to further leaks.

The document EP 2 265 395 B1 further discloses a type of telescopic cylinder having two oil columns connected in series on the rolling stock. The complete adjustment path can only be passed through by using both oil columns.

Furthermore, adjusting cylinders are known in compression frames (AWC cylinder) in so-called sequential circuit. These are technically very complex and must be kept in sync by additional valves.

In particular, in edger stands with a large opening width of Anstellsysteme, as required for example in heavy plate mills, there is a requirement the Anstellsysteme with a very high pitch of about 150 mm / sec to proceed. This is to be traversed within a short period of about 15 seconds of the entire Anstellweg. This is necessary, for example, in terms of process technology, since the ingots are turned in heavy plate mills to produce the required large width on an upstream rotary drive. As a result, when viewed in the rolling direction narrow ingot by turning on the rotary drive in the rolling direction then very wide.

So far, this fast Anstellgeschwindigkeit the employment is realized by a mechanical employment with electromechanical drive and air-operated brake. The mechanical adjustment accomplishes the coarse adjustment of the positioning system. As a rule, in addition to the mechanical employment one Fine employment required. This is designed as a hydraulic short-stroke adjustment and is responsible for the control operation with automatic width control and short-stroke control to reduce the loss of picking.

In this known system of mechanical / hydraulic employment a waiver of the mechanical adjustment and the execution of the Anstellsystems as purely hydraulic Langhubanstellung has not been economical, since it was not possible without providing correspondingly high pumping power and at the same time a simple execution of the hydraulic Langhubanstellung To realize required high Anstellgeschwindigkeiten.

It is therefore an object of the present invention to provide a quick adjustment within a compact system of hydraulic cylinders without having to design the hydropump station to be unnecessarily large. Even edger stands with smaller opening widths, as are customary, for example, in hot strip mills, the present invention can contribute to relieving the pumping station. So far, this has been accomplished by the so-called sequential circuit.

This object is achieved by the features specified in claim 1, in particular the fact that the Anstellzylinderschnellverstellung consists on each side of Staucherständers from at least one double cylinder, the double cylinder consists of two coupled separately controllable cylinders and on the one hand for Schnellanstellung and on the other is designed for the Regelanstellung the compression roll.

In this way, it is possible to realize a reliable quick adjustment of positioning cylinders, in particular in a compression frame by means of a purely hydraulic positioning system, comprising the Anstellzylinderschnellverstellung invention. This is in the cases of advantage, in which a long and fast cylinder stroke is required, the otherwise high capacity to the Require pumping power of the hydraulic systems. Furthermore, additional actuators such as the mechanical adjustment with the associated electrical components (displacement sensor, limit switch, positioning motor and corresponding infeeds) are saved. Furthermore, the use of double cylinders reduces energy consumption, which in turn increases the cost efficiency of the entire edger frame.

According to an advantageous embodiment of the Anstellzylinderschnellverstellung invention, it is provided that the cylinder piston of Schnellanstellung and the housing of Regelanstellung are connected to the same fixed shore of Staucherständers and additionally the housing of Schnellanstellung can be integrally formed with the piston rod Regelanstellung. In this case, a shore is understood to mean an abutment on which the forces implied by the setting cylinder quick adjustment and regulation adjustment are supported and ultimately transmitted to the rolling stock via the compression rollers. In the present case, the bank can include the Staucherständer with crosshead and the top and bottom arranged stand rails.

In a multi-part embodiment of the Anstellzylinderschnellverstellung invention, the cylinder piston of Schnellanstellung can be connected to the cylinder piston of Regelanstellung, while the housing of the Schnellanstellung can be connected to the same fixed bank of the housing Regelanstellung.

According to another multi-part embodiment of the Anstellzylinderschnellverstellung invention, it is provided that the cylinder housing of the Schnellanstellung is connected to the piston rod of Regelanstellung, while the cylinder piston of Schnellanstellung is connected to the same fixed bank of the housing Regelanstellung. In a further preferred embodiment, the Schnellanstellung and Regelanstellung can be designed independently controllable and triggered by the control movement of the housing of the Schnellanstellung or the cylinder piston, the movement of the cylinder piston the Regelanstellung then conditional. It is further contemplated that the cylinder pistons of Schnellanstellung and Regelanstellung may have the same stroke.

According to an advantageous embodiment of the present invention, the Schnellanstellung compared to the Regelanstellung on a higher adjustment speed, which may be due to the area ratios of the cylinder piston between quick and standard setting at the same volume flow of fluid over the control position by a multiple higher and on the Regelanstellung the required Apply rolling force to the compression roller.

According to a further particularly advantageous embodiment, it is provided that the displaced hydraulic fluid volume in the non-active part of the double cylinder during the adjustment movement in the other cylinder chamber can be passed, possibly missing fluid volume can be nachgefördert in the hydraulic system and excess fluid volume can be derived. For this purpose, a reservoir or a reservoir can be provided.

It can also be provided that the cylinder piston of the control position of the double cylinder is designed as a piston and two oppositely directed piston rods. In this case, the oppositely directed piston rods of Regelanstellung the double cylinder may have the same diameter. The cylinder piston of the quick adjustment of the double cylinder can be designed as a piston with two oppositely directed piston rods. The oppositely directed piston rods of the quick adjustment of the double cylinder can also have the same diameter. It is envisaged that with two or more jobs per side only one job per side is designed as a double cylinder, the other not designed as a double cylinder jobs are designed as control positions and can be driven via the, in the process of the cylinder, each displaced fluid volume.

According to a particularly advantageous embodiment of the present invention, the cylinders of the double cylinder are structurally nested. This allows a compact and space-saving design can be achieved. This is particularly advantageous if existing compression mills are converted at the site and this additional space can be created.

It is advantageous if the piston of the control position forms the housing of the quick adjustment. This contributes to a very compact, self-contained construction of a piston / cylinder unit formed in this way, consisting of the quick setting and the associated adjustment position. Furthermore, the control position is assigned a cylinder head, which can reduce the lateral forces on the employment of the onslaught. Also, the cylinder piston can be equipped with a rotation.

It is advantageous if every job is assigned a distance measuring system. This makes it possible to determine exactly traversing states.

In order to improve the employment of the compression rollers, it is advantageous if the travel paths of the control positions of a page are synchronized control technology, so that the stroke for the individual control positions of a page in the edger stand per side is the same size. That is, the stroke of the rule positions of a page should be the same size. On the other hand, that too mean that both sides do not necessarily have to have the same hub with each other.

The controls of the individual jobs per side of the double cylinder and the other possible jobs can be summarized in a control unit and controlled by this.

It is advantageous if the respective cylinders of the double cylinder (quick adjustment and regulation position) can be controlled by independently operating valves. As a result, the operating conditions in the double cylinders can be individually matched to one another. The case used and installed control valves in the hydraulic system can be designed as a servo or proportional, or directional control valves.

According to a particularly advantageous embodiment of the Anstellzylinderschnellverstellung invention, the control of the jobs can be connected to sequential circuits, or be provided. As a result, a particularly good synchronized pre-positioning of the jobs of a page can be achieved.

The invention is explained in more detail below with reference to an embodiment. Show it:

Fig. 1 The schematic representation of a stuffer in a partial view in section with

the Anstellzylinderschnellverstellung invention with two double cylinders for Schnellanstellung and Regelanstellung; 2 shows the representation of a possible shift diagram for a double cylinder of the Anstellzylinderschnellverstellung invention in section.

Fig. 3 is a schematic representation of the hydraulic fluid flow in an extending movement of the double cylinder after

Fig. 2 in section;

Fig. 4 is a schematic representation of a possible circuit diagram of the double cylinder, the Anstellzylinderschnellverstellung invention, the with a

Control cylinder is connected;

Fig. 5 is a schematic representation of the hydraulic fluid flow in an extending movement of the double cylinder after

Fig. 4 in section.

As shown in FIG. 1, the Anstellzylinderschnellverstellung 9 invention is formed as an integral part of a stuffer 10. The stuffer 10 is used to compress the edges of an incoming into the stuffer 10 rolling stock 1 1, thus the width of the incoming rolling stock 1 1 in the other

Targeted to influence rolling process. For this purpose, the stuffer 10 of one side comprises at least one stuffer stand 20 which is connected to a stator crosshead 21.

Furthermore, upper and lower uprights 22 and 23 are provided. An adjoining compression roll unit 30 consists essentially of an upper and lower Stauchwalzeneinbaustück 32 and 33 in which a compression roll 31 is rotatably mounted.

The balancing of the rolling force transmitted to the compression roll 31 takes place by means of a compression roll balancing 40. The compression roll balancing 40 comprises a balancing crosshead 41 and a balancing cylinder 42. The balancing crosspiece 41 is connected to the edging roll chocks 32, 33. The Balancierzylinder 42 acts on the Balanciertraverse 41 and the associated compression roller chocks 32, 33 on the double cylinder 50 and exerts no labor on the rolling stock 1 1. In this embodiment, the double cylinders 50 are respectively associated with the upper and lower upsetting roll chocks 32 and 33 and in the linear direction of force.

The double cylinder 50 consists of the Regelanstellung 51 and the associated Schnellanstellung 52. The rod side 51 a of Regelanstellung 51 forms a housing 54a for the piston 54 of Schnellanstellung 52 from. The piston 54 is connected to the housing of the Regelanstellung 51. The Regelanstellung 51 is also a piston 53 assigned. The piston 53 has a larger diameter than the piston rod 53 a connected to it. The piston rod 53a at the same time forms the housing 54a of the Schnellanstellung. Its conclusion, in the direction of the compression roll 31, is the arrangement in a cylinder head 55. The Schnellanstellung 52 is associated with a displacement sensor 56 via which the travel of the piston 53 and 54 can be determined. Furthermore, the quick adjustment 52 is associated with a rotation 57, which prevents the pistons 53 and 54 rotate in the respective cylinders about its longitudinal axis.

Fig. 2 shows a possible circuit 60 for Anstellzylinderschnellverstellung 9 with the double cylinder 50 provided for this purpose. For this purpose, at least a first control valve 61 for Schnellanstellung 52 and at least a second Control valve 62 for the Regelanstellung 51 provided. The circuit 60 for the Schnellanstellung 52 via at least one first short-circuit valve 63 which is disposed between the inlet and outlet 63a for the hydraulic fluid and these quasi directly connects. Furthermore, at least one further second short-circuit valve 64 is provided, which connects the piston side of the quick adjustment with a suitable preloaded system for the purpose of volume compensation. The circuit 60 of the Regelanstellung 51 also takes place via at least one short-circuit valve 65, which connects the inlet and outlet 65a together. The hydraulic fluid can flow in a circuit and can be collected in a fluid reservoir and fed from there via a pump P in the circuit 60.

Fig. 3 describes the fluid flows in an extending movement in the direction of arrow with the Schnellanstellung. The circuit 60 described in FIG. 2 - the quick setting - connects with the valve 61 the piston volume 54 of the Schnellanstellung 52 with the pressure supply and the rod volume 70a of Schnellanstellung with the return. As a result, the quick setting is actively activated and moved. At the same time, the circuit 60 interconnects the two cylinder volumes of the control setting 51 via the valve 65, so that the fluid can be displaced directly from one cylinder chamber to the other by the movement caused by the quick setting.

4 shows a possible circuit diagram 80 of the double cylinder 50 with a connected control cylinder in a sequential circuit 81. The circuit consists of at least one additional first short-circuit valve 83 and at least one additional second short-circuit valve 84. Thus, the fluid from a cylinder chamber of Regelanstellung 51 directly in the oppositely arranged cylinder chamber of the subsequent Regelanstellung 51 B are displaced. In the same way, the displaced fluid of the control position 51 B can get directly into the oppositely arranged cylinder chamber of the control position 51. By volume differences in the cylinder chambers or pressure lines, which may be due to production, missing or excess fluid volume can be supplied via the valve 82 into the reservoir or derived.

FIG. 5 is a schematic representation of the fluid flow 90 in a sequential circuit in an extending movement of a double cylinder 50 which is connected to a control position 51 and a Schnellanstellung 52. By extension movement is meant the movement of the control adjustment 51 in the direction of the arrow and thus against the compression roller and in the direction of the rolling stock.

LIST OF REFERENCE NUMBERS

Anstellzylinderschnellverstellung

Staucher partial view in section

rolling

Staucherständer

Stand crosshead

Stand upwards

Stand spar below

Compression roller unit

edging roll

Upset roll chock above

Compression roller chock below

Stauchwalzenbalancierung

Balanciertraverse

balancing cylinder

double cylinder

rule employment

a rod side

B standard employment

Quick job

Cylinder piston of the standard position

a piston rod

Cylinder pistons of the Schnellanstellung

a housing

cylinder head

encoder

twist

possible circuit diagram of a double cylinder Control valve quick start

Control valve standard position

first short-circuit valve

a inlet and outlet (pressure pipes)

second short-circuit valve

Short-circuit valve regulation

, 66a fluid supply

Extend motion fluid flow for (60) in quick adjustment mode

Circuit diagram of the double cylinder with a connected control cylinder

sequencer

Control valve standard position

first short-circuit valve in the sequential circuit

second short-circuit valve in the sequential circuit

Fluid flow in extension movement for (80) of a double cylinder in the

Operating mode quick adjustment

pump

Claims

claims

1 . Anstellzylinderschnellverstellung (9) for long, fast strokes in Stauchgerüsten, minimum consisting of Staucherständer (20), Anstellsystem, Ausbalancierungssystem and Stauchwalzensätzen, comprising at least one piston, which on Stauchwalzeneinbaustücke (32, 33) at least one compression roll (31) on both sides for hiring against the rolling stock (1 1) acts and wherein the employment of the compression roll (31) on each side hydraulically actuated by a fluid and the Anstellzylinderschnellverstellung (9) is fixed in Staucherständer (20) and applies the force required for the upsetting process, characterized in that the Anstellzylinderschnellverstellung (9) on each side of the Staucherständers (20) consists of at least one double cylinder (50), wherein the double cylinder (50) consists of two coupled separately controllable cylinders and on the one hand for the Schnellanstellung and the other for the Regelanstellung the Stauchwa Lze (31) is formed.

2. Anstellzylinderschnellverstellung according to claim 1, characterized in that the cylinder piston (54) of the Schnellanstellung (52) and the housing of Regelanstellung (51) are connected to the same fixed bank of Staucherständers (20).

3. Anstellzylinderschnellverstellung according to claim 2, characterized in that the housing of the Schnellanstellung (52) with the piston rod (53 a) of the control position (51) is integrally formed.

4. Anstellzylinderschnellverstellung according to claim 1, characterized in that the cylinder piston (54) of the Schnellanstellung (52) with the piston rod (53 a) of the Regelanstellung (51) is connected, while the Ge Quick set housing (52) is connected to the same fixed bank of the controller's housing (51).

5. Anstellzylinderschnellverstellung according to claim 1, characterized in that the cylinder housing of Schnellanstellung (52) with the piston rod (53 a) of Regelanstellung (51) is connected, while the cylinder piston (54) of Schnellanstellung (52) with the same fixed bank of the housing Regular employment (51) is connected.

6. Anstellzylinderschnellverstellung according to claims 1 to 5, characterized in that the Schnellanstellung (52) and the Regelanstellung (51) are formed independently controllable and triggered by the control movement of the housing (54 a) or the cylinder piston (54) of the Schnellanstellung (52) the movement of the cylinder piston (53) of the Regelanstellung (51) conditionally.

7. Anstellzylinderschnellverstellung according to claim 6, characterized in that the cylinder pistons (54, 53) of the Schnellanstellung (52) and the Regelanstellung (51) have the same stroke.

8. Anstellzylinderschnellverstellung according to claim 7, characterized in that the Schnellanstellung (52) relative to the control position (51) has a higher adjustment speed, due to the area ratios of the cylinder piston (54, 53) between rapid and control position (52, 51) at the same Volume flow of the fluid compared to the control position (51) is several times higher and on the Regelanstellung (51), the required rolling force on the compression roller (31) can be applied.

9. Anstellzylinderschnellverstellung according to claim 8, characterized in that the displaced hydraulic fluid volume in the non-active part of the double cylinder (50) during the adjusting movement in the respective the cylinder chamber is conductive, wherein missing fluid volume is nachförder- bar, or excess fluid volume can be derived.

10. Anstellzylinderschnellverstellung according to claim 9, characterized in that the cylinder piston (53) of the Regelanstellung (51) of the double cylinder (50) as a piston with two oppositely directed piston rods (51 a, 53 a) is formed.

1 1. Anstellzylinderschnellverstellung according to claim 10, characterized in that the oppositely directed piston rods (51 a, 53 a) of the control position (51) of the double cylinder (50) have the same diameter.

12. Anstellzylinderschnellverstellung according to claims 1 to 1 1, characterized in that the cylinder piston (54) of the Schnellanstellung (52) of the double cylinder (50) as a piston (54) and two oppositely directed piston rods is formed.

13. Anstellzylinderschnellverstellung according to claim 12, characterized in that the oppositely directed piston rods of Schnellanstellung (52) of the double cylinder (50) have the same diameter.

14. Anstellzylinderschnellverstellung according to claims 1 to 13, characterized in that at two or more jobs per side only one job per side as a double cylinder (50) is formed, wherein the other not designed as a double cylinder jobs as Regelanstellungen (51) are formed and can be driven by the volume of fluid displaced during the movement of the cylinder piston (53).

15. Anstellzylinderschnellverstellung according to claim 14, characterized in that the cylinder of the double cylinder (50) structurally intertwined nested are formed to thereby achieve a compact design.

16. Anstellzylinderschnellverstellung according to claim 15, characterized in that the cylinder piston (53) of the Regelanstellung (51) the housing (cylinder) of Schnellanstellung (52) is formed.

17. Anstellzylinderschnellverstellung according to claims 1 to 16, characterized in that the Regelanstellung (51) is associated with a cylinder head (55) which reduces the lateral forces on the employment of the onslaught.

18. Anstellzylinderschnellverstellung according to claim 17, characterized in that the cylinder pistons (53, 54) with an anti-rotation (57) are formed.

19. Anstellzylinderschnellverstellung according to claims 1 to 18, characterized in that each employment a Wegmesssystem (56) is assigned.

20. Anstellzylinderschnellverstellung according to claim 19, characterized in that the travel paths of the control positions are synchronized control technology, so that the stroke for the individual control positions (51) in the edger stand per side is the same size.

21. Anstellzylinderschnellverstellung according to claim 20, characterized in that the controls of the jobs per side of the double cylinder (50) and other jobs are summarized in a control unit and controlled by this.

22. Anstellzylinderschnellverstellung according to claim 21, characterized in that the respective cylinders of the double cylinder (50) from under- independently operating valves (61, 62, 63, 64, 65, 82, 83, 84) are controllable.

23. Anstellzylinderschnellverstellung according to claim 22, characterized in that the control valves (61, 62, 63, 64, 65, 82, 83, 84) are designed as servo or proportional, or directional control valves.

24. Anstellzylinderschnellverstellung according to claims 1 to 23, characterized in that the cylinder chambers of a plurality of control positions (51, 51 B) with short-circuit valves (83, 84) are connected, so that in this way a synchronized pre-positioning of jobs one side in the edger can be achieved.