EP3544750B1 - Edging stand with an adjusting cylinder quick adjustment - Google Patents

Description

The invention relates to an upsetting stand with an adjustment cylinder quick adjustment for long, rapid lifting movements in upsetting stands, at least consisting of an upsetting stand, adjustment system, balancing system and upsetting roller sets, each comprising at least one piston, which acts on both sides of the upsetting roller chocks to act against the rolling stock and where the on the upsetting roller can be actuated hydraulically on each side by means of a fluid and the quick adjustment cylinder is fastened in the upsetting stand and applies the force required for the upsetting process.

The adjusting device in upsetting stands has the task of setting the required roll gap, maintaining it and regulating it if necessary. The terms quick employment and regular employment are used here. The quick adjustment is used to quickly open or close the roll gap. The standard setting is the setting in which the rolling force is ultimately transferred to the rolling stock with the roll gap previously set by the quick setting. The standard setting keeps the roll gap within a predefined range Range of values constant. The system is only kept free of play via an upsetting roller balancing, ie there is no play between the upsetting roller chock, cylinder head and the cylinder piston.

In upsetting stands, adjusting devices are known as purely mechanical, as purely hydraulic or as a combination of mechanical and hydraulic adjustment. It is technically possible and sensible to arrange one or two positions on each side.

For example, a purely hydraulic adjusting device in compression stands in the roughing stand upsetter of a hot strip mill is known. This is designed as a classic differential cylinder, consisting of a piston, cylinder cover and cylinder base.

This design has limits both in the required fluid requirement and thus the travel speed as well as in the sensitivity to lateral force when the piston rod is fully extended.

From the publication 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 pointing in opposite directions, and the piston is inserted in a recess in the cylinder base or cylinder cover, these being arranged coaxially Have holes for the passage of the piston rods. However, this solution has the disadvantage that a very high pumping capacity is required for the required working speeds.

From the publication EP 2 411 165 B1 a device for edge rolling of metal plates is known. This device comprises a roller, which is mounted on a block, comprises at least one edge processing hydraulic cylinder with a relatively large working surface, at least one further hydraulic cylinder being provided with a relatively small working surface, and each Cylinder has an associated piston, the pistons being mechanically coupled such that movement of one causes movement of the other. The device requires a positive connection, which may be detachable for maintenance purposes, between the employment, the balancing cylinder and the balancing traverse. This can always lead to leaks at the connection points. Furthermore, impermissibly high transverse forces can act on the cylinder piston, which can damage the piston rod and other guide elements, which in turn leads to further leaks.

The publication EP 2 265 395 B1 further discloses a type of telescopic cylinder which has two oil columns connected in series to the rolling stock. The entire adjustment path can only be covered by using both oil columns.

From the publication JP S60 129407 a generic device is known with which different compression forces can be provided.

From the publication JP S59 220205 A discloses an apparatus with which press operation and caliber rolling can be carried out under optimal conditions by a composite cylinder equipped with a large piston at high speed and low speed and a small piston at high power and high speed.

In addition, pitch cylinders in compression stands (AWC cylinders) in a so-called sequential circuit are known. These are very complex in terms of control technology and must be kept in sync with additional valves.

Particularly in upsetting stands with a large opening width of the pitching systems, as is required, for example, in heavy plate mills, there is a requirement to move the pitching systems at a very high pitching speed of approx. 150 mm / sec. The entire pitch should be covered within a short period of approx. 15 seconds. This is process engineering, for example required because the ingots are rotated in heavy plate lines to produce the required large width on an upstream rotating roller table. As a result, a narrow ingot, viewed in the rolling direction, becomes very wide by turning on the rotating roller table in the rolling direction.

Up to now, this fast adjustment speed of the adjustment has been realized by a mechanical adjustment with electromechanical drive and air-operated brake. The mechanical adjustment accomplishes the rough adjustment of the adjustment system. As a rule, a fine adjustment is required in addition to the mechanical adjustment. This is carried out as a hydraulic short-stroke adjustment and is responsible for regular operation with automatic width control and short-stroke control to reduce the crop losses.

In this known system of mechanical / hydraulic adjustment, dispensing with the mechanical adjustment and the execution of the adjustment system as a purely hydraulic long-stroke adjustment has so far not been economical, since it was not possible without providing correspondingly high pumping capacities and at the same time simple execution of the hydraulic long-stroke adjustment to realize the required high setting speeds.

It is therefore an object of the present invention to provide quick adjustment within a compact system of hydraulic cylinders, without the hydraulic pump station having to be made unnecessarily large. Compression stands with smaller opening widths, as are common, for example, in hot strip mills, can help to relieve the pressure on 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 in that the adjusting cylinder quick adjustment consists of at least one double cylinder on each side of the upsetting stand, the double cylinder than consists of two coupled separately controllable cylinders and is designed for quick adjustment on the one hand and for regulating adjustment of the compression roller on the other.
(Continue as in the originally submitted documents on page 4, paragraph 5)

In this way, it is possible to implement a reliable rapid adjustment of the adjustment cylinders, in particular in a compression frame, by means of a purely hydraulic adjustment system, comprising the adjustment cylinder quick adjustment according to the invention. This is advantageous in cases where a long and at the same time fast cylinder stroke is required, the otherwise high capacities to the Pump performance of the hydraulic systems require. In addition, additional actuators such as mechanical adjustment with the associated electrical components (travel sensors, limit switches, positioning motors and corresponding feeds) are saved. Furthermore, the use of double cylinders reduces energy consumption, which in turn increases the cost efficiency of the entire compression frame.

According to an advantageous embodiment of the adjusting cylinder quick adjustment according to the invention, it is provided that the cylinder piston of the quick adjustment and the housing of the control adjustment are connected to the same fixed bank of the upsetting stand and, in addition, the housing of the quick adjustment can be formed in one piece with the piston rod of the control adjustment. In this case, bank is understood to mean an abutment on which the forces implied by the adjusting cylinder quick adjustment and the control adjustment are supported and ultimately transferred to the rolling stock via the upsetting rollers. In the present case, the bank can comprise the edger stand with a crosshead and the stand bars arranged at the top and bottom.

In a multi-piece embodiment of the adjusting cylinder quick adjustment according to the invention, the cylinder piston of the quick adjustment can be connected to the cylinder piston of the control adjustment, while the housing of the quick adjustment can be connected to the same fixed bank of the housing of the control adjustment.

According to another multi-piece embodiment of the adjusting cylinder quick adjustment according to the invention, it is provided that the cylinder housing of the quick adjustment is connected to the piston rod of the control adjustment, while the cylinder piston of the quick adjustment is connected to the same fixed bank of the housing of the control adjustment.

In a further preferred embodiment, the quick adjustment and the control adjustment can be designed to be controllable independently of one another and the movement of the housing of the quick adjustment or the cylinder piston triggered by the activation then causes the movement of the cylinder piston of the control adjustment. It is also provided that the cylinder pistons of the quick adjustment and the control adjustment can have the same stroke.

According to an advantageous embodiment of the present invention, the quick adjustment compared to the control adjustment has a higher adjustment speed, which can be several times higher compared to the control adjustment due to the area relationships of the cylinder pistons between quick adjustment and control adjustment with the same volume flow of the fluid, and the required adjustment via the control adjustment Applies rolling force to the upsetting 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 can be directed into the other cylinder chamber during the adjustment movement, any missing fluid volume being able to be fed into the hydraulic system and excess fluid volume being able to be drained off. For this purpose, a reservoir or an expansion tank 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. The oppositely directed piston rods of the control position of the double cylinder can 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 provided that in the case of two or more positions on each side, only one position on each side is designed as a double cylinder, the further positions not being designed as double cylinders being designed as control positions and being able to be driven via the fluid volume displaced when the cylinder is moved.

According to a particularly advantageous embodiment of the present invention, the cylinders of the double cylinder are structurally nested in one another. This enables a compact and space-saving design to be achieved. This is particularly advantageous if existing upset rolling mills are converted at the place of use and additional space can thereby be created.

It is advantageous if the piston of the control adjustment 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 adjustment and the associated adjustment adjustment. Furthermore, the control position is assigned a cylinder head which can reduce the lateral forces on the position resulting from the tapping joint. The cylinder pistons can also be equipped with an anti-rotation device.

It is advantageous if a position measuring system is assigned to each position. In this way, exact travel states can be determined.

In order to improve the setting of the upsetting rollers, it is advantageous if the travels of the regulating positions on one side are synchronized in terms of control technology, so that the stroke for the individual regulating positions on one side in the edging stand is of the same size on each side. This means that the stroke of the standard settings on one side should be the same. On the other hand, it can mean that both sides do not necessarily have to have the same stroke.

The controls of the individual positions on each side of the double cylinder and the other possible positions can be combined in a control unit and controlled by this.

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

According to a particularly advantageous embodiment of the rapid adjustment cylinder according to the invention, the control of the positions can be connected or provided with sequential circuits. In this way, a particularly good synchronized pre-positioning of the positions on one side can be achieved.

Fig. 1

Die schematische Darstellung eines Stauchers in einer Teilansicht im Schnitt mit der erfindungsgemäßen Anstellzylinderschnellverstellung mit zwei Doppelzylindern für die Schnellanstellung und die Regelanstellung;

Fig. 2

die Darstellung eines möglichen Schaltschemas für eines Doppelzylinders der erfindungsgemäßen Anstellzylinderschnellverstellung im Schnitt;

Fig. 3

die schematische Darstellung des hydraulischen Fluidstroms bei einer ausfahrenden Bewegung des Doppelzylinders nach Fig. 2 im Schnitt;

Fig. 4

die schematische Darstellung eines möglichen Schaltschemas des Doppelzylinders, der erfindungsgemäßen Anstellzylinderschnellverstellung, der mit einem Regelzylinder verbunden ist;

Fig. 5

die schematische Darstellung des hydraulischen Fluidstroms bei einer ausfahrenden Bewegung des Doppelzylinders nach Fig. 4 im Schnitt.

The invention is explained in more detail below using an exemplary embodiment. Show it:

Fig. 1

The schematic representation of an edger in a partial view in section with the adjusting cylinder quick adjustment according to the invention with two double cylinders for quick adjustment and control adjustment;

Fig. 2

the representation of a possible circuit diagram for a double cylinder of the adjusting cylinder quick adjustment according to the invention in section;

Fig. 3

the schematic representation of the hydraulic fluid flow after an extending movement of the double cylinder after Fig. 2 on average;

Fig. 4

the schematic representation of a possible circuit diagram of the double cylinder, the adjusting cylinder quick adjustment according to the invention, which is connected to a control cylinder;

Fig. 5

the schematic representation of the hydraulic fluid flow after an extending movement of the double cylinder after Fig. 4 on average.

As the Fig. 1 shows, the adjusting cylinder quick adjustment 9 according to the invention is designed as an integral part of an edger 10. The upsetter 10 serves to compress the edges of a rolling stock 11 entering the upsetter 10 in order to influence the width of the incoming rolling stock 11 in a targeted manner in the further rolling process. For this purpose, the edger 10 comprises at least one edger stand 20 on one side, which is connected to a stand crosshead 21.

Upper and lower uprights 22 and 23 are also provided. An adjoining compression roller unit 30 essentially consists of an upper and lower upsetting roller chocks 32 and 33 in which an upsetting roller 31 is rotatably supported.

The rolling force transmitted to the upsetting roller 31 is balanced with the aid of an upsetting roller balance 40. The upsetting roller balance 40 comprises a balancing crossbar 41 and a balancing cylinder 42. The balancing crossbar 41 is connected to the upsetting roller chocks 32, 33. The balancing cylinder 42 acts on the double cylinder 50 via the balancing crossbar 41 and the upsetting roller chocks 32, 33 connected therewith and does not exert any work force on the rolling stock 11. In this embodiment, the double cylinders 50 are assigned to the upper and lower upsetting roller chocks 32 and 33 and in the linear direction of force.

The double cylinder 50 consists of the control setting 51 and the quick setting 52 connected to it. The rod side 51a of the control setting 51 forms a housing 54a for the piston 54 of the quick setting 52. The piston 54 is connected to the housing of the control position 51. A piston 53 is also assigned to the control setting 51. The piston 53 has a larger diameter than the piston rod 53a connected to it. The piston rod 53a also forms the housing 54a for quick adjustment. The arrangement, in the direction of the upsetting roller 31, ends in a cylinder head 55. The rapid adjustment 52 is assigned a displacement sensor 56, via which the travel of the pistons 53 and 54 can be determined. Furthermore, the quick adjustment 52 is assigned an anti-rotation device 57, which prevents the pistons 53 and 54 from rotating in the corresponding cylinders about their longitudinal axis.

The Fig. 2 shows a possible circuit 60 for the adjusting cylinder quick adjustment 9 with the double cylinder 50 provided for this purpose. For this purpose there is at least one first control valve 61 for the quick adjustment 52 and at least one second Control valve 62 is provided for the control setting 51. The circuit 60 for the quick adjustment 52 takes place via at least one first short-circuit valve 63, which is arranged between the inflow and outflow 63a for the hydraulic fluid and connects them quasi directly to one another. Furthermore, at least one further second short-circuit valve 64 is provided that connects the piston side of the quick adjustment with a suitable pretensioned system for the purpose of volume compensation. The circuit 60 of the control setting 51 likewise takes place via at least one short-circuit valve 65, which connects the inlet and outlet 65a to one another. The hydraulic fluid can flow in a circuit and can be collected in a fluid supply and from there can be fed into the circuit 60 via a pump P.

Fig. 3 describes the fluid flows when moving out in the direction of the arrow with the quick adjustment. In the Fig. 2 Circuit 60 described - the quick adjustment - connects with the valve 61 the piston volume 54 of the quick adjustment 52 with the pressure supply and the rod volume 70a of the quick adjustment with the return. As a result, the quick adjustment is actively controlled and moved. At the same time, the circuit 60 connects the two cylinder volumes of the control setting 51 to one another 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.

Fig. 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 can flow from one cylinder chamber of the control position 51 directly into the opposite one Cylinder chamber of the following control setting 51B can be 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.

Due to volume differences in the cylinder chambers or pressure lines, which may be production-related, missing or excess fluid volume can be supplied or removed via the valve 82 into the storage container.

The Fig. 5 is a schematic representation of the fluid flow 90 in a sequential circuit during an extending movement of a double cylinder 50 which is connected to a control setting 51 and a quick setting 52. Extending movement means the movement of the control setting 51 in the direction of the arrow and thus against the upsetting roller and in the direction of the rolling stock.

Reference symbol list

9

Quick adjustment cylinder

10th

Staucher partial view in section

11

Rolling stock

20th

Upright stand

21

Stand crosshead

22

Stand spar above

23

Stand spar below

30th

Upset roller unit

31

Upsetting roller

32

Upset roller chock above

33

Upset roller chock below

40

Balancing roller balancing

41

Balancing crossbar

42

Balancing cylinder

50

Double cylinder

51

Regular employment

51a

Rod side

51B

Regular employment

52

Quick employment

53

Cylinder piston of the standard setting

53a

Piston rod

54

Cylinder piston for quick adjustment

54a

casing

55

Cylinder head

56

Weggeber

57

Anti-rotation device

60

possible circuit diagram of a double cylinder

61

Control valve quick adjustment

62

Control valve control valve

63

first short circuit valve

63a

Inlet and outlet (pressure lines)

64

second short circuit valve

65

Short circuit valve control setting

66, 66a

Fluid supply

70

Fluid flow with extending movement for (60) in the quick adjustment operating mode

80

Circuit diagram of the double cylinder with a connected control cylinder

81

Sequential circuit

82

Control valve control valve

83

first short-circuit valve in the sequential circuit

84

second short-circuit valve in the sequential circuit

90

Fluid flow with extending movement for (80) a double cylinder in the quick adjustment operating mode

P

pump

Claims (24)

1. Edging stand with an adjustment cylinder quick-action adjusting means (9) for lengthy, rapid stroke movements, the edging stand consisting at least of edging housing (20), adjustment system, equalising system and edging roll sets (31), the adjustment cylinder quick-action adjusting means (9) comprising at least a piston, which acts by way of edging roll chocks (32, 33) of at least one edging roll (31) on both sides for adjustment relative to the rolling material (11) and wherein the adjustment of the edging roll (31) is hydraulically actuable on each side by means of a fluid and the adjustment cylinder quick-action adjusting means (9) is secured in the edging housing (20) and exerts the force required for the edging process, wherein the adjustment cylinder quick-action adjusting means (9) consists of at least one double-acting cylinder (50) on each side of the edging housing (20), characterised in that the double-acting cylinder (50) consists of two separately controllable cylinders coupled together and is constructed on the one hand for quick-action adjusting means (52) and on the other hand for regulating adjusting means (51B) of the edging roll (31).
2. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to claim 1, characterised in that the cylinder piston (54) of the quick-action adjusting means (52) and the housing of the regulating adjusting means (51) are connected with the same fixed border of the edging housing (20).
3. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to claim 2, characterised in that the housing of the quick-action adjusting means (52) is constructed integrally with the piston rod (53a) of the regulating adjusting means (51).
4. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to claim 1, characterised in that the cylinder piston (54) of the quick-action adjusting means (52) is connected with the piston rod (53a) of the regulating adjusting means (51), whereas the housing of the quick-action adjusting means (52) is connected with the same fixed border of the housing of the regulating adjusting means (51).
5. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to claim 1, characterised in that the cylinder housing of the quick-action adjusting means (52) is connected with the piston rod (53a) of the regulating adjusting means (51), whereas the cylinder piston (54) of the quick-action adjusting means (52) is connected with the same fixed border of the housing of the regulating adjusting means (51).
6. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to any one of claims 1 to 5, characterised in that the quick-action adjusting means (52) and the regulating adjusting means (51) are constructed to be activatable independently of one another and the movement, which is triggered by the activation, of the housing (54a) or of the cylinder piston (54) of the quick-action adjusting means (52) causes the movement of the cylinder piston (53) of the regulating adjusting means (51).
7. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to claim 6, characterised in that the cylinder pistons (54, 53) of the quick-action adjusting means (52) and the regulating adjusting means (51) have the same stroke travel.
8. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to claim 7, characterised in that the quick-action adjusting means (52) has a higher adjustment speed relative to the regulating adjusting means (51), which due to the area relationships of the cylinder pistons (54, 53) between quick-action adjusting means (52) and regulating adjusting means (51) is higher by a multiple for the same volume flow of the fluid relative to the regulating adjusting means (51) and the required rolling force can be exerted on the edging roll (31) by way of the regulating adjusting means (51).
9. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to claim 8, characterised in that the displaced hydraulic fluid volume in the non-active part of the double-acting cylinder (50) during the adjusting movement can be conducted into the respective other cylinder chamber, wherein a deficient fluid volume can be required or excess fluid volume can be conducted away.
10. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to claim 9, characterised in that the cylinder piston (53) of the regulating adjusting means (51) of the double-acting cylinder (50) is constructed as a piston with two oppositely directed piston rods (51a, 53a).
11. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to claim 10, characterised in that the oppositely directed piston rods (51a, 53a) of the regulating adjusting means (51) of the double-acting cylinder (50) have the same diameter.
12. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to any one of claims 1 to 11, characterised in that the cylinder piston (54) of the quick-action adjusting means (52) of the double-acting cylinder (50) is constructed as a piston (54) and two oppositely directed piston rods.
13. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to claim 12, characterised in that the oppositely directed piston rods of the quick-action adjusting means (52) of the double-acting cylinder (50) have the same diameter.
14. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to any one of claims 1 to 13, characterised in that in the case of two or more adjusting means per side only one adjusting means per side is constructed as a double-acting cylinder (50), wherein the further adjusting means not constructed as a double-acting cylinder are constructed as regulating adjusting means (51) and are drivable by way of the fluid volume respectively displaced on movement of the cylinder piston (53).
15. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to claim 14, characterised in that the cylinders of the double-acting cylinder (50) are configured to be constructionally nested one in the other so as to thereby achieve a compact mode of construction.
16. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to claim 15, characterised in that the cylinder piston (53) of the regulating adjusting means (51) forms the housing (cylinder) of the quick-action adjusting means (52).
17. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to any one of claims 1 to 16, characterised in that a cylinder head (55), which reduces the transverse forces acting from the pass impact on the adjusting means, is associated with the regulating adjusting means (51).
18. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to claim 17, characterised in that the cylinder pistons (53, 54) are constructed with securing means (57) against twisting.
19. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to any one of claims 1 to 18, characterised in that a travel measuring system (56) is associated with each adjusting means.
20. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to claim 19, characterised in that the movement travels of the regulating adjusting means can be synchronised by way of regulation so that the stroke for the individual regulating adjusting means (51) in the edging stand is formed to be the same per side.
21. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to claim 20, characterised in that the controls of the adjusting means per side of the double-acting cylinder (50) and further adjusting means are combined in a control unit and are controllable by this.
22. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to claim 21, characterised in that the respective cylinders of the double-acting cylinder (50) are controllable by valves (61, 62, 63, 64, 65, 82, 83, 84) operating independently of one another.
23. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to claim 22, characterised in that the control valves (61, 62, 63, 64, 65, 82, 83, 84) are constructed as servo-valves or proportional-valves or travel valves.
24. Edging stand with an adjustment cylinder quick-action adjusting means (9) according to any one of claims 1 to 23, characterised in that the cylinder chambers of several regulating adjusting means (51, 51B) are connected with bypass valves (83, 84) so that a synchronised pre-positioning of the adjusting means per side in the edging stand is thereby achievable.

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