EP2729263B9 - Pinch roll device - Google Patents
Pinch roll device Download PDFInfo
- Publication number
- EP2729263B9 EP2729263B9 EP12748552.2A EP12748552A EP2729263B9 EP 2729263 B9 EP2729263 B9 EP 2729263B9 EP 12748552 A EP12748552 A EP 12748552A EP 2729263 B9 EP2729263 B9 EP 2729263B9
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- EP
- European Patent Office
- Prior art keywords
- roll
- rolls
- hydraulic
- pressure
- pinch roll
- Prior art date
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- 238000000034 method Methods 0.000 claims description 31
- 230000033001 locomotion Effects 0.000 claims description 21
- 230000002441 reversible effect Effects 0.000 claims description 18
- 239000012530 fluid Substances 0.000 claims description 17
- 230000005540 biological transmission Effects 0.000 claims description 13
- 238000013459 approach Methods 0.000 claims description 11
- 238000005096 rolling process Methods 0.000 description 7
- 238000013016 damping Methods 0.000 description 4
- 238000011144 upstream manufacturing Methods 0.000 description 4
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 238000005259 measurement Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000009257 reactivity Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000006641 stabilisation Effects 0.000 description 1
- 238000011105 stabilization Methods 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 238000013519 translation Methods 0.000 description 1
Images
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B39/00—Arrangements for moving, supporting, or positioning work, or controlling its movement, combined with or arranged in, or specially adapted for use in connection with, metal-rolling mills
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B39/00—Arrangements for moving, supporting, or positioning work, or controlling its movement, combined with or arranged in, or specially adapted for use in connection with, metal-rolling mills
- B21B39/006—Pinch roll sets
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B38/00—Methods or devices for measuring, detecting or monitoring specially adapted for metal-rolling mills, e.g. position detection, inspection of the product
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
- B21B37/58—Roll-force control; Roll-gap control
- B21B37/62—Roll-force control; Roll-gap control by control of a hydraulic adjusting device
Definitions
- the present invention relates to a pinch roll device for rolled metallurgic products.
- pinch roll devices comprising systems for monitoring both the distance between the rolls and the pressure exerted by the rolls on the product when rolling.
- the one described in Patent US 6920772 is known, for example, in which the rolls are connected to two cranks, respectively, connected to a single electric ratio motor.
- the controlled rotation of the ratio motor controls, by means of the two cranks, the reciprocal approach of the two rolls in one direction and the moving apart in the opposite direction.
- the ratio motor by means of the two cranks allows to adjust the thrust force of each roll against the other roll, thus also adjusting the pressure exerted by the rolls on the product being rolled.
- the juddering of the pinch rolls causes a surface fault of the rolled product which reduces quality and increases material rejects.
- Another object is to make available a new pinch roll device for rolled metallurgic products which is completely automatic and which does not require any manual intervention by the operator, e.g. for compensating roll wear.
- a further object is to allow a high through speed, up to 150 m/s, of the product between the rolls to be achieved.
- Another object of the present invention is to make available a pinch roll device controlled by a hydraulic circuit having size, in terms of length of the hydraulic line and amount of operating fluid, much smaller than the prior art.
- a further object is to make available an operation method for the above-mentioned pinch roll device.
- the present invention allows to obtain a method of operating a pinch roll device for metallurgic products with an optimized control comprising a step of checking the position, which allows to set the distance between the rolls before the passage of the product, and a step of checking the pressure, which allows to adjust the roll thrust when rolling.
- the two steps are carried out alternatively with respect to each other, allowing to optimize the control cycle which thus may be carried out rapidly, thus favoring an increase of the through speed of the product between rolls.
- Including a first roll and a second roll reciprocally interconnected by means of a mechanical and/or hydraulic connection allows to reciprocally approach or space apart the two rolls in a symmetric manner with respect to the crossing axis, so as to accurately and effectively control the size of the passage gap.
- the hydraulic actuator being directly active on only one of the two rolls, while the other is controlled by a geared transmission between the two rolls allows to synchronize the movement due to the direct coupling of the first and second rolls, in a simpler manner than the other known solutions, e.g. the one in US 6920772 , where a mechanical linkage transmission connects the operating member to both rolls.
- the use of two hydraulic actuators respectively acting on the two rolls and connected to each other by means of a compensation circuit allows to obtain the same operating accuracy and the same constructional simplicity.
- Using a hydraulic control circuit further allows to obtain a stabilization of the system by damping the stresses between rolls and rolled product operated by the hydraulic fluid. Furthermore, the hydraulic circuit being closed and pressurized allows to have very small size with respect to the typical hydraulic circuits which include a hydraulic unit.
- Using the reversible pump controlled by the electric motor allows to omit the servo valve normally used in hydraulic circuits and to additionally decrease the amount of fluid needed by the hydraulic circuit and the overall length thereof.
- a pinch roll device for a round-section, rolled metallurgic product is indicated by reference numeral 1 as a whole.
- a pinch roll device provided in accordance with the present invention may be appropriately configured to hold any rolled metallurgic product, e.g. a flat-section rolled product.
- Device 1 comprises a first pinch roll 2 and a second pinch roll 3 which is identical to the first roll 3, between which a substantially circular passage gap 5 for a wire rod 10 is defined.
- Gap 5 defines a crossing axis X, coaxial to gap 5, with which the wire rod 10 is aligned in operation when passing passage gap 5.
- the first and second rolls 2, 3 can rotate about a first rotation axis Y1 and a second rotation axis Y2, respectively, to draw by friction the wire rod 10 through the passage gap 5.
- the rotation axes Y1, Y2 are parallel to each other and equally spaced apart from the crossing axis X, with respect to which they are arranged on the opposite side.
- the shape and size of gap 5 comply with those of the wire rod 10, and gap 5 is delimited by two annular grooves 5a, 5b provided on the cylindrical peripheral surface of the pinch rolls 2, 3, respectively.
- the first and second rolls 2, 3 are restrained to a first lever arm 7 and second lever arm 8, respectively, so as to rotate about respective rotation axes Y1, Y2.
- the rotation of the pinch rolls 2, 3 about the respective axes Y1, Y2, integral with the first and second arms 7, 8, respectively, is obtained by means of a conventional and known actuator comprising a drive motor (not shown) connected to the rolls by means of a transmission comprising a pair of driven toothed wheels 2a, 3a, coaxial with axes Y1, Y2, and a pair of drive toothed wheels 2b, 3b, meshing with each other so as to be counter-rotating.
- the driven toothed wheels 2a, 3a mesh with the toothed drive wheels 2b, 3b, respectively, from which they receive motion.
- the rotation motion is transmitted by the drive motor to the toothed drive wheel 3b, by means of a motion output shaft 3c.
- the motion is transmitted from the drive toothed wheel 3b to the other drive toothed wheel 2b and to the driven toothed wheel 3a.
- the motion is transmitted from the drive toothed wheel 2b to the other driven toothed wheel 2a. Due to the described coupling, the driven toothed wheels 2a, 3a, and therefore the respective rolls 2, 3, are counter-rotating.
- the first and second arms 7, 8 are equal to each other and rotationally supported with respect to a fixed reference system integral with the crossing axis X by means of a pair of respective hinges which define a third rotation axis Z1 and a fourth rotation axis Z2, respectively, which are parallel to each other and equally spaced apart from crossing axis X, respect to which they are arranged on opposite side.
- the first and second arms 7, 8 can rotate about Z1 and Z2, respectively, to reciprocally either approach or space apart the first and second rolls 2, 3, so as to reduce or increase the width of the passage gap 5, respectively.
- the third and fourth rotation axes Z1, Z2 are spaced apart along the respective arm 7, 8, from the first and the second rotation axes Y1, Y2, respectively, and parallel thereto.
- the four axes Y1, Y2, Z1 and Z2 form a parallel axis system in all operating conditions of device 1.
- device 1 In order to control the rotation of the lever arms 7, 8 and therefore to reciprocally approach or space apart the first and the second rolls 2, 3, device 1 comprises a hydraulic circuit 20 in which a hydraulic fluid, e.g. oil, circulates and a mechanical gear transmission 11, by means of which the first and second rolls 2, 3 are interconnected.
- a hydraulic fluid e.g. oil
- the hydraulic circuit 20 is closed and pressurized, therefore no hydraulic control unit is required, and comprises a hydraulic actuator 21 connected to the first roll 2 to approach it to or space it apart from the second roll 3.
- the actuator 21 comprises a stem 31 hinged at a free end 31 a thereof to the first lever arm 7, close to the first roll 2.
- the translation of stem 31 determines a corresponding rotation of the lever arm 7 about the third rotation axis Z1. The same rotation is transmitted to the second arm 8 by means of transmission 11.
- the transmission 11, which thus allows the hydraulic actuator 21 to be connected to the second roll 3, by means of the first roll 2, comprises the lever arms 7, 8 and a gear 12 between the first lever arm 7 and the second lever arm 8.
- Gear 12 comprises a first toothed sector 12a and a second toothed sector 12b integral with the first and second arms 7, 8, respectively, and meshing with each other so that each rotation imparted by the actuator 21 to the first arm 7 is transmitted to the second arm 8.
- the first and second toothed sectors 12a,b are provided at the end of a third arm 32 and of a fourth arm 33, respectively, being integral with the first and second arms 7, 8, aligned with each other and orthogonal to crossing axis X.
- the arms 32, 33 are arranged on opposite sides with respect to the crossing axis X so that the first and second toothed sectors 12a, b mesh with each other at the same crossing axis X.
- the transmission ratio of the gear 12 is unitary so that each rotation of the first arm 7 corresponds to an equal, opposite rotation of the second arm 8.
- Gear 12 allows to obtain a synchronous, coordinated movement of the first and second lever arms 7, 8 and of the rolls 2, 3 restrained thereto. Therefore, the assembly consisting of the first arm 7 and the first roll 2 restrained thereto is equal and symmetric, with respect to axis X, to the assembly of the second arm 8 and the second roll 3 restrained thereto in all operating conditions.
- the first and second rolls 2, 3 are interconnected to each other by means of another type of mechanical connection, free from gears, comprising a plurality of linkages for example.
- the hydraulic actuator 21 is of the double-effect type, comprising a first chamber 21 a and a second chamber 21 b, with a piston 22 connected to stem 31 and to a secondary stem 31 b sliding therebetween and being also opposed to stem 31 and having an equal diameter.
- the hydraulic circuit 20 comprises a reversible pump 9, connected to the first and second chambers 21 a, b of the actuator by means of a first branch 20a and a second branch 20b of the hydraulic circuit 20, respectively.
- the rotation of the reversible pump 9 in one direction or in the other allows to send oil directly to either one or the other of the chambers 21a, b of actuator 21, respectively, thus determining the movement of piston 22 and stem 31 in either one direction or in the opposite direction.
- Pump 9 which controls the movement of piston 22 is operated by an electric motor 9a; the position of piston 22 inside the cylinder thus depends on the angular position of the motor 9a of pump 9, while the movement speed of the cylinder depends on the angular speed of pump 9.
- the motor 9a of pump 9 determines each fluid movement in the hydraulic circuit 20: therefore, if motor 9a does not operate the pump 9, the fluid flow in each point of the hydraulic circuit 20 is substantially zero and the piston 22 does not move.
- a connection branch is provided between the first branch 20a and the second branch 20b of the hydraulic circuit 20, being equipped with a maximum pressure valve 29 calibrated so as to protect the hydraulic circuit from pressure overloads resulting from excessive, even pulsing loads applied to the first roll 2 and transmitted to the actuator 2 through stem 31.
- the first and second branches 20a, b are connected upstream of the reversible pump 9 to a top-up source 27, which allows to top-up any leakage of fluid from the hydraulic circuit 20.
- a first check valve 28a and a second check valve 28b oriented so as to prevent the flow from the pump 9 to the top-up source 27 and to allow the flow in the opposite direction, are provided between the top-up source 27 and the reversible pump 9 on the first and second branches 20a, b, respectively.
- the amount of fluid needed for the operation of the hydraulic circuit 20, given by the sum of the circulating fluid and the fluid present in the top-up source 27, may advantageously range from 0.5 to 2 liters, preferably from 0.7 to 1.4 liters.
- the hydraulic circuit 20 As the hydraulic circuit 20 is closed, it is also possible to contain its size: the overall length of the hydraulic line in which the fluid circulates is advantageously from 0.5 to 1.5 meters, preferably from 0.7 to 1 meter.
- a feedback control circuit 30 is included, comprising the electric motor 9a connected to pump 9 by means of a connector 9b.
- the control circuit 30 further comprises a pressure sensor 25, located in the first branch 20a of the hydraulic circuit 20, between the actuator 21 and the maximum pressure valve 29, and a position sensor 24 in the actuator 21.
- the pressure sensor 25 allows to measure the pressure in the circuit, and in particular in the chamber 21a, and thus to determine the force F1 transmitted by the actuator 21 to the first roll 2 through the stem 31. Force F1 is transmitted from the first roll to the wire rod 10.
- an equal opposite force F2 transmitted from the second roll 3 to the wire rod 10 corresponds to force F1.
- the rolling force and pressure can be controlled by controlling the pressure in the hydraulic circuit 20.
- the position sensor 24 allows to measure the movement of piston 22, and thus to determine the movement of the first roll 2.
- the position of the first roll 2 can be controlled by controlling the position of piston 22, therefore by means of the transmission 11, the position of the second roll 3 can also be controlled, thus adjusting the width of the passage gap 5.
- the control circuit 30 further comprises a control unit 26 by means of which the electric motor 9a is controlled.
- the control unit 26 is connected to the position sensor 24 and to the pressure sensor 25, so to obtain a feedback control.
- the control unit 26 receives pressure and position data measured by the sensors 25, 24 and processes them to determine the force F1 and width values of the passage gap 5. The control unit 26 then compares these values to respective reference values and therefore controls the electric motor 9a to either modify or keep the force F1 and the width of the passage gap 5, according to an operation method 100, the significant steps of which are described below.
- a constructional variant of a pinch roll device for a wire rod differs from device 1 in that it comprises a different hydraulic circuit 41, as described in greater detail below.
- Other components of device 40 are not described in detail because they are identical to the above-described respective components of device 1.
- the hydraulic circuit 41 differs from the hydraulic circuit 20 of device 1 in that it comprises a pair of single-effect, hydraulic actuators 42, 43 connected to the first roll 2 and to the second roll 3, respectively, instead of the double-effect, hydraulic actuator 21.
- Each of the hydraulic actuators 42, 43 comprises a piston 22 sliding between a respective upper first chamber 42a, 43a and a respective lower chamber 42b, 43b.
- the upper chambers 42a, 43a of the hydraulic actuators 42, 43 are connected to the first and second branches 20a, b of the hydraulic circuit 41, respectively.
- the lower chambers 42b, 43b of the hydraulic actuators 42, 43 are connected to each other by means of a hydraulic connection consisting of a compensation circuit 44, by means of which the first and second rolls 2, 3 are interconnected so that when the first roll 2 is moved from and to said second roll 3, the latter is simultaneously moved from and to the first roll 2.
- the first roll 2 and the second roll 3 are also either symmetrically spaced apart or approached with respect to the crossing axis X.
- the operation method 100 of device 1, which may be implemented in the control unit 26, comprises an initial step 50 in which the method checks whether the rolls 2, 3 are stationary with respect to the respective rotation axes Y1, Y2, or are rotating. If the rolls 2, 3 are stationary, the method 100 ends going to a next stopping step 51. If the rolls 2, 3 are rotating by means of the pair of toothed wheels 2a, 3a, the method 100 continues with a next step 52 in which it checks whether the control motor 9a of pump 9 is off or running. If the motor 9a is off, the method 100 ends and goes to the stopping step 51.
- the method 100 continues with a next step of setting the reference values 53, in which the type and features of the product being machined, e.g. the wire rod 10, are identified and a first reference value 61 of the position of piston 22 and a second reference value 71 of the pressure in the circuit 20 are set as a function of the identified product.
- the reference values 53 in which the type and features of the product being machined, e.g. the wire rod 10, are identified and a first reference value 61 of the position of piston 22 and a second reference value 71 of the pressure in the circuit 20 are set as a function of the identified product.
- the method 100 continues with a next step 54 of checking the presence or absence of the metallurgic product to be machined, e.g. the wire rod 10, in the passage gap 5 between the rolls 2, 3.
- the control unit 26 receives an external datum which identifies the presence or absence of the metallurgic product to be machined, obtained by means of one or more sensors (not shown), e.g. photocells, arranged upstream of the passage gap 5 and connected to the control unit 26.
- the method 100 continues with a step 110 of checking the position of piston 22 and thus of the first roll 2.
- the method 100 continues with a pressure checking step 120, in which the pressure within actuator 21 is checked.
- the method 100 includes the step 80 of checking the end of machining, in which it checks, by means of a signal supplied by the control unit 26, e.g. by means of a switch or other type of control actuatable by an operator, whether the machining process is underway or has ended. If the rolling process has ended, the method 100 ends with a final step 81 in which the first and second rolls 2, 3 are taken to the maximum reciprocal distance. Alternatively, if the rolling process has not ended, the method 100 continues by repeating step 53 of setting the reference values.
- the position checking step 110 comprises a first sub-step 60 of determining, by means of the measurement supplied by the position sensor 24, a measured value of the current position of piston 22, which can be associated with the position of the first roll 2 due to the connection by means of stem 31.
- a second position comparing sub-step 62 follows the first sub-step in order to compare the measured value of the position identified by the first sub-step 60 with the reference position value 61. The comparison is carried out by subtracting the measured value from the reference value.
- the position checking step 110 continues with a third checking sub-step 64, in which the method checks whether the subtraction carried out during the second sub-step 62 has a zero result or a result different from zero.
- the position checking step 110 ends and the method 100 continues with the machining-end checking step 80, while if the result if other than zero, the position checking step 110 continues with a fourth sub-step 63, in which a movement is imposed by means of the motor 9a and the reversible pump 9 on the piston 22 to reach the position corresponding to the reference value 61.
- the movement imposed on the piston 22 is proportional to the difference between the measured position value and the reference position value 61.
- the position checking step 110 ends and the method 100 continues with the machining-end checking step 80.
- the pressure checking step 120 comprises a fifth fast approaching sub-step 59, in which the rolls 2, 3 are approached to the metallurgic product to be machined, which is followed by a sixth sub-step 70 of determining a measured value of the pressure in the first branch 20a of the hydraulic circuit 20, upstream of the reversible pump 9, by means of the measurement supplied by the pressure sensor 25, which pressure value can be associated with the pressure of the first chamber 21a of actuator 21 due to the proximity of the pressure sensor 25 to the actuator 21.
- a seventh pressure comparing sub-step 72 follows the sixth sub-step to compare the measured pressure value identified in the sixth sub-step 70 with the reference position value 71. The comparison is carried out by subtracting the measured value from the reference value.
- the pressure checking step 120 continues with a eighth checking sub-step 75, in which the method checks whether the result of the subtraction carried out in the seventh sub-step 72 is zero or different from zero, If the result is zero, the pressure checking step 120 proceeds with a ninth sub-step 74 of refreshing the reference position, in which the first reference value 61 of the position of piston 22 is updated to the current value. At the end of the ninth sub-step 74, the pressure checking step 120 is carried out, and the method 100 continues with the machining-end checking step 80.
- the pressure checking step 120 proceeds with a tenth sub-step 73, in which a movement is imposed by means of the motor 9a and the reversible pump 9 on the piston 22 to reach the pressure corresponding to the reference value 71.
- the movement imposed on the piston 22 is proportional to the difference between the measured pressure value and the reference pressure value 71.
- the pressure checking step 120 ends and the method 100 continues with the machining-end checking step 80.
- the above-described method in which the force checking step 110 and the position checking step 120 are carried out alternatively to each other, may be carried out very rapidly, at a frequency typically of the order of 3000 Hz. This results in the possibility of reaching feeding speeds along the crossing axis X for the products to be machined of the order of 150 m/s.
- the above-described method 100 may be also used in pinch roll devices other than device 1, provided that they comprise:
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Description
- The present invention relates to a pinch roll device for rolled metallurgic products.
- In the technical field of line processes for semi-finished metallurgic products, e.g. wire rods, it is known to use pinch roll devices comprising systems for monitoring both the distance between the rolls and the pressure exerted by the rolls on the product when rolling.
- Among the devices of the aforesaid type, the one described in Patent
US 6920772 is known, for example, in which the rolls are connected to two cranks, respectively, connected to a single electric ratio motor. The controlled rotation of the ratio motor controls, by means of the two cranks, the reciprocal approach of the two rolls in one direction and the moving apart in the opposite direction. When a product being machined is present between the rolls, the ratio motor by means of the two cranks allows to adjust the thrust force of each roll against the other roll, thus also adjusting the pressure exerted by the rolls on the product being rolled. - The device described in
US 6920772 has a series of drawbacks, caused by its constructional complexity and the inevitable presence of backlash in the transmission chain between the servo motor and the rolls, determined by the type and number of the mechanical members chosen to connect the servo motor to the rolls. Therefore, such a device does not allow to effectively control the distance between the rolls both during the waiting step, i.e. when the product to be rolled is not present between the rolls, and during the working step, when the product to be rolled is in contact with the rolls. During the working step, in devices as the one described inUS 6920772 , in which the distance between the rolls is adjusted only by means of a kinematic chain comprising electromechanical members, the dynamic stresses caused by the contact between product and rolls determine the juddering of the rolls, and the consequent intermittent loss of contact between rolls and rolled product. The impossibility of ensuring a constant pinching action implies the instability of the device which is also transmitted upstream of the rolling line. - Furthermore, the juddering of the pinch rolls causes a surface fault of the rolled product which reduces quality and increases material rejects.
- Other pinch roll devices, as those described in
US2003/034376 (on which the preamble of claim 1 is based) and inEP019298 - low operating speed of the servo valve (of the order of 40-50 Hz), with consequent low reactivity of the hydraulic circuit;
- open circuit operation with consequent need to provide external hydraulic attachments;
- high running and maintenance costs because the servo valves normally have low life cycles.
- The devices described in
US2003/034376 and inEP0192982 are also improvable with regards to roll positioning accuracy. - It is the object of the present invention to provide a new pinch roll device for rolled metallurgic products which allows to solve the mentioned drawbacks of the prior art, thus allowing to accurately control both the reciprocal distance of the pinch rolls and the pressure exerted by the rolls on the product when rolling, in order to ensure a continuous, even contact between rolls and rolled product.
- Another object is to make available a new pinch roll device for rolled metallurgic products which is completely automatic and which does not require any manual intervention by the operator, e.g. for compensating roll wear.
- A further object is to allow a high through speed, up to 150 m/s, of the product between the rolls to be achieved.
- Another object of the present invention is to make available a pinch roll device controlled by a hydraulic circuit having size, in terms of length of the hydraulic line and amount of operating fluid, much smaller than the prior art.
- A further object is to make available an operation method for the above-mentioned pinch roll device.
- In accordance with the invention, the aforesaid technical problem is solved by means of a pinch roll device having the features set forth in independent claim 1, and by means of a method having the features set forth in independent claim 8.
- Similarly as described above with regards to the first aspect, the present invention allows to obtain a method of operating a pinch roll device for metallurgic products with an optimized control comprising a step of checking the position, which allows to set the distance between the rolls before the passage of the product, and a step of checking the pressure, which allows to adjust the roll thrust when rolling. The two steps are carried out alternatively with respect to each other, allowing to optimize the control cycle which thus may be carried out rapidly, thus favoring an increase of the through speed of the product between rolls.
- Other advantages of the present invention are achieved by means of a pinch roll device in accordance with the dependent claims, as explained in greater detail in the description that follows.
- Including a first roll and a second roll reciprocally interconnected by means of a mechanical and/or hydraulic connection allows to reciprocally approach or space apart the two rolls in a symmetric manner with respect to the crossing axis, so as to accurately and effectively control the size of the passage gap. In particular, the hydraulic actuator being directly active on only one of the two rolls, while the other is controlled by a geared transmission between the two rolls allows to synchronize the movement due to the direct coupling of the first and second rolls, in a simpler manner than the other known solutions, e.g. the one in
US 6920772 , where a mechanical linkage transmission connects the operating member to both rolls. Alternatively, the use of two hydraulic actuators respectively acting on the two rolls and connected to each other by means of a compensation circuit allows to obtain the same operating accuracy and the same constructional simplicity. - Using a hydraulic control circuit further allows to obtain a stabilization of the system by damping the stresses between rolls and rolled product operated by the hydraulic fluid. Furthermore, the hydraulic circuit being closed and pressurized allows to have very small size with respect to the typical hydraulic circuits which include a hydraulic unit.
- In the hydraulic circuit, using a reversible pump controlled by an electric motor, controlled in turn by a control unit connected to the position and pressure sensors, allows to implement a hydroelectric type control system in which the hydraulic part is used to control the reciprocal approach or spacing apart of the rolls, while the electric part allows to effectively obtain position and pressure feedback control. This allows to advantageously integrate the features of the hydraulic systems, in particular the possibility of exerting high pressures, with the features of the electric systems, in particular control speed and reliability.
- Using the reversible pump controlled by the electric motor allows to omit the servo valve normally used in hydraulic circuits and to additionally decrease the amount of fluid needed by the hydraulic circuit and the overall length thereof.
- Further features and advantages of the present invention will become more apparent in the following detailed description of a preferred embodiment, provided by way of non-exclusive, indicative non-limiting example, with reference to the accompanying drawings, in which:
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figure 1 is a diagrammatic view of a pinch roll device for rolled metallurgical products in accordance with the present invention, -
figure 2 is a front view of some of the components of the device infigure 1 ; -
figure 3 is a side view of the components infigure 2 , -
figure 4 is a diagrammatic view of a constructional variant of the device infigure 1 , -
figure 5 is a block diagram of a method for operating a pinch roll device for rolled metallurgic products in accordance with the present invention. - With reference to accompanying
figures 1-3 , a pinch roll device for a round-section, rolled metallurgic product is indicated by reference numeral 1 as a whole. In general, a pinch roll device provided in accordance with the present invention may be appropriately configured to hold any rolled metallurgic product, e.g. a flat-section rolled product. - Device 1 comprises a
first pinch roll 2 and asecond pinch roll 3 which is identical to thefirst roll 3, between which a substantially circular passage gap 5 for awire rod 10 is defined. Gap 5 defines a crossing axis X, coaxial to gap 5, with which thewire rod 10 is aligned in operation when passing passage gap 5. - The first and
second rolls wire rod 10 through the passage gap 5. The rotation axes Y1, Y2 are parallel to each other and equally spaced apart from the crossing axis X, with respect to which they are arranged on the opposite side. The shape and size of gap 5 comply with those of thewire rod 10, and gap 5 is delimited by twoannular grooves pinch rolls second rolls pinch rolls toothed wheels toothed wheels toothed wheels toothed drive wheels toothed drive wheel 3b, by means of amotion output shaft 3c. The motion is transmitted from the drivetoothed wheel 3b to the other drivetoothed wheel 2b and to the driventoothed wheel 3a. The motion is transmitted from the drivetoothed wheel 2b to the other driventoothed wheel 2a. Due to the described coupling, the driventoothed wheels respective rolls - The first and second arms 7, 8 are equal to each other and rotationally supported with respect to a fixed reference system integral with the crossing axis X by means of a pair of respective hinges which define a third rotation axis Z1 and a fourth rotation axis Z2, respectively, which are parallel to each other and equally spaced apart from crossing axis X, respect to which they are arranged on opposite side.
- The first and second arms 7, 8 can rotate about Z1 and Z2, respectively, to reciprocally either approach or space apart the first and
second rolls - In order to control the rotation of the lever arms 7, 8 and therefore to reciprocally approach or space apart the first and the
second rolls hydraulic circuit 20 in which a hydraulic fluid, e.g. oil, circulates and amechanical gear transmission 11, by means of which the first andsecond rolls - The
hydraulic circuit 20 is closed and pressurized, therefore no hydraulic control unit is required, and comprises ahydraulic actuator 21 connected to thefirst roll 2 to approach it to or space it apart from thesecond roll 3. Theactuator 21 comprises astem 31 hinged at afree end 31 a thereof to the first lever arm 7, close to thefirst roll 2. The translation ofstem 31 determines a corresponding rotation of the lever arm 7 about the third rotation axis Z1. The same rotation is transmitted to the second arm 8 by means oftransmission 11. - The
transmission 11, which thus allows thehydraulic actuator 21 to be connected to thesecond roll 3, by means of thefirst roll 2, comprises the lever arms 7, 8 and agear 12 between the first lever arm 7 and the second lever arm 8.Gear 12 comprises a firsttoothed sector 12a and a secondtoothed sector 12b integral with the first and second arms 7, 8, respectively, and meshing with each other so that each rotation imparted by theactuator 21 to the first arm 7 is transmitted to the second arm 8. - The first and second
toothed sectors 12a,b are provided at the end of athird arm 32 and of afourth arm 33, respectively, being integral with the first and second arms 7, 8, aligned with each other and orthogonal to crossing axis X. Thearms toothed sectors 12a, b mesh with each other at the same crossing axis X. The transmission ratio of thegear 12 is unitary so that each rotation of the first arm 7 corresponds to an equal, opposite rotation of the second arm 8.Gear 12 allows to obtain a synchronous, coordinated movement of the first and second lever arms 7, 8 and of therolls first roll 2 restrained thereto is equal and symmetric, with respect to axis X, to the assembly of the second arm 8 and thesecond roll 3 restrained thereto in all operating conditions. - According to another constructional variant of the invention (not shown), the first and
second rolls - The
hydraulic actuator 21 is of the double-effect type, comprising afirst chamber 21 a and asecond chamber 21 b, with apiston 22 connected to stem 31 and to asecondary stem 31 b sliding therebetween and being also opposed to stem 31 and having an equal diameter. In order to control the movement ofpiston 22, thehydraulic circuit 20 comprises areversible pump 9, connected to the first andsecond chambers 21 a, b of the actuator by means of afirst branch 20a and asecond branch 20b of thehydraulic circuit 20, respectively. The rotation of thereversible pump 9 in one direction or in the other allows to send oil directly to either one or the other of thechambers 21a, b ofactuator 21, respectively, thus determining the movement ofpiston 22 and stem 31 in either one direction or in the opposite direction. -
Pump 9 which controls the movement ofpiston 22 is operated by anelectric motor 9a; the position ofpiston 22 inside the cylinder thus depends on the angular position of themotor 9a ofpump 9, while the movement speed of the cylinder depends on the angular speed ofpump 9. - As the
hydraulic circuit 20 is closed and pressurized, i.e. free from hydraulic control unit, the same amount of fluid always circulates therein. Themotor 9a ofpump 9 determines each fluid movement in the hydraulic circuit 20: therefore, ifmotor 9a does not operate thepump 9, the fluid flow in each point of thehydraulic circuit 20 is substantially zero and thepiston 22 does not move. - A connection branch is provided between the
first branch 20a and thesecond branch 20b of thehydraulic circuit 20, being equipped with amaximum pressure valve 29 calibrated so as to protect the hydraulic circuit from pressure overloads resulting from excessive, even pulsing loads applied to thefirst roll 2 and transmitted to theactuator 2 throughstem 31. The first andsecond branches 20a, b are connected upstream of thereversible pump 9 to a top-upsource 27, which allows to top-up any leakage of fluid from thehydraulic circuit 20. Afirst check valve 28a and asecond check valve 28b, oriented so as to prevent the flow from thepump 9 to the top-upsource 27 and to allow the flow in the opposite direction, are provided between the top-upsource 27 and thereversible pump 9 on the first andsecond branches 20a, b, respectively. - The amount of fluid needed for the operation of the
hydraulic circuit 20, given by the sum of the circulating fluid and the fluid present in the top-upsource 27, may advantageously range from 0.5 to 2 liters, preferably from 0.7 to 1.4 liters. As thehydraulic circuit 20 is closed, it is also possible to contain its size: the overall length of the hydraulic line in which the fluid circulates is advantageously from 0.5 to 1.5 meters, preferably from 0.7 to 1 meter. - The
reversible pump 9 and thus theactuator 21 are actuated in a controlled manner. Afeedback control circuit 30 is included, comprising theelectric motor 9a connected to pump 9 by means of aconnector 9b. Thecontrol circuit 30 further comprises apressure sensor 25, located in thefirst branch 20a of thehydraulic circuit 20, between the actuator 21 and themaximum pressure valve 29, and aposition sensor 24 in theactuator 21. Thepressure sensor 25 allows to measure the pressure in the circuit, and in particular in thechamber 21a, and thus to determine the force F1 transmitted by theactuator 21 to thefirst roll 2 through thestem 31. Force F1 is transmitted from the first roll to thewire rod 10. In order to achieve the device balance, obtained through the connection between the arms 7, 8 by means oftransmission 11, an equal opposite force F2 transmitted from thesecond roll 3 to thewire rod 10 corresponds to force F1. The rolling force and pressure can be controlled by controlling the pressure in thehydraulic circuit 20. Theposition sensor 24 allows to measure the movement ofpiston 22, and thus to determine the movement of thefirst roll 2. The position of thefirst roll 2 can be controlled by controlling the position ofpiston 22, therefore by means of thetransmission 11, the position of thesecond roll 3 can also be controlled, thus adjusting the width of the passage gap 5. Thecontrol circuit 30 further comprises acontrol unit 26 by means of which theelectric motor 9a is controlled. Thecontrol unit 26 is connected to theposition sensor 24 and to thepressure sensor 25, so to obtain a feedback control. Thecontrol unit 26 receives pressure and position data measured by thesensors control unit 26 then compares these values to respective reference values and therefore controls theelectric motor 9a to either modify or keep the force F1 and the width of the passage gap 5, according to anoperation method 100, the significant steps of which are described below. - With reference to
figure 4 , a constructional variant of a pinch roll device for a wire rod, indicated byreference numeral 40 as a whole, differs from device 1 in that it comprises a differenthydraulic circuit 41, as described in greater detail below. Other components ofdevice 40 are not described in detail because they are identical to the above-described respective components of device 1. Thehydraulic circuit 41 differs from thehydraulic circuit 20 of device 1 in that it comprises a pair of single-effect,hydraulic actuators first roll 2 and to thesecond roll 3, respectively, instead of the double-effect,hydraulic actuator 21. Each of thehydraulic actuators piston 22 sliding between a respective upperfirst chamber lower chamber upper chambers hydraulic actuators second branches 20a, b of thehydraulic circuit 41, respectively. Thelower chambers hydraulic actuators compensation circuit 44, by means of which the first andsecond rolls first roll 2 is moved from and to saidsecond roll 3, the latter is simultaneously moved from and to thefirst roll 2. As in the variant infigure 3 , in the variant infigure 4 , thefirst roll 2 and thesecond roll 3 are also either symmetrically spaced apart or approached with respect to the crossing axis X. When thereversible pump 9 sends oil directly to theupper chamber 42a ofactuator 42 by means of thefirst branch 20a, therespective piston 22 moves towards thelower chamber 42b, while simultaneously pushing the oil through thecompensation circuit 44, into thelower chamber 43b ofactuator 43, therespective piston 22 of which moves towards the respectiveupper chamber 43a. Alternatively, when thereversible pump 9 sends oil directly to theupper chamber 43a ofactuator 43 by means of thesecond branch 20b, therespective piston 22 moves towards thelower chamber 43b, while simultaneously pushing the oil through thecompensation circuit 44, into thelower chamber 42b ofactuator 42, in which therespective piston 22 moves towards the respectiveupper chamber 42a. - According to a further constructional variant of the invention (not shown), a pinch roll device according to the present invention comprises a hydraulic circuit similar to
circuit 41 but not including thetransmission 11. - With reference to the diagram in
figure 5 , theoperation method 100 of device 1, which may be implemented in thecontrol unit 26, comprises aninitial step 50 in which the method checks whether therolls rolls method 100 ends going to a next stoppingstep 51. If therolls toothed wheels method 100 continues with anext step 52 in which it checks whether thecontrol motor 9a ofpump 9 is off or running. If themotor 9a is off, themethod 100 ends and goes to the stoppingstep 51. If themotor 9a is running, themethod 100 continues with a next step of setting the reference values 53, in which the type and features of the product being machined, e.g. thewire rod 10, are identified and afirst reference value 61 of the position ofpiston 22 and asecond reference value 71 of the pressure in thecircuit 20 are set as a function of the identified product. - The
method 100 continues with anext step 54 of checking the presence or absence of the metallurgic product to be machined, e.g. thewire rod 10, in the passage gap 5 between therolls step 54, thecontrol unit 26 receives an external datum which identifies the presence or absence of the metallurgic product to be machined, obtained by means of one or more sensors (not shown), e.g. photocells, arranged upstream of the passage gap 5 and connected to thecontrol unit 26. - When the absence of the metallurgic product to be machined in the passage gap 5 is identified during the checking
step 54, themethod 100 continues with astep 110 of checking the position ofpiston 22 and thus of thefirst roll 2. Alternatively, when the presence of metallurgic product to be machined is identified in the passage gap 5 in the checkingstep 54, themethod 100 continues with apressure checking step 120, in which the pressure withinactuator 21 is checked. - At the end of either the
position checking step 110 and thepressure checking step 120, themethod 100 includes thestep 80 of checking the end of machining, in which it checks, by means of a signal supplied by thecontrol unit 26, e.g. by means of a switch or other type of control actuatable by an operator, whether the machining process is underway or has ended. If the rolling process has ended, themethod 100 ends with afinal step 81 in which the first andsecond rolls method 100 continues by repeatingstep 53 of setting the reference values. - If the
position checking step 110 comprises afirst sub-step 60 of determining, by means of the measurement supplied by theposition sensor 24, a measured value of the current position ofpiston 22, which can be associated with the position of thefirst roll 2 due to the connection by means ofstem 31. A secondposition comparing sub-step 62 follows the first sub-step in order to compare the measured value of the position identified by the first sub-step 60 with thereference position value 61. The comparison is carried out by subtracting the measured value from the reference value. Theposition checking step 110 continues with athird checking sub-step 64, in which the method checks whether the subtraction carried out during the second sub-step 62 has a zero result or a result different from zero. If the result is zero, theposition checking step 110 ends and themethod 100 continues with the machining-end checking step 80, while if the result if other than zero, theposition checking step 110 continues with a fourth sub-step 63, in which a movement is imposed by means of themotor 9a and thereversible pump 9 on thepiston 22 to reach the position corresponding to thereference value 61. The movement imposed on thepiston 22 is proportional to the difference between the measured position value and thereference position value 61. At the end of the fourth sub-step 63, theposition checking step 110 ends and themethod 100 continues with the machining-end checking step 80. - The
pressure checking step 120 comprises a fifth fast approachingsub-step 59, in which therolls sixth sub-step 70 of determining a measured value of the pressure in thefirst branch 20a of thehydraulic circuit 20, upstream of thereversible pump 9, by means of the measurement supplied by thepressure sensor 25, which pressure value can be associated with the pressure of thefirst chamber 21a ofactuator 21 due to the proximity of thepressure sensor 25 to theactuator 21. A seventhpressure comparing sub-step 72 follows the sixth sub-step to compare the measured pressure value identified in the sixth sub-step 70 with thereference position value 71. The comparison is carried out by subtracting the measured value from the reference value. Thepressure checking step 120 continues with a eighth checkingsub-step 75, in which the method checks whether the result of the subtraction carried out in the seventh sub-step 72 is zero or different from zero, If the result is zero, thepressure checking step 120 proceeds with aninth sub-step 74 of refreshing the reference position, in which thefirst reference value 61 of the position ofpiston 22 is updated to the current value. At the end of the ninth sub-step 74, thepressure checking step 120 is carried out, and themethod 100 continues with the machining-end checking step 80. If the result of the subtraction calculated in the eighth checkingsub-step 75 is not zero, but other than zero, thepressure checking step 120 proceeds with a tenth sub-step 73, in which a movement is imposed by means of themotor 9a and thereversible pump 9 on thepiston 22 to reach the pressure corresponding to thereference value 71. The movement imposed on thepiston 22 is proportional to the difference between the measured pressure value and thereference pressure value 71. At the end of the tenth sub-step 73, thepressure checking step 120 ends and themethod 100 continues with the machining-end checking step 80. - The above-described method, in which the
force checking step 110 and theposition checking step 120 are carried out alternatively to each other, may be carried out very rapidly, at a frequency typically of the order of 3000 Hz. This results in the possibility of reaching feeding speeds along the crossing axis X for the products to be machined of the order of 150 m/s. - The above-described
method 100 may be also used in pinch roll devices other than device 1, provided that they comprise: - a first pinch roll and a second pinch roll, a passage gap for a rolled metallurgic product being defined therebetween, which are rotatable about a first rotation axis Y1 and second rotation axis Y2, respectively, to draw by friction said metallurgic product through the passage gap,
- a hydraulic actuator connected to the rolls to approach them or space them apart in a controlled manner, so as to reduce or increase the width of the passage gap, respectively,
- a reversible pump connected to the hydraulic actuator to slidingly move the piston connected to the first and/or second pinch roll.
- The described technical solutions allow to fully solve the set task and objects with reference to the mentioned prior art, thus obtaining a plurality of further advantages, including:
- using a high-efficiency, closed hydraulic circuit in which only a minimum amount of fluid is moved, i.e. only that needed for moving the piston of the hydraulic actuator. This allows to obtain a hydraulic circuit characterized by high reactivity. This is further encouraged by the use of a hydraulic pump controlled by an electric motor which allows to reach operating speeds (up to 200 - 300 Hz), which are significantly higher than those which can be achieved by means of servo valves;
- obtaining a device which is not affected by the inevitable wear of the pinch rolls, which may be compensated by the rotation of the lever arms which support the rolls;
- providing a self-damping system, in which the damping function is performed by the fluid in the hydraulic control circuit and which thus does not require the insertion of additional damping elements;
- using a hydraulic system free from servo valves thus allowing to significantly reduce running and maintenance costs.
Claims (10)
- A pinch roll device (1, 40) for rolled metallurgic products, comprising:- a first pinch roll (2) and a second pinch roll (3), between which a passage gap (5) for a rolled metallurgic product (10) is defined, said first and second rolls (2, 3) being rotatable about first and second rotation axes (Y1, Y2), respectively, to draw by friction said metallurgic product (10) through said gap (5),- a hydraulic circuit (20, 41) acting on said first and second rolls (2, 3) to reciprocally either approach or space apart said first and second rolls (2, 3) so as to either reduce or increase the width of said passage gap (5), respectively, said hydraulic circuit (20) comprising at least one hydraulic actuator (21, 42, 43) connected to said first roll (2) and/or to said second roll (3) to either reciprocally approach or space apart said first and second rolls (2, 3),- a pressure sensor (25) in said hydraulic circuit (20, 41) to determine the force transmitted by said actuator (21, 42) to said first roll (2) and/or to said second roll (3),- a position sensor (24) in said actuator (21, 42) to determine the movement of said first roll (2) and/or of said second roll (3),
characterized in that said hydraulic circuit (20, 41) is a closed and pressurized circuit and in that it further comprises:- a reversible pump (9) in said hydraulic circuit (20, 41), said pump (9) being connected to a first chamber (21 a, 42a) and a second chamber (21 b, 43a) of said at least one hydraulic actuator (21, 42, 43) to slidingly move a piston (22) of said at least one hydraulic actuator (21, 42, 43), said piston being connected to said first roll (2) and/or to said second roll (3), the rotation of said reversible pump (9) in one direction or in the other allowing to send a fluid directly to either one or the other of said first and second chambers (21 a, 42a; 21 b, 43a), respectively and wherein said reversible pump (9) is operated by an electric motor (9a) which determines each fluid movement in said hydraulic circuit. - A pinch roll device (1) according to claim 1, wherein said first and second rolls (2, 3) are reciprocally interconnected by means of a mechanical and/or hydraulic connection (11, 44).
- A pinch roll device (1) according to claim 2, wherein said hydraulic circuit (20, 41) comprises a hydraulic actuator (21, 42) connected to said first roll (2) and said connection (11, 44) comprises a geared transmission (11) between said first and second rolls (2, 3) to connect said hydraulic actuator (21, 42) to said second roll (3), by means of said first roll (2).
- A pinch roll device (1) according to claim 2 or 3, wherein said hydraulic circuit (41) comprises a pair of hydraulic actuators (42, 43) connected to said first and second rolls (2, 3), respectively, to move said first roll (2) from and to said second roll (3) while moving said second roll (3) from and to said first roll (2), said connection (11, 44) comprising a compensation circuit (44) between said first and second rolls (2, 3).
- A pinch roll device (1) according to claim 3 or 4, wherein said transmission (11) comprises first and second lever arm (7, 8), said first and second rolls (2, 3) being respectively restrained thereto, so as to rotate about respective rotation axes (Y1, Y2), said first and second arm (7, 8) being rotatable about a third rotation axis and a fourth rotation axis (Z1, Z2), respectively, to reciprocally either approach or space apart said first and second rolls (2, 3), said gear (12) comprising at least a first toothed sector (12a) and a second toothed sector (12b), integral with said first and second arms (7, 8), respectively, said first and second toothed sectors (12a, 12b) being meshed with each other to transmit the rotation between said first and second levers (7, 8).
- A pinch roll device (1) according to claim 5, wherein said first, second, third and fourth rotation axes (Y1, Y2, Z1, Z2) are parallel to one another.
- A pinch roll device (1) according to claim 1, wherein said pump (9) is controlled by an electric motor (9a) controlled means of a control unit (26) connected to said position sensor (24) and to said pressure sensor (25), the position of said piston (22) depending on the angular position of said motor (9a), the speed of said piston (22) depending on the angular speed of said pump (9).
- A method (100) of operating a pinch roll device (1) for rolled metallurgic products, said device comprising:- a first pinch roll (2) and a second pinch roll (3), between which a passage gap (5) for a rolled metallurgic product (10) is defined, said first and second rolls (2, 3) being rotatable about first and second rotation axes (Y1, Y2), respectively, to draw by friction said metallurgic product (10) through said gap,- a hydraulic closed and pressurized circuit (20, 41) comprising at least one hydraulic actuator (21, 42, 43) connected to said first roll and second roll (2, 3) to reciprocally either approach or space apart said rolls (2, 3) so as to either reduce or increase the width of said passage gap (5), respectively,- a reversible pump (9) connected to a first chamber (21a, 42a) and a second chamber (21b, 43a) of said at least one hydraulic actuator (21, 42, 43) to slidingly move a piston (22) of said at least one hydraulic actuator (21, 42, 43), said piston being connected to said first roll (2) and/or to said second roll (3), and wherein said reversible pump (9) is operated by an electric motor (9a) which determines each fluid movement in said hydraulic circuitsaid method (100) comprising:- a step (54) of checking either the presence or absence of said metallurgic product (10) in said passage gap (5),- a step (110) of checking the position of said first roll (2), implemented when the absence of said metallurgic product (10) in said passage gap (5) is identified in said checking step (54),- a step (120) of checking the pressure of said hydraulic actuator (21), implemented when the presence of said metallurgic product (10) in said passage gap (5) is identified, said pressure checking step (120) comprising a sub-step (74) of refreshing said position reference value, said sub-step (74) of refreshing said position reference value is operated when said measured pressure value is identified as equal to said pressure reference value in said pressure comparing sub-step (72).
- An operation method (100) according to claim 8, wherein said step (110) of checking the position of said first roll (2) comprises a position comparing sub-step (62) to compare a measured position value, which may be associated with the position of said first roll (2), with a reference position value.
- An operation method (100) according to claim 8 or 9, wherein said step (120) of checking the pressure in said hydraulic actuator (21) comprises a pressure comparing sub-step (72) to compare a measured pressure value, which may be associated with said hydraulic actuator (21), with a reference pressure value.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT001274A ITMI20111274A1 (en) | 2011-07-08 | 2011-07-08 | DRIVING DEVICE FOR LAMINATED METALLURGICAL PRODUCTS |
PCT/IB2012/053464 WO2013008159A2 (en) | 2011-07-08 | 2012-07-06 | Pinch roll device for rolled metallurgic products |
Publications (3)
Publication Number | Publication Date |
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EP2729263A2 EP2729263A2 (en) | 2014-05-14 |
EP2729263B1 EP2729263B1 (en) | 2015-11-18 |
EP2729263B9 true EP2729263B9 (en) | 2016-04-13 |
Family
ID=44511227
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP12748552.2A Active EP2729263B9 (en) | 2011-07-08 | 2012-07-06 | Pinch roll device |
Country Status (7)
Country | Link |
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US (1) | US20140137617A1 (en) |
EP (1) | EP2729263B9 (en) |
JP (1) | JP5806400B2 (en) |
KR (1) | KR20140032480A (en) |
CN (1) | CN103702776B (en) |
IT (1) | ITMI20111274A1 (en) |
WO (1) | WO2013008159A2 (en) |
Families Citing this family (8)
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CN106807763B (en) * | 2015-11-27 | 2018-09-11 | 北京京诚瑞信长材工程技术有限公司 | A kind of pinch roller structural assembly |
CN106269924B (en) * | 2016-10-13 | 2019-02-19 | 北京京诚瑞信长材工程技术有限公司 | Pinch roller |
CN110052501B (en) * | 2019-04-15 | 2020-03-13 | 燕山大学 | Spring swinging box type under-actuated symmetrical clamping and conveying mechanism |
CN110883108B (en) * | 2019-11-19 | 2021-09-07 | 张家港宏昌钢板有限公司 | Spiral shell production and processing device with pinch roll |
CN111330982A (en) * | 2020-03-16 | 2020-06-26 | 哈尔滨哈飞工业有限责任公司 | Control system of pinch roll of high-speed wire rod production line |
CN112518017B (en) * | 2020-11-17 | 2023-09-12 | 中冶华天南京工程技术有限公司 | Intelligent adjusting system and adjusting method for pinch roll before shearing |
CN115159225A (en) * | 2022-06-30 | 2022-10-11 | 广西广盛新材料科技有限公司 | Roll gap deviation control method, roll gap deviation control device, computer and readable storage medium |
CN116037698B (en) * | 2023-02-07 | 2023-07-21 | 浙江菲尔特过滤科技股份有限公司 | Metal fiber processing equipment and processing method based on roll forging |
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DE2412642A1 (en) * | 1974-03-13 | 1975-09-18 | Mannesmann Meer Ag | CONTINUOUS COOLING DEVICE FOR A COIL ROLLING MILL IN A PLANT FOR HOT ROLLING COPPER TUBE BLUDS |
US4294917A (en) | 1979-05-22 | 1981-10-13 | Ciba-Geigy Ag | Photographic silver halide material containing a dye filter or a dye anti-halation layer |
JPS5954803A (en) * | 1982-09-22 | 1984-03-29 | Komatsu Ltd | Hydraulic system |
JPS60240912A (en) * | 1984-05-15 | 1985-11-29 | Sanki Eng Co Ltd | Hydraulic device for control of movable fire grate in refuse incinerator |
DE3507251A1 (en) * | 1985-03-01 | 1986-09-04 | SMS Schloemann-Siemag AG, 4000 Düsseldorf | DRIVER FOR ROLLER TAPE |
JPS63218458A (en) * | 1987-03-05 | 1988-09-12 | Sumitomo Metal Ind Ltd | Hydraulic motor drive device |
JPH0238020A (en) * | 1988-07-29 | 1990-02-07 | Hiroshi Sato | Apparatus and method for electrically controlling liquid pressure of plastic molding machine |
CN2067613U (en) * | 1990-02-24 | 1990-12-19 | 冶金工业部钢铁研究总院 | Hydraulic system for axially moving roller |
DE4238154A1 (en) * | 1992-11-12 | 1994-05-19 | Schloemann Siemag Ag | Hydraulic feed drive for flying upsetting presses |
JPH0852514A (en) * | 1994-08-12 | 1996-02-27 | Ishikawajima Harima Heavy Ind Co Ltd | Pinch roll device |
JPH10166199A (en) * | 1996-12-05 | 1998-06-23 | Daiichi Denki Kk | Plastic working device of hydraulic drive system |
JP2000246317A (en) * | 1999-03-02 | 2000-09-12 | Daido Steel Co Ltd | Reduction mechanism |
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JP2002147405A (en) * | 2000-11-14 | 2002-05-22 | Toyooki Kogyo Co Ltd | Hydraulic driver |
US6920772B1 (en) * | 2003-02-12 | 2005-07-26 | Morgan Construction Company | Pinch roll unit |
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-
2011
- 2011-07-08 IT IT001274A patent/ITMI20111274A1/en unknown
-
2012
- 2012-07-06 EP EP12748552.2A patent/EP2729263B9/en active Active
- 2012-07-06 WO PCT/IB2012/053464 patent/WO2013008159A2/en active Application Filing
- 2012-07-06 JP JP2014518056A patent/JP5806400B2/en active Active
- 2012-07-06 US US14/131,388 patent/US20140137617A1/en not_active Abandoned
- 2012-07-06 KR KR1020147001134A patent/KR20140032480A/en not_active Application Discontinuation
- 2012-07-06 CN CN201280033730.0A patent/CN103702776B/en active Active
Also Published As
Publication number | Publication date |
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US20140137617A1 (en) | 2014-05-22 |
EP2729263B1 (en) | 2015-11-18 |
KR20140032480A (en) | 2014-03-14 |
EP2729263A2 (en) | 2014-05-14 |
CN103702776A (en) | 2014-04-02 |
CN103702776B (en) | 2017-02-15 |
WO2013008159A3 (en) | 2013-03-14 |
ITMI20111274A1 (en) | 2013-01-09 |
WO2013008159A2 (en) | 2013-01-17 |
JP5806400B2 (en) | 2015-11-10 |
JP2014521514A (en) | 2014-08-28 |
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