Method and device for predicting power consumption per ton of steel for screw-down mechanism

Abstract

The invention provides a ton steel power consumption prediction method and device for a pressing mechanism, and belongs to the technical field of steel rolling, and the method comprises the steps: determining the number of total pressing passes of a to-be-produced steel plate and the rolling reduction of each pass according to the preset steel plate production thickness; according to the rolling reduction of each pass, the rolling power consumption of the rolling mechanism in each pass and the lifting power consumption of the rolling mechanism in the reset process are determined; and according to the pressing power consumption, the lifting power consumption and the weight of the steel plate to be produced, the power consumption per ton of steel of the pressing mechanism is determined. According to the technical scheme, theoretical calculation of the power consumption of the rolling mill screw-down mechanism of each pass can be carried out in combination with the engineering actual rolling schedule, single-rack multi-pass rolling full-schedule power consumption prediction is achieved, the relation between the power consumption per ton of steel and the rolling schedule in the single-rack multi-pass rolling process is quantified, and the prediction accuracy is improved. The method has guiding significance in the aspects of rolling schedule setting, steel mill production scheduling, power consumption saving and the like, and meanwhile, the method also plays a reference role in motor type selection design of a rolling mill screw-down system.

Description

Technical Field

[0001] This application belongs to the technical field of steel rolling. Specifically, it relates to a method, device, electronic device, computer-readable storage medium, and computer program product for predicting the power consumption per ton of steel for a screwdown mechanism. Background Art

[0002] Heavy plates are important steel products, widely used in various industries such as infrastructure construction, shipbuilding, construction machinery, containers, energy, and construction, and play an important role in national economic construction. With the gradual advancement of the green and sustainable development strategy and the approaching of the important time nodes of the "dual carbon" goal, the requirements for power consumption in the heavy plate rolling process are getting higher and higher, and quantitative research on it is needed. For the convenience of comparison, a new parameter - power consumption per ton of steel, that is, the electric energy consumed to produce one ton of steel, is proposed.

[0003] However, currently, there are rich varieties of heavy plate steel grades, and the incoming material specifications and target specifications are also different, making it increasingly difficult to quantitatively predict the power consumption per ton of steel for the screwdown mechanism. Summary of the Invention

[0004] Aiming at at least one problem existing in the prior art, this application provides a method and device for predicting the power consumption per ton of steel for a screwdown mechanism, which can combine the actual engineering rolling schedule, perform theoretical calculations on the power consumption of the screwdown mechanism of the rolling mill in each pass, and achieve the prediction of the power consumption of the entire rolling schedule of multi-pass rolling of a single stand.

[0005] According to the first aspect of this application, a method for predicting the power consumption per ton of steel for a screwdown mechanism is provided, including:

[0006] Determine the total number of screwdown passes and the screwdown amount in each pass of the steel plate to be produced according to the preset production thickness of the steel plate.

[0007] Determine the screwdown power consumption of the screwdown mechanism in each pass and the lifting power consumption of the screwdown mechanism during the reset process according to the screwdown amount in each pass.

[0008] Determine the power consumption per ton of steel of the screwdown mechanism according to the screwdown power consumption, the lifting power consumption, and the weight of the steel plate to be produced.

[0009] In some optional ways of this embodiment, it further includes:

[0010] Determine the equivalent static torque, equivalent dynamic torque, lifting equivalent static torque of the screwdown mechanism, the first rotational speed acceleration when the motor accelerates, the second rotational speed acceleration when the motor decelerates, the motor screwdown acceleration time, the motor screwdown deceleration time, the motor lifting acceleration time, and the motor lifting deceleration time.

[0011] In some optional ways of this embodiment, the determining the screwdown power consumption of the screwdown mechanism in each pass according to the screwdown amount in each pass includes:

[0012] Determine the first reduction power change of the reduction mechanism when the motor accelerates according to the equivalent static torque of reduction, the equivalent dynamic torque, and the first rotational speed acceleration.

[0013] Determine the maximum rotational speed of the motor for reduction of the reduction mechanism in each pass according to the reduction amount in each pass.

[0014] Determine the second reduction power change of the motor of the reduction mechanism during deceleration according to the maximum rotational speed of the motor for reduction, the second rotational speed acceleration, the motor reduction acceleration time, the equivalent static torque of reduction, and the equivalent dynamic torque.

[0015] Determine the reduction power consumption of the reduction mechanism in each pass according to the motor reduction acceleration time, the motor reduction deceleration time, the first reduction power change, and the second reduction power change.

[0016] In some optional embodiments of the present embodiment, the determining the reduction power consumption of the reduction mechanism in each pass according to the reduction amount in each pass includes:

[0017] Determine the maximum rotational speed of the motor for reduction of the reduction mechanism in each pass according to the reduction amount in each pass.

[0018] Determine the reduction power consumption of the reduction mechanism in each pass according to the equivalent static torque of reduction, the maximum rotational speed of the motor for reduction, the first rotational speed acceleration, and the second rotational speed acceleration.

[0019] In some optional embodiments of the present embodiment, the determining the maximum rotational speed of the motor for reduction of the reduction mechanism in each pass according to the reduction amount in each pass includes:

[0020] Obtain the worm gear transmission ratio and the pitch of the reduction screw of the reduction mechanism.

[0021] Determine the maximum rotational speed of the motor for reduction of the reduction mechanism in each pass according to the worm gear transmission ratio, the pitch of the reduction screw, the first rotational speed acceleration, the second rotational speed acceleration, and the reduction amount in each pass.

[0022] In some optional embodiments of the present embodiment, the determining the lifting power consumption of the reduction mechanism during the reset process according to the reduction amount in each pass includes:

[0023] Determine the first lifting power change of the motor of the reduction mechanism when the motor accelerates according to the equivalent static torque of lifting, the equivalent dynamic torque, and the first rotational speed acceleration.

[0024] Determine the maximum rotational speed of the motor for lifting of the reduction mechanism according to the reduction amount in each pass.

[0025] Determine the second lifting power change during the motor deceleration of the screw down mechanism according to the lifted equivalent static torque, the equivalent dynamic torque, the second rotational speed acceleration, the maximum rotational speed of the motor for lifting, and the motor lifting acceleration time.

[0026] Determine the lifting power consumption of the screw down mechanism during the reset process according to the motor lifting acceleration time, the motor lifting deceleration time, the first lifting power change, and the second lifting power change.

[0027] In some optional embodiments of the present embodiment, determining the lifting power consumption of the screw down mechanism during the reset process according to the screw down amount of each pass includes:

[0028] Determine the maximum rotational speed of the motor for lifting of the screw down mechanism according to the screw down amount of each pass.

[0029] Determine the lifting power consumption of the screw down mechanism during the reset process according to the lifted equivalent static torque, the maximum rotational speed of the motor for lifting, the first rotational speed acceleration, and the second rotational speed acceleration.

[0030] In some optional embodiments of the present embodiment, determining the maximum rotational speed of the motor for lifting of the screw down mechanism according to the screw down amount of each pass includes:

[0031] Obtain the worm gear ratio of the screw down mechanism and the pitch of the screw down screw.

[0032] Determine the total screw down amount of the screw down mechanism during the screw down process according to the screw down amount of each pass.

[0033] Determine the maximum rotational speed of the motor for lifting of the screw down mechanism according to the worm gear ratio, the total screw down amount, the pitch of the screw down screw, the first rotational speed acceleration, and the second rotational speed acceleration.

[0034] In some optional embodiments of the present embodiment, determining the screw down equivalent static torque of the screw down mechanism includes:

[0035] Determine the first frictional torque between the pivot portion of the screw down screw and the thrust block.

[0036] Determine the second frictional torque between the screw down screw and the nut thread.

[0037] Determine the screw down equivalent static torque of the screw down mechanism according to the first frictional torque, the second frictional torque, the worm gear ratio of the screw down mechanism, and the transmission efficiency of the screw down mechanism.

[0038] In some optional embodiments of the present embodiment, determining the first frictional torque between the pivot portion of the screw down screw and the thrust block includes:

[0039] Determine the acting force of the screw down mechanism on a screw down screw, the sliding friction coefficient between the thrust washer and the pivot, and the average diameter of the thrust rolling bearing;

[0040] Determine the first frictional torque between the pivot portion of the screw down screw and the thrust block according to the acting force, the sliding friction coefficient, and the average diameter of the thrust rolling bearing.

[0041] In some optional embodiments, the determination of the second frictional torque between the screw down screw and the nut thread includes:

[0042] Determine the friction angle between the screw down screw and the nut, the lead angle between the screw down screw and the nut thread, the pitch, and the pitch diameter of the screw down screw;

[0043] Determine the second frictional torque between the screw down screw and the nut thread according to the friction angle, the lead angle, the pitch, and the pitch diameter of the screw down screw.

[0044] In some optional embodiments, the determination of the acting force of the screw down mechanism on a screw down screw includes:

[0045] Determine the hydraulic cylinder pressure of the upper backup roll balance mechanism according to the total gravity of the upper backup roll balance force balance components and the upper backup roll balance coefficient;

[0046] Determine the bending roll pressure of the upper work roll according to the total gravity of the upper work roll balance force balance components and the upper work roll balance coefficient;

[0047] Determine the overbalance force of the upper backup roll balance according to the total gravity of the upper backup roll balance force balance components and the hydraulic cylinder pressure of the upper backup roll balance mechanism;

[0048] Determine the overbalance force of the upper work roll balance according to the total gravity of the upper work roll balance force balance components and the bending roll pressure of the upper work roll;

[0049] Determine the total overbalance force according to the overbalance force of the upper backup roll balance and the overbalance force of the upper work roll balance, and determine the acting force of the screw down mechanism on a screw down screw according to the total overbalance force.

[0050] In some optional embodiments, the determination of the equivalent dynamic torque of the screw down mechanism includes:

[0051] Determine the sum of the flywheel torques of all rotating parts on the screw down screw shaft, the sum of the flywheel torques of the rotating parts on the motor reducer shaft, and the sum of the flywheel torques of all moving parts in the screw down mechanism;

[0052] Determine the equivalent driving torque of the screw-down mechanism according to the worm gear transmission ratio of the screw-down mechanism, the sum of the flywheel torques of all rotating parts on the screw-down screw shaft, the sum of the flywheel torques of the rotating parts on the motor reducer shaft, and the sum of the flywheel torques of all moving parts in the screw-down mechanism.

[0053] In some alternative embodiments of the present embodiment, determining the sum of the flywheel torques of all rotating parts on the screw-down screw shaft includes:

[0054] Determine the worm wheel flywheel torque according to the worm wheel tooth flywheel torque and the worm wheel central shaft flywheel torque;

[0055] Determine the sum of the flywheel torques of all relevant rotating parts on the screw-down screw shaft according to the flywheel torque of the screw-down screw and the flywheel torques of other rotating parts;

[0056] Determine the sum of the flywheel torques of all rotating parts on the screw-down screw shaft according to the worm wheel flywheel torque and the sum of the flywheel torques of all relevant rotating parts on the screw-down screw shaft.

[0057] In some alternative embodiments of the present embodiment, determining the sum of the flywheel torques of the rotating parts on the motor reducer shaft includes:

[0058] Determine the flywheel torque of the motor, the flywheel torque of the reducer worm, and the flywheel torque of the brake disc coupling;

[0059] Determine the sum of the flywheel torques of the rotating parts on the motor reducer shaft according to the flywheel torque of the motor, the flywheel torque of the reducer worm, and the flywheel torque of the brake disc coupling.

[0060] In some alternative embodiments of the present embodiment, determining the sum of the flywheel torques of all moving parts in the screw-down mechanism includes:

[0061] Determine the screw-down speed of the screw-down screw, the weights of all moving parts in the screw-down mechanism, and the rated speed of the motor output shaft;

[0062] Determine the sum of the flywheel torques of all moving parts in the screw-down mechanism according to the screw-down speed of the screw-down screw, the weights of all moving parts in the screw-down mechanism, and the rated speed of the motor output shaft.

[0063] In some alternative embodiments of the present embodiment, determining the lifting equivalent static torque of the screw-down mechanism includes:

[0064] Determine the third frictional torque between the screw-down screw and the nut thread according to the friction angle, the lead angle, the pitch, and the mean diameter of the screw-down screw;

[0065] Determine the equivalent static torque for lifting of the screwdown mechanism based on the first frictional torque, the third frictional torque, the worm gear transmission ratio of the screwdown mechanism, and the transmission efficiency of the screwdown mechanism.

[0066] In some alternative embodiments of the present embodiment, determining the motor screwdown acceleration time and the motor screwdown deceleration time includes:

[0067] Determine the motor screwdown acceleration time based on the first rotational speed acceleration and the maximum motor screwdown speed;

[0068] Determine the motor screwdown deceleration time based on the second rotational speed acceleration and the maximum motor screwdown speed.

[0069] In some alternative embodiments of the present embodiment, determining the motor lifting acceleration time and the motor lifting deceleration time includes:

[0070] Determine the motor lifting acceleration time based on the first rotational speed acceleration and the maximum motor lifting speed;

[0071] Determine the motor lifting deceleration time based on the second rotational speed acceleration and the maximum motor lifting speed.

[0072] In some alternative embodiments of the present embodiment, determining the specific power consumption of the screwdown mechanism per ton of steel based on the screwdown power consumption, the lifting power consumption, and the weight of the steel plate to be produced includes:

[0073] Determine the total screwdown power consumption of the screwdown mechanism based on the screwdown power consumption of the screwdown mechanism in each pass;

[0074] Determine the specific power consumption of the screwdown mechanism per ton of steel based on the total screwdown power consumption, the lifting power consumption, and the weight of the steel plate to be produced.

[0075] According to the second aspect of the present application, there is also provided a device for predicting the specific power consumption of a screwdown mechanism per ton of steel, the device including:

[0076] A pass determination module configured to determine the total number of screwdown passes of the steel plate to be produced and the screwdown amount for each pass according to a preset steel plate production thickness;

[0077] A first power consumption determination module configured to determine the screwdown power consumption of the screwdown mechanism in each pass and the lifting power consumption of the screwdown mechanism during the reset process according to the screwdown amount for each pass;

[0078] A second power consumption determination module configured to determine the specific power consumption of the screwdown mechanism per ton of steel based on the screwdown power consumption, the lifting power consumption, and the weight of the steel plate to be produced.

[0079] According to the third aspect of the present application, there is also provided an electronic device, including a memory, a processor, and a computer program stored on the memory and executable on the processor. When the processor executes the program, the steps of the method for predicting the power consumption per ton of steel for a screwdown mechanism are implemented.

[0080] According to the fourth aspect of the present application, there is also provided a computer-readable storage medium, on which a computer program is stored. When the computer program is executed by a processor, the steps of the method for predicting the power consumption per ton of steel for a screwdown mechanism are implemented.

[0081] According to the fifth aspect of the present application, there is also provided a computer program product, including a computer program / instructions. When the computer program / instructions are executed by a processor, the steps of the method for predicting the power consumption per ton of steel for a screwdown mechanism are implemented.

[0082] The method and device for predicting the power consumption per ton of steel for a screwdown mechanism provided by the present application can combine the actual engineering rolling schedule, perform theoretical calculations on the power consumption of the screwdown mechanism of each pass of the rolling mill, achieve the prediction of the power consumption of the entire process of single-stand multi-pass rolling, quantify the relationship between the power consumption per ton of steel and the rolling schedule in the process of single-stand multi-pass rolling, and have guiding significance for aspects such as the setting of the rolling schedule, the production scheduling of steel mills, and the saving of power consumption. At the same time, it also plays a reference role in the motor selection design of the screwdown system of the rolling mill. Description of the Drawings

[0083] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the following will briefly introduce the drawings required to be used in the description of the embodiments or the prior art. Obviously, the drawings in the following description are only some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on these drawings.

[0084] Figure 1 One of the flowcharts of the method for predicting the power consumption per ton of steel for a screwdown mechanism according to an embodiment of the present application;

[0085] Figure 2 Two of the flowcharts of the method for predicting the power consumption per ton of steel for a screwdown mechanism according to an embodiment of the present application;

[0086] Figure 3 A schematic diagram showing the change of rotational speed with time during the screwdown process according to an embodiment of the present application;

[0087] Figure 4 Three of the flowcharts of the method for predicting the power consumption per ton of steel for a screwdown mechanism according to an embodiment of the present application;

[0088] Figure 5 A schematic diagram showing the change of rotational speed with time during the lifting process according to an embodiment of the present application;

[0089] Figure 6 Schematic structural diagram of a per-ton steel power consumption prediction device for a screwdown mechanism according to an embodiment of the present application.

[0090] Figure 7 Block diagram of an electronic device for implementing a per-ton steel power consumption prediction method for a screwdown mechanism according to an embodiment of the present application. Specific embodiments

[0091] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

[0092] It should be understood that the heavy plate rolling process is realized by using a four-high rolling mill. During the rolling gap of a single-stand multi-pass rolling, the roll gap of the rolling mill needs to be adjusted according to the rolling process. Different roll gap adjustment amounts correspond to different screwdown motor powers, which increases the difficulty of predicting and calculating the per-ton steel power consumption of the screwdown mechanism. At the same time, the response speed of the motor determines the roll gap adjustment time. Selecting a motor with appropriate power and fast response speed helps to improve production efficiency.

[0093] For this reason, an embodiment of the present application provides a per-ton steel power consumption prediction method for a screwdown mechanism, such as the screwdown mechanism of a single-stand multi-pass rolling of a four-high rolling mill, which can help design engineers complete the selection of the screwdown motor, avoid performance waste, and reduce the manufacturing cost of the medium and heavy plate rolling production line. As Figure 1 shown, the method includes:

[0094] Step 1: Determine the total number of screwdown passes and the screwdown amount of each pass of the steel plate to be produced according to the preset production thickness of the steel plate.

[0095] Step 2: Determine the screwdown power consumption of the screwdown mechanism in each pass and the lifting power consumption of the screwdown mechanism during the reset process according to the screwdown amount of each pass.

[0096] Step 3: Determine the per-ton steel power consumption of the screwdown mechanism according to the screwdown power consumption, the lifting power consumption, and the weight of the steel plate to be produced.

[0097] The technical solution of a method for predicting the power consumption per ton of steel for a screwdown mechanism provided by an embodiment of the present application can combine the actual rolling schedule in engineering, perform theoretical calculations on the power consumption of the screwdown mechanism of the rolling mill for each pass, achieve the prediction of the power consumption of the entire schedule for single-stand multi-pass rolling, quantify the relationship between the power consumption per ton of steel and the rolling schedule during the single-stand multi-pass rolling process, and has guiding significance for aspects such as setting the rolling schedule, steel plant production scheduling, and saving power consumption. At the same time, it also plays a reference role in the motor selection design of the screwdown system of the rolling mill.

[0098] The following introduces Figure 1 each step of

[0099] Step 1: Determine the total number of screwdown passes and the screwdown amount for each pass of the steel plate to be produced according to the preset thickness of the steel plate to be produced.

[0100] In this embodiment, taking the 3800 mm production line of a certain steel plant as an example, producing steel Q345B, with a slab size of 3500 mm × 2300 mm × 300 mm and a preset thickness of the steel plate to be produced of 50 mm, that is, it is necessary to roll the thickness from 300 mm to 50 mm through a single stand in multiple passes. It should be noted that the rolling schedule is automatically generated by the setting system. In this example, the total number of screwdown passes and the screwdown amount for each pass of the steel plate to be produced are shown in Table 1, where the total number of screwdown passes of the steel plate to be produced is 12.

[0101] Table 1

[0102] Pass 1 2 3 4 5 6 Reduction / (mm) 39.00 35.00 32.10 27.87 25.11 21.32 Pass 7 8 9 10 11 12 Reduction / (mm) 19.60 15.00 13.75 8.94 7.81 4.50

[0103] In another example, taking the 3800 mm production line of a certain steel plant as an example, producing steel EH36, with a slab size of 4043 mm × 2600 mm × 250 mm and a preset thickness of the steel plate to be produced of 10.5 mm, that is, it is necessary to roll the thickness from 250 mm to 10.5 mm through a single stand in multiple passes. The rolling schedule is automatically generated by the setting system. In this example, the total number of screwdown passes and the screwdown amount for each pass of the steel plate to be produced are shown in Table 2, where the total number of screwdown passes of the steel plate to be produced is 22.

[0104] Table 2

[0105] Pass 1 2 3 4 5 6 Reduction / (mm) 26.00 24.40 21.86 19.51 20.38 18.25 Pass 7 8 9 10 11 12 Reduction / (mm) 16.86 13.96 12.78 10.60 9.89 8.43 Pass 13 14 15 16 17 18 Reduction / (mm) 7.48 5.86 5.81 4.78 4.10 2.67 Pass 19 20 21 22 — — Reduction / (mm) 2.73 1.78 1.16 0.22 — —

[0106] Step 2: Determine the screwdown power consumption of the screwdown mechanism for each pass and the lifting power consumption of the screwdown mechanism during the reset process according to the screwdown amount for each pass.

[0107] In this embodiment, according to the screwdown amount for each pass determined above, through calculation, the screwdown power consumption of the screwdown mechanism for each pass and the lifting power consumption of the screwdown mechanism during the reset process can be determined. Among them, the screwdown power consumption for each pass is represented by Q j and the lifting power consumption is represented by Qs representation

[0108] Step 3: Determine the power consumption per ton of steel of the pressing mechanism according to the pressing power consumption, the lifting power consumption, and the weight of the steel plate to be produced.

[0109] In this embodiment, according to the above slab size and the preset thickness of the steel plate to be produced, the actual size of the steel plate to be produced can be determined. For example, if the slab size is 4043 mm × 2600 mm × 250 mm and the preset thickness of the steel plate to be produced is 10.5 mm, then the actual size of the finally produced steel plate is 4043 mm × 2600 mm × 10.5 mm; further, according to the type of steel to be produced, such as EH36, the density of the steel to be produced can be determined. Thus, according to the size and density of the steel plate, the weight m of the steel plate to be produced can be determined, and the unit is ton.

[0110] Furthermore, according to the pressing power consumption of the pressing mechanism in each pass, determine the total pressing power consumption of the pressing mechanism, that is, the pressing power consumption in each pass; according to the total pressing power consumption, the lifting power consumption, and the weight of the steel plate to be produced, determine the power consumption per ton of steel of the pressing mechanism. The specific formula is as follows:

[0111]

[0112] where D is the power consumption per ton of steel, with the unit of kW·h / t, Q is the total power consumption of the pressing mechanism in the pressing process and the lifting process, with the unit of kW·h / t; j t is the total number of pressing passes, such as 12 or 22 in the aforementioned example; Q j is the pressing power consumption in each pass; Q s is the lifting power consumption; is the total pressing power consumption of the pressing mechanism, and m is the weight of the steel plate to be produced.

[0113] In some alternative ways of this embodiment, in order to implement the method for predicting the power consumption per ton of steel, it is also necessary to determine the equivalent static torque K1 of the pressing mechanism, the equivalent dynamic torque K2, the equivalent static torque K3 of the lifting, the first rotational acceleration ε1 when the motor accelerates, the second rotational acceleration ε2 when the motor decelerates, the motor pressing acceleration time t a1 、the motor pressing deceleration time t a2 、the motor lifting acceleration time t b1 and the motor lifting deceleration time t b2 。

[0114] In some alternative ways of this embodiment, as Figure 2 shown, step 2 further includes:

[0115] Step 21A. Determine the first reduction power variation during the acceleration of the reduction mechanism's motor based on the equivalent static reduction torque, the equivalent dynamic torque, and the first rotational speed acceleration.

[0116] It should be understood that the power N can be expressed as a function of time t. After differentiating the single-pass reduction process, the differential of electrical energy N(t)dt can be obtained, and after integrating it, the single-pass reduction power consumption can be obtained as follows:

[0117]

[0118] where N a1 (t) is the variation of the power with time during the acceleration stage of the reduction motor, that is, the first reduction power variation during the acceleration of the reduction mechanism's motor; N a2 (t) is the variation of the power with time during the deceleration stage of the reduction motor, that is, the second reduction power variation during the deceleration of the reduction mechanism's motor; 0 to t a1 is the motor reduction acceleration time; t a1 to t a1 +t a2 is the motor reduction deceleration time.

[0119] In a specific example, the first reduction power variation N a1 (t) is determined based on the following formula:

[0120]

[0121] In the formula, K1 is the equivalent static reduction torque; K2 is the equivalent dynamic torque; ε1 is the rotational speed acceleration during the acceleration of the motor, that is, the first rotational speed acceleration during the acceleration of the motor.

[0122] Step 22A. Determine the maximum rotational speed of the reduction mechanism's motor in each pass based on the reduction amount in each pass.

[0123] In this embodiment, the variation of the rotational speed during the reduction process is as Figure 3 shown. It can be seen that t a1 is the reduction acceleration time and t a2 is the reduction deceleration time. Further, based on the reduction amount Δh j in each pass, determine the maximum rotational speed n r of the reduction mechanism's motor in each pass, specifically:

[0124] First, obtain the worm gear ratio i of the reduction mechanism and the pitch S of the reduction screw. For example, the worm gear ratio is 18.33 and the pitch of the reduction screw is 60 mm. Those skilled in the art can set the corresponding worm gear ratio and pitch of the reduction screw according to actual process requirements, and this application does not limit this.

[0125] Secondly, based on the worm gear transmission ratio i, the pitch S of the screw-down screw, the first rotational acceleration ε1, the second rotational acceleration ε2, and the reduction amount Δh for each pass j , the maximum rotational speed n of the motor for the screw-down mechanism in each pass is determined based on the following formula r :

[0126]

[0127] Among them, the calculation formula for the screw-down acceleration time is as follows:

[0128]

[0129] That is to say, in this embodiment, based on the first rotational acceleration ε1 and the maximum rotational speed n of the motor for the screw-down r , the screw-down acceleration time t of the motor can be determined a1 .

[0130] Among them, the calculation formula for the screw-down deceleration time is as follows:

[0131]

[0132] That is to say, in this embodiment, based on the second rotational acceleration ε2 and the maximum rotational speed n of the motor for the screw-down r , the screw-down deceleration time t of the motor can be determined a2 .

[0133] Step 23A: Based on the maximum rotational speed of the motor for the screw-down, the second rotational acceleration, the screw-down acceleration time of the motor, the equivalent static torque K1 for the screw-down, and the equivalent dynamic torque K2, determine the change in the second screw-down power of the motor of the screw-down mechanism during deceleration.

[0134] In this embodiment, based on the maximum rotational speed n of the motor for the screw-down r , the second rotational acceleration ε2, the screw-down acceleration time t of the motor a1 , the equivalent static torque K1 for the screw-down, and the equivalent dynamic torque K2, based on the following formula, determine the change in the second screw-down power N a2 (t) of the motor of the screw-down mechanism during deceleration:

[0135]

[0136] Step 24A: Based on the screw-down acceleration time of the motor, the screw-down deceleration time of the motor, the change in the first screw-down power, and the change in the second screw-down power, determine the power consumption for the screw-down of the screw-down mechanism in each pass.

[0137] In this embodiment, based on the following formula, according to the motor lowering acceleration time t a1 , the motor lowering deceleration time t a2 , the first lowering power change N a1 (t) and the second lowering power change N a2 (t), determine the lowering power consumption Q of the lowering mechanism in each pass j :

[0138]

[0139] Furthermore, on the basis of having determined N a1 (t) and N a2 (t) above, substituting them into the above formula gives:

[0140]

[0141] After arrangement, it can be obtained:

[0142]

[0143] After arrangement, it can be obtained:

[0144]

[0145] That is to say, in this embodiment, after determining the maximum motor lowering speed n r of the lowering mechanism in each pass according to the lowering amount in each pass, further, the lowering power consumption Q of the lowering mechanism in each pass can be directly determined according to the equivalent static torque K1 of the lowering, the maximum motor lowering speed n r , the first rotational speed acceleration ε1 and the second rotational speed acceleration ε2, thereby reducing the calculation amount and improving the efficiency of determining the lowering power consumption. j

[0146] In some optional ways of this embodiment, as Figure 4 shown, step 2 further includes:

[0147] Step 21B: Determine the first lifting power change during the motor acceleration of the lowering mechanism according to the equivalent static torque of the lifting, the equivalent dynamic torque and the first rotational speed acceleration.

[0148] It should be understood that the power N can be expressed as a function of time t. After differentiating the lifting process, the differential of electrical energy N(t)dt can be obtained, and after integrating it, the power consumption of the lifting process can be obtained, as follows:

[0149]

[0150] Among them, it should be understood that N s1 ​(t) is the variation of power with time during the acceleration and lifting stage of the screw-down motor, i.e., the first lifting power variation when the screw-down mechanism motor accelerates; N s2 (t) is the variation of power with time during the deceleration and lifting stage of the screw-down motor, i.e., the second lifting power variation when the screw-down mechanism motor decelerates; from 0 to t b1 is the motor lifting acceleration time; t b1 to t b1 +t b2 is the motor lifting deceleration time.

[0151] In a specific example, according to the lifting equivalent static torque K3, the equivalent dynamic torque K2, and the first rotational speed acceleration ε1, determine the first lifting power variation N when the screw-down mechanism motor accelerates s1 (t):

[0152]

[0153] Step 22B. Determine the maximum rotational speed of the screw-down mechanism motor according to the screw-down amount of each pass.

[0154] During the lifting process of this embodiment, a triangular speed regime is adopted for lifting. After rolling, the lifting distance is:

[0155]

[0156] where, Δh j is the screw-down amount of the screw-down mechanism in each pass; h z is the total screw-down amount of the screw-down mechanism during the screw-down process; since the screw-down mechanism needs to lift back to the initial position after completing the screw-down process, thus, the total screw-down amount is the lifting distance.

[0157] In this embodiment, the variation of the speed with time during the lifting process of the screw-down device is as Figure 5 shown, and it can be seen that t b1 is the lifting acceleration time and t b2 is the lifting deceleration time. Further, according to the screw-down amount Δh j of each pass, determine the maximum rotational speed n z of the screw-down mechanism motor, specifically:

[0158] First, obtain the worm gear transmission ratio i and the screw pitch S of the screw-down mechanism. For example, the worm gear transmission ratio is 18.33 and the screw pitch of the screw-down screw is 60 mm. Those skilled in the art can set the corresponding worm gear transmission ratio and screw pitch according to actual process requirements, and this application does not limit this.

[0159] Second, according to the screw-down amount Δh j, determine the total reduction amount h of the reduction mechanism during the reduction process z , referring to the above description, it will not be elaborated herein in this application.

[0160] Secondly, according to the worm gear transmission ratio i, the total reduction amount h z , the pitch S of the reduction screw, the first rotational acceleration ε1 and the second rotational acceleration ε2, based on the following formula, determine the maximum rotational speed n of the motor lifting of the reduction mechanism z :

[0161]

[0162] Among them, the calculation formula for the lifting acceleration time is as follows:

[0163]

[0164] That is to say, in this embodiment, according to the first rotational acceleration ε1 and the maximum rotational speed n of the motor lifting z , the motor lifting acceleration time t can be determined b1 .

[0165] Among them, the calculation formula for the lifting deceleration time is as follows:

[0166]

[0167] That is to say, in this embodiment, according to the second rotational acceleration ε2 and the maximum rotational speed n of the motor lifting z , determine the motor lifting deceleration time t b2 .

[0168] Step 23B: According to the lifting equivalent static torque, the equivalent dynamic torque, the second rotational acceleration, the maximum rotational speed of the motor lifting, and the motor lifting acceleration time, determine the second lifting power change when the motor of the reduction mechanism decelerates.

[0169] In this embodiment, according to the lifting equivalent static torque K3, the equivalent dynamic torque K2, the second rotational acceleration ε2, the maximum rotational speed n of the motor lifting z and the motor lifting acceleration time t b1 , based on the following formula, determine the second lifting power change N s2 (t) of the motor of the reduction mechanism when decelerating:

[0170]

[0171] Step 24B. Determine the lifting power consumption of the lowering mechanism during the reset process according to the motor lifting acceleration time, the motor lifting deceleration time, the first lifting power change, and the second lifting power change.

[0172] In this embodiment, based on the following formula, according to the motor lifting acceleration time t b1 、the motor lifting deceleration time t b2 、the first lifting power change N s1 (t), and the second lifting power change N s2 (t), determine the lifting power consumption Q s of the lowering mechanism during the reset process:

[0173]

[0174] Further, on the basis of having determined N s1 (t) and N s2 (t) above, substituting them into the above formula gives:

[0175]

[0176] After arrangement, it can be obtained:

[0177]

[0178] After arrangement, it can be obtained:

[0179]

[0180] That is to say, in this embodiment, after determining the maximum lifting speed n j of the motor of the lowering mechanism according to the reduction amount Δh z of each pass; further, the lifting power consumption Q z of the lowering mechanism during the reset process can be directly determined according to the equivalent static torque K3 for lifting, the maximum lifting speed n s of the motor, the first rotational acceleration ε1, and the second rotational acceleration ε2, thereby reducing the calculation amount and improving the efficiency of determining the lifting power consumption.

[0181] So far, on the basis of having determined the lowering power consumption and the lifting power consumption under each pass, the total power consumption Q of the lowering mechanism in the embodiment above during the lowering process and the lifting process can be written as:

[0182]

[0183] In some optional ways of this embodiment, the static torque M jincluding the frictional torque (thrust bearing type) M1 between the pivot part of the screwdown screw and the thrust block and the frictional torque (screwdown) M between the screwdown screw and the nut thread 2下 , the torque required for the motor output shaft to apply this screwdown static torque, that is, the screwdown equivalent static torque satisfies the following formula:

[0184]

[0185] where M1 is the frictional torque between the pivot part of the screwdown screw and the thrust block, that is, the first frictional torque between the pivot part of the screwdown screw and the thrust block; M 2下 is the frictional torque between the screwdown screw and the nut thread, that is, the second frictional torque between the screwdown screw and the nut thread; i is the worm gear transmission ratio of the screwdown mechanism; η is the transmission efficiency of the screwdown mechanism.

[0186] That is to say, in this embodiment, first, determine the first frictional torque M1 between the pivot part of the screwdown screw and the thrust block; second, determine the second frictional torque M 2下 between the screwdown screw and the nut thread; 2下 Finally, according to the first frictional torque M1, the second frictional torque M

[0187] Next, a method for determining the first frictional torque M1 between the pivot part of the screwdown screw and the thrust block will be described:

[0188] First, determine the force P1 exerted by the screwdown mechanism on one screwdown screw, the sliding friction coefficient μ between the thrust pad and the pivot d and the average diameter d of the thrust rolling bearing p ;

[0189] Finally, according to the force P1, the sliding friction coefficient μ d and the average diameter d of the thrust rolling bearing p , based on the following formula, determine the first frictional torque M1 between the pivot part of the screwdown screw and the thrust block:

[0190]

[0191] In the formula, P1 is the force acting on one screwdown screw; μ d is the sliding friction coefficient between the thrust pad and the pivot, generally 0.1 - 0.2, for example, take 0.17; d p is the average diameter of the thrust rolling bearing (the diameter between the pivots at the end of the screwdown screw (thrust bearing)), and the unit is mm.

[0192] It should be noted that the force P1 exerted by the lowering mechanism on a lowering screw is related to the total overbalance force F0 of the lowering mechanism, specifically satisfying P1 = 0.5F0. Therefore, in this embodiment, it is also necessary to pre-determine the total overbalance force of the lowering mechanism. Specifically:

[0193] First, determine the hydraulic cylinder pressure of the upper backup roll balance mechanism according to the total gravity of the upper backup roll balance force balance components and the upper backup roll balance coefficient.

[0194] In this embodiment, the total gravity G of the upper backup roll balance force balance components b is pre-determined by the following method:

[0195] G b =(m4 + m6 + m7 + m8 + m9)g

[0196] In the formula, m4 is the mass of the upper backup roll assembly (excluding the backup roll), with the unit of kg; m6 is the mass of two lowering screws, with the unit of kg; m7 is the mass of two press head assemblies, with the unit of kg; m8 is the mass of the mill guide and the moving parts in descaling and cooling water, with the unit of kg; m9 is the mass of the upper support roll balance mechanism, with the unit of kg; g is the acceleration due to gravity.

[0197] Among them, the hydraulic cylinder pressure of the upper backup roll balance mechanism (i.e., the balance force) Q b satisfies:

[0198]

[0199] In the formula, D b is the diameter of the hydraulic cylinder rod of the backup roll balance mechanism, with the unit of mm; P b is the working pressure of the hydraulic cylinder of the backup roll balance mechanism, with the unit of MPa.

[0200] The upper backup roll balance coefficient k1 is the ratio of the hydraulic cylinder pressure Q of the upper backup roll balance mechanism b to the total gravity G of the upper backup roll balance force balance components b , that is:

[0201]

[0202] It should be noted that during the actual production process, the working pressure P of the hydraulic cylinder of the backup roll balance mechanism b is a variable, that is, by changing the working pressure P of the hydraulic cylinder of the backup roll balance mechanism b , different Q can be obtained b , until the upper backup roll balance coefficient k1 is within the range of 1.2 to 1.4. Specifically, the value of k1 depends on the actual situation, and this application does not limit it.

[0203] Secondly, determine the bending roll pressure of the upper work roll according to the total gravity of the balance components of the upper work roll balance force and the balance coefficient of the upper work roll.

[0204] In this embodiment, the total gravity G of the balance components of the upper work roll balance force w is determined in advance by the following method:

[0205] G w = (m2 + m3 + m 10 )g

[0206] where m2 is the assembly mass of the upper work roll, with the unit of kg; m3 is the mass of the upper backup roll, with the unit of kg; m 10 is the mass of the connecting shaft of the upper work roll, with the unit of kg.

[0207] Among them, the bending roll pressure (i.e., the balance force) Q of the upper work roll w satisfies:

[0208]

[0209] where n is the number of bending roll cylinders of the upper work roll, with the unit of piece; D w is the piston diameter of a single work roll bending roll cylinder, with the unit of mm; d w is the piston rod diameter of a single work roll bending roll cylinder, with the unit of mm; P w is the working pressure of the rodless cavity of a single work roll bending roll cylinder, with the unit of MPa; p w is the working pressure of the rod cavity of a single work roll bending roll cylinder, with the unit of MPa.

[0210] The balance coefficient k2 of the upper work roll is the ratio of the bending roll pressure Q of the upper work roll w and the total gravity G of the balance components of the upper work roll balance force w , that is:

[0211]

[0212] It should be noted that in the actual production process, the working pressure P of the rodless cavity of a single work roll bending roll cylinder w and the working pressure p of the rod cavity of a single work roll bending roll cylinder w are variables. That is, by changing P w and p w to obtain different Q w , until the balance coefficient k2 of the upper work roll is within the range of 1.2 to 1.4. The specific value of k1 depends on the actual situation, and this application does not limit it.

[0213] Secondly, determine the overbalance force for the balance of the upper backup roll according to the total gravity of the balance components of the upper backup roll balance force and the hydraulic cylinder pressure of the upper backup roll balance mechanism.

[0214] In this embodiment, on the basis of having already determined the total gravity G of the upper support roll balance force balance component b and the hydraulic cylinder pressure Q of the upper support roll balance mechanism b the overbalance force Q for the upper support roll balance is determined based on the following formula bg :

[0215] Q bg = Q b - G b

[0216] Secondly, according to the total gravity of the upper work roll balance force balance component and the bending roll pressure of the upper work roll, the overbalance force for the upper work roll balance is determined.

[0217] In this embodiment, on the basis of having already determined the total gravity G of the upper work roll balance force balance component w and the bending roll pressure Q of the upper work roll w the overbalance force Q for the upper work roll balance is determined based on the following formula wg :

[0218] Q wg = Q w - G w

[0219] Finally, according to the overbalance force of the upper support roll balance and the overbalance force of the upper work roll balance, the total overbalance force is determined, and based on the total overbalance force, the acting force of the screw down mechanism on one screw down screw is determined.

[0220] In this embodiment, the sum of the overbalance force Q of the upper support roll balance bg and the overbalance force Q of the upper work roll balance wg is the total overbalance force F0, that is:

[0221] F0 = Q bg + Q wg

[0222] As known from the foregoing, the acting force P1 of the screw down mechanism on one screw down screw satisfies the relationship: P1 = 0.5F0. Thus, based on the total overbalance force F0, the acting force P1 of the screw down mechanism on one screw down screw can be determined.

[0223] Next, a method for determining the second frictional torque M 2下 between the screw down screw and the nut thread is described:

[0224] First, determine the friction angle ρ between the screw down screw and the nut, the lead angle α, the pitch S, and the mean diameter d2 of the screw down screw between the screw down screw and the nut thread.

[0225] Among them, the friction angle ρ between the screw-down screw and the nut satisfies ρ = arctan(0.1); the lead angle α between the screw-down screw and the nut thread satisfies:

[0226]

[0227] Finally, according to the friction angle ρ, the lead angle α, the pitch, and the mean diameter d2 of the screw-down screw, the second frictional torque M between the screw-down screw and the nut thread is determined 2下 .

[0228] Among them, when the screw-down mechanism is being lowered, based on the following formula, the second frictional torque M between the screw-down screw and the nut thread is determined 2下 :

[0229]

[0230] From this, it can be obtained that:

[0231]

[0232] It should be noted that the transmission efficiency η of the screw-down mechanism includes the transmission efficiency η1 of the worm and worm gear transmission mechanism and the transmission efficiency η2 of the screw-down screw. Among them, the transmission efficiency of the worm and worm gear transmission mechanism is taken as 0.85, and the transmission efficiency η2 of the screw-down screw satisfies:

[0233]

[0234] In some optional ways of this embodiment, the screw-down driving torque M d can be calculated by the following formula:

[0235]

[0236] In the formula, (GD 2 ) z is the total flywheel torque of the transmission system of the screw-down mechanism, with the unit of kN·m2; is the motor acceleration, with the unit of r / (s·min), and satisfies:

[0237]

[0238] The equivalent driving torque converted to the motor shaft is:

[0239]

[0240] In the formula, (GD 2 )′ z is the flywheel torque of all moving parts converted to the motor shaft. Among them, (GD 2 )′ [[ID=IS65]] z satisfies:

[0241]

[0242] Where, (GD 2 )1 is the sum of the flywheel moments of all rotating parts on the screw down shaft; (GD 2 )2 is the sum of the flywheel moments of the rotating parts on the motor reducer shaft; (GD 2 )3 is the sum of the flywheel moments of all moving parts in the screw down mechanism; i is the worm gear ratio of the screw down mechanism.

[0243] That is to say, in this embodiment, after determining the sum of the flywheel moments of all rotating parts on the screw down shaft (GD 2 )1, the sum of the flywheel moments of the rotating parts on the motor reducer shaft (GD 2 )2, and the sum of the flywheel moments of all moving parts in the screw down mechanism (GD 2 )3, the equivalent driving moment K2 of the screw down mechanism can be further determined.

[0244] Next, a method for determining the sum of the flywheel moments of all rotating parts on the screw down shaft (GD 2 )1 will be described:

[0245] First, according to the flywheel moment of the worm gear and the flywheel moment of the worm center shaft, determine the flywheel moment of the worm gear (GD 2 ) 11 ;

[0246] Secondly, according to the flywheel moment of the screw down and the flywheel moments of other rotating parts, determine the sum of the flywheel moments of all relevant rotating parts on the screw down shaft (GD 2 ) 12 ;

[0247] Finally, according to the flywheel moment of the worm gear (GD 2 ) 11 and the sum of the flywheel moments of all relevant rotating parts on the screw down shaft (GD 2 ) 12 , determine the sum of the flywheel moments of all rotating parts on the screw down shaft (GD 2 )1, which satisfies:

[0248] (GD 2 )1 = (GD 2 ) 11 + (GD 2 ) 12

[0249] Next, a method for determining the sum of the flywheel moments of the rotating parts on the motor reducer shaft (GD 2 )2 will be described:

[0250] First, determine the flywheel torque of the motor (GD 2 ) 21 , the flywheel torque of the worm of the reducer (GD 2 ) 22 and the flywheel torque of the brake disc coupling (GD 2 ) 23 ;

[0251] Finally, based on the flywheel torque of the motor (GD 2 ), 21 the flywheel torque of the worm of the reducer (GD 2 ), 22 and the flywheel torque of the brake disc coupling (GD 2 ), 23 determine the sum of the flywheel torques of the rotating parts of the motor reducer shaft (GD 2 )2, which satisfies:

[0252] (GD 2 )2 = (GD 2 ) 21 + (GD 2 ) 22 + (GD 2 ) 23

[0253] Next, a method for determining the sum of the flywheel torques of all moving parts in the screw-down mechanism (GD 2 )3 will be described:

[0254] First, determine the screw-down speed v of the screw-down screw, the weight G of all moving parts in the screw-down mechanism g and the rated speed n of the motor output shaft e .

[0255] In this embodiment, the screw-down speed v of the screw-down screw is obtained by the following method:

[0256]

[0257] In the formula, n e is the rated speed of the motor output shaft, with the unit of r / min; S is the pitch; i is the worm and worm gear transmission ratio.

[0258] Finally, based on the screw-down speed v of the screw-down screw, the weight G of all moving parts in the screw-down mechanism g and the rated speed n of the motor output shaft e , based on the following formula, determine the sum of the flywheel torques of all moving parts in the screw-down mechanism (GD 2 )3:

[0259]

[0260] Among them, G g is the weight of all moving parts in the pressing mechanism, including the weight of two pressing screws and the assembly of two pressing heads.

[0261] Thus, it can be obtained that:

[0262]

[0263] So far, the previously determined first pressing power change N a1 (t) and the second pressing power change N a2 (t) can also be expressed as:

[0264]

[0265]

[0266] It should be noted that the power required for the rotation of the pressing motor needs to satisfy:

[0267]

[0268] Among them, N e is the rated power. The rated power of the actually selected motor should satisfy:

[0269]

[0270] In some optional ways of this embodiment, according to the previously determined friction angle ρ, lead angle α, mean diameter d2 of the pressing screw, and pitch S, the third frictional torque M 2上 between the threads of the pressing screw and the nut can be determined during the lifting stage:

[0271]

[0272] Furthermore, according to the previously determined first frictional torque M1, the third frictional torque M 2上 , the worm gear ratio i of the pressing mechanism, and the transmission efficiency η of the pressing mechanism, the lifting equivalent static torque K3 of the pressing mechanism can be determined, which satisfies:

[0273]

[0274] So far, the previously determined first lifting power change N s1 (t) and the second lifting power change N s2 (t) can also be expressed as:

[0275]

[0276]

[0277] So far, based on the above method, the embodiments of this application have been able to determine the electric consumption for rolling down and lifting for each pass. Still taking the examples in Table 1 and Table 2 above for illustration:

[0278] Among them, the parameters of the rolling-down motor equipment: the rated speed of the motor is 675 r / min, the time required to accelerate from standstill to the rated speed is 1.66 s, the transmission ratio of the worm and worm gear is 18.33, and the pitch of the rolling-down screw is 60 mm; through the above method, the electric consumption for rolling down, lifting, and electric consumption per ton of steel corresponding to each pass in Table 1 can be calculated. The details are shown in Table 3:

[0279] Table 3

[0280]

[0281] Among them, the parameters of the rolling-down motor equipment: the rated speed of the motor is 675 r / min, the time required to accelerate from standstill to the rated speed is 1.66 s, the transmission ratio of the worm and worm gear is 18.33, and the pitch of the rolling-down screw is 60 mm; through the above method, the electric consumption for rolling down, lifting, and electric consumption per ton of steel corresponding to each pass in Table 2 can be calculated. The details are shown in Table 4:

[0282] Table 4

[0283]

[0284]

[0285] The above embodiments show that this prediction algorithm can quantitatively predict the energy consumption per ton of steel of the rolling-down mechanism in heavy plate rolling, which has guiding significance for quantifying and saving electric consumption.

[0286] The technical solution of this application can combine the actual rolling schedule in engineering to perform theoretical calculations on the electric consumption of the rolling-down mechanism of the rolling mill for each pass, realize the prediction of the electric consumption of the entire rolling schedule of multi-pass rolling on a single stand, quantify the relationship between the electric consumption per ton of steel and the rolling schedule in the process of multi-pass rolling on a single stand, and has guiding significance for aspects such as setting the rolling schedule, steel mill production scheduling, and saving electric consumption. At the same time, it also plays a reference role in the motor selection design of the rolling-down system of the rolling mill.

[0287] Based on the same inventive concept, an embodiment of the present application further provides a prediction device for the power consumption per ton of steel of a screwdown mechanism, which can be used to implement the method described in the above embodiment, as described in the following embodiment. Since the principle of the problem solved by the prediction device for the power consumption per ton of steel of a screwdown mechanism is similar to that of the prediction method for the power consumption per ton of steel of a screwdown mechanism, the implementation of the prediction device for the power consumption per ton of steel of a screwdown mechanism can refer to the implementation of the prediction method for the power consumption per ton of steel of a screwdown mechanism, and the repeated parts will not be described again. As used hereinafter, the term "unit" or "module" may be a combination of software and / or hardware that can achieve a predetermined function. Although the systems described in the following embodiments are preferably implemented in software, implementation in hardware, or a combination of software and hardware is also possible and contemplated.

[0288] As Figure 6 shown, the prediction device for the power consumption per ton of steel of a screwdown mechanism includes:

[0289] A pass determination module 601, configured to determine the total number of passes of the screwdown of the steel plate to be produced and the amount of screwdown for each pass according to a preset production thickness of the steel plate;

[0290] A first power consumption determination module 602, configured to determine the screwdown power consumption of the screwdown mechanism for each pass and the lifting power consumption of the screwdown mechanism during the reset process according to the amount of screwdown for each pass;

[0291] A second power consumption determination module 603, configured to determine the power consumption per ton of steel of the screwdown mechanism according to the screwdown power consumption, the lifting power consumption, and the weight of the steel plate to be produced.

[0292] In some optional embodiments of this embodiment, it further includes:

[0293] A parameter determination module, configured to determine the equivalent static torque of the screwdown of the screwdown mechanism, the equivalent dynamic torque, the equivalent static torque of the lifting, the first rotational speed acceleration when the motor accelerates, the second rotational speed acceleration when the motor decelerates, the motor screwdown acceleration time, the motor screwdown deceleration time, the motor lifting acceleration time, and the motor lifting deceleration time.

[0294] In some optional embodiments of this embodiment, the first power consumption determination module is further configured to:

[0295] Determine the first change in screwdown power of the motor of the screwdown mechanism when the motor accelerates according to the equivalent static torque of the screwdown, the equivalent dynamic torque, and the first rotational speed acceleration;

[0296] Determine the maximum rotational speed of the motor of the screwdown mechanism for each pass according to the amount of screwdown for each pass;

[0297] Determine the change in the second press-down power of the motor of the press-down mechanism during deceleration based on the maximum rotational speed of the motor during press-down, the second rotational speed acceleration, the motor press-down acceleration time, the equivalent static torque during press-down, and the equivalent dynamic torque.

[0298] Determine the power consumption of the press-down during each pass based on the motor press-down acceleration time, the motor press-down deceleration time, the first press-down power change, and the second press-down power change.

[0299] In some alternative embodiments of the present embodiment, the first power consumption determination module is further configured to:

[0300] Determine the maximum rotational speed of the motor of the press-down mechanism during each pass based on the amount of press-down during each pass.

[0301] Determine the power consumption of the press-down during each pass based on the equivalent static torque during press-down, the maximum rotational speed of the motor during press-down, the first rotational speed acceleration, and the second rotational speed acceleration.

[0302] In some alternative embodiments of the present embodiment, the step of determining the maximum rotational speed of the motor of the press-down mechanism during each pass based on the amount of press-down during each pass includes:

[0303] Obtain the worm gear transmission ratio and the pitch of the press-down screw of the press-down mechanism.

[0304] Determine the maximum rotational speed of the motor of the press-down mechanism during each pass based on the worm gear transmission ratio, the pitch of the press-down screw, the first rotational speed acceleration, the second rotational speed acceleration, and the amount of press-down during each pass.

[0305] In some alternative embodiments of the present embodiment, the first power consumption determination module is further configured to:

[0306] Determine the change in the first lifting power of the motor of the press-down mechanism during acceleration based on the equivalent static torque during lifting, the equivalent dynamic torque, and the first rotational speed acceleration.

[0307] Determine the maximum rotational speed of the motor of the press-down mechanism during lifting based on the amount of press-down during each pass.

[0308] Determine the change in the second lifting power of the motor of the press-down mechanism during deceleration based on the equivalent static torque during lifting, the equivalent dynamic torque, the second rotational speed acceleration, the maximum rotational speed of the motor during lifting, and the motor lifting acceleration time.

[0309] Determine the power consumption of the press-down mechanism during the reset process based on the motor lifting acceleration time, the motor lifting deceleration time, the first lifting power change, and the second lifting power change.

[0310] In some alternative embodiments of the present embodiment, the first power consumption determination module is further configured to:

[0311] Determine the maximum lifting speed of the motor of the screw-down mechanism according to the reduction amount of each pass;

[0312] Determine the lifting power consumption of the screw-down mechanism during the reset process according to the equivalent static torque of lifting, the maximum lifting speed of the motor, the first rotational acceleration, and the second rotational acceleration.

[0313] In some alternative embodiments of the present embodiment, determining the maximum lifting speed of the motor of the screw-down mechanism according to the reduction amount of each pass includes:

[0314] Obtain the worm gear drive ratio and the pitch of the screw-down screw of the screw-down mechanism;

[0315] Determine the total reduction amount of the screw-down mechanism during the reduction process according to the reduction amount of each pass;

[0316] Determine the maximum lifting speed of the motor of the screw-down mechanism according to the worm gear drive ratio, the total reduction amount, the pitch of the screw-down screw, the first rotational acceleration, and the second rotational acceleration.

[0317] In some alternative embodiments of the present embodiment, determining the equivalent static torque of the screw-down of the screw-down mechanism includes:

[0318] Determine the first frictional torque between the pivot portion of the screw-down screw and the thrust block;

[0319] Determine the second frictional torque between the screw-down screw and the nut thread;

[0320] Determine the equivalent static torque of the screw-down of the screw-down mechanism according to the first frictional torque, the second frictional torque, the worm gear drive ratio of the screw-down mechanism, and the transmission efficiency of the screw-down mechanism.

[0321] In some alternative embodiments of the present embodiment, determining the first frictional torque between the pivot portion of the screw-down screw and the thrust block includes:

[0322] Determine the force exerted by the screw-down mechanism on one screw-down screw, the sliding friction coefficient between the thrust pad and the pivot, and the average diameter of the thrust rolling bearing;

[0323] Determine the first frictional torque between the pivot portion of the screw-down screw and the thrust block according to the force, the sliding friction coefficient, and the average diameter of the thrust rolling bearing.

[0324] In some alternative embodiments of the present embodiment, determining the second frictional torque between the screw-down screw and the nut thread includes:

[0325] Determine the friction angle between the screw-down screw and the nut, the lead angle, the pitch of the screw thread between the screw-down screw and the nut, and the pitch diameter of the screw-down screw;

[0326] Determine the second frictional torque between the screw-down screw and the nut thread according to the friction angle, the lead angle, the pitch, and the pitch diameter of the screw-down screw.

[0327] In some optional embodiments of the present embodiment, the determination of the force exerted by the screw-down mechanism on one screw-down screw includes:

[0328] Determine the hydraulic cylinder pressure of the upper backup roll balancing mechanism according to the total gravity of the upper backup roll balance force balancing components and the upper backup roll balance coefficient;

[0329] Determine the bending roll pressure of the upper work roll according to the total gravity of the upper work roll balance force balancing components and the upper work roll balance coefficient;

[0330] Determine the overbalance force of the upper backup roll balance according to the total gravity of the upper backup roll balance force balancing components and the hydraulic cylinder pressure of the upper backup roll balance mechanism;

[0331] Determine the overbalance force of the upper work roll balance according to the total gravity of the upper work roll balance force balancing components and the bending roll pressure of the upper work roll;

[0332] Determine the total overbalance force according to the overbalance force of the upper backup roll balance and the overbalance force of the upper work roll balance, and determine the force exerted by the screw-down mechanism on one screw-down screw according to the total overbalance force.

[0333] In some optional embodiments of the present embodiment, the determination of the equivalent dynamic torque of the screw-down mechanism includes:

[0334] Determine the sum of the flywheel torques of all rotating parts on the screw-down screw shaft, the sum of the flywheel torques of the rotating parts on the motor reducer shaft, and the sum of the flywheel torques of all moving parts in the screw-down mechanism;

[0335] Determine the equivalent dynamic torque of the screw-down mechanism according to the worm gear transmission ratio of the screw-down mechanism, the sum of the flywheel torques of all rotating parts on the screw-down screw shaft, the sum of the flywheel torques of the rotating parts on the motor reducer shaft, and the sum of the flywheel torques of all moving parts in the screw-down mechanism.

[0336] In some optional embodiments of the present embodiment, the determination of the sum of the flywheel torques of all rotating parts on the screw-down screw shaft includes:

[0337] Determine the flywheel torque of the worm gear according to the flywheel torque of the worm gear teeth and the flywheel torque of the worm gear central shaft;

[0338] Determine the sum of the flywheel torques of all relevant rotating parts on the screw-down shaft based on the flywheel torque of the screw-down screw and the flywheel torques of other rotating parts.

[0339] Determine the sum of the flywheel torques of all rotating parts on the screw-down shaft based on the flywheel torque of the worm gear and the sum of the flywheel torques of all relevant rotating parts on the screw-down shaft.

[0340] In some alternative embodiments of the present embodiment, determining the sum of the flywheel torques of the rotating parts on the motor reducer shaft includes:

[0341] Determine the flywheel torque of the motor, the flywheel torque of the reducer worm, and the flywheel torque of the brake disc coupling.

[0342] Determine the sum of the flywheel torques of the rotating parts on the motor reducer shaft based on the flywheel torque of the motor, the flywheel torque of the reducer worm, and the flywheel torque of the brake disc coupling.

[0343] In some alternative embodiments of the present embodiment, determining the sum of the flywheel torques of all moving parts in the screw-down mechanism includes:

[0344] Determine the screw-down speed of the screw-down screw, the weights of all moving parts in the screw-down mechanism, and the rated speed of the motor output shaft.

[0345] Determine the sum of the flywheel torques of all moving parts in the screw-down mechanism based on the screw-down speed of the screw-down screw, the weights of all moving parts in the screw-down mechanism, and the rated speed of the motor output shaft.

[0346] In some alternative embodiments of the present embodiment, determining the lifting equivalent static torque of the screw-down mechanism includes:

[0347] Determine the third frictional torque between the screw-down screw and the nut thread based on the friction angle, the lead angle, the pitch, and the mean diameter of the screw-down screw.

[0348] Determine the lifting equivalent static torque of the screw-down mechanism based on the first frictional torque, the third frictional torque, the worm gear transmission ratio of the screw-down mechanism, and the transmission efficiency of the screw-down mechanism.

[0349] In some alternative embodiments of the present embodiment, determining the motor screw-down acceleration time and the motor screw-down deceleration time includes:

[0350] Determine the motor screw-down acceleration time based on the first rotational acceleration and the maximum motor screw-down speed.

[0351] Determine the motor screw-down deceleration time based on the second rotational acceleration and the maximum motor screw-down speed.

[0352] In some alternative embodiments of the present embodiment, determining the motor lifting acceleration time and the motor lifting deceleration time includes:

[0353] Determining the motor lifting acceleration time according to the first rotational speed acceleration and the maximum rotational speed of the motor lifting;

[0354] Determining the motor lifting deceleration time according to the second rotational speed acceleration and the maximum rotational speed of the motor lifting.

[0355] In some alternative embodiments of the present embodiment, the second power consumption determination module is further configured to:

[0356] Determining the total rolling-down power consumption of the rolling-down mechanism according to the rolling-down power consumption of the rolling-down mechanism in each pass;

[0357] Determining the power consumption per ton of steel of the rolling-down mechanism according to the total rolling-down power consumption, the lifting power consumption, and the weight of the steel plate to be produced.

[0358] According to an embodiment of the present disclosure, the present disclosure also provides an electronic device, a readable storage medium, and a computer program product.

[0359] An electronic device includes: at least one processor; and a memory communicatively connected to the at least one processor; wherein the memory stores instructions executable by the at least one processor, and the instructions are executed by the at least one processor to enable the at least one processor to execute the steps of a method for predicting the power consumption per ton of steel of a rolling-down mechanism in the foregoing embodiment.

[0360] A non-transitory computer-readable storage medium storing computer instructions, wherein the computer instructions are used to cause a computer to execute the steps of a method for predicting the power consumption per ton of steel of a rolling-down mechanism in the foregoing embodiment.

[0361] A computer program product includes computer programs / instructions, and when the computer programs / instructions are executed by a processor, the steps of the method for predicting the power consumption per ton of steel of a rolling-down mechanism are implemented.

[0362] Figure 7 A schematic block diagram of an example electronic device 500 that can be used to implement embodiments of the present disclosure is shown. The electronic device is intended to represent various forms of digital computers, such as, a laptop computer, a desktop computer, a workbench, a personal digital assistant, a server, a blade server, a mainframe computer, and other suitable computers. The electronic device can also represent various forms of mobile devices, such as, a personal digital processor, a cellular phone, a smart phone, a wearable device, and other similar computing devices. The components shown herein, their connections and relationships, and their functions are merely examples and are not intended to limit the implementation of the present disclosure described and / or claimed herein.

[0363] As Figure 7 shown, device 500 includes a computing unit 501, which can perform various appropriate actions and processes according to a computer program stored in a read-only memory (ROM) 502 or a computer program loaded from a storage unit 508 into a random access memory (RAM) 503. In the RAM 503, various programs and data required for the operation of the device 500 can also be stored. The computing unit 501, the ROM 502, and the RAM 503 are connected to each other via a bus 504. An input / output (I / O) interface 505 is also connected to the bus 504.

[0364] Multiple components in the device 500 are connected to the I / O interface 505, including: an input unit 506, such as a keyboard, a mouse, etc.; an output unit 507, such as various types of displays, speakers, etc.; a storage unit 508, such as a magnetic disk, an optical disc, etc.; and a communication unit 509, such as a network card, a modem, a wireless communication transceiver, etc. The communication unit 509 allows the device 500 to exchange information / data with other devices via a computer network such as the Internet and / or various telecommunication networks.

[0365] The computing unit 501 can be various general-purpose and / or special-purpose processing components with processing and computing capabilities. Some examples of the computing unit 501 include but are not limited to a central processing unit (CPU), a graphics processing unit (GPU), various dedicated artificial intelligence (AI) computing chips, various computing units running machine learning model algorithms, a digital signal processor (DSP), and any appropriate processor, controller, microcontroller, etc. The computing unit 501 executes the various methods and processes described above, such as the steps of a method for predicting the power consumption per ton of steel for a screwdown mechanism.

[0366] For example, in some embodiments, a method for predicting the power consumption per ton of steel for a screwdown mechanism can be implemented as a computer software program, which is tangibly contained in a machine-readable medium, such as the storage unit 508. In some embodiments, part or all of the computer program can be loaded and / or installed onto the device 500 via the ROM 502 and / or the communication unit 509. When the computer program is loaded into the RAM 503 and executed by the computing unit 501, one or more steps of a method for predicting the power consumption per ton of steel for a screwdown mechanism described above can be executed. Alternatively, in other embodiments, the computing unit 501 can be configured to execute the steps of a method for predicting the power consumption per ton of steel for a screwdown mechanism by any other appropriate means (e.g., by means of firmware).

[0367] The various embodiments of the systems and techniques described above in this specification can be implemented in digital electronic circuitry, integrated circuit systems, field programmable gate arrays (FPGAs), application specific integrated circuits (ASICs), application specific standard products (ASSPs), systems-on-chip (SOCs), complex programmable logic devices (CPLDs), computer hardware, firmware, software, and / or combinations thereof. These various embodiments can include: being implemented in one or more computer programs that are executable and / or interpretable on a programmable system including at least one programmable processor, which can be a special-purpose or general-purpose programmable processor that receives data and instructions from, and transmits data and instructions to, a storage system, at least one input device, and at least one output device.

[0368] The program code for implementing the methods of the present disclosure can be written in any combination of one or more programming languages. These program codes can be provided to a processor or controller of a general purpose computer, special purpose computer, or other programmable data processing apparatus, such that the program codes, when executed by the processor or controller, cause the functions / operations specified in the flowchart and / or block diagram to be implemented. The program code can be executed entirely on the machine, partly on the machine, as a stand-alone software package partly on the machine and partly on a remote machine, or entirely on the remote machine or server.

[0369] In the context of the present disclosure, a machine-readable medium can be a tangible medium that can contain or store a program for use by or in connection with an instruction execution system, apparatus, or device. A machine-readable medium can be a machine-readable signal medium or a machine-readable storage medium. A machine-readable medium can include, but is not limited to, electronic, magnetic, optical, electromagnetic, infrared, or semiconductor systems, apparatus, or devices, or any suitable combination of the foregoing. More specific examples of a machine-readable storage medium would include an electrical connection based on one or more wires, a portable computer diskette, a hard disk, a random access memory (RAM), a read-only memory (ROM), an erasable programmable read-only memory (EPROM or Flash memory), an optical fiber, a portable compact disc read-only memory (CD-ROM), an optical storage device, a magnetic storage device, or any suitable combination of the foregoing.

[0370] To provide interaction with a user, the systems and techniques described herein can be implemented on a computer having: a display device for displaying information to the user (e.g., a CRT (cathode ray tube) or LCD (liquid crystal display) monitor); and a keyboard and a pointing device (e.g., a mouse or a trackball) by which the user can provide input to the computer. Other kinds of devices can also be used to provide interaction with the user; for example, the feedback provided to the user can be any form of sensory feedback (e.g., visual feedback, auditory feedback, or tactile feedback); and input from the user can be received in any form (including acoustic input, voice input, or tactile input).

[0371] The systems and techniques described herein can be implemented in a computing system including backend components (e.g., as a data server), or a computing system including middleware components (e.g., an application server), or a computing system including frontend components (e.g., a user computer having a graphical user interface or a web browser through which the user can interact with an implementation of the systems and techniques described herein), or a computing system including any combination of such backend components, middleware components, or frontend components. The components of the system can be interconnected by any form or medium of digital data communication (e.g., a communication network). Examples of communication networks include: local area network (LAN), wide area network (WAN), and the Internet.

[0372] A computer system can include a client and a server. The client and the server are generally far from each other and typically interact through a communication network. The client - server relationship is created by computer programs running on the respective computers and having a client - server relationship with each other. The server can be a cloud server, or a server of a distributed system, or a server incorporating blockchain.

[0373] It should be understood that various forms of the processes shown above can be used, with steps reordered, added, or deleted. For example, the steps recited in this disclosure can be executed in parallel, sequentially, or in a different order, as long as the desired results of the technical solution of this disclosure can be achieved, and no limitation is imposed herein.

[0374] In the description of this application, it should be noted that the orientation or positional relationship indicated by terms such as "upper", "lower", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing this application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation of this application. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0375] It should also be noted that in the description of the present application, relational terms such as first and second are only used to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any actual relationship or order between these entities or operations. Moreover, the terms "comprise", "include" or any other variant thereof are intended to cover non-exclusive inclusion, such that a process, method, article or device comprising a series of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such process, method, article or device. Without further limitation, an element defined by the statement "comprising an..." does not exclude the presence of additional identical elements in the process, method, article or device comprising the element.

[0376] The above specific embodiments do not constitute a limitation on the protection scope of the present disclosure. Those skilled in the art should understand that various modifications, combinations, sub-combinations and substitutions can be made according to design requirements and other factors. Any modifications, equivalent substitutions and improvements made within the spirit and principle of the present disclosure shall be included within the protection scope of the present disclosure.

Claims

1. A method for predicting power consumption per ton of steel for a press mechanism, characterized in that: include: Determine the total number of press passes and the amount of press reduction for each pass of the steel plate to be produced based on the preset production thickness of the steel plate; Determining the power consumption of the pressing mechanism in each pass and the power consumption of the pressing mechanism in the resetting process according to the pressing amount of each pass; The power consumption per ton of steel of the pressing mechanism is determined based on the pressing power consumption, the lifting power consumption and the weight of the steel plate to be produced.

2. The method according to claim 1, characterized in that Also includes: Determine the equivalent static torque, equivalent dynamic torque, equivalent static torque of the pressing mechanism, the first speed acceleration when the motor accelerates, the second speed acceleration when the motor decelerates, the motor pressing acceleration time, the motor pressing deceleration time, the motor lifting acceleration time and the motor lifting deceleration time.

3. The method according to claim 2, characterized in that Determining the power consumption of the pressing mechanism in each pass according to the pressing amount of each pass includes: determining a first pressing power change of the motor of the pressing mechanism when accelerating according to the pressing equivalent static torque, the equivalent dynamic torque, and the first speed acceleration; Determining the maximum rotational speed of the motor of the pressing mechanism in each pass according to the pressing amount of each pass; Determining a second pressing power change of the motor of the pressing mechanism during deceleration according to the maximum pressing speed of the motor, the second speed acceleration, the pressing acceleration time of the motor, the pressing equivalent static torque, and the equivalent dynamic torque; The power consumption of the pressing mechanism in each pass is determined based on the motor pressing acceleration time, the motor pressing deceleration time, the first pressing power change and the second pressing power change.

4. The method according to claim 2, characterized in that Determining the power consumption of the pressing mechanism in each pass according to the pressing amount of each pass includes: Determining the maximum rotational speed of the motor of the pressing mechanism in each pass according to the pressing amount of each pass; The power consumption of the pressing mechanism in each pass is determined according to the pressing equivalent static torque, the maximum pressing speed of the motor, the first speed acceleration, and the second speed acceleration.

5. The method according to claim 3 or 4, characterized in that The step of determining the maximum rotational speed of the motor of the pressing mechanism in each pass according to the pressing amount of each pass includes: Obtaining the worm gear ratio and the screw pitch of the pressing mechanism; The maximum speed of the motor of the pressing mechanism in each pass is determined according to the worm gear transmission ratio, the pressing screw pitch, the first speed acceleration, the second speed acceleration and the pressing amount of each pass.

6. The method according to claim 2, characterized in that The step of determining the lifting power consumption of the pressing mechanism during the resetting process according to the pressing amount of each pass includes: determining a first lifting power change when a motor of the pressing mechanism accelerates according to the lifting equivalent static torque, the equivalent dynamic torque, and the first speed acceleration; Determining the maximum speed of the motor of the pressing mechanism according to the pressing amount of each pass; determining a second lifting power change when the motor of the pressing mechanism decelerates according to the lifting equivalent static torque, the equivalent dynamic torque, the second speed acceleration, the maximum lifting speed of the motor, and the motor lifting acceleration time; The lifting power consumption of the pressing mechanism during the resetting process is determined according to the motor lifting acceleration time, the motor lifting deceleration time, the first lifting power change, and the second lifting power change.

7. The method according to claim 2, characterized in that The step of determining the lifting power consumption of the pressing mechanism during the resetting process according to the pressing amount of each pass includes: Determining the maximum speed of the motor of the pressing mechanism according to the pressing amount of each pass; The lifting power consumption of the pressing mechanism during the resetting process is determined according to the lifting equivalent static torque, the maximum lifting speed of the motor, the first speed acceleration, and the second speed acceleration.

8. The method according to claim 6 or 7, characterized in that Determining the maximum speed of the motor of the pressing mechanism according to the pressing amount of each pass includes: Obtaining the worm gear ratio and the screw pitch of the pressing mechanism; Determining the total pressing amount of the pressing mechanism in the pressing process according to the pressing amount of each pass; The maximum lifting speed of the motor of the pressing mechanism is determined according to the worm gear transmission ratio, the total pressing amount, the pressing screw pitch, the first speed acceleration and the second speed acceleration.

9. The method according to claim 2, characterized in that Determining the equivalent static moment of the pressing mechanism includes: determining a first friction torque between a pivot portion of the depression screw and the thrust block; Determine the second friction torque between the pressed screw and the nut thread; The equivalent static torque of the press-down mechanism is determined according to the first friction torque, the second friction torque, the worm gear transmission ratio of the press-down mechanism, and the transmission efficiency of the press-down mechanism.

10. The method according to claim 9, characterized in that The step of determining a first friction torque between the pivot portion of the pressing screw and the thrust block comprises: determining the force applied by the pressing mechanism to a pressing screw, the coefficient of sliding friction between the thrust pad and the pivot, and the average diameter of the thrust rolling bearing; A first friction torque between a pivot portion of the pressing screw and a thrust block is determined based on the acting force, the sliding friction coefficient, and the average diameter of the thrust rolling bearing.

11. The method according to claim 9, characterized in that Determining the second friction torque between the pressed screw and the nut thread includes: Determine the friction angle between the screw and the nut, the lead angle between the screw and the nut threads, the thread pitch, and the pitch diameter of the screw; A second friction torque between the screw thread and the nut thread is determined according to the friction angle, the lead angle, the pitch, and the center diameter of the screw thread.

12. The method according to claim 10, characterized in that Determining the force exerted by the pressing mechanism on a pressing screw includes: Determine the hydraulic cylinder pressure of the upper support roller balancing mechanism according to the total gravity of the upper support roller balancing force balancing component and the upper support roller balancing coefficient; Determine the bending pressure of the upper work roll according to the total gravity of the upper work roll balancing force balancing component and the upper work roll balancing coefficient; determining an overbalancing force of the upper support roller balance according to the total gravity of the upper support roller balancing force balancing component and the pressure of the hydraulic cylinder of the upper support roller balancing mechanism; determining an overbalancing force of the upper work roll balance according to the total gravity of the upper work roll balancing force balancing component and the upper work roll bending pressure; The total overbalance force is determined according to the overbalance force of the upper support roller balance and the overbalance force of the upper working roller balance, and the force of the press-down mechanism on a press-down screw is determined according to the total overbalance force.

13. The method according to claim 2, characterized in that Determining the equivalent torque of the pressing mechanism includes: Determine the sum of the flywheel torques of all rotating parts on the screw shaft, the sum of the flywheel torques of the rotating parts of the motor reducer shaft, and the sum of the flywheel torques of all moving parts in the pressing mechanism; The equivalent torque of the pressing mechanism is determined based on the worm gear transmission ratio of the pressing mechanism, the sum of the flywheel torques of all rotating parts on the pressing screw shaft, the sum of the flywheel torques of the rotating parts of the motor reducer shaft, and the sum of the flywheel torques of all moving parts in the pressing mechanism.

14. The method according to claim 13, characterized in that Determine the sum of the flywheel torques of all rotating parts on the screw shaft, including: Determine the worm flywheel torque based on the worm gear flywheel torque and the worm center shaft flywheel torque; According to the flywheel torque of the pressing screw and the flywheel torque of other rotating parts, determine the sum of the flywheel torques of all relevant rotating parts on the pressing screw shaft; The sum of the flywheel torques of all rotating parts on the press-down screw shaft is determined according to the sum of the flywheel torque of the worm gear and the flywheel torques of all relevant rotating parts on the press-down screw shaft.

15. The method according to claim 13, characterized in that Determining the sum of the flywheel torques of the rotating parts of the motor reducer shaft includes: Determine the motor flywheel torque, reducer worm flywheel torque, and brake disc coupling flywheel torque; The sum of the flywheel torques of the motor reducer shaft rotating parts is determined based on the motor flywheel torque, the reducer worm flywheel torque and the brake disc coupling flywheel torque.

16. The method according to claim 13, characterized in that Determine the sum of the flywheel torques of all moving parts in the hold-down mechanism, including: Determining the speed of the screw down, the weight of all moving parts in the down mechanism, and the rated speed of the motor output shaft; The sum of the flywheel torques of all moving parts in the pressing mechanism is determined according to the pressing speed of the pressing screw, the weight of all moving parts in the pressing mechanism and the rated speed of the motor output shaft.

17. The method according to claim 11, characterized in that The determining of the lifting equivalent static moment of the pressing mechanism includes: determining a third friction torque between the screw thread and the nut thread according to the friction angle, the lead angle, the thread pitch, and the center diameter of the screw thread; The lifting equivalent static torque of the press-down mechanism is determined according to the first friction torque, the third friction torque, the worm gear transmission ratio of the press-down mechanism, and the transmission efficiency of the press-down mechanism.

18. The method according to claim 5, characterized in that Determining the motor pressing acceleration time and the motor pressing deceleration time includes: Determining the motor pressing acceleration time according to the first speed acceleration and the maximum speed of the motor pressing down; The motor pressing deceleration time is determined according to the second speed acceleration and the maximum speed of the motor pressing down.

19. The method according to claim 8, characterized in that Determining the motor lifting acceleration time and the motor lifting deceleration time includes: Determining the motor lifting acceleration time according to the first speed acceleration and the motor lifting maximum speed; The motor lifting deceleration time is determined according to the second speed acceleration and the motor lifting maximum speed.

20. The method according to claim 1, wherein The step of determining the power consumption per ton of steel of the press-down mechanism according to the press-down power consumption, the lift power consumption, and the weight of the steel plate to be produced comprises: Determining the total power consumption of the pressing mechanism according to the power consumption of the pressing mechanism in each pass; The power consumption per ton of steel of the pressing mechanism is determined based on the total power consumption for pressing down, the power consumption for lifting up and the weight of the steel plate to be produced.

21. A device for predicting power consumption per ton of steel for a press mechanism, characterized in that: include: A pass determination module is configured to determine the total number of reduction passes and the reduction amount of each pass of the steel plate to be produced according to a preset production thickness of the steel plate; a first power consumption determination module configured to determine the pressing power consumption of the pressing mechanism in each pass and the lifting power consumption of the pressing mechanism in the resetting process according to the pressing amount of each pass; The second power consumption determination module is configured to determine the power consumption per ton of steel of the pressing mechanism based on the pressing power consumption, the lifting power consumption and the weight of the steel plate to be produced.

22. An electronic device comprising a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein: When the processor executes the program, the steps of a method for predicting power consumption per ton of steel for a press mechanism as described in any one of claims 1 to 20 are implemented.

23. A computer-readable storage medium having a computer program stored thereon, characterized in that: When the computer program is executed by a processor, the steps of a method for predicting power consumption per ton of steel for a press mechanism as described in any one of claims 1 to 20 are implemented.

24. A computer program product comprising a computer program / instructions, characterized in that When the computer program / instruction is executed by a processor, the steps of a method for predicting power consumption per ton of steel for a press mechanism as described in any one of claims 1 to 20 are implemented.

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