CN113198855A - Swing lifting type spring damping gravity billet tilter - Google Patents

Abstract

The invention provides a swinging lifting type spring damping gravity billet tilter, wherein a sliding spiral cam adjusting mechanism is connected with a variable four-bar linkage swinging mechanism, a swinging power mechanism is connected with the variable four-bar linkage swinging mechanism, a lifting power mechanism is respectively connected with the variable four-bar linkage swinging mechanism and an adjustable tensioning chain wheel lifting mechanism, and the lifting power mechanism is used for providing power for the adjustable tensioning chain wheel lifting mechanism; the adjustable tension sprocket lifting mechanism is arranged on the upright post and connected with the gravity type spring tipping mechanism. The swing lifting type spring damping gravity billet tilter can overturn a high-temperature billet discharged from a heating furnace of a section/bar hot rolling production line by 90 degrees before rolling, meets the requirements of a field rolling deformation process, can remove overheated iron oxide on the surface of the billet, improves the surface appearance quality of a rolled material, improves the rhythm of field production, and reduces process faults.

Description

Swing lifting type spring damping gravity billet tilter

Technical Field

The invention relates to the technical field of steel rolling, in particular to a swing lifting type spring damping gravity billet tilter.

Background

At present, the two ways of manual intervention and turning or mechanical turning are commonly adopted in domestic hot rolling production lines to solve the problem of on-site hot billet turning. Manual intervention manual steel turnover is large in field workload, severe in environment, easy to cause personal safety accidents, and not beneficial to reasonable allocation of human resources, and special persons need to watch the steel; the mechanical turnover mostly adopts a hydraulic turnover type tilting gear, the structure is complex and heavy, a special hydraulic transmission mechanism needs to be configured, an actuating mechanism is arranged below a tapping roller way, the field installation and operation maintenance are extremely inconvenient, a concrete foundation needs to be separately and additionally poured and installed, the cost is high, the iron scale accumulation of a slag discharge channel is easily caused, the working efficiency of the roller way and a slag flushing system is influenced, the requirement on the professional skill quality of field personnel and the maintenance and use cost are high, and once a hydraulic system leakage fault occurs, an emergent oil fire accident is easily caused, and the serious loss of the field personnel and property is caused. Therefore, how to research and develop an automatic billet turnover machine with simple structure, flexible and efficient action, convenient disassembly and assembly and low maintenance and use cost, meeting the field rolling process requirement is a technical bottleneck problem to be solved urgently in the current hot rolling production field.

Disclosure of Invention

The invention aims to provide a swinging lifting type spring damping gravity billet tilter which can overturn a high-temperature billet discharged from a heating furnace of a section/bar hot rolling production line by 90 degrees before rolling, change the sequence of the meshing surfaces of the billet in conjugate pass rolling between two rollers, improve the control precision of the material shape at the inlet of a rolling mill, meet the process requirement of on-site rolling deformation, remove overheated iron oxide on the surface of the billet, improve the surface appearance quality of a rolled material, improve the on-site production rhythm, reduce the rolling current and reduce process faults.

In order to achieve the above purpose, the invention provides the following technical scheme:

a swing lifting type spring damping gravity billet tilter comprises a swing power mechanism, a lifting power mechanism, a sliding spiral cam adjusting mechanism, a variable four-connecting-rod swing mechanism, an adjustable tensioning chain wheel lifting mechanism and a gravity type spring tilting mechanism; the sliding spiral cam adjusting mechanism is connected with the variable four-bar linkage swinging mechanism and is used for adjusting the abscissa and/or the ordinate of a swinging rod seat in the variable four-bar linkage swinging mechanism so as to linearly adjust the swinging angle of an upright post in the variable four-bar linkage swinging mechanism; the swing power mechanism is connected with the variable four-connecting-rod swing mechanism and used for providing power for the variable four-connecting-rod swing mechanism; the lifting power mechanism is respectively connected with the variable four-connecting-rod swinging mechanism and the adjustable tensioning chain wheel lifting mechanism and is used for providing power for the adjustable tensioning chain wheel lifting mechanism; the adjustable tension sprocket lifting mechanism is arranged on the stand column and is connected with the gravity type spring tipping mechanism, and the adjustable tension sprocket lifting mechanism is used for changing the direction of power output by the lifting power mechanism so as to drive the gravity type spring tipping mechanism to do reciprocating linear motion up and down; the steel billet is placed at the tail end of the gravity type spring tipping mechanism, and the gravity type spring tipping mechanism reciprocates linearly up and down or swings left and right to enable the steel billet to reach a tipping angle of critical balance, so that the steel billet is turned over.

Further, in the above swing elevating spring damping gravity billet tipper, the sliding spiral cam adjusting mechanism comprises a sliding spiral mechanism, a wedge type sliding cam mechanism and a push rod frame; the sliding screw mechanism comprises a first speed reducing motor, a transverse adjusting nut and a transverse adjusting screw rod, wherein the output end of the first speed reducing motor is fixedly connected with one end of the transverse adjusting screw rod, and the transverse adjusting nut is in threaded connection with the transverse adjusting screw rod; the wedge type sliding cam mechanism comprises a swing frame, a longitudinal adjusting nut, a longitudinal adjusting screw rod, a diagonal slideway and an ejector rod; the bottom of the swing frame is hinged with the upper plane of the transverse adjusting nut, the longitudinal adjusting screw rod is rotatably arranged on the inner side of the swing frame, the longitudinal adjusting nut is in threaded connection with the longitudinal adjusting screw rod, the bottom of the longitudinal adjusting screw rod is hinged with the upper plane of the transverse adjusting nut, one end of the oblique slideway is hinged with the longitudinal adjusting nut, and the other end of the oblique slideway is hinged with the upper plane of the transverse adjusting nut; one end of the ejector rod is hinged to the inclined slide way, the other end of the ejector rod is fixedly connected with the bottom of the swing rod seat, a sleeve is arranged at the top of the ejector rod frame, the bottom of the ejector rod frame is fixedly arranged, and the ejector rod is arranged in the sleeve.

Further, in the above swing elevation type spring damping gravity billet tipper, the sliding spiral cam adjusting mechanism further comprises an L-shaped slideway and a locking bolt; the bottom of the L-shaped slideway is fixedly arranged, and the bottom of the ejector rod frame is in sliding connection with the top of the L-shaped slideway; the locking bolt is arranged between the bottom of the ejector rod frame and the top of the L slide way, and the locking bolt is used for fixedly connecting the bottom of the ejector rod frame with the top of the L slide way.

Further, in the swing lifting type spring damping gravity billet tilter, the variable four-bar linkage swing mechanism further comprises a connecting bar, a swing bar, a base, a swing bar upper slide seat, a swing bar lower slide seat and a lifting arm; one end of the upright post is hinged with the base, and one end of the swing rod is hinged with one end of the swing rod seat; one end of the lifting arm is in adjustable sliding connection with one side of the upright post, and the other end of the lifting arm is hinged with one end of the connecting rod; one end of the upper sliding seat of the swing rod is in adjustable sliding connection with one side of the swing rod, and the other end of the upper sliding seat of the swing rod is hinged with the other end of the connecting rod; one end of the swing rod lower sliding seat is connected with the other side of the swing rod in an adjustable sliding mode, the other end of the swing rod lower sliding seat is hinged to the output end of the swing power mechanism, the tail end of the swing power mechanism is hinged to the base, and the tail end of the lifting power mechanism is hinged to the connecting rod.

Further, in the above swing elevation type spring damping gravity billet tilter, the connecting rod comprises a connecting rod sleeve, two connecting rod beams, a fastening bolt, a support, an adjusting rod and a fixing nut; the connecting rod sleeves are of hollow box-shaped structures, and the other ends of the two connecting rod beams are symmetrically inserted from the two ends of the connecting rod sleeves; two sides of the connecting rod sleeve are respectively provided with two groups of threaded holes in a mirror symmetry manner, and the fastening bolt is screwed into the threaded holes and is in contact with the connecting rod beam so as to fixedly connect the connecting rod beam with the connecting rod sleeve; the other end of the lifting arm is hinged with one end of one connecting rod beam, and the other end of the upper sliding seat of the swing rod is hinged with one end of the other connecting rod beam; the support is fixedly arranged on the connecting rod beam, the fixing nut is fixedly arranged on the connecting rod sleeve, one end of the adjusting rod is rotatably matched with the support, the other end of the adjusting rod is matched with the fixing nut, and the tail end of the lifting power mechanism is hinged with the connecting rod sleeve; the variable four-bar linkage swing mechanism also comprises two sets of swing rod rocker arm pull rod mechanisms, and each set of swing rod rocker arm pull rod mechanism comprises a rocker arm pull rod, two rocker arm earrings and a rocker arm; one end of the rocker arm is hinged with the swing rod, the other end of the rocker arm is hinged with one end of one rocker arm ear ring, one end of the other rocker arm ear ring in one set of rocker arm pull rod mechanism is hinged with the upper swing rod sliding seat, and one end of the other rocker arm ear ring in the other set of rocker arm pull rod mechanism is hinged with the lower swing rod sliding seat; the rocker arm pull rod is of a double-spiral structure rotating synchronously, and the two ends of the rocker arm pull rod are respectively matched with the other ends of the rocker arm earrings by adopting fine external threads in positive and negative rotation directions.

Further, in the above swing elevation type spring damping gravity billet tipper, the variable four-bar linkage swing mechanism further comprises a lifting arm reel, a fixed pulley, a lifting arm reel support, a fixed pulley support, a second speed reduction motor and a steel wire rope; the fixed pulley is fixedly arranged at the top of one side of the upright post through the fixed pulley support, the lifting arm winding drum is fixedly arranged at the bottom of one side of the upright post through the lifting arm winding drum support, the output end of the second speed reducing motor is fixedly connected with the lifting arm winding drum, and the lifting arm is slidably connected with one side of the upright post; one end of the steel wire rope is fixedly connected with the lifting arm, and the other end of the steel wire rope bypasses the fixed pulley and is fixedly connected with the lifting arm winding drum.

Further, in the swing lifting type spring damping gravity billet tilter, the adjustable tensioning sprocket lifting mechanism comprises a tensioning sprocket assembly, a sleeve roller chain and a lifting trolley; the tensioning chain wheel assembly comprises a chain wheel, a chain wheel shaft and a tensioning plate; the chain wheel is rotatably arranged at one end of the tension plate through the chain wheel shaft, and the other end of the tension plate is fixedly arranged at the top end of the upright post; the lifting trolley comprises a trolley wheel shaft, a trolley pressing plate, a lifting plate and two telescopic beams; the telescopic beam is a long strip-shaped plate-shaped member, a groove slideway is arranged in the middle of the telescopic beam in the height direction, the groove slideway extends from the rear end face of the telescopic beam to the front end face of the telescopic beam, the length direction of the groove slideway is consistent with the length direction of the telescopic beam, the lifting plate is fixedly arranged on the upper surfaces of the two telescopic beams, two ends of the trolley pressing plate are fixedly arranged on the rear end faces of the two telescopic beams, and the gravity type spring tipping mechanism is fixedly arranged on the front end face of the telescopic beam; the trolley wheel shaft is arranged in the groove slideway in a sliding manner, two opposite inner side walls of the upright post are provided with guide slideways, and two ends of the trolley wheel shaft are respectively connected with the guide slideways in a sliding manner; one end of the sleeve roller chain is fixedly connected with the output end of the lifting power mechanism, and the other end of the sleeve roller chain bypasses the chain wheel to be fixedly connected with the lifting plate.

Furthermore, in the swing lifting type spring damping gravity billet tilter, the lifting trolley further comprises an adjusting rod and a second deep groove ball bearing; a step blind hole is formed in the geometric symmetry center line of the trolley wheel shaft, the second deep groove ball bearing is arranged in the step blind hole, and a fine-tooth nut is arranged in the middle of the trolley pressing plate and is in threaded fit with the adjusting rod; one end of the adjusting rod penetrates through the trolley pressing plate to be matched with the second deep groove ball bearing.

Further, in the above swing elevation type spring damping gravity billet tipper, the gravity type spring tipper comprises a cross beam, two sets of bearing rod assemblies, two sets of material supporting arms and two sets of rotary spring damping bodies; the two groups of bearing rod assemblies are fixedly arranged at two ends of the cross beam, the cross beam is fixedly arranged on the front end face of the telescopic beam, and the two groups of bearing rod assemblies are arranged in a mirror symmetry mode about the geometric symmetry center line of the lifting trolley; the material supporting arm comprises a transverse part, a vertical part and a movable lug plate, the lower end of the vertical part is fixedly connected with the transverse part and divides the transverse part into a material supporting arm front section and a material supporting arm tail section, the length of the material supporting arm front section is greater than that of the material supporting arm tail section, the movable lug plate is arranged on the material supporting arm front section, and one end of the bearing rod component is hinged with the upper end of the vertical part; the two groups of rotary spring damping bodies are respectively hinged on the outer side surfaces of the tails of the two groups of material supporting arms which are arranged in a mirror symmetry manner; the rotary spring damping body comprises a guide rod, a damping spring, a spring seat and a lifting nut; the lifting nut with bearing bar subassembly screw-thread fit, the side of lifting nut is provided with articulated gudgeon, articulated gudgeon with the through-hole of spring holder side is articulated, damping spring axial suit is in on the guide bar, damping spring's one end is fixed, damping spring's the other end moves about, the top of guide bar slides and sets up in the oblong hole on spring holder upper portion, the bottom of guide bar with the lateral surface of holding in the palm material arm afterbody is articulated.

Further, in the above swing elevation type spring damping gravity billet tipper, the rotary spring damping body further comprises a base nut; the guide rod is a screw shaft with a through-long full-thread structure, and the base nut is in threaded fit with the lower part of the guide rod; the top of the damping spring is in pressing contact with the upper plane of the spring seat, and the bottom of the damping spring is fixedly mounted on the base nut.

The analysis shows that the embodiment of the swing lifting type spring damping gravity billet tilter disclosed by the invention realizes the following technical effects:

the swing lifting type spring damping gravity billet tilter can overturn a high-temperature billet discharged from a heating furnace of a section/bar hot rolling production line by 90 degrees before rolling, change the sequence of the meshing surfaces of the billet in conjugate pass rolling between two rollers, improve the control precision of the imported billet shape of a rolling mill, meet the process requirement of field rolling deformation, remove overheated iron oxide on the surface of the billet, improve the surface appearance quality of a rolled material, improve the rhythm of field production, reduce the rolling current and reduce process faults. Meanwhile, the swing lifting type spring damping gravity billet tilter has the remarkable characteristics of simple structure, low cost, reliable work, rapid response and suitability for strong use, and is a novel billet tilter with wide application, high automation degree, convenient installation and strong universality.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the invention and, together with the description, serve to explain the invention and not to limit the invention. Wherein:

FIG. 1 is a schematic structural diagram of an embodiment of the present invention; FIG. 2 is an exploded view of a system according to an embodiment of the present invention; FIG. 3 is a schematic diagram of the movement of the variable four-bar linkage swing mechanism in accordance with one embodiment of the present invention; FIG. 4 is a schematic diagram of the movement of the adjustment mechanism of the swing frame according to an embodiment of the present invention; FIG. 5 is a schematic diagram of the movement of a rocker arm-pull mechanism in an embodiment of the present invention; FIG. 6 is a schematic diagram of the movement of the material holding arm mechanism according to an embodiment of the present invention; fig. 7 is a schematic structural diagram of a swing power mechanism according to an embodiment of the present invention; FIG. 8 is a schematic structural view of a swing frame according to an embodiment of the present invention; FIG. 9 is a schematic view of a structure of a top rack according to an embodiment of the present invention; FIG. 10 is a schematic structural diagram of a swing link according to an embodiment of the present invention; FIG. 11 is a schematic view of a connecting rod according to an embodiment of the present invention; FIG. 12 is a cross-sectional view taken along line A-A of FIG. 11; FIG. 13 is a schematic view of a structure at a pillar according to an embodiment of the present invention; FIG. 14 is a cross-sectional view taken along line A-A of FIG. 13; FIG. 15 is a cross-sectional view taken along line B-B of FIG. 13; FIG. 16 is a cross-sectional view taken along line C-C of FIG. 13; FIG. 17 is a schematic structural view of the lifting cart and the material supporting arm according to an embodiment of the present invention; FIG. 18 is a view from the direction M of FIG. 17; FIG. 19 is a pneumatic control schematic of an embodiment of the present invention; FIG. 20 is a schematic view of a lift arm according to an embodiment of the present invention; FIG. 21 is a schematic view of the lift arm reel of one embodiment of the present invention; FIG. 22 is a schematic structural view of a fixed pulley according to an embodiment of the present invention; FIG. 23 is a schematic view of the structure of the tensioning sprocket according to an embodiment of the present invention; FIG. 24 is a schematic view of the structure at the sprocket in an embodiment of the present invention; FIG. 25 is a schematic view of the lifting cart according to an embodiment of the present invention; FIG. 26 is a cross-sectional view taken along line A-B-C of FIG. 25; FIG. 27 is a schematic view of the structure of a load bearing bar assembly according to an embodiment of the present invention; FIG. 28 is a schematic structural view of a material supporting arm according to an embodiment of the present invention; FIG. 29 is a kinematic diagram of an embodiment of the present invention; FIG. 30 is a schematic process diagram of an initial station in accordance with an embodiment of the present invention; FIG. 31 is a schematic view of an empty lift station in accordance with an embodiment of the present invention; FIG. 32 is a schematic view of a heavy lift tipping station embodiment of the present invention; FIG. 33 is a schematic view of a process of dropping back the gravity flipping station according to an embodiment of the present invention; FIG. 34 is a schematic view of a process for returning to its original position after completion of the tilting of the blank according to an embodiment of the present invention; FIG. 35 is a schematic view of a process for a heavy swing station according to an embodiment of the present invention; FIG. 36 is a schematic diagram of a swing flipping station in accordance with an embodiment of the present invention.

Description of reference numerals:

1-a swing power mechanism, 11-a swing cylinder, 111-a swing cylinder earring, 1111-a second pin shaft, 12-a first hinged support, 13-a second hinged support, 14-a first pin shaft, 15-a base, 2-a lifting power mechanism, 21-a lifting cylinder, 22-a sliding base, 23-a T-shaped bolt, 3-a sliding spiral cam adjusting mechanism, 31-a first speed reducing motor, 32-a bearing seat, 321-a first sliding bearing, 33-a transverse adjusting screw rod, 34-a transverse adjusting nut, 341-a third pin shaft, 342-a fourth pin shaft, 35-a swinging frame, 351-a swinging frame gland, 352-a swinging frame cross beam, 353-a hand wheel, 354-a first deep groove ball bearing, 36-a longitudinal adjusting nut, 361-a fifth pin shaft, 37-longitudinal adjusting screw rod, 38-swinging hinged ball head, 39-top rod, 391-sliding hinged ball head, 392-inclined slideway, 393-top rod frame, 3931-locking bolt, 394-L slideway, 4-variable four-bar swinging mechanism, 41-swinging bar, 411-first shaft sleeve, 412-swinging bar seat, 413-sixth pin shaft, 414-swinging bar upper slide seat, 4141-seventh pin shaft, 4142-second shaft sleeve, 415-swinging bar lower slide seat, 4151-slide bolt, 42-swinging arm, 421-eighth pin shaft, 422-swinging arm ear ring, 423-swinging arm pull rod, 424-ninth pin shaft, 43-connecting rod, 431-connecting rod beam, 432-support seat, 433-adjusting rod, 434-connecting rod sleeve, 4341-fastening bolt, 435-a third shaft sleeve, 4351-a tenth pin shaft, 44-an upright post, 441-an eleventh pin shaft, 442-a third hinge seat, 45-a lifting arm, 452-a steel wire rope, 453-a set screw, 454-a second speed reducing motor, 455-a lifting arm reel, 456-a lifting arm reel support, 457-a fixed pulley support, 458-a fixed pulley, 5-an adjustable tension sprocket lifting mechanism, 51-a tension sprocket component, 511-a sprocket, 512-a sprocket shaft, 513-a tension plate, 514-a fixed bolt, 515-a tension screw pair, 516-installation channel steel, 52-a roller sleeve chain, 53-a lifting trolley, 531-a trolley wheel shaft, 532-a second deep groove ball bearing, 533-a trolley pressing plate, 534-an adjusting rod and 535-a balancing weight, 536-third deep groove ball bearing, 5361-bearing block, 537-lifting plate, 538-telescopic beam, 6-gravity spring tilting mechanism, 61-cross beam, 62-bearing rod assembly, 621-bearing rod, 622-handle, 623-upper gland, 624-fourth deep groove ball bearing, 625-sleeve, 626-bearing nut, 628-lower gland, 63-material supporting arm, 631-thirteenth pin shaft, 633-fourth shaft sleeve, 634-movable lug plate, 635-lead screw, 636-fifth shaft sleeve, 637-fourteenth pin shaft, 64-rotary spring damping body, 641-lifting nut, 642-spring seat, 643-damping spring, 644-guide rod and 645-gasket.

Detailed Description

The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings. The various examples are provided by way of explanation of the invention, and not limitation of the invention. In fact, it will be apparent to those skilled in the art that modifications and variations can be made in the present invention without departing from the scope or spirit thereof. For instance, features illustrated or described as part of one embodiment, can be used with another embodiment to yield a still further embodiment. It is therefore intended that the present invention encompass such modifications and variations as fall within the scope of the appended claims and equivalents thereof.

In the description of the present invention, the terms "longitudinal", "lateral", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, which are for convenience of description of the present invention only and do not require that the present invention must be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. The terms "connected," "connected," and "disposed" as used herein are intended to be broadly construed, and may include, for example, fixed and removable connections; can be directly connected or indirectly connected through intermediate components; the connection may be a wired electrical connection, a wireless electrical connection, or a wireless communication signal connection, and a person skilled in the art can understand the specific meaning of the above terms according to specific situations.

One or more examples of the invention are illustrated in the accompanying drawings. The detailed description uses numerical and letter designations to refer to features in the drawings. Like or similar designations in the drawings and description have been used to refer to like or similar parts of the invention. As used herein, the terms "first," "second," "third," and "fourth," etc. may be used interchangeably to distinguish one component from another and are not intended to indicate the position or importance of an individual component.

As shown in fig. 1 to 36, according to an embodiment of the present invention, there is provided a swing lift type spring damping gravity billet tipper, which includes a swing power mechanism 1, a lift power mechanism 2, a sliding spiral cam adjusting mechanism 3, a variable four-bar linkage swing mechanism 4, an adjustable tension sprocket lifting mechanism 5 and a gravity spring tipper 6; the sliding spiral cam adjusting mechanism 3 is connected with the variable four-bar linkage swinging mechanism 4, and the sliding spiral cam adjusting mechanism 3 is used for adjusting the abscissa and/or the ordinate of the swing rod seat 412 in the variable four-bar linkage swinging mechanism 4, so as to linearly adjust the swinging angle of the upright post 44 in the variable four-bar linkage swinging mechanism 4; the swing power mechanism 1 is connected with the variable four-bar linkage swing mechanism 4, and the swing power mechanism 1 is used for providing power for the variable four-bar linkage swing mechanism 4; the lifting power mechanism 2 is respectively connected with the variable four-connecting-rod swing mechanism 4 and the adjustable tensioning sprocket lifting mechanism 5, and the lifting power mechanism 2 is used for providing power for the adjustable tensioning sprocket lifting mechanism 5; the adjustable tension sprocket lifting mechanism 5 is arranged on the upright post 44, the adjustable tension sprocket lifting mechanism 5 is connected with the gravity type spring tipping mechanism 6, and the adjustable tension sprocket lifting mechanism 5 is used for changing the direction of power output by the lifting power mechanism 2 so as to drive the gravity type spring tipping mechanism 6 to do reciprocating linear motion up and down; the steel billet is placed at the tail end of the gravity type spring tipping mechanism 6, and the gravity type spring tipping mechanism 6 reciprocates linearly up and down or swings left and right to enable the steel billet to reach a tipping angle of critical balance, so that the steel billet is turned.

In the above embodiment, the swing power mechanism 1 and the lifting power mechanism 2 are power mechanisms of the turning machine and are used for providing power sources for the movement of each mechanism of the turning machine, the swing power mechanism 1 is disposed at the most upstream of the turning machine and is used for providing power for the variable four-bar linkage swing mechanism 4, and the lifting power mechanism 2 is disposed at the downstream of the variable four-bar linkage swing mechanism 4 and is used for providing power for the adjustable tensioning sprocket lifting mechanism 5. The sliding spiral cam adjusting mechanism 3 is arranged at the bottom of the variable four-bar linkage swinging mechanism 4, mainly formed by combining a sliding spiral mechanism and a wedge type sliding cam mechanism together, and mainly provides online real-time horizontal coordinate and vertical coordinate adjustment for a swinging rod seat 412 in the variable four-bar linkage swinging mechanism 4, so that the motion track of a swinging rod 41 is changed regularly, synchronous linear fine adjustment of the swinging angle of an internal core component upright post 44 in the variable four-bar linkage swinging mechanism 4 is realized, and the requirements of site differentiation processes are met. The variable four-bar linkage swing mechanism 4 is arranged at the downstream of a power unit of the lower end swing mechanism and is used for converting the reciprocating linear motion of the lower end swing power mechanism 1 into periodic rotary motion and then transmitting the periodic rotary motion to the upright post 44, so that the upright post can swing left and right around a fixed hinged point in a reciprocating manner, and the regular change of the motion track of the upright post is realized by the local adjustment of an internal adjustable component and the linear fine adjustment matched with the external sliding spiral cam adjusting mechanism 3, so that the process requirement of the synchronous linear adjustment of the inclined swing angle of the upright post 44 of the internal core component is met; the adjustable tensioning chain wheel lifting mechanism 5 is arranged at the upstream of the gravity type spring tipping mechanism 6 and is used for changing the action direction of the oblique pulling force output by the upper end lifting power mechanism 2, transmitting the changed action direction to the lifting trolley 53 and driving the lifting trolley 53 to reciprocate freely and linearly up and down along the slideway of the upright post 44; the gravity type spring tipping mechanism 6 is arranged at the most downstream of the whole system and is an actuating mechanism at the core of the system, the material supporting arm 63 linearly reciprocates up and down by up-and-down sliding of the lifting trolley 53, meanwhile, the gravity type spring tipping mechanism can realize downward fixed-angle elastic damping swinging of the gravity type spring tipping mechanism, the gravity type spring tipping mechanism can be matched with the left-and-right swinging of the upstream upright post 44 to turn the billet to a tipping angle with critical balance, the kinetic energy is impacted by the gravity of the billet in the rapid linear descending process of the material supporting arm 63, the instant 90-degree overturning of thermal billet impact grounding is realized, the scale on the surface of the billet is removed at the same time, and the regular swinging of the variable four-bar swinging mechanism 4 can be matched for direct falling and overturning, wherein the two overturning modes, namely, lifting impact type and lifting swinging type can be selected according to the actual working condition on site. As shown in fig. 29 to fig. 36, the lifting impact type here means that the lifting motion of the lifting trolley 53 in the upright column 44 makes the material supporting arm 63 perform its own elastic damping swing with a downward fixed angle while performing an upward linear motion, so as to turn the billet to a tipping angle of critical balance, and impact kinetic energy by the gravity of the billet during the rapid linear descending process of the material supporting arm, so as to break the attitude balance of the hot billet, realize 90 ° turning of the billet at the moment of impact contact, and simultaneously remove the scale on the surface of the billet, specifically, 5 steps are performed: the method comprises the following steps of firstly, an initial station, secondly, a no-load lifting station, thirdly, a heavy-load lifting tipping station, fourthly, falling back to a gravity overturning station, and fifthly, restoring the blank to the original position after the blank is tipped; the lifting swing type means that the lifting motion of the lifting trolley 53 in the upright post 44 causes the material supporting arm 63 to move linearly upwards and simultaneously realize elastic damping swing of a downward fixed angle, so that the steel billet is turned to a critical balanced tipping angle, the upright post 44 continuously drives the material supporting arm 63 to continuously tilt and turn, so that the steel billet does complex parabolic track motion until the steel billet touches the roller way plane, instantaneous gravity fall-back and turning are realized, the first step 2 and the last step 1 are completely the same as the lifting impact type, but the middle step 2 is completely different, the tilting angle of the lifting impact type blank in the swing arm is far smaller than that of the lifting swing type, the former causes the blank to impact and contact with the roller way working surface by the vertical up-and-down motion, and the latter causes the blank to contact with the roller way by the further tilting parabolic motion of the swing arm, the blank has both horizontal movement and vertical downward movement, and the resultant movement track is a complex parabola. The lifting swing type concrete steps are as follows: the method comprises the following steps of firstly, initial station, secondly, no-load lifting station, thirdly, heavy-load lifting tipping station, fourthly, heavy-load swinging station, fifthly, swinging and turning station, and sixthly, restoring the blank to the original position after the blank is tipped. The tilter realizes constant-angle inclination in the rising process of a hot billet in a material supporting arm 63 by means of damping buffering of a rotary spring damping body, so that the hot billet reaches a critical tilting angle, the rising potential energy is converted into descending impact kinetic energy in the falling process of a lifting trolley 53, the attitude balance is broken instantaneously when the billet in a critical tilting state contacts the surface of a roller way under the action of instantaneous impact load, gravity impact overturning is realized, the surface layer of the billet is removed of overheated iron scale, and the aim of automatically overturning the billet by 90 degrees is efficiently and conveniently realized.

As shown in fig. 1 and 19, the swing power mechanism 1 and the lifting power mechanism 2 are stacked up and down, and have two sets of upper and lower units in a spatial layout, the lifting power mechanism 2 is arranged above the upper unit, and the swing power mechanism 1 is arranged below the lower unit. The two groups of independent power units are independently controlled by double cylinders and double gas circuits, are respectively controlled by two sets of independent pneumatic electromagnetic directional valves, flow regulating valves, pressure reducing valves and an operation table remote electric control system PLC on site, and are assisted by a plurality of sets of electromagnetic inductors arranged on site, so that the cylinders of the 2 groups of the system respectively move independently or are combined according to certain logic programming, and the cylinders sequentially and sequentially cooperate to act, can synchronously respond, delay and sequentially act, and cooperate to complete the action decomposition process requirement of a blank overturning complex motion track flow.

Meanwhile, as shown in fig. 1 and fig. 19, the swing cylinder 11 in the swing power mechanism 1 and the tail of the lifting cylinder 21 in the lifting power mechanism 2 both adopt the same design scheme of a convenient and fast dismounting structure, and the tail parts of the cylinder barrels are respectively connected with the first hinged support 12 through bolts, but the other members of the matched hinge pairs are obviously different. The swing cylinder adopts a bolt connection or welding fixation mode to spatially fix the second hinged support 13 and the base 15, and the first hinged support 12 and the second hinged support 13 form a full-space fixed hinged pair through the cooperation of the first pin shaft 14 of the middle component and the radial spherical plain bearing, so that the moving freedom degrees in the horizontal plane of the swing cylinder 11 in the transverse direction and the longitudinal direction of 2 directions are completely limited, only the spatial rotation freedom degree is kept, the Y-shaped ear ring at the head of the piston rod is hinged with the swing rod 41 through the second pin shaft 1111 to form a power unit of a lower end swing mechanism, and the swing rod 41 is driven to swing left and right around the swing rod support 412; the first hinge base 12 matched with the lifting cylinder 21 forms a longitudinal sliding hinge pair with the sliding base 22 through the first pin shaft 14 and the radial spherical plain bearing, is integrally arranged on the upper plane of the connecting rod sleeve 434 to form a power source of the lifting mechanism at the upper end, and is hinged with the inner chain link of the sleeve roller chain 52 through the Y-shaped ear ring at the head part of the piston rod of the first hinge base to transmit the output tension of the lifting cylinder 21 so as to meet the design requirement of precise fine adjustment of the stroke of the on-site cylinder and the meshing wrap angle of the chain wheel 511. The upper plane of the connecting rod sleeve 434 matched with the sliding seat 22 is designed with an oval sliding groove, the lower bottom surface is milled with a through long T-shaped groove, the sliding seat 22 can longitudinally slide on the upper plane of the connecting rod sleeve 434 within a certain range, the horizontal coordinate position of the plane of the lifting cylinder 21 is adjusted, and after the adjustment is in place, the connecting and compressing are finally carried out through 2 groups of T-shaped bolts 23. The swing cylinder 11 and the lifting cylinder 21 in the power mechanism are respectively controlled by two independent pneumatic electromagnetic directional valves on site, the two cylinders can independently act, the two cylinders can also act in a certain logic sequence after being optimized by an electric control system, and the length of the response time and the speed of the action rhythm are realized by the logic programming of an electric PLC on a control panel of a main operating board. The pneumatic control loop controls the pressure and flow of the pneumatic system by adopting a pressure reducing valve and a throttle valve, and regulates and controls the running speed of the pneumatic system, so that the descending speed of the lifting trolley 53 is changed, the instant gravity impact during blank turning is reduced, and the sudden impact fatigue fracture of the working surface of the roller way is prevented. Meanwhile, a buffer damping spring can be additionally arranged on the lower bottom surface of the upright post 44, and the buffer damping spring is in instant collision contact with the telescopic beam 538 to absorb the descending impact kinetic energy of the lifting trolley 53, slow down the gravity overload impact and prolong the service life of the equipment. The buffering springs can be cylindrical spiral compression springs or disc springs according to actual requirements on site, the disc springs are preferably selected, the rigidity and the load characteristic curve of the combined springs are changed through different combination modes (folding or involution) and quantity selection of the disc springs, and the actual working condition requirements on site are met.

In addition, the electric control system of the tilter adopts PLC auxiliary control, a light-sensitive proximity switch can be additionally arranged at a proper position of a billet conveying roller way, when a discharged billet is conveyed to a position close to a tilting area, a sensor catches a thermal state light-sensitive signal and transmits the thermal state light-sensitive signal to a remote main control box through a data line, a direct current digital electric signal is output after the PLC logic programming of an internal core part, an on-site pneumatic electromagnetic reversing valve is sequentially electrified to act, sequential or synchronous logic movement of two cylinders is respectively controlled, 90-degree tilting in the lifting and falling process of the thermal state billet on the roller way is realized, the rolling biting surface of the billet is changed, the on-site rolling process requirement is met, the overheating iron scale on the surface layer of the billet is removed, and the surface quality of a rolled billet finished product is improved. The main control box of the steel turnover machine can realize unmanned remote automatic control of the turnover machine through bidirectional interlocking and logical operation with the front-drive roller way electric control system PLC, and can realize the manual remote control of the operation table through manual switching of the operation table. The lifting cylinder 21 and the swing cylinder 11 preferably adopt SC series cylinders with internal pistons provided with magnetic rings, when the swing cylinder 11 acts to cause the upright post 44 to swing to a certain angle or the lifting cylinder 21 acts to cause the lifting trolley 53 to rise to a certain height, the electromagnetic sensors arranged on the external pull rods of the two cylinders receive magnetic signals of the magnetic rings of the internal pistons of the cylinders and synchronously convert the magnetic signals into direct-current digital electric signals, and the direct-current digital electric signals are transmitted to the electromagnetic reversing valves of the two cylinders after PLC programming conversion, so that the two cylinders stop acting instantaneously or synchronously complete reverse movement, and the action flow of turning the billet by 90 degrees is completed. Therefore, the telescopic limit positions of the piston rods of the two air cylinders can be controlled by adjusting the position of the electromagnetic inductor on the air cylinder pull rod, and the full-automatic control of the blank overturning process is realized by means of the logic programming of the electric control system PLC. If a common cylinder is selected, 2 sets of electromagnetic induction switches are additionally arranged at a certain proper position of the stroke of the upright post 44 or the cylinder piston to realize the automatic control positioning action.

Preferably, as shown in fig. 1, 4, 7 to 9, in an embodiment of the present invention, the sliding spiral cam adjusting mechanism 3 adopts a unit combination design scheme of embedding a superimposed wedge type sliding cam mechanism above the sliding spiral mechanism, and the transverse adjusting nut 34, the transverse adjusting spiral rod 33 and other accessories together form the sliding spiral mechanism, which is disposed below the sliding spiral cam adjusting mechanism 3; the swing frame 35, the inclined slideway 392, the mandril 39 and other related accessories form a wedge type sliding cam mechanism which is superposed above the adjusting mechanism. The sliding screw mechanism and the wedge type sliding cam mechanism are mutually matched to act to adjust the vertical coordinate of the swing rod seat 412. The sliding screw mechanism and the wedge type sliding cam mechanism are symmetrically arranged below the swing rod 41 and are integrally installed on the base 15. The first speed reducing motor 31 is directly flange-fixed on the bearing seat 32 on the transmission side, two groups of bearing seats 32 on the transmission side and the non-transmission side are completely the same structural design and are jointly fixed on the base 15, which is convenient for spatial layout and on-site assembly and disassembly, and drives the circumferential forward and reverse rotation of the transverse adjusting screw rod 33 through the radial support and sliding antifriction of the two groups of first sliding bearings 321, so that the transverse adjusting nut 34 matched with the transverse adjusting motor is axially and linearly transversely moved left and right, the inclined slide way 392 fixed above the transverse adjusting nut 34 is driven to synchronously and axially and linearly slide, the ejector rod 39 is driven to vertically and linearly move up and down, the vertical coordinate of the fixed hinge chain of the oscillating rod 41 is changed, and the inclination angle of the upright column 44 is finally adjusted in real time.

Preferably, as shown in fig. 7 to 9, in an embodiment of the present invention, an L-shaped slideway 394 is fixedly welded above the bearing seat 32 disposed on the non-transmission side, the bottom of the top bar frame 393 is designed to be a concave structure, and integrally covers the cantilever rail of the L-shaped slideway 394, and lubricating grease is applied to the matching surfaces of the two, so that the top bar frame 393 can manually adjust the transverse positioning parameters thereof, and is finally fixed by a locking bolt 3931, thereby changing the abscissa of the swing link 41 fixing the hinge chain. It can be seen that two regulation schemes are provided in the invention, both the purpose of adjusting the inclination angle of the upright post 44 can be achieved, and the vertical coordinate of the oscillating bar 41 can be automatically regulated in real time by means of intermittent forward and reverse rotation of the first speed reducing motor 31 through an electromagnetic induction switch arranged on site; the horizontal coordinate of the top rod frame 393 needs to be manually adjusted on the L-shaped slide rail 394 through manual intervention, or the bottom of the L-shaped slide rail 394 and the bottom of the top rod frame 393 are designed into a sliding spiral pair structure and are provided with a speed reduction motor and a corresponding electromagnetic induction switch, so that the online automatic real-time adjustment and control of the horizontal coordinate of the fixed hinged chain of the oscillating bar 41 can be realized, and a specific adjusting scheme can be selected according to the actual working condition on site.

Preferably, as shown in fig. 4, 7 to 9, in an embodiment of the present invention, the transverse adjusting nut 34 is designed as an integral rectangular parallelepiped structure, and forms a sliding screw pair by matching a full-length thread internal thread profile turned on an end surface thereof with the transverse adjusting screw rod 33. The upper plane of the transverse adjusting nut 34 is designed with two groups of fixed hinge pairs, one group is used for hinging the inclined slideway 392, and the other group is combined with the hinged swinging frame 35 and the swinging hinged ball 38. The inner side of the swing frame 35 is provided with a longitudinal adjusting screw rod 37, and is connected with the swing frame 35 into a whole through a first deep groove ball bearing 354 fixed in a swing frame gland 351 to form a rigid integral component capable of swinging. The longitudinal adjusting screw rod 37 is made of 20Cr alloy steel, the tail part of the longitudinal adjusting screw rod is designed to be in a mode that a cambered surface bulge is wrapped and hinged with a cambered surface groove of the swinging hinged ball head 38, 360-degree omnibearing rotation freedom degree is achieved, wherein a central arc of the cambered surface bulge is a semi-circular arc, the swinging hinged ball head 38 matched with the cambered surface bulge is made of a tin-phosphor bronze ZCuSn10P1 material, good abrasion and friction resistance is achieved, the radial and axial supporting effect of a thrust sliding bearing is achieved, an additional virtual constraint is provided for the longitudinal adjusting screw rod 37, the stress condition of the longitudinal adjusting screw rod 37 is improved, local unbalance loading deformation is prevented, the longitudinal adjusting screw rod 37 can synchronously swing left and right along with the swing frame 35 and the longitudinal adjusting screw rod 37, and a group of swinging three-in-one-step is formed.

Preferably, as shown in fig. 7 to 9, in one embodiment of the present invention, the longitudinal adjusting nut 36 in the swing frame 35 uses a 60 ° fine triangular internal thread with a large equivalent friction coefficient and a good thread form self-locking property, and is engaged with the longitudinal adjusting screw rod 37 to be movable up and down along its axis. The longitudinal adjusting nut 36 is provided with a set of fixed hinge pairs on its side to hinge with the inclined slide 392. When the hand wheel 353 is manually operated to rotate, the longitudinal adjusting screw rod 37 synchronously rotates in the circumferential direction, so that a triple coaxial composite hinged component formed by the swinging hinged ball head 38, the longitudinal adjusting screw rod 37 and the swinging frame 35 synchronously swings left and right in a small range around a third pin 341 fixed on the transverse adjusting nut 34, the longitudinal adjusting nut 36 is driven to slide up and down along the axis of the longitudinal adjusting screw rod 37, an inclined slide way 392 hinged with the longitudinal adjusting nut 36 swings left and right around a fourth pin 342 of a fixed hinge point on the transverse adjusting nut 34, the inclined included angle between the inclined slide way 392 and the horizontal plane is finally changed, and the ejector rod 39 is pushed to move up and down linearly.

Preferably, as shown in fig. 7 to 9, in one embodiment of the present invention, the upper surface of the inclined slide 392 is milled with a groove structure, and the sliding hinge ball 391 is embedded in the groove slide and can slide linearly along the groove. In order to reduce friction retardation, the sliding hinged ball head 391 is made of tin-zinc-lead bronze, and extreme pressure lithium-based lubricating grease is coated in the groove of the inclined slideway 392. The sliding hinge ball 391 is provided with a spherical groove and is wrapped and hinged with a ball head protrusion at the bottom of the push rod 39 by 360 degrees, and when the sliding hinge ball 391 slides along the oblique slide way 392, the push rod 39 can be pushed to vertically lift and descend under the restriction of the transverse displacement of the push rod frame 393. Preferably, the ejector rod frame 393 is an integral welding insertion component, the top of the ejector rod frame is provided with a sleeve, the inner side wall of the sleeve is embedded with a sliding bearing made of bronze and coated with lubricating grease for friction reduction, and the sleeve is movably matched with the ejector rod 39 and restricts the freedom degree of the transverse left-right movement of the ejector rod. The top rod 39 is a three-in-one assembly structure, the bottom of the top rod is rotatably matched with a ball head protrusion and matched with the sliding hinged ball head 391, the top of the top rod is rotatably matched with a circular pressure plate and matched with a T-shaped groove at the bottom of the swing rod seat 412, and the swing rod seat 412 and the top rod 39 are welded and fixed on site, so that the swing rod seat 412 and the top rod 39 are connected into a rigid integral component. In order to ensure the accuracy and convenience of field installation and positioning, the lower bottom surface of the swing rod seat 412 is provided with a T-shaped groove for matching with the ejector rod 39.

As shown in fig. 4, the swing frame 35, the longitudinal adjusting screw rod 37, the longitudinal adjusting nut 36, the swinging hinged ball 38, the inclined slide 392 and the transverse adjusting nut 34 of the upper half of the sliding spiral cam adjusting mechanism 3 are combined together to form a typical planar link rod guide mechanism in mechanical design, the upper plane of the transverse adjusting nut 34 is the planar link rod guide mechanism carrier platform, the upper plane is provided with a third pin 341, the swing frame 35, the longitudinal adjusting screw rod 37 and the swinging hinged ball 38 are coaxially and compositely hinged, and form a planar II-level rod group with a spatial degree of freedom of 0 after being screwed with the longitudinal adjusting nut 36, and are rotatably hinged with the inclined slide 392 as an I-level mechanism through a fifth pin 361, the inclined slide 392 is hinged with the upper plane of the transverse adjusting nut 34 through a fourth pin 342 to form a planar link rod swinging mechanism with a spatial degree of freedom of 1, in addition, ramp 392 is a non-circular wedge cam.

Preferably, as shown in fig. 1 to 5 and 10 to 16, in an embodiment of the present invention, the variable four-bar linkage 4 is an intermediate process component of a system, and is a planar four-bar linkage typically used in mechanical design, and mainly includes a vertical column 44, a third hinge seat 442, a connecting rod 43, a swing rod 41, and a swing rod seat 412, where the third hinge seat 442 is fixed on the base 15 and is rotatably hinged to the vertical column 44, and both the abscissa and the ordinate of the hinge pair are fixed bidirectionally and non-adjustable; two ends of the connecting rod 43 are respectively provided with a group of rotating pairs which are respectively hinged with the upright post 44 and the swing rod 41 in a rotating way. Compared with the common plane four-bar mechanism, in the invention, the swing link seat 412 hinged with the swing link 41 can change the horizontal coordinate and the vertical coordinate of the swing link in real time under the driving of the sliding spiral cam adjusting mechanism 3, so as to change the geometric motion track of the swing link 41 and finally influence the vertical inclination angle of the upright post 44, thereby meeting the design process requirement of the expected angle in the steel turning action process. The connecting rod 43 adopts a design scheme of a combined sleeved split structure, and the main structure of the connecting rod is formed by inserting and assembling 2 groups of connecting rod beams 431 with completely consistent and symmetrical structures into the connecting rod sleeve 434 from two ends respectively. The connecting rod sleeve 434 is welded by steel plates to form a hollow box-shaped structure, a long elliptical hole is milled on the upper plane of the connecting rod sleeve, the connecting rod sleeve is connected and fixed with the sliding seat 22 of the lifting cylinder 21 through the T-shaped bolt 23, and a T-shaped groove is milled on the lower plane of the connecting rod sleeve, so that the square head of the T-shaped bolt 23 can be conveniently slid and fixed. The lifting cylinder 21 can slide back and forth on the plane of the connecting rod sleeve 434, so that the horizontal coordinate of the lifting cylinder can be adjusted in a micro-scale mode, and the process requirement of accurate fine adjustment of the stroke of the cylinder and the meshing wrap angle of the chain wheel can be met. Two side steel plates of the connecting rod sleeve 434 are respectively provided with 2 groups of internal threads M20 in mirror symmetry, and the connecting rod beam 431 and the connecting rod sleeve 434 are fixedly connected into a three-in-one integral rigid member through the clamping force of 2 groups of fastening bolts 4341 which are screwed with the internal threads. The third shaft sleeve 435 with tin, zinc, lead, bronze and copper materials is embedded in the connecting rod beam 431 and is movably hinged with the lifting arm 45 and the swing rod upper sliding seat 414 respectively, and the swing rod upper sliding seat 414 and the lifting arm 45 are adjustable sliding revolute pairs on the swing rod 41 and the upright post 44 respectively.

To facilitate adjustment of the mating telescopic length of 2-bar set 431 within bar set 434, the longitudinal length geometry of link 43 is varied, thereby adjusting its trajectory of motion and ultimately affecting the vertical tilt angle of the upright 44, preferably, as shown in figures 1, 11 and 12, in one embodiment of the present invention, 2 sets of adjusting mechanisms are specially added on the connecting rod 43, the support 432 adopts a design scheme of split up-down structure, the lower half part is fixedly welded on the connecting rod beam 431, the support 432 and the adjusting rod 433 are rotatably matched through a convex-concave platform inside the support 432, and bears the axial push/pull force, where the axial section of one end of the adjusting rod 433 is concave, i.e. a groove is provided at a certain distance from the end surface of one end of the adjusting rod 433, and correspondingly, a through hole formed between the upper half part and the lower half part of the support 432 is provided with a protrusion, i.e. a convex-concave table is formed, the protrusion is matched with the groove at one end of the adjusting rod 433 to realize the rotary matching of one end of the adjusting rod 433 and the support 432. The other end of the adjusting rod 433 is screwed with the nut of M36 fixed on the connecting rod sleeve 434, and the connecting rod beam 431 can be freely extended and retracted in the connecting rod sleeve 434 conveniently and rapidly by the axial push/pull force transmitted by the rotation of the adjusting rod 433, and is locked and positioned by the fastening bolt 4341 after reaching the expected adjusting position. The 2 sets of adjusting rods 433 are manually driven, can independently act respectively, can also be adjusted in a matching way, and can be flexibly operated according to actual requirements on site. Therefore, the telescopic split-type inserted connecting rod scheme is one of the prominent invention points in the invention.

Preferably, as shown in fig. 1 and 10, in an embodiment of the present invention, the swing link assembly is an adjustable three-pair member with vertically symmetrical T-shaped slideways, and is mainly formed by combining a swing link 41, a swing link upper slide 414, a swing link lower slide 415, and an upper and a lower two sets of swing link pull rods 423 which are respectively independent relatively, and the swing link assembly itself includes 2 sets of rotating pairs for manually sliding to adjust the position coordinates and 1 set of rotating pairs for automatically and linearly adjusting the coordinate parameters. The swing rod 41 is an integral plate type special-shaped component with a symmetrical structure, is formed by cutting a 55mm thick steel plate wire, is provided with a first shaft sleeve 411 made of bronze in an embedded mode at the bottom end, is fixedly hinged with a swing rod seat 412, and can change the horizontal plane horizontal coordinate of the swing rod 41 and adjust the self motion track through the action of a sliding spiral cam adjusting mechanism 3 arranged below the swing rod. The bottom of the swing rod upper sliding seat 414 is designed with a T-shaped groove which can be sleeved on the swing rod 41 and can freely slide on the T-shaped slide way of the swing rod 41 in a reciprocating manner, the top of the swing rod upper sliding seat 414 is designed with 2 groups of rotary hinge pairs, one group is used for hinging the connecting rod 43 and transmitting the power of the swing rod 41, the other group is hinged with a swing arm ear loop 422 and is connected with the swing arm 42 through a swing arm pull rod 423 which is rotatably matched with the swing arm ear loop to form a set of complete four-connecting-rod adjusting mechanism which is used for adjusting the space position coordinate parameters of the hinge pair at the tail end of the connecting rod 43 and changing the motion trail of the connecting rod 43. One end of the rocker arm 42 is hinged to the swing rod 41, the other end of the rocker arm is hinged to the rocker arm ear ring 422, and the top of the rocker arm is provided with an elongated handle which is equivalent to a labor-saving lever and is convenient for manual operation. The rocker arm pull rod 423 is designed by adopting a synchronous rotating double-helix structure, the two ends of the rocker arm pull rod 423 respectively adopt fine-tooth external threads in positive and negative rotation directions to be respectively matched with 2 sets of rocker arm ear rings 422 hinged on the rocker arm 42 and the rocker arm upper slide seat 414 in a rotating mode, when the rocker arm pull rod 423 is rotated in positive/negative directions, the plane linear distance of the central points of 2 hinged revolute pairs on the rocker arm 42 and the rocker arm upper slide seat 414 can be correspondingly extended or shortened, so that the problem that the adjustment sliding stroke distance of the rocker arm upper slide seat 414 is short due to the limitation of the swing inclination angle of the rocker arm 42 is compensated, and the adjustment range of the rocker arm pull rod is expanded. The swing rod lower sliding seat 415 adopts the same rocker arm and pull rod combination structure to manually adjust the spatial position coordinates of the swing cylinder earrings 111, so as to compensate the stroke of the swing cylinder 11 and meet the process design requirement of the swing inclination angle of the swing rod 41. In practical application, the first speed reducing motor 31 and the swing cylinder 11 can be independently adjusted to act, or can be matched to act according to a certain rule after being logically programmed by an electric control system to realize online real-time fine adjustment.

As shown in fig. 1, 3 and 5, two sets of longitudinally slidable and adjustable revolute pairs, namely, a second pin 1111 and a seventh pin 4141, are designed on the body of the swing link 41, and are respectively arranged on the lower swing link slide 415 and the upper swing link slide 414, and the fine adjustment of the position is performed through the swing link rocker arm pull rod mechanism, so as to change the horizontal coordinate and the vertical coordinate of the swing link 41, thereby changing the track parameters of the connecting rod 43 and the swing cylinder 11, and further affecting the overall motion track of the whole variable four-bar linkage swing mechanism 4. Structurally, the upper and lower sets of rocker arm and pull rod mechanisms matched with the upper rocker slide 414 and the lower rocker slide 415 are all designed in the same structure, and the only difference is that the length of the rocker arm and pull rod 423 is slightly different. The swing rod, swing arm and pull rod mechanism also adopts a design scheme of a plane multi-rod mechanism combining an I-level mechanism and a II-level rod set in mechanical principle design, a swing arm 42 is hinged with a swing rod 41 body through an eighth pin shaft 421 and can swing left and right to form the I-level mechanism, a swing arm ear loop 422 and swing arm pull rod combination is combined with a swing rod upper sliding seat 414 or a swing rod lower sliding seat 415 through a ninth pin shaft 424 (an inner pair of the II-level rod set) to form the II-level rod set comprising two movable components (the swing rod upper sliding seat 414 or the swing rod lower sliding seat 415 and the swing arm ear loop 422 and swing arm pull rod combination) and 3 low pairs (2 rotating low pairs formed by the eighth pin shaft 421 and the ninth pin shaft 424 and 1 moving low pair formed by the swing rod 41 and the swing rod upper sliding seat 414 or the swing rod lower sliding seat 415). The I-level mechanism and the II-level rod group are connected through an eighth pin 421 to form a rocker arm pull rod mechanism, the design calculation of the internal degree of freedom is that F is 3n-2PL-PH is 3 x 3-2 x 4-0 x 1, the requirement of the degree of freedom of the plane link motion design is met, the upper rocker slide 414 or the lower rocker slide 415 can slide linearly and regularly under the condition that the rocker arm 42 swings, and therefore the plane position parameter coordinates of the seventh pin 4141 and the second pin 1111 are changed.

Preferably, as shown in fig. 1, 13 to 17, in an embodiment of the present invention, the upright column 44 is a core component in the entire variable four-bar linkage swing mechanism 4, and the upright column 44 is a steel rivet of an integral frame structure, and mainly functions to enable the supporting arm 63 to drive the billet to continuously tilt through the swinging of the upright column 44 in the case that the supporting arm 63 is forced to bear the dead weight of the billet to tilt to a certain angle, so that the tilting tilt angle of the billet is superposed on the gravity critical tilting angle. The body of the upright post 44 is formed by welding common hot rolled channel steel, 1 group of rotary hinge pairs are designed at the bottom, the rotary hinge pairs can swing left and right around a third hinge seat 442 fixed on the base 15, and the final stacking inclination angle of the subsequent material supporting arm 63 is directly influenced by the size of the inclined swing angle. Preferably, the main frames on both sides of the upright column 44 are made of 180 hot rolled channel steel, the channel steel grooves are used as guide slideways, the second deep groove ball bearings 532 in the trolley wheel shaft 531 are directly arranged, so that the trolley wheel shaft can roll straightly up and down along the channel steel grooves, and bearing stoppers 5361 are welded on the inner sides of the upper and lower flanges of the channel steel to prevent the trolley wheel shaft 531 from moving axially, so that the lifting trolley 53 only keeps the longitudinal freedom degree of up and down movement and limits the left and right transverse freedom degrees under the working condition of reducing lifting retardation by adopting rolling friction. The top end of the upright post 44 is provided with a tension chain wheel assembly 51, and the central line of the chain wheel 511 is consistent with the geometric symmetrical central line of the upright post 44 and the axial line of the piston rod of the lifting cylinder 21, so that the chain shaking/chain dropping caused by unbalance loading is prevented, and the engagement of the chain links is convenient to enter and exit.

Preferably, as shown in fig. 1, 13 to 16, and 20 to 24, in an embodiment of the present invention, 1 group of L-shaped sliding rails are welded and fixed to side wings of a channel steel of a main frame of the column 44, and are arranged in mirror symmetry with a geometric symmetry center line of the column 44, and are in concave-convex fit with a base groove of the lifting arm 45, so that the lifting arm 45 can linearly slide up and down along a side flange of the column 44, and a longitudinal coordinate of a tenth pin 4351 on the lifting arm 45 is changed, thereby affecting movement trajectories of the connecting rod 43 hinged to the lifting arm 45 and other components in the variable four-bar linkage swing mechanism 4, and finally affecting an inclined swing angle of the column 44. The up-down linear sliding of the lifting arm 45 is realized by the lifting arm reel 455 and the fixed pulley 458 which are arranged on the side wing of the main frame channel steel of the upright post 44, the whole process synchronous automatic linear fine adjustment can be realized by the programming of the power control system PLC and the control cooperation of the electromagnetic induction switch, and the inclination swing angle of the upright post 44 is automatically adjusted in the running process of the equipment, so that the process design requirement of the billet steel turning critical superposition inclination angle is met. The lifting arm reel 455 is designed to be axially wide and has a double-flange structure, one end of the lifting arm reel 455 is supported by the second speed reduction motor 454, the other end of the lifting arm reel 455 is antifriction-supported by the bronze sliding bearing sleeve made of the same material on the lifting arm reel support 456, and similarly, the fixed pulley 458 is antifriction-supported by the bronze sliding bearing sleeve made of the same material, and a groove is designed on the pulley to prevent the steel wire rope 452 from falling off. Fixed pulley 458 is welded and fixed at the top of the main frame channel steel side wing of the upright post 44 through a fixed pulley support 457, lifting arm reel 455 is welded and fixed at the bottom of the main frame channel steel side wing of the upright post 44 through a lifting arm reel support 456, and a lifting arm 45 capable of sliding up and down is arranged in the middle of the main frame channel steel side wing of the upright post 44. When the lifting arm drum 455 rotates forward and backward under the driving of the second speed reduction motor 454, the wire rope 452 fixed on the surface of the lifting arm drum correspondingly extends or shortens, and the lifting arm 45 connected with the wire rope 452 slides linearly up and down through the load transmission of the fixed pulley 458 and the change of the force direction, so that the vertical coordinate of the lifting arm drum is changed in real time, and online synchronous fine adjustment is realized. The first speed reduction motor 31 and the second speed reduction motor 454 can independently adjust and act, and can also act in a matching way according to a certain rule after being programmed by an electric control PLC logic, so that the online real-time fine adjustment of the parameters of 2 local key points is realized. The descending motion of the lifting arm 45 mainly depends on gravity, the ascending motion mainly depends on the lifting force of the lifting arm reel 455, and besides the on-line linear fine adjustment can be realized, the lifting arm 45 can also be fixed on the L-shaped slide rail of the upright post 44 by the tightening force of its own set screw 453 to form 1 set of fixed rotating hinges, and the specific adjustment mode can be selected according to the actual working conditions in the field. Preferably, in order to facilitate the winding of the steel wire rope 452 and prevent the up-and-down sliding retardation of the lifting arm 45 caused by the unbalance loading, the invention adopts a double-steel-wire-rope synchronous lifting scheme, 2 sets of steel wire ropes 452 with completely the same structure are adopted on site, correspondingly, the number of the pulley assemblies 458 and the fixed pulley supports 457 is two, the two fixed pulleys 458 can improve the stress environment of the lifting arm 45 and prevent the unbalance loading from influencing the flexibility of the up-and-down sliding thereof, the 2 sets of steel wire ropes 452 are arranged on two sides of the geometric symmetry axis of the lifting arm 45 in a mirror symmetry manner and are firmly connected with the geometric symmetry axis, and after double-winding around the fixed pulleys 458, the two ends of the lifting arm reel 455 are uniformly wound, and the lifting arm 45 is driven to lift by the rotation of the lifting arm reel 455 and synchronous extension or shortening. In addition, the matching surfaces of the L-shaped sliding rail and the groove at one end of the lifting arm 45 are coated with lubricating grease to reduce friction, so that the lifting arm 45 can conveniently slide up and down along the L-shaped sliding rail.

As shown in fig. 3, the variable four-bar linkage swing mechanism 4 is a typical planar four-bar linkage mechanism in mechanical principles, and the upright 44 is fixedly hinged to a third hinge base 442 fixed to the base 15 by an eleventh pin 441 to form an I-stage mechanism having a spatial degree of freedom of 1 and capable of swinging left and right; the link 43 and the swing link 41 are movably hinged through an inner pair (a seventh pin 4141) to jointly form a II-level rod set including 2 outer pairs, 1 inner pair, and the spatial degree of freedom is 0, wherein one of the 2 outer pairs included in the II-level rod set is movably hinged with the swing link base 412 through a sixth pin 413, and the other outer pair is movably hinged with the I-level mechanism, i.e., the upright post 44, of the next level through a tenth pin 4351 to jointly form a II-level mechanism assembly which is flexibly hinged with 1I-level mechanism and 1 II-level rod set and moves regularly. The variable four-bar linkage 4 comprises 3 free moving members (upright 44, link 43 and swing rod 41) and 4 sets of rotation pairs (sixth pin 413, seventh pin 4141, tenth pin 4351 and eleventh pin 441), and the degree of spatial freedom of the four-bar linkage is F-3 n-2PL-PH 3-2 4-0-1, which completely meets the requirement of mechanical design on the limitation of the number of spatial degrees of freedom of the prime mover, so that the whole variable four-bar linkage 4 can drive the link 43 and the upright 44 to move regularly and in a fixed track manner on the premise that the swing rod 41 driven by the swing power mechanism 1 is the active member.

Preferably, as shown in fig. 1, 17, 18, 25 and 26, in an embodiment of the present invention, the adjustable tension sprocket lifting mechanism 5 mainly comprises a tension sprocket assembly 51 and a lifting cart 53, which are important parts in the power output transmission process of the present invention. The tensioning chain wheel assembly 51 is arranged at the topmost end of the upright post 44 and mainly plays a role in force transmission and guiding, the meshing wrap angle of the chain wheel 511 is adjusted, the downward oblique output tension of the lifting cylinder 21 is converted into vertical lifting tension through flexible connection of the sleeve roller chain 52, and the lifting trolley 53 is pulled to linearly lift along main frame channel steel on two sides of the upright post 44. The mounting channel steel 516 at the top end of the upright post 44 is a mounting base platform of the tensioning chain wheel assembly 51, the geometric symmetrical center line of the upright post 44 is used as an assembly reference line, the mounting channel steel is directly welded and fixed at the top end of the upright post 44, the chain wheel 511 and the piston rod of the lifting cylinder 21 are arranged in a collinear manner, 2 strip-shaped steel plates with the thickness of 14mm are welded on the back surface of the mounting channel steel 516 to form a slide way, and the tensioning plate 513 is wrapped, so that the tensioning plate can linearly reciprocate up and down along the slide way. 2 sets of self-aligning roller bearings are designed in the chain wheel 511 and integrally sleeved on the tensioning plate 513 after being assembled with the chain wheel shaft 512. An oblong through hole is milled in the tensioning plate 513, so that 2 sets of fixing bolts 514 fixed on the back surface of the mounting channel 516 can slide longitudinally in the oblong hole relatively. In order to facilitate fine adjustment and fixation of the ordinate of the sprocket 511, a tensioning nut is welded to the back of the mounting channel 516 and is in threaded fit with a tensioning screw to form a tensioning screw pair 515, so that the tensioning screw pushes against the tensioning plate 513 to manually lift and finely adjust and slide along the slideway, and after the tensioning screw is adjusted in place, the mounting channel 516 and the tensioning plate 513 are tightly connected into a rigid integral component by using a fixing bolt 514.

Preferably, as shown in fig. 1, 17, 25 and 26, in an embodiment of the present invention, the lifting trolley 53 is an extremely important sliding lifting member in the system, and the lifting trolley 53 mainly functions to change the vertical coordinate of the bearing rod assembly 62 and the material supporting arm 63 in the gravity type spring tilting mechanism 6, convert the power output of the lifting cylinder 21 into gravitational potential energy on the height of the billet, and provide energy reserve for the kinetic energy impact of the subsequent billet fall-back and overturn. The lifting trolley 53 is designed as a rectangular frame assembly structure, and is formed by combining 2 telescopic beams 538 on two side surfaces, 1 trolley pressure plate 533 on the back and 1 lifting plate 537 on the top, wherein the lifting plate 537 on the top is directly welded on the upper surfaces of the 2 telescopic beams 538 and flexibly connected with the sleeve roller chain 52 to transfer the output tension of the lifting cylinder 21. The trolley pressing plates 533 are fixed to the rear end faces of the 2 telescopic beams 538 by bolts, and fine-pitch nuts of M36 are arranged at the middle positions of the trolley pressing plates and are screwed with the adjusting rods 534. The adjusting rod 534 is provided with a counterweight 535 to balance the additional tilting moment of the supporting arm 63 under the working condition of lifting the supported steel billet, so as to increase the stability of the upright post 44. In the actual use process, the counterweight 535 can be rotated on the adjusting rod 534 on site according to the actual weight of steel billets of different specifications, and the horizontal coordinate of the counterweight 535 is changed, so that the moment arm distance of the gravity center of the counterweight 535 relative to the center point of the rotating pair of the third hinged support 442 is changed, the actual requirement of on-site tilting moment balance is met, the stability and flexibility of system movement are improved, and the response time is shortened.

Preferably, as shown in fig. 17, 25 and 26, in an embodiment of the present invention, the telescopic beam 538 is an elongated plate-shaped member, a groove slideway is provided in the middle of the telescopic beam 538 in the height direction, the groove slideway extends from the rear end surface of the telescopic beam 538 to the front end surface of the telescopic beam 538, and the length direction of the groove slideway is consistent with the length direction of the telescopic beam 538, that is, the groove slideway is milled in the middle of the telescopic beam 538 and covers the upper and lower surfaces of the trolley axle 531 with a square cross-section structure, so that the trolley axle 531 can slide longitudinally along the slideway. The trolley wheel shaft 531 is milled with a step blind hole at the position of the geometric symmetry center line, and a third deep groove ball bearing 536 is designed to be matched with the adjusting rod 534, so that the adjusting rod 534 and the trolley wheel shaft 531 are connected into an integral component which can rotate relatively movably and can synchronously and longitudinally slide along the axis of the adjusting rod 534. When the adjusting rod 534 is manually rotated, because the trolley wheel shaft 531 is stationary relative to the upright post 44, the internal threads on the trolley pressing plate 533 can longitudinally reciprocate along the axis of the adjusting rod 534, so as to drive the 2 telescopic beams 538 to be sleeved on the upper and lower surfaces of the trolley wheel shaft 531, and to transversely slide and adjust along the self slideway, and finally change the plane coordinate of the material supporting arm 63 relative to the steel billet, so as to adapt to the special working condition that the steel billet cannot be touched by the material supporting arm 63 or the contact amount is less under the condition that the base 15 is installed and positioned on site due to the limitation of the layout of the installation structure. Wherein, for reducing the friction retardation, improve the flexibility and the accurate nature of lift dolly 53 elevating movement, dolly shaft 531 both sides are equipped with second deep groove ball bearing 532 respectively, adopt rolling friction's form to make deep groove ball bearing roll the slip from top to bottom in the channel-section steel recess of stand 44 both sides, for preventing second deep groove ball bearing 532's axial cluster, at stand 44 trough steel upper and lower flange's avris welding bearing dog 5361, fixed shafting assembly.

Preferably, as shown in fig. 1, 17 and 27, in an embodiment of the present invention, the gravity spring tilting mechanism 6 is mainly composed of a load bearing rod assembly 62 and a material supporting arm 63, and is a core execution member of the present invention. The bearing rod assembly 62 is a sliding screw pair mechanism which is supported by a set of nuts to rotate and moves linearly in the axial direction of a screw, and 2 sets of the sliding screw pair mechanism are designed in total, are directly welded and fixed on the cross beam 61 and are arranged in a mirror symmetry mode relative to the geometric symmetry center line of the lifting trolley 53. The sleeve 625 is designed as a rectangular hollow structure, and has 2 sets of step holes bored therein, 2 sets of fourth deep groove ball bearings are independently sleeved with each other, and are axially and bidirectionally fixed by an upper gland 623 and a lower gland 628 respectively to form a set of complete integral double rolling bearing support base, which is welded and fixed on the lateral surface of the cross beam 61, and finally integrally welded with the cross beam 61 on the front end surface of a telescopic beam 538 in the lifting trolley 53, and fixedly connected with the lifting trolley 53 to form a rigid integral component. The material supporting arm 63 is a most downstream ring in the system and is also a most central key execution component in the whole system, and 2 groups in total are arranged in a mirror image bilateral symmetry way relative to the geometric symmetry center line of the lifting trolley 53, and the design of the process movement track directly influences the action accuracy and the operation efficiency of billet turning.

As shown in fig. 1, 6 and 28, the material supporting arm 63 is a core part of the design of the present invention and is also a key actuator, and the structural design of the position also adopts the motion design principle of a planar multi-rod mechanism, and a new link mechanism is designed by repeatedly overlapping a II-level rod group with a degree of freedom of 0 on an I-level mechanism with a degree of freedom of 1 for combination. In the invention, a material supporting arm 63 is hinged on a bearing rod 621 and can swing up and down to form an I-level mechanism; the spring seat 642 is hinged on the lifting nut 641 fixed on the bearing rod 621 and is matched with the guide rod 644 through inner pair movement to form a II-level rod group, the thirteenth pin 631 rotatably hinges the I-level mechanism and the II-level rod group, and the damping spring 643 is adopted to buffer and absorb vibration to jointly form a new plane multi-rod mechanism.

Preferably, as shown in fig. 18 and 27, in an embodiment of the present invention, the bearing nut 626 is a hollow double-shoulder cylinder structure, a through long unthreaded hole is drilled in the center, M50 fine threads and internal threads are machined, the bearing nut is designed to be screwed with the external threads and the thread form of the bearing rod 621, 2 sets of upper and lower cylindrical shoulders are symmetrically designed on the outer cylindrical surface of the bearing nut, the upper and lower sets of cylindrical shoulders are respectively sleeved on the upper and lower 2 sets of fourth deep groove ball bearing inner rings of the sleeve 625, and 4 sets of handles 622 are welded and fixed on the top of the bearing nut 626, so as to facilitate labor saving operation. When the handle 622 is rotated forward/backward, the bearing nut 626 can freely rotate circumferentially and flexibly around its own axis under the bearing and antifriction of the fourth deep groove ball bearing in the sleeve 625, and the bearing rod 621 matched with the bearing nut 626 in a rotating manner can synchronously and linearly ascend or descend, so that the space distance between the working surface of the material supporting arm 63 and the lower bottom surface of the steel billet can be accurately adjusted, and the design stroke of the lifting cylinder 21 can be compensated to the maximum extent under the working condition that the base 15 is installed and fixed and cannot be used for continuously adjusting the overall elevation of the equipment. Bearing bar 621 is 60 triangle-shaped tooth type external screw threads of long and thin rod-shaped structure, the bottom welding has the earrings of fork type structure, the fourth axle sleeve 633 of antifriction bronze material of embedded dress in the earrings, with holding in the palm material arm 63 activity hinge joint, it relies on the tooth type auto-lock nature anticreep location of the triangle-shaped screw thread of above-mentioned slip spiral pair to wait to hold in the palm material arm 63 installation elevation adjustment after targetting in place, prevent that bearing bar 621 suddenly became invalid gliding in bearing nut 626, in addition, the bearing bar 621 top is furnished with 2 sets of lock nut soon and is relaxed, increase fixed connection's reliability, prevent to become invalid and weigh down. The material supporting arm 63 is of an asymmetric T-shaped plate frame structure, the front end bearing area is slightly long and is used for supporting steel billets, the tail portion is short and is mainly used for placing rotary spring dampers 64, the whole material supporting arm is formed by linearly cutting thick steel plates of 50mm, a transverse moving slide way of 10mm width is reserved in the middle and is used for assembling movable lug plates 634, and transverse movement of the movable lug plates is facilitated during transverse adjustment. The upper end of the vertical part of the material supporting arm 63 is provided with a set of sliding bearing revolute pair, and the fourth shaft sleeve 633 is assembled in an embedded manner and hinged with a fork-shaped structure lug ring at the bottom of the bearing rod 621, and can freely rotate and swing left and right around the axis of a fourteenth pin 637 so as to change the horizontal inclination angle of the material supporting arm 63 and the billet. The bottom design of holding in the palm the material arm anterior segment has the interior outer hole to have 2 groups of slide bearings of obvious size difference to the fifth axle sleeve 636 of antifriction is slided in the embedding assembly, so that the dismouting, make lead screw 635 can follow the terminal surface of holding in the palm the material arm front segment, and vertical the suit is in 2 groups of integral slide bearings.

Preferably, as shown in fig. 18, 27 and 28, in an embodiment of the present invention, the bottom of the movable ear plate 634 is designed with an internal thread to be screwed with the external thread profile of the lead screw 635 to form a set of manual sliding screw pairs, and when the lead screw 635 is rotated manually in forward/reverse directions, the movable ear plate 634 linearly slides back and forth along the axis of the lead screw 635, so as to drive the stopper welded and fixed to the top of the movable ear plate 634 to linearly move left and right along the slide way in the middle of the front section of the material supporting arm, so as to meet the requirement of precise position adjustment for supporting and matching steel billets of different cross-sectional specifications with the material supporting arm 63 at different positions in the longitudinal direction of the raceway, so that the steel billets are tilted and turned over at the optimal matching position on the material supporting arm 63. The other main function of the movable ear plate 634 is to restrain the transverse sliding of the billet, prevent the inclined billet from sliding off the upper surface of the material supporting arm 63 during the ascending process of the lifting trolley 53, and during the rapid descending process of the material supporting arm 63, the moment when the billet contacts the ground and overturns plays a role in bearing and overturning support, so that the inclined billet breaks the moment dynamic balance of the billet inclination state along the side line contacting with the movable ear plate 634 under the actions of the billet dead weight and descending impact load, and passes over the dynamic balance inclination angle, and the fixed pivot rotates, thereby realizing the automatic overturning of the billet. The thirteenth pin shaft 631 fixed by welding at the tail section of the material supporting arm is in rotary hinged fit with the guide rod 644, and is respectively provided with a set of rotary spring damping bodies 64, 2 sets in total, and the rotary spring damping bodies are respectively hinged on the outer side surfaces of 2 sets of material supporting arms 63 symmetrically arranged in mirror image mode.

Preferably, as shown in fig. 18, 27 and 28, in an embodiment of the present invention, the rotary spring damper 64 is mainly composed of a guide rod 644, a damping spring 643, a spring seat 642 and a lifting nut 641, and mainly functions to provide a reverse balance damping torque when the material supporting arm 63 is tilted with a heavy load, to slow down the swing impact, and to provide a reset turning torque when the material supporting arm 63 continues to descend with an empty load after unloading the billet, so that it can be swung again to the original horizontal position to prepare for the billet turning posture of the next round. The lifting nut 641 is sleeved on the bearing rod 621 and can slide up and down along the axis of the bearing rod, a hinged trunnion is arranged on the side face of the lifting nut and is hinged with the spring seat 642 in a rotating mode, the main function of the lifting nut is to adjust the horizontal included angle between the guide rod 644 and the material supporting arm 63, further adjust the action direction of the elastic force output by the damping spring 643, enable the guide rod 644 to move flexibly, enable the top of the guide rod 644 to freely slide in a long oval hole in the upper plane of the spring seat 642 without stagnation and keep the horizontal state after the material supporting arm 63 is unloaded and reset. After the lifting nut 641 is adjusted and positioned by field experiments, the upper and lower nuts screwed on the bearing rod 621 can be used for fixing and locking. If there is a significant retardation in the movement of the guide rod 644, the rotational position of the upper and lower 2 nuts on the load-bearing rod 621 can be adjusted to make the upper and lower planes of the lifting nut 641 not tightly locked, but leave a suitable fit clearance, so that the lifting nut 641 can slide up and down on the load-bearing rod 621 to a small extent, and retain its axial degree of freedom. The spring seat 642 is of a right-angled L-shaped structure, a long elliptical hole is milled on the upper plane and matched with the guide rod 644, so that the top of the spring seat can slide in a long elliptical hole slideway, the long elliptical hole refers to the situation that two ends of the cross section of the hole are circular arcs, end points corresponding to the two circular arcs are connected linearly to form a long elliptical hole shape, a through hole in the side surface of the spring seat 642 is hinged and matched with a pin shaft on the lifting nut 641, the spring seat 642 can freely rotate around the pin shaft axis of the lifting nut 641 to adapt to the change of the motion matching angle of the spring seat 642, the damping spring 643 and the guide rod 644, the freedom of movement is reserved, and the action direction of output elastic force is not inclined to cause unbalance loading and slippage retardation. The guide rod 644 is a screw shaft having a full-length structure, and a washer and a nut 645 screwed thereto are provided on a lower portion thereof. The damping spring 643 is axially sleeved on the guide rod 644 and fixed at one end and movably supported at the other end, the top of the damping spring 643 is a fixed end and is in pressing contact with the upper plane of the spring seat 642, the bottom of the damping spring 643 is an adjusting movable end and is vertically arranged on the gasket 645 and can slide up and down along the axis of the guide rod 644 along with the gasket 645, the gasket 645 mainly plays a role of a spring mounting base, when the gasket 645 rotates, the precompression of the damping spring 643 can be adjusted, the pretightening force of the damping spring is changed, and therefore the load characteristic curve of the spring is optimized, and the material supporting arm 63 can freely buffer tilting swing under heavy load and can flexibly reset horizontally under no load. The damping spring 643 can be cylindrical helical compression springs or disc springs according to actual requirements on site, disc springs are preferably selected, and the rigidity and the load characteristic curve of the combined springs are changed through different combination modes (folding or involution) and quantity matching of the disc springs, so that actual working condition requirements on site are met.

The sliding friction parts involved in the invention are all made of bronze materials with sufficient rigidity, strength, wear resistance and antifriction property and are coated with extreme pressure lithium-based lubricating ester, so that the friction resistance is reduced, the friction power loss of the system is reduced, and the operation flexibility is improved. Considering the practical working conditions of high temperature, low speed and intermittent transmission on site and the good machining process performance of materials, the tin phosphor bronze ZCuSn10P1 and the tin bronze CuPb5Sn5Zn5 with good antifriction performance are preferably selected, and the material has the remarkable characteristics of low hardness, high plasticity, small elastic modulus, good running-in performance, compliance and embedding performance, and high compressive and impact load fatigue strength. If limited by market supply and cost, the material ZCuAl10Fe3 with higher mechanical strength and wear resistance can be used instead. The bearing spiral components related in the invention are preferably made of alloy steel 20Cr with good comprehensive mechanical property, and if the comprehensive cost is considered, the bearing spiral components can be replaced by high-quality carbon structural steel 45 through modulation treatment.

In addition, this tipper adopts the overhead modularization design thinking, unify the mounting platform, all mechanisms are all concentrated the symmetrical arrangement on base 15, the overall layout is succinct compact, be convenient for on-the-spot installation and maintenance, complete equipment installation elevation all lies in above the roll table working face, can use the driving to wholly hoist this equipment on the roll table apron, and adopt on-the-spot welding or bolted connection's mode to make base 15 and roll table apron walk the platform and firmly link, on-the-spot moment of tumbling and the impact load that receives all transmit the roll table basis through roll table apron and roll table, need not do the concrete foundation in addition for this billet tipper alone, have the quick, the convenient, low cost's of dismouting showing characteristics.

From the above description, it can be seen that the above-described embodiments of the present invention achieve the following technical effects: the swinging lifting type spring damping gravity billet tilter is mainly formed by combining six parts, namely a swinging power mechanism 1, a lifting power mechanism 2, a sliding spiral cam adjusting mechanism 3, a variable four-bar linkage swinging mechanism 4, an adjustable tensioning chain wheel lifting mechanism 5 and a gravity type spring tilting mechanism 6.

The turnover machine adopts a plane low-pair multi-rod mechanism formed by hinging and combining a revolute pair and a sliding pair, has the characteristics of compact structural layout, large radial contact area, low bearing pressure and wear resistance, and can accurately turn and regulate the postures of hot-rolled/cold-rolled steel billets of different specifications. The invention adopts a unique design scheme in the sliding spiral cam adjusting mechanism 3, the variable four-bar linkage swinging mechanism 4 and the gravity type spring tipping mechanism 6 to accurately regulate and control the local motion track and stress distribution of each component in the tipper, finally influences the track parameter of the downstream executing mechanism and meets the actual requirement of the site working condition parameter. The turnover machine has the advantages that the design of the multiple auxiliary adjusting mechanisms is adopted, the phase adjusting freedom of each component is more during the actual operation, the flexibility and the track variability of the motion of each component are extremely strong, the turnover machine can adapt to various different working condition occasions, and the modular design of unit combination is adopted, so that various subsystems such as the variable four-bar linkage swing mechanism 4, the swing frame adjusting mechanism, the swing rod rocker arm pull rod mechanism, the material supporting arm mechanism and the like can be combined for motion and can be disassembled to be used as relatively independent subsystems to be applied to other mechanical design related fields, different design requirements are met, and the turnover machine has good interchange universality.

Meanwhile, the swing lifting type spring damping gravity billet tilter can overturn the high-temperature billet discharged from a heating furnace of a section/bar hot rolling production line by 90 degrees before rolling, change the sequence of the meshing surfaces of the billet in conjugate pass rolling between two rollers, improve the control precision of the imported billet of a rolling mill, meet the process requirement of on-site rolling deformation, clear away the overheated iron oxide on the surface of the billet, improve the surface appearance quality of the rolled material, improve the on-site production rhythm, reduce the rolling current and reduce the process faults. The tilter has the remarkable characteristics of simple structure, low cost, reliable work, rapid response and strong adaptability, and is a novel steel billet tilter which has wide application, high automation degree, convenient installation and strong universality.

In addition, the tilter has the obvious characteristics of multiple degrees of freedom, small volume, light weight, compact structural layout, convenient disassembly and maintenance and high automatic adjustment precision, is particularly suitable for the process optimization adjustment of the bite surface of the rolling mill in the most upstream rolling procedure after hot-rolled section steel and plate/wire hot billets are discharged from the furnace and the improvement of the appearance surface quality of finished products, reduces the process fault of a roughing mill and improves the on-site rolling rhythm.

The above is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made to the present invention by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (10)

1. A swing lifting type spring damping gravity billet tilter is characterized by comprising a swing power mechanism, a lifting power mechanism, a sliding spiral cam adjusting mechanism, a variable four-connecting-rod swing mechanism, an adjustable tensioning chain wheel lifting mechanism and a gravity type spring tilting mechanism;

the sliding spiral cam adjusting mechanism is connected with the variable four-bar linkage swinging mechanism and is used for adjusting the abscissa and/or the ordinate of a swinging rod seat in the variable four-bar linkage swinging mechanism so as to linearly adjust the swinging angle of an upright post in the variable four-bar linkage swinging mechanism;

the swing power mechanism is connected with the variable four-connecting-rod swing mechanism and used for providing power for the variable four-connecting-rod swing mechanism;

the lifting power mechanism is respectively connected with the variable four-connecting-rod swinging mechanism and the adjustable tensioning chain wheel lifting mechanism and is used for providing power for the adjustable tensioning chain wheel lifting mechanism;

the adjustable tension sprocket lifting mechanism is arranged on the stand column and is connected with the gravity type spring tipping mechanism, and the adjustable tension sprocket lifting mechanism is used for changing the direction of power output by the lifting power mechanism so as to drive the gravity type spring tipping mechanism to do reciprocating linear motion up and down;

the steel billet is placed at the tail end of the gravity type spring tipping mechanism, and the gravity type spring tipping mechanism reciprocates linearly up and down or swings left and right to enable the steel billet to reach a tipping angle of critical balance, so that the steel billet is turned over.

2. The swing lift spring damped gravity billet tipper of claim 1, wherein said sliding screw cam adjustment mechanism comprises a sliding screw mechanism, a cam-type sliding cam mechanism, and a ram frame;

the sliding screw mechanism comprises a first speed reducing motor, a transverse adjusting nut and a transverse adjusting screw rod, wherein the output end of the first speed reducing motor is fixedly connected with one end of the transverse adjusting screw rod, and the transverse adjusting nut is in threaded connection with the transverse adjusting screw rod;

the wedge type sliding cam mechanism comprises a swing frame, a longitudinal adjusting nut, a longitudinal adjusting screw rod, a diagonal slideway and an ejector rod;

the bottom of the swing frame is hinged with the upper plane of the transverse adjusting nut, the longitudinal adjusting screw rod is rotatably arranged on the inner side of the swing frame, the longitudinal adjusting nut is in threaded connection with the longitudinal adjusting screw rod, the bottom of the longitudinal adjusting screw rod is hinged with the upper plane of the transverse adjusting nut, one end of the oblique slideway is hinged with the longitudinal adjusting nut, and the other end of the oblique slideway is hinged with the upper plane of the transverse adjusting nut;

one end of the ejector rod is hinged to the inclined slide way, the other end of the ejector rod is fixedly connected with the bottom of the swing rod seat, a sleeve is arranged at the top of the ejector rod frame, the bottom of the ejector rod frame is fixedly arranged, and the ejector rod is arranged in the sleeve.

3. The swing lift spring damped gravity billet tipper of claim 2, wherein said sliding helical cam adjustment mechanism further comprises an L-shaped slide and a locking bolt;

the bottom of the L-shaped slideway is fixedly arranged, and the bottom of the ejector rod frame is in sliding connection with the top of the L-shaped slideway;

the locking bolt is arranged between the bottom of the ejector rod frame and the top of the L slide way, and the locking bolt is used for fixedly connecting the bottom of the ejector rod frame with the top of the L slide way.

4. The swing elevating spring damped gravity billet tipper of claim 1, wherein said variable four-bar linkage swing mechanism further comprises a linkage, a swing link, a base, a swing link upper slide, a swing link lower slide and an elevating arm;

one end of the upright post is hinged with the base, and one end of the swing rod is hinged with one end of the swing rod seat;

one end of the lifting arm is in adjustable sliding connection with one side of the upright post, and the other end of the lifting arm is hinged with one end of the connecting rod;

one end of the upper sliding seat of the swing rod is in adjustable sliding connection with one side of the swing rod, and the other end of the upper sliding seat of the swing rod is hinged with the other end of the connecting rod;

one end of the swing rod lower sliding seat is connected with the other side of the swing rod in an adjustable sliding mode, the other end of the swing rod lower sliding seat is hinged to the output end of the swing power mechanism, the tail end of the swing power mechanism is hinged to the base, and the tail end of the lifting power mechanism is hinged to the connecting rod.

5. The swing elevating spring damping gravity billet tipper of claim 4, wherein said linkage comprises a linkage sleeve, two linkage beams, a set bolt, a support, an adjustment rod and a fixing nut;

the connecting rod sleeves are of hollow box-shaped structures, and the other ends of the two connecting rod beams are symmetrically inserted from the two ends of the connecting rod sleeves;

two sides of the connecting rod sleeve are respectively provided with two groups of threaded holes in a mirror symmetry manner, and the fastening bolt is screwed into the threaded holes and is in contact with the connecting rod beam so as to fixedly connect the connecting rod beam with the connecting rod sleeve;

the other end of the lifting arm is hinged with one end of one connecting rod beam, and the other end of the upper sliding seat of the swing rod is hinged with one end of the other connecting rod beam;

the support is fixedly arranged on the connecting rod beam, the fixing nut is fixedly arranged on the connecting rod sleeve, one end of the adjusting rod is rotatably matched with the support, the other end of the adjusting rod is matched with the fixing nut, and the tail end of the lifting power mechanism is hinged with the connecting rod sleeve;

the variable four-bar linkage swing mechanism also comprises two sets of swing rod rocker arm pull rod mechanisms, and each set of swing rod rocker arm pull rod mechanism comprises a rocker arm pull rod, two rocker arm earrings and a rocker arm;

one end of the rocker arm is hinged with the swing rod, the other end of the rocker arm is hinged with one end of one rocker arm ear ring, one end of the other rocker arm ear ring in one set of rocker arm pull rod mechanism is hinged with the upper swing rod sliding seat, and one end of the other rocker arm ear ring in the other set of rocker arm pull rod mechanism is hinged with the lower swing rod sliding seat;

the rocker arm pull rod is of a double-spiral structure rotating synchronously, and the two ends of the rocker arm pull rod are respectively matched with the other ends of the rocker arm earrings by adopting fine external threads in positive and negative rotation directions.

6. The swing elevating spring damped gravity billet tipper of claim 4, wherein said variable four-bar linkage swing mechanism further comprises a lifting arm drum, a fixed pulley, a lifting arm drum support, a fixed pulley support, a second gear motor and a wire rope;

the fixed pulley is fixedly arranged at the top of one side of the upright post through the fixed pulley support, the lifting arm winding drum is fixedly arranged at the bottom of one side of the upright post through the lifting arm winding drum support, the output end of the second speed reducing motor is fixedly connected with the lifting arm winding drum, and the lifting arm is slidably connected with one side of the upright post;

one end of the steel wire rope is fixedly connected with the lifting arm, and the other end of the steel wire rope bypasses the fixed pulley and is fixedly connected with the lifting arm winding drum.

7. The pendulum lifting spring damped gravity billet tipper of claim 1, wherein the adjustable tension sprocket lift mechanism comprises a tension sprocket assembly, a bush roller chain and a lift car;

the tensioning chain wheel assembly comprises a chain wheel, a chain wheel shaft and a tensioning plate;

the chain wheel is rotatably arranged at one end of the tension plate through the chain wheel shaft, and the other end of the tension plate is fixedly arranged at the top end of the upright post;

the lifting trolley comprises a trolley wheel shaft, a trolley pressing plate, a lifting plate and two telescopic beams;

the telescopic beam is a long strip-shaped plate-shaped member, a groove slideway is arranged in the middle of the telescopic beam in the height direction, the groove slideway extends from the rear end face of the telescopic beam to the front end face of the telescopic beam, the length direction of the groove slideway is consistent with the length direction of the telescopic beam, the lifting plate is fixedly arranged on the upper surfaces of the two telescopic beams, two ends of the trolley pressing plate are fixedly arranged on the rear end faces of the two telescopic beams, and the gravity type spring tipping mechanism is fixedly arranged on the front end face of the telescopic beam;

the trolley wheel shaft is arranged in the groove slideway in a sliding manner, two opposite inner side walls of the upright post are provided with guide slideways, and two ends of the trolley wheel shaft are respectively connected with the guide slideways in a sliding manner;

one end of the sleeve roller chain is fixedly connected with the output end of the lifting power mechanism, and the other end of the sleeve roller chain bypasses the chain wheel to be fixedly connected with the lifting plate.

8. The swing elevating spring damped gravity billet tipper of claim 7, wherein said lift carriage further comprises an adjustment bar and a second deep groove ball bearing;

a step blind hole is formed in the geometric symmetry center line of the trolley wheel shaft, the second deep groove ball bearing is arranged in the step blind hole, and a fine-tooth nut is arranged in the middle of the trolley pressing plate and is in threaded fit with the adjusting rod;

one end of the adjusting rod penetrates through the trolley pressing plate to be matched with the second deep groove ball bearing.

9. The swing lift spring damped gravity billet tipper of claim 7, wherein said gravity spring tipper mechanism comprises a cross beam, two sets of load bearing rod assemblies, two sets of load bearing arms, and two sets of rotary spring dampers;

the two groups of bearing rod assemblies are fixedly arranged at two ends of the cross beam, the cross beam is fixedly arranged on the front end face of the telescopic beam, and the two groups of bearing rod assemblies are arranged in a mirror symmetry mode about the geometric symmetry center line of the lifting trolley;

the material supporting arm comprises a transverse part, a vertical part and a movable lug plate, the lower end of the vertical part is fixedly connected with the transverse part and divides the transverse part into a material supporting arm front section and a material supporting arm tail section, the length of the material supporting arm front section is greater than that of the material supporting arm tail section, the movable lug plate is arranged on the material supporting arm front section, and one end of the bearing rod component is hinged with the upper end of the vertical part;

the two groups of rotary spring damping bodies are respectively hinged on the outer side surfaces of the tails of the two groups of material supporting arms which are arranged in a mirror symmetry manner;

the rotary spring damping body comprises a guide rod, a damping spring, a spring seat and a lifting nut;

the lifting nut with bearing bar subassembly screw-thread fit, the side of lifting nut is provided with articulated gudgeon, articulated gudgeon with the through-hole of spring holder side is articulated, damping spring axial suit is in on the guide bar, damping spring's one end is fixed, damping spring's the other end moves about, the top of guide bar slides and sets up in the oblong hole on spring holder upper portion, the bottom of guide bar with the lateral surface of holding in the palm material arm afterbody is articulated.

10. The pendulum lifting spring-damped gravity billet tipper of claim 9, wherein the rotary spring-damped body further comprises a base nut;

the guide rod is a screw shaft with a through-long full-thread structure, and the base nut is in threaded fit with the lower part of the guide rod;

the top of the damping spring is in pressing contact with the upper plane of the spring seat, and the bottom of the damping spring is fixedly mounted on the base nut.

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