CN115780521A - Hydraulic control system and control method for core rod support frame adjusting device - Google Patents
Hydraulic control system and control method for core rod support frame adjusting device Download PDFInfo
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- CN115780521A CN115780521A CN202211506370.3A CN202211506370A CN115780521A CN 115780521 A CN115780521 A CN 115780521A CN 202211506370 A CN202211506370 A CN 202211506370A CN 115780521 A CN115780521 A CN 115780521A
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Abstract
The invention discloses a hydraulic control system and a control method for a core rod support frame adjusting device, wherein the system comprises: the hydraulic control system comprises a pressure reducing valve, a first hydraulic control one-way valve, a second hydraulic control one-way valve, a third hydraulic control one-way valve, a two-position four-way electromagnetic reversing valve, a three-position four-way high-frequency response proportional reversing valve, an adjusting hydraulic cylinder and an opening hydraulic cylinder. In the invention, the rodless cavity of the adjusting hydraulic cylinder is filled with hydraulic oil, so that when the hydraulic cylinder is opened to act on the piston rod of the adjusting hydraulic cylinder, the hydraulic oil in the rodless cavity can be used as a hydraulic spring to absorb impact and can buffer transient acting force generated when the mandrel carrier roller is opened and closed.
Description
Technical Field
The invention relates to the technical field of steel rolling control, in particular to a hydraulic control system and a hydraulic control method for a core rod support frame adjusting device.
Background
Rolling machinery, especially a continuous rolling mill in hot rolling seamless steel pipe production equipment, is the most widely used longitudinal rolling forming equipment today. In the process of rolling steel pipes, a roller and a mandrel on a continuous pipe mill can form a fixed pass, and the roller can transmit huge rolling force to the mandrel through a rolled piece, so that the stability of the mandrel in the process of rolling the steel pipes directly influences the wall thickness precision of finished pipes, namely the stability of the mandrel has important influence on the quality of the finished pipes and the productivity of the whole unit. In actual production, different steel pipes need to be configured with different mandrels, and after the mandrels of different specifications are replaced according to the requirements of a steel pipe rolling process, the positions of mandrel supports must be correspondingly adjusted so that the mandrels are in correct positions. At present, the position of a mandrel support is mainly adjusted through a mandrel support adjusting device, so that the stability of a mandrel in the rolling process is ensured.
In the prior art, the mandrel support frame adjusting device comprises a lifting motor and a worm gear lead screw lifter, wherein a base of the worm gear lead screw lifter is fixed on a rolling mill frame, and the lifting motor can drive a lead screw of the worm gear lead screw lifter to move. After the position of the mandrel support frame is adjusted, the mandrel support frame, an opening hydraulic cylinder and a closing hydraulic cylinder which can drive the mandrel support frame to move and a mandrel carrier roller are matched to complete the rolling process of the steel pipe, wherein the opening hydraulic cylinder can drive the mandrel carrier roller to open, and the closing hydraulic cylinder can drive the mandrel carrier roller to close. In the rolling process, the opening hydraulic cylinder and the closing hydraulic cylinder can indirectly adjust the opening and closing state of the mandrel carrier roller by controlling the swing of the swing arm. The moving stroke of a piston rod of the opening hydraulic cylinder is limited by a screw rod of a worm gear screw rod lifter, so that the size of the opening of the mandrel support frame is finally controlled.
However, in the rolling process, due to the high rolling speed, before the hollow billet reaches the position of the mandrel carrier roller, the mandrel carrier roller must be opened quickly to prevent the hollow billet from colliding with the mandrel carrier roller, and further steel piling and other accidents occur. For this reason, the opening hydraulic cylinder and the closing hydraulic cylinder need to have sufficiently fast opening and closing speeds. In the actual rolling process, the transient acting force generated when the mandrel carrier roller is opened and closed directly acts on the base of the worm gear-screw rod lifter by opening the piston rod of the hydraulic cylinder, so that the base of the worm gear-screw rod lifter can be fatigue-broken and cannot continuously work in long-term operation, and the continuous production of the continuous tube rolling mill can be greatly influenced. Meanwhile, a screw rod structure of the worm gear and screw rod lifter has an adjusting gap, and the worm gear and screw rod lifter is easy to have position adjusting errors, so that the front end of a piston rod of the hydraulic cylinder is opened to be positioned and a deviation can occur. For example, when the extending position of a piston rod of an opening hydraulic cylinder is too small, a mandrel carrier roller is easy to gouge the surface of a mandrel when being closed, and the mandrel is damaged; when the extending position of a piston rod of the opening hydraulic cylinder is too large, the clearance between a mandrel carrier roller and a mandrel is large when the mandrel carrier roller is closed, so that the stability of the mandrel in the rolling process cannot be effectively ensured, the wall thickness precision of an outlet steel pipe of a continuous rolling mill is directly influenced, and further the quality of a finished pipe is influenced.
Disclosure of Invention
In order to solve some or all technical problems in the prior art, the invention provides a hydraulic control system and a control method for a mandrel support adjusting device.
The technical scheme of the invention is as follows:
according to a first aspect of the present invention there is provided a hydraulic control system for a mandrel support adjustment apparatus, the system comprising: a pressure reducing valve, a first hydraulic control one-way valve, a second hydraulic control one-way valve, a third hydraulic control one-way valve, a two-position four-way electromagnetic directional valve, a three-position four-way high-frequency response proportional directional valve, an adjusting hydraulic cylinder and an opening hydraulic cylinder, wherein,
an oil inlet of the pressure reducing valve is connected to a hydraulic oil inlet, an oil outlet of the pressure reducing valve is connected to a port P of the two-position four-way electromagnetic directional valve, and an oil outlet of the pressure reducing valve is also connected to an oil outlet of the first hydraulic control one-way valve;
an A port of the two-position four-way electromagnetic reversing valve is connected to a closed end, a B port of the two-position four-way electromagnetic reversing valve is connected to a control port of the first hydraulic control one-way valve, a control port of the second hydraulic control one-way valve and a control port of the third hydraulic control one-way valve, a T port of the two-position four-way electromagnetic reversing valve is connected to an oil return pipeline, when an electromagnet Y1 of the two-position four-way electromagnetic reversing valve is electrified, the A port is communicated with the T port, and the B port is communicated with the P port;
a port P of the three-position four-way high-frequency-response proportional reversing valve is connected to an oil inlet of the first hydraulic control one-way valve, a port A of the three-position four-way high-frequency-response proportional reversing valve is connected to an oil inlet of the second hydraulic control one-way valve, a port B of the three-position four-way high-frequency-response proportional reversing valve is connected to an oil inlet of the third hydraulic control one-way valve, a port T of the three-position four-way high-frequency-response proportional reversing valve is connected to an oil return pipeline, when the three-position four-way high-frequency-response proportional reversing valve is in a middle position, the port T, the port A and the port B are communicated, and the port P is not communicated with the ports;
the adjusting hydraulic cylinder comprises a rod cavity and a rodless cavity, a piston rod of the adjusting hydraulic cylinder is inserted into the rod cavity, the piston rod of the adjusting hydraulic cylinder can abut against a piston rod of the opening hydraulic cylinder, an oil outlet of the second hydraulic control one-way valve is connected to the rod cavity of the adjusting hydraulic cylinder, and an oil outlet of the third hydraulic control one-way valve is connected to the rodless cavity of the adjusting hydraulic cylinder;
the opening hydraulic cylinder is configured to be fixedly arranged on a rolling mill stand, one end of a piston rod of the opening hydraulic cylinder can abut against a right bearing moving column on the rolling mill stand, and the other end of the piston rod of the opening hydraulic cylinder can abut against the end of the piston rod of the adjusting hydraulic cylinder.
Optionally, the system further comprises: a displacement sensor and a controller, wherein the controller is connected with the displacement sensor,
the displacement sensor is arranged on the adjusting hydraulic cylinder and configured to sense the position of a piston rod of the adjusting hydraulic cylinder, the displacement sensor, the three-position four-way high-frequency-response proportional reversing valve and the two-position four-way electromagnetic reversing valve are electrically connected with the controller, and the controller is configured to adjust the three-position four-way high-frequency-response proportional reversing valve according to the position of the piston rod sensed by the displacement sensor.
Optionally, when the three-position four-way high-frequency response proportional reversing valve is in the left position, the port A is communicated with the port T, and the port B is communicated with the port P; when the three-position four-way high-frequency response proportional reversing valve is in the right position, the port A is communicated with the port P, and the port B is communicated with the port T.
Optionally, the controller is a PLC control device.
Optionally, the system further comprises: a pilot-operated type priority unloading valve and a plug-in type one-way valve are inserted,
the P port of the inserted pilot type priority unloading valve is connected with a rodless cavity of the adjusting hydraulic cylinder, the X port of the inserted pilot type priority unloading valve is connected with a rod cavity of the adjusting hydraulic cylinder, and the T port and the Y port of the inserted pilot type priority unloading valve are both connected to an oil return pipeline; an oil inlet of the cartridge check valve is connected to an oil return pipeline, and an oil outlet of the cartridge check valve is connected to a rod cavity of the adjusting hydraulic cylinder.
Optionally, the system further comprises: the hydraulic oil return device comprises a pipe type one-way valve, wherein the pipe type one-way valve is connected to an oil return pipeline in series, and an oil outlet of the pipe type one-way valve is connected to a hydraulic oil outlet.
According to a second aspect of the present invention, there is also provided a control method for controlling a mandrel holder adjusting device hydraulic control system according to the first aspect of the present invention, the control method comprising:
moving a piston rod of the adjusting hydraulic cylinder to a required position according to the requirements of the rolling process;
electrifying an electromagnet Y1 of the two-position four-way electromagnetic directional valve to enable hydraulic oil to enter a control port of the first hydraulic control one-way valve, a control port of the second hydraulic control one-way valve and a control port of the third hydraulic control one-way valve;
and electrifying the electromagnet Y2 of the three-position four-way high-frequency-response proportional reversing valve, so that the hydraulic oil enters a rod cavity and a rodless cavity of the adjusting hydraulic cylinder through the pressure reducing valve and the three-position four-way high-frequency-response proportional reversing valve.
The technical scheme of the invention has the following main advantages:
in the hydraulic control system of the mandrel support frame adjusting device, the rodless cavity of the adjusting hydraulic cylinder is filled with hydraulic oil, so that when the opening hydraulic cylinder acts on the piston rod of the adjusting hydraulic cylinder, the hydraulic oil in the rodless cavity can be used as a hydraulic spring to absorb impact, and the transient acting force generated when the mandrel carrier roller is opened and closed can be buffered.
Drawings
The accompanying drawings, which are included to provide a further understanding of embodiments of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 is a schematic diagram of an installation configuration of a hydraulic control system of a mandrel support adjustment apparatus in a continuous tube mill according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of the hydraulic control system of the mandrel holder adjustment apparatus according to one embodiment of the present invention.
Description of reference numerals:
11: pressure reducing valve 21: first pilot-operated check valve 22: second hydraulic control one-way valve
23: third pilot operated check valve 13: two-position four-way electromagnetic reversing valve
14: the three-position four-way high-frequency response proportional reversing valve 15: plug-in mounting type one-way valve
16: a pilot type priority unloading valve 17 is inserted: adjusting hydraulic cylinder
18: opening the hydraulic cylinder 19: the displacement sensor 30: controller
31: tube check valve 32: oil circuit block 200: rolling mill housing
210: the mandrel support frame 220: core rod carrier roller 230: core rod
240: closing the hydraulic cylinder 251: right bearing post 252: left bearing column
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the technical solutions of the present invention will be clearly and completely described below with reference to the specific embodiments of the present invention and the accompanying drawings. It is to be understood that the described embodiments are merely a few embodiments of the invention, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments of the present invention without making any creative effort, shall fall within the protection scope of the present invention.
The technical scheme provided by the embodiment of the invention is described in detail below with reference to the accompanying drawings.
In an embodiment of the invention, a hydraulic control system of a mandrel support adjusting device is provided, which is used for being arranged on a tandem rolling mill, can replace the existing worm gear screw rod lifter, can accurately control and adjust the stroke of a hydraulic cylinder, and can buffer the transient acting force generated when a mandrel carrier roller is opened and closed in the actual rolling process, thereby prolonging the service life of the whole device and ensuring the rolling quality. The hydraulic control system of the mandrel holder adjusting device in the present embodiment will be further described below with reference to fig. 1 and 2.
Specifically, as shown in fig. 1 and 2, the hydraulic control system of the mandrel support adjusting device according to the present embodiment includes: the hydraulic control system comprises a pressure reducing valve 11, a first hydraulic control one-way valve 21, a second hydraulic control one-way valve 22, a third hydraulic control one-way valve 23, a two-position four-way electromagnetic reversing valve 13, a three-position four-way high-frequency-response proportional reversing valve 14, an adjusting hydraulic cylinder 17 and an opening hydraulic cylinder 18.
An oil inlet of the pressure reducing valve 11 is connected to a hydraulic oil inlet, an oil outlet of the pressure reducing valve 11 is connected to a port P of the two-position four-way electromagnetic directional valve 13, and an oil outlet of the pressure reducing valve 11 is further connected to an oil outlet of the first hydraulic control one-way valve 21.
It can be understood that the pressure reducing valve 11 is arranged on the oil inlet pipeline, the hydraulic oil enters the pressure reducing valve 11 from the hydraulic oil inlet through the pipeline to realize pressure reduction, and then the hydraulic oil passing through the pressure reducing valve 11 is divided into two paths, wherein one path flows to the port P of the two-position four-way electromagnetic directional valve 13, and the other path flows to the oil outlet of the first hydraulic control one-way valve 21.
The A port of the two-position four-way electromagnetic directional valve 13 is connected to the closed end, the B port of the two-position four-way electromagnetic directional valve 13 is connected to the control port of the first hydraulic control one-way valve 21, the control port of the second hydraulic control one-way valve 22 and the control port of the third hydraulic control one-way valve 23, the T port of the two-position four-way electromagnetic directional valve 13 is connected to the oil return pipeline, in addition, when the electromagnet Y1 of the two-position four-way electromagnetic directional valve 13 is electrified, the A port is communicated with the T port, and the B port is communicated with the P port.
It can be understood that the two-position four-way electromagnetic directional valve 13 has four ports A, B, P, T, where the port a is connected to the closed end, the port B is connected to the control port of the first pilot-operated check valve 21, the control port of the second pilot-operated check valve 22 and the control port of the third pilot-operated check valve 23, and the port T is connected to the oil return line.
And the electromagnet Y1 can control the position of the valve core of the two-position four-way electromagnetic directional valve 13 through power on or power off. In this embodiment, when the electromagnet Y1 is energized, the port a communicates with the port T, the port B communicates with the port P, and when the electromagnet Y1 is de-energized, the port a communicates with the port P, and the port B communicates with the port T.
The port P of the three-position four-way high-frequency-response proportional reversing valve 14 is connected to an oil inlet of a first hydraulic control one-way valve 21, the port A of the three-position four-way high-frequency-response proportional reversing valve 14 is connected to an oil inlet of a second hydraulic control one-way valve 22, the port B of the three-position four-way high-frequency-response proportional reversing valve 14 is connected to an oil inlet of a third hydraulic control one-way valve 23, the port T of the three-position four-way high-frequency-response proportional reversing valve 14 is connected to an oil return pipeline, when the three-position four-way high-frequency-response proportional reversing valve 14 is located in the middle position, the port T, the port A and the port B are communicated, and the port P is not communicated with the three ports.
It can be understood that the three-position four-way high-frequency-response proportional reversing valve 14 also has A, B, P, T four ports, where the port P is connected to the oil inlet of the first pilot-controlled check valve 21, the port a is connected to the oil inlet of the second pilot-controlled check valve 22, the port B is connected to the oil inlet of the third pilot-controlled check valve 23, and the port T is connected to the oil return line.
When the three-position four-way high-frequency-response proportional reversing valve 14 is located at the middle position, the port T, the port A and the port B are communicated, and the port P and the three ports are not communicated. In the present embodiment, the solenoid Y2 can control the position of the spool of the three-position, four-way, high-frequency-response proportional directional valve 14 by receiving an electric signal.
The adjusting hydraulic cylinder 17 comprises a rod cavity and a rodless cavity, a piston rod of the adjusting hydraulic cylinder 17 is inserted into the rod cavity, the piston rod of the adjusting hydraulic cylinder 17 can extend out of the rod cavity and abut against the piston rod of the opening hydraulic cylinder 18, an oil outlet of the second hydraulic control one-way valve 22 is connected to the rod cavity of the adjusting hydraulic cylinder 17, and an oil outlet of the third hydraulic control one-way valve 23 is connected to the rodless cavity of the adjusting hydraulic cylinder 17.
It will be appreciated that the cylinder of the adjusting cylinder 17 may be divided into two chambers based on the movement of the piston rod of the adjusting cylinder 17, wherein the chamber containing the piston rod is a rod chamber and the other is a rodless chamber. The rod chamber is connected to the oil outlet of the second pilot check valve 22 through a pipe, which is capable of receiving hydraulic oil from the second pilot check valve 22, and the rod-less chamber is connected to the oil outlet of the third pilot check valve 23 through a pipe, which is capable of receiving hydraulic oil from the third pilot check valve 23.
Furthermore, the piston rod of the adjusting cylinder 17 can abut against the piston rod of the opening cylinder 18 so as to position the piston rod of the opening cylinder 18.
The opening cylinder 18 is disposed to be fixed to the mill stand 200, and one end of a piston rod of the opening cylinder 18 can abut against the right bearing post 251 on the mill stand 200, and the other end can abut against an end of a piston rod of the adjusting cylinder 17.
It will be understood that the cylinder barrel of the opening cylinder 18 can be fixed on the rolling stand 200, the piston rod of the opening cylinder 18 can be driven and abutted to the right-hand bearing post 251 on the rolling stand 200, and, when it is retracted, can abut the end of the piston rod of the adjusting cylinder 17.
In the present embodiment, the piston rod that opens the hydraulic cylinder 18 can be controlled by an external separate hydraulic control valve.
As shown in fig. 1, before the rolling process is started, the piston rod of the adjusting hydraulic cylinder 17 is adjusted to a desired position according to the mandrel diameter determined by the tandem rolling process. Then the electromagnet Y1 is energized, at this time, the first pilot-operated check valve 21, the second pilot-operated check valve 22 and the third pilot-operated check valve 23 are opened simultaneously, an electric signal is input to the electromagnet Y2, and hydraulic oil enters the rod cavity and the rodless cavity of the adjusting hydraulic cylinder 17 through the pressure reducing valve 11, the first pilot-operated check valve 21, the three-position four-way high-frequency-response proportional reversing valve 14, the second pilot-operated check valve 22 and the third pilot-operated check valve 23, respectively.
In the process, the pressure reducing valve 11 can not only ensure the pressure stability of the hydraulic oil entering the three-position four-way high-frequency-response proportional reversing valve 14, improve the positioning precision of the adjusting hydraulic cylinder 17, but also effectively reduce the adjusting force of the adjusting hydraulic cylinder 17 and prevent the fixing device of the adjusting hydraulic cylinder 17 from being damaged due to overlarge adjusting force.
In the present embodiment, in order to ensure that the hydraulic oil can be reliably cut off and to avoid the positional deviation of the cylinder caused by the hydraulic oil entering the high-frequency proportional valve, the first pilot-operated check valve 21 is intentionally installed in the reverse direction. Therefore, only when the electromagnet Y1 of the two-position four-way electromagnetic directional valve 13 is electrified, the hydraulic oil enters the control ports of the first hydraulic control one-way valve 21, the second hydraulic control one-way valve 22 and the third hydraulic control one-way valve 23, and at this time, the first hydraulic control one-way valve 21, the second hydraulic control one-way valve 22 and the third hydraulic control one-way valve 23 are opened at the same time.
Preferably, the main valve spool of the three-position four-way high-frequency-response proportional reversing valve 14 is provided with position feedback, and the adjusting hydraulic cylinder 17 can be adjusted in place quickly and in real time.
In an alternative embodiment, the proportional electromagnet of the three-position four-way high-frequency-response proportional reversing valve 14 can drive the main valve spool to act after being electrified, and the main valve spool is provided with a position sensor. Through the position sensor, the continuous controllable internal feedback can be realized by the opening direction and the opening amount of the valve core of the main valve moving in the valve body, and the flow of hydraulic oil entering the adjusting hydraulic cylinder 17 can be adjusted by accurately controlling the follow-up variable displacement of the valve core of the main valve.
During the actual rolling, as shown in fig. 1, the piston rod of the opening hydraulic cylinder 18 is driven to move toward the right bearing column 251 and push the right bearing column 251 to move leftward, and at the same time, the piston rod of the closing hydraulic cylinder 240 located on the left side is retracted, so that the three mandrel idlers 220 are opened, thereby allowing the mandrel 230 to penetrate between the three mandrel idlers 220 along the tandem mill center line.
After the mandrel 230 reaches a predetermined position, the piston rod of the closing hydraulic cylinder 240 located on the left side rapidly extends and pushes the left bearing post 252 to move rightward, while the piston rod of the opening hydraulic cylinder 18 retracts until the rear end of the piston rod of the opening hydraulic cylinder 18 abuts on the end of the piston rod of the adjusting hydraulic cylinder 17. The three mandrel idlers 220 hold the mandrel 230 tightly, and when the piston rod of the adjusting hydraulic cylinder 17 is impacted by the piston rod of the opening hydraulic cylinder 18, the rodless cavity of the adjusting hydraulic cylinder 17 is filled with hydraulic oil, and the hydraulic oil can be used as a hydraulic spring to absorb the impact. Therefore, the transient acting force generated when the core rod carrier roller 220 is opened and closed is buffered, and the service life of the whole device is prolonged.
Further, in order to effectively control the position of the piston rod of the adjusting hydraulic cylinder 17, as shown in fig. 2, the hydraulic control system of the mandrel support adjusting device further includes: a displacement sensor 19 and a controller 30.
Specifically, the displacement sensor 19 is disposed on the adjusting hydraulic cylinder 17, the displacement sensor 19 is configured to sense a position of a piston rod of the adjusting hydraulic cylinder 17, the displacement sensor 19, the three-position four-way high frequency response proportional directional valve 14, and the two-position four-way electromagnetic directional valve 13 are all electrically connected to the controller 30, and the controller 30 is configured to adjust the three-position four-way high frequency response proportional directional valve 14 according to the position of the piston rod sensed by the displacement sensor 19.
In practical application, when the displacement sensor 19 detects that the position change of the piston rod of the adjusting hydraulic cylinder 17 exceeds a set range value, a corresponding adjusting position signal is transmitted to the controller 30, the controller 30 controls the electromagnet Y1 of the two-position four-way electromagnetic directional valve 13 to be electrified, the first hydraulic control one-way valve 21, the second hydraulic control one-way valve 22 and the third hydraulic control one-way valve 23 are opened simultaneously, and meanwhile, the controller 30 inputs an adjusting signal to the electromagnet Y2 of the three-position four-way high-frequency-response proportional directional valve 14 to change the position of the valve core of the three-position four-way high-frequency-response proportional directional valve 14, so that hydraulic oil is quickly compensated to a set value for a rod cavity and a rodless cavity, the piston rod of the adjusting hydraulic cylinder 17 reaches a required position, and the adjusting position of the core rod carrier roller is guaranteed to be accurate and controllable.
It can be understood that before rolling begins, the closing hydraulic cylinder 240 will push the left bearing column 252 to move right, the mandrel carrier roller 220 holds the mandrel tightly, the right bearing column 251 is simultaneously pushed to abut against the left end of the piston rod of the opening hydraulic cylinder 18, and the right end of the piston rod of the opening hydraulic cylinder 18 will abut against the piston rod of the adjusting hydraulic cylinder 17.
In the rolling process, before the hollow billet reaches the position of the mandrel carrier roller 220, the mandrel carrier roller 220 must be opened rapidly, the left end of the piston rod of the opening hydraulic cylinder 18 pushes the right bearing column 251 to move left, the right end of the piston rod of the opening hydraulic cylinder 18 is separated from the piston rod of the adjusting hydraulic cylinder 17, the three mandrel carrier rollers 220 are opened, and simultaneously the piston rod of the closing hydraulic cylinder 240 contracts and retracts.
Specifically, in the present embodiment, when the three-position four-way high frequency response proportional directional valve 14 is in the left position, the port a communicates with the port T, and the port B communicates with the port P; when the three-position four-way high-frequency-response proportional reversing valve 14 is positioned at the right position, the port A is communicated with the port P, and the port B is communicated with the port T.
Therefore, when oil is needed to be supplemented to the rod cavity, the three-position four-way high-frequency-response proportional reversing valve 14 can be located at the right position, and when oil is needed to be supplemented to the rodless cavity, the three-position four-way high-frequency-response proportional reversing valve 14 can be located at the left position.
Illustratively, the controller 30 may be a PLC control device.
Further, in the present embodiment, as shown in fig. 2, the hydraulic control system of the mandrel holder adjusting device further includes: a pilot type priority unloading valve 16 and a plug type one-way valve 15 are plugged.
Specifically, a P port of the cartridge pilot type priority unloading valve 16 is connected with a rodless cavity of the adjusting hydraulic cylinder 17, an X port of the cartridge pilot type priority unloading valve 16 is connected with a rod cavity of the adjusting hydraulic cylinder 17, and a T port and a Y port of the cartridge pilot type priority unloading valve 16 are both connected to an oil return pipeline; an oil inlet of the cartridge type one-way valve 15 is connected to an oil return pipeline, and an oil outlet of the cartridge type one-way valve 15 is connected to a rod cavity of the adjusting hydraulic cylinder 17.
Therefore, in practical use, when the adjusting hydraulic cylinder 17 is in a high-frequency adjusting process, once the oil pressure in the rod cavity or the rodless cavity is too high, the pilot-operated unloading valve 16 can be inserted to pre-unload sudden pressure changes of the rod cavity and the rodless cavity of the adjusting hydraulic cylinder 17 at the same time, so that the adjusting hydraulic cylinder 17 is prevented from having large pressure impact on the opening hydraulic cylinder 18 or the rolling stand 200.
In addition, in the present embodiment, both the inserted check valve 15 and the inserted pilot type priority unloading valve 16 can be integrally inserted into the oil path block 32, so that the hydraulic oil is ensured not to leak, and the whole structure is more compact.
Optionally, in this embodiment, as shown in fig. 2, the hydraulic control system of the mandrel support adjusting device further includes: a tubular check valve 31. Wherein, the tubular check valve 31 is connected in series to the oil return pipeline, and the oil outlet of the tubular check valve 31 is connected to the hydraulic oil outlet.
In practical use, when the oil pressure impact pressure of the rodless cavity exceeds the protection pressure set by the inserted pilot type priority unloading valve 16, the pressure can be relieved to an oil return pipeline through the inserted pilot type priority unloading valve 16, and meanwhile, the rod cavity of the hydraulic cylinder 17 is adjusted to quickly supplement oil through the inserted one-way valve 15. At this time, the tubular check valve 31 can ensure that the oil return line is filled with low-pressure hydraulic oil at any time.
Thus, in the present embodiment, by providing the pipe check valve 31 in the return line, on the one hand, it is possible to quickly replenish the rod chamber when the hydraulic impact pressure in the rodless chamber exceeds the protection pressure set by the cartridge pilot type priority unloading valve 16, and on the other hand, it is possible to maintain the return back pressure at the T port of the three-position four-way high-frequency-response proportional directional valve 14, thereby improving the responsiveness of the directional valve.
In the present embodiment, there is also provided a control method for controlling a hydraulic control system of a mandrel bar support adjusting apparatus in the present embodiment, the control method including:
moving a piston rod of the adjusting hydraulic cylinder to a required position according to the requirements of the rolling process;
electrifying an electromagnet Y1 of the two-position four-way electromagnetic directional valve to enable hydraulic oil to enter a control port of the first hydraulic control one-way valve, a control port of the second hydraulic control one-way valve and a control port of the third hydraulic control one-way valve;
and electrifying the electromagnet Y2 of the three-position four-way high-frequency-response proportional reversing valve, so that the hydraulic oil enters a rod cavity and a rodless cavity of the adjusting hydraulic cylinder through the pressure reducing valve and the three-position four-way high-frequency-response proportional reversing valve.
Thus, the system in this embodiment has the following advantages:
firstly, a rodless cavity of an adjusting hydraulic cylinder is filled with hydraulic oil, so that when the hydraulic cylinder is opened to act on a piston rod of the adjusting hydraulic cylinder, the hydraulic oil in the rodless cavity can be used as a hydraulic spring to absorb impact and can buffer transient acting force generated when a mandrel carrier roller is opened and closed, compared with the prior art, the problem of cracking of a lifter base caused by adjustment and positioning of a worm gear screw lifter is effectively solved, and the hydraulic control system of the mandrel support frame adjusting device is low in failure rate, compact in structure and low in equipment maintenance cost, the service life of the whole device can be prolonged, and the production efficiency is improved;
secondly, the position of the piston rod of the hydraulic cylinder is sensed and adjusted by the displacement sensor, so that the controller can input an electric signal to the three-position four-way high-frequency-response proportional reversing valve according to the position information sensed by the displacement sensor, and can adjust and adjust the position of the piston rod of the hydraulic cylinder in time, thereby positioning the opening size of the mandrel carrier roller in real time, quickly and accurately, avoiding the adjustment error caused by the gap between the lead screws when a worm gear lead screw lifter is adopted for adjustment in the prior art, further effectively solving the problem of surface gouging of the mandrel, ensuring the stability of the mandrel in the rolling process and improving the wall thickness precision of a finished product pipe;
thirdly, by arranging the cartridge pilot type priority unloading valve, the pressure mutation of a rod cavity and a rodless cavity of the adjusting hydraulic cylinder can be pre-unloaded simultaneously, so that the adjusting hydraulic cylinder is prevented from generating rigid impact on a rolling mill frame;
fourthly, through setting up cartridge formula check valve, can mend oil rapidly after the pole chamber transient state position changes, moreover, when the adjustment pneumatic cylinder is in the locking rolling state, this cartridge formula structure can avoid hydraulic oil to appear leaking.
It is noted that, in this document, relational terms such as "first" and "second," and the like, may be used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. In addition, "front", "rear", "left", "right", "upper" and "lower" in this document are referred to the placement states shown in the drawings.
Finally, it should be noted that: the above examples are only for illustrating the technical solutions of the present invention, and not for limiting the same; although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions of the embodiments of the present invention.
Claims (7)
1. A hydraulic control system for a mandrel support adjustment apparatus, the system comprising: a pressure reducing valve, a first hydraulic control one-way valve, a second hydraulic control one-way valve, a third hydraulic control one-way valve, a two-position four-way electromagnetic directional valve, a three-position four-way high-frequency response proportional directional valve, an adjusting hydraulic cylinder and an opening hydraulic cylinder, wherein,
an oil inlet of the pressure reducing valve is connected to a hydraulic oil inlet, an oil outlet of the pressure reducing valve is connected to a port P of the two-position four-way electromagnetic directional valve, and an oil outlet of the pressure reducing valve is also connected to an oil outlet of the first hydraulic control one-way valve;
an A port of the two-position four-way electromagnetic reversing valve is connected to a closed end, a B port of the two-position four-way electromagnetic reversing valve is connected to a control port of the first hydraulic control one-way valve, a control port of the second hydraulic control one-way valve and a control port of the third hydraulic control one-way valve, a T port of the two-position four-way electromagnetic reversing valve is connected to an oil return pipeline, when an electromagnet Y1 of the two-position four-way electromagnetic reversing valve is electrified, the A port is communicated with the T port, and the B port is communicated with the P port;
a port P of the three-position four-way high-frequency-response proportional reversing valve is connected to an oil inlet of the first hydraulic control one-way valve, a port A of the three-position four-way high-frequency-response proportional reversing valve is connected to an oil inlet of the second hydraulic control one-way valve, a port B of the three-position four-way high-frequency-response proportional reversing valve is connected to an oil inlet of the third hydraulic control one-way valve, a port T of the three-position four-way high-frequency-response proportional reversing valve is connected to an oil return pipeline, when the three-position four-way high-frequency-response proportional reversing valve is in a middle position, the port T, the port A and the port B are communicated, and the port P is not communicated with the three ports;
the adjusting hydraulic cylinder comprises a rod cavity and a rodless cavity, a piston rod of the adjusting hydraulic cylinder is inserted into the rod cavity, the piston rod of the adjusting hydraulic cylinder can extend out of the rod cavity and is abutted to the piston rod of the opening hydraulic cylinder, an oil outlet of the second hydraulic control one-way valve is connected to the rod cavity of the adjusting hydraulic cylinder, and an oil outlet of the third hydraulic control one-way valve is connected to the rodless cavity of the adjusting hydraulic cylinder;
the opening hydraulic cylinder is configured to be fixedly arranged on a rolling mill stand, one end of a piston rod of the opening hydraulic cylinder can abut against a right bearing moving column on the rolling mill stand, and the other end of the piston rod of the opening hydraulic cylinder can abut against the end of the piston rod of the adjusting hydraulic cylinder.
2. The mandrel support frame adjustment apparatus hydraulic control system of claim 1, further comprising: a displacement sensor and a controller, wherein the controller is connected with the displacement sensor,
the displacement sensor is arranged on the adjusting hydraulic cylinder and configured to sense the position of a piston rod of the adjusting hydraulic cylinder, the displacement sensor, the three-position four-way high-frequency-response proportional reversing valve and the two-position four-way electromagnetic reversing valve are electrically connected with the controller, and the controller is configured to adjust the three-position four-way high-frequency-response proportional reversing valve according to the position of the piston rod sensed by the displacement sensor.
3. The hydraulic control system of the mandrel support frame adjusting device according to claim 2, wherein when the three-position four-way high frequency response proportional reversing valve is in the left position, the port a is communicated with the port T, and the port B is communicated with the port P; when the three-position four-way high-frequency response proportional reversing valve is in the right position, the port A is communicated with the port P, and the port B is communicated with the port T.
4. The hydraulic control system of a mandrel support stand adjusting device of claim 2, wherein the controller is a PLC control device.
5. The mandrel support frame adjustment apparatus hydraulic control system of claim 1, further comprising: a pilot-operated type priority unloading valve and a plug-in type one-way valve are inserted,
the P port of the inserted pilot type priority unloading valve is connected with a rodless cavity of the adjusting hydraulic cylinder, the X port of the inserted pilot type priority unloading valve is connected with a rod cavity of the adjusting hydraulic cylinder, and the T port and the Y port of the inserted pilot type priority unloading valve are both connected to an oil return pipeline; an oil inlet of the cartridge check valve is connected to an oil return pipeline, and an oil outlet of the cartridge check valve is connected to a rod cavity of the adjusting hydraulic cylinder.
6. The mandrel support frame adjustment apparatus hydraulic control system of claim 1, further comprising: the hydraulic oil return device comprises a pipe type one-way valve, wherein the pipe type one-way valve is connected to an oil return pipeline in series, and an oil outlet of the pipe type one-way valve is connected to a hydraulic oil outlet.
7. A control method for controlling the mandrel holder adjusting apparatus hydraulic control system of claim 1, the control method comprising:
moving a piston rod of the adjusting hydraulic cylinder to a required position according to the requirements of the rolling process;
electrifying an electromagnet Y1 of the two-position four-way electromagnetic directional valve to enable hydraulic oil to enter a control port of the first hydraulic control one-way valve, a control port of the second hydraulic control one-way valve and a control port of the third hydraulic control one-way valve;
and electrifying the electromagnet Y2 of the three-position four-way high-frequency-response proportional reversing valve, so that the hydraulic oil enters a rod cavity and a rodless cavity of the adjusting hydraulic cylinder through the pressure reducing valve and the three-position four-way high-frequency-response proportional reversing valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211506370.3A CN115780521A (en) | 2022-11-29 | 2022-11-29 | Hydraulic control system and control method for core rod support frame adjusting device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211506370.3A CN115780521A (en) | 2022-11-29 | 2022-11-29 | Hydraulic control system and control method for core rod support frame adjusting device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN115780521A true CN115780521A (en) | 2023-03-14 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202211506370.3A Pending CN115780521A (en) | 2022-11-29 | 2022-11-29 | Hydraulic control system and control method for core rod support frame adjusting device |
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| Country | Link |
|---|---|
| CN (1) | CN115780521A (en) |
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2022
- 2022-11-29 CN CN202211506370.3A patent/CN115780521A/en active Pending
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