CN115815338B - A Hydraulic Pressing System for Super Large Shaft Cross Wedge Rolling Mill Applicable to Two-machine Linkage - Google Patents

Abstract

The invention discloses a hydraulic pressing system of a super-large shaft wedge cross rolling mill suitable for double-machine linkage, which comprises the following components: the hydraulic pressing system of the first rolling mill, the hydraulic pressing system of the second rolling mill and the constant-pressure oil source; the first rolling mill hydraulic reduction system includes: the rolling mill comprises a first rolling mill pressing device, a first rolling mill roller balance hydraulic device and a first rolling mill prestress hydraulic device; the second rolling mill hydraulic pressing system comprises a second rolling mill pressing device, a second rolling mill roller balance hydraulic device and a second rolling mill prestress hydraulic device. By adopting the technical scheme of the invention, the working requirement of the double-machine linkage cross wedge rolling mill for preparing the ultra-large shaft parts is met, the requirement of double-machine linkage working of the large-scale cross wedge rolling mill with high pressure and large flow of a pressing system is met, the requirement of large prestress required under the condition of large rolling force value of the ultra-large cross wedge rolling mill is met, the constant prestress of a rolling mill frame in the rolling process is ensured, and meanwhile, the energy-saving effect is achieved.

Description

A Hydraulic Pressing System for Super Large Shaft Cross Wedge Rolling Mill Applicable to Two-machine Linkage

technical field

The invention belongs to the technical field of cross wedge rolling, and in particular relates to a hydraulic pressing system for a double-machine linkage super large shaft type cross wedge rolling mill.

Background technique

Cross wedge rolling is an efficient and clean plastic forming technology for parts. Its process is suitable for the production of shaft parts with rotating bodies. It can not only replace the rough turning process to produce various shaft parts, but also provide various molds. Forging parts provide precise die forging blanks. Its process features: (1) high production efficiency; (2) high material utilization; (3) long mold life; (4) good product quality.

In order to meet the production needs, and aiming at the technical limitations of the existing rapid forging process, such as low production efficiency, many consumables, high cost, and heavy pollution, a high-efficiency and clean cross wedge rolling technology solution is proposed to prepare super-large shaft parts. The largest cross wedge rolling mill in the world; at the same time, the rigidity of the rolling mill, the strength of the roll, and the dimensional accuracy of the product are taken into account to ensure the efficient and high-quality production of super-large shaft parts.

However, designing a super-large axial cross wedge rolling mill according to the design idea of a traditional rolling mill will lead to a huge structure of the rolling mill, which will greatly increase the manufacturing cost, and at the same time it is difficult to guarantee the yield of the product. For shaft parts, the rolling mill is arranged in series with double racks, which can realize two-pass precise rolling of the rolled piece, ensuring high rigidity, large bearing capacity, high geometric precision control and high reliability of the rolling mill, and greatly improving the quality of super-large shafts. Forming efficiency and precision of parts.

In order to ensure the final dimensional accuracy of super-large shaft parts, it is necessary to meet the high-pressure pressing, fast response and high-precision coordinated control of the two-frame pressing system. If electric pressing is used to control four motors separately, it is difficult to meet high-pressure pressing and coordinated control accuracy, while hydraulic pressing can realize a set of hydraulic pumps to control the pressing of two rolling mills at the same time, and the pressing force is large. Because of its small inertia, fast action speed and high sensitivity, the lowering device can make the pressing system obtain higher precision, and can well control the dimensional deviation to ensure the yield of the axle.

Due to the size and quality of super-large shaft cross wedge rolling mills, it is difficult to eliminate the fit gap between related parts. At the same time, it is necessary to quickly replace the rolls or molds according to the rolling specifications of the products to meet the needs of the rolling rhythm of products of different specifications. The purpose of the balance device is to eliminate the impact phenomenon caused by the fit gap between the relevant parts in the working frame during the rolling process, so as to ensure the rolling accuracy of the rolled piece. The hydraulic balancing device has a compact structure, is suitable for balancing the upper rolls of various heights, and can meet the requirements of the geometrical precision control of super-large axles; at the same time, it is easy to disassemble, which can significantly speed up the roll changing process, which is beneficial to the work of the rapid roll changing system.

The use of super-large cross-wedge rolling mills to prepare shaft parts also puts forward higher requirements for the rigidity of the rolling mill stand, which directly determines the product dimensions and precision. Using the prestressing method to increase the rigidity of the rolling mill stand is a relatively economical method. The traditional cross wedge mill prestressing device mainly adds height-adjustable support columns in the upper and lower roll bearing housings. The way to obtain the compressive stress of the support columns mainly depends on the pressure The motor, worm gear and worm mechanism in the lower device are jointly realized by the structure of the pressing screw pair. This method is simple in structure and convenient in control, but it can only be used on cross wedge rolling mills that require a small prestressing effect, and for super large axle cross wedge For rolling mills, due to the large value of the rolling force, it is difficult for the traditional structure to meet the prestressing requirements of the rolling force.

Contents of the invention

The technical problem to be solved by the present invention is to provide a hydraulic pressing system suitable for a double-machine linkage super-large cross-wedge rolling mill to meet the working requirements of the double-machine linkage cross-wedge rolling mill for preparing super-large shaft parts. It satisfies the requirements of double-machine linkage work of large-scale cross-wedge rolling mills with high pressure and high flow in the reduction system, and meets the large prestressing requirements required for large-scale cross-wedge rolling mills when the rolling force value is large, ensuring During the rolling process, the prestress of the rolling mill stand is constant, and at the same time, the effect of energy saving is achieved.

To achieve the above object, the present invention provides the following scheme:

A hydraulic pressure reduction system for a super-large axial cross wedge rolling mill that is suitable for double-machine linkage, including: the hydraulic pressure reduction system of the first rolling mill, the hydraulic pressure reduction system of the second rolling mill, and a constant pressure oil source; the hydraulic pressure reduction system of the first rolling mill Including: the first rolling mill pressing device, the first rolling mill roll balance hydraulic device, the first rolling mill prestressing hydraulic device; the second rolling mill hydraulic pressing system includes the second rolling mill pressing device, the second rolling mill roll balancing hydraulic device, the second Rolling mill prestress hydraulic device;

Among them, the first rolling mill depressing device and the second rolling mill depressing device form the depressing device, the first rolling mill roll balance hydraulic device and the second rolling mill roll balancing hydraulic device form the balancing device, the first rolling mill prestress hydraulic device and the second rolling mill The prestressing hydraulic device constitutes the prestressing device; the pressing device is distributed on the archway and the upper bearing seat, the balance device is distributed at both ends of the pressing device and connected with the balance beam, and the prestressing device is distributed on the upper bearing seat and the lower bearing seat Between; the constant pressure oil source is used to supply oil to the hydraulic pressing system of the first rolling mill and the hydraulic pressing system of the second rolling mill.

Preferably, the constant pressure oil source includes a first constant pressure oil source and a second constant pressure oil source, the first constant pressure oil source supplies oil to the first rolling mill hydraulic pressing system, and the second constant pressure oil source supplies oil to the second rolling mill hydraulic system Depression system; a first accumulator and a second accumulator are arranged at the oil outlets of the first constant pressure oil source and the second constant pressure oil source to absorb the first constant pressure oil source and the second constant pressure oil Pressure and flow pulsations generated by hydraulic pumps in the source.

As a preference, one end of the first two-position two-way electromagnetic reversing valve is connected to the oil outlet of the first accumulator through an oil pipe, and the other end is connected to the main pressure oil pipe of the hydraulic pressing system of the first rolling mill through an oil pipe. The oil return port of the accumulator is connected to the oil return tank through the oil pipe; one end of the second two-position two-way electromagnetic reversing valve is connected to the oil outlet of the second accumulator through the oil pipe, and the other end is connected to the hydraulic pressure system of the second rolling mill through the oil pipe. The main pressure oil pipe is connected, and the oil return port of the second accumulator is connected to the oil return tank through the oil pipe.

Preferably, the first rolling mill depressing device includes a first transmission side depressing device and a first operating side depressing device; the first rolling mill roll balance hydraulic device includes a first transmission side roll balance hydraulic device and a first operating side roll balance hydraulic device device; the first rolling mill prestress hydraulic device includes the first transmission side prestress hydraulic device and the first operation side prestress hydraulic device; wherein, the first transmission side depressing device, the first operation side depressing device, the first transmission side The roll balancing hydraulic device, the first operating side roll balancing hydraulic device, the first transmission side prestressing hydraulic device, and the first operating side prestressing hydraulic device are respectively connected to the main pressure oil pipe and the main oil return pipe.

Preferably, the first drive-side depressing device and the first operation-side depressing device adopt a combined throttling and speed-regulating circuit in which an electromagnetic ball valve controls a cartridge valve.

Preferably, the roll balance hydraulic device on the first drive side and the roll balance hydraulic device on the first operation side adopt differential control, and can be switched between force control and position control.

As a preference, the position closed-loop and pressure closed-loop control of the first transmission side pressing device and the first operation side pressing device are coordinated; the position closed loop and pressure of the first transmission side roll balance hydraulic device and the first operation side roll balance hydraulic device are controlled Closed-loop cooperative control; coordinated control of the position closed-loop and pressure closed-loop of the prestressed hydraulic device on the first transmission side and the prestressed hydraulic device on the first operating side.

As preferably, the rolling mill energy parameters of the first rolling mill hydraulic pressing system are as follows: the normal rolling force is 3300KN, and the maximum rolling force is 4950KN; the rolling mill energy parameters of the second rolling mill hydraulic pressing system are as follows: the normal rolling force is 3600KN, the maximum rolling force is 5400KN.

Compared with the prior art, the present invention has the following technical effects and advantages:

1. The present invention satisfies the working requirements of the double-machine linkage ultra-large shaft cross wedge rolling mill for preparing large shaft parts;

2. The hydraulic pressing system designed by the present invention is suitable for the double-machine linkage work of large-scale axial wedge rolling mills with high pressure and large flow;

3. The hydraulic device designed by the present invention facilitates the roll changing operation, satisfies the large prestress requirement required by the large-scale cross-wedge rolling mill when the rolling force value is large, and ensures that the rolling mill stand is stable during the rolling process. The magnitude of the prestress is constant;

4. The energy-saving effect of the hydraulic pressing system designed in the present invention is remarkable;

5. The coordinated control of position closed loop and pressure closed loop in each device ensures the control accuracy of the entire hydraulic pressing system.

Description of drawings

In order to illustrate the embodiments of the present invention or the technical solutions in the prior art more clearly, the following will briefly introduce the drawings required in the embodiments.

Fig. 1 is the structural schematic diagram of the ultra-large shaft type cross wedge rolling mill of twin machine linkage;

Fig. 2 is the side view of the ultra-large shaft type cross wedge rolling mill with double-machine linkage;

Fig. 3 is the hydraulic principle diagram of the hydraulic pressing system of the ultra-large shaft type cross wedge rolling mill with two-machine linkage;

Fig. 4 is a hydraulic principle diagram of the hydraulic pressing system of the first rolling mill;

Fig. 5 is the oil circuit diagram of the device's constant pressure oil source, oil return tank and accumulator.

Among them, 1-depression device, 2-balance device, 3-balance beam, 4-upper bearing seat, 5-prestressing device, 6-lower bearing seat, 7-archway, 1.1-first constant pressure oil source, 1.2 -Second constant pressure oil source, 2.1-first servo valve, 2.2-second servo valve, 2.3-third servo valve, 2.4-fourth servo valve, 3.1-first two-position four-way proportional reversing valve, 3.2 -The second two-position four-way proportional directional valve, 3.3-the third two-position four-way proportional directional valve, 3.4-the fourth two-position four-way proportional directional valve, 3.5-the fifth two-position four-way proportional directional valve , 3.6- the sixth two-position four-way proportional directional control valve, 3.7- the seventh two-position four-way proportional directional control valve, 3.8- the eighth two-position four-way proportional directional control valve, 4.1- the first cartridge valve, 4.2- The second cartridge valve, 4.3-the third cartridge valve, 4.4-the fourth cartridge valve, 4.5-the fifth cartridge valve, 4.6-the sixth cartridge valve, 4.7-the seventh cartridge valve, 4.8-the eighth cartridge valve Cartridge valve, 5.1-first proportional relief valve, 5.2-second proportional relief valve, 5.3-third proportional relief valve, 5.4-fourth proportional relief valve, 6.1-first three-position four-way proportional switch Directional valve, 6.2- the second three-position four-way proportional directional valve, 6.3- the third three-position four-way proportional directional valve, 6.4- the fourth three-position four-way proportional directional valve, 7.1- the first hydraulic control one-way Valve, 7.2-second hydraulic control check valve, 7.3-third hydraulic control check valve, 7.4-fourth hydraulic control check valve, 7.5-fifth hydraulic control check valve, 7.6-sixth hydraulic control check valve Valve, 7.7-the seventh hydraulic control check valve, 7.8-the eighth hydraulic control check valve, 7.9-the ninth hydraulic control check valve, 7.10-the tenth hydraulic control check valve, 7.11-the eleventh hydraulic control check valve Directional valve, 7.12-twelfth hydraulic control check valve, 8.1-first proportional pressure reducing valve, 8.2-second proportional pressure reducing valve, 8.3-third proportional pressure reducing valve, 8.4-fourth proportional pressure reducing valve, 8.5-fifth proportional pressure reducing valve, 8.6-sixth proportional pressure reducing valve, 8.7-seventh proportional pressure reducing valve, 8.8-eighth proportional pressure reducing valve, 9.1-first pressure sensor, 9.2-second pressure sensor, 9.3-third pressure sensor, 9.4-fourth pressure sensor, 9.5-fifth pressure sensor, 9.6-sixth pressure sensor, 9.7-seventh pressure sensor, 9.8, eighth pressure sensor, 9.9-ninth pressure sensor, 9.10 - tenth pressure sensor, 9.11 - eleventh pressure sensor, 9.12 - twelfth pressure sensor, 10.1 - first accumulator, 10.2 - second accumulator, 10.3 - third accumulator, 11.1 - first Two-position two-way electromagnetic reversing valve, 11.2-second two-position two-way electromagnetic reversing valve, 12.1-first relief valve, 12.2-second relief valve, 12.3-third relief valve, 12.4-fourth Relief valve, 12.5-fifth relief valve, 12.6-sixth relief valve, 12.7-seventh relief valve, 12.8-eighth relief valve, 13.1-first one-way valve, 13.2-second one-way valve Valve, 13.3-the third one-way valve, 13.4-the fourth one-way valve, 14.1-the first electromagnetic ball valve, 14.2-the second electromagnetic ball valve, 14.3-the third electromagnetic ball valve, 14.4-the fourth electromagnetic ball valve, 15-return oil tank , C1-first transmission side press down cylinder, C2-first operation side press down cylinder, C3-first balance hydraulic cylinder, C4-second balance hydraulic cylinder, C5-first prestressed hydraulic cylinder, C6-second Prestressed hydraulic cylinder, C7-the third prestressed hydraulic cylinder, C8-the fourth prestressed hydraulic cylinder, C9-the second transmission side pressure cylinder, C10-the second operation side pressure cylinder, C11-the third balance hydraulic cylinder , C12-fourth balance hydraulic cylinder, C13-fifth prestressed hydraulic cylinder, C14-sixth prestressed hydraulic cylinder, C15-seventh prestressed hydraulic cylinder, C16-eighth prestressed hydraulic cylinder, F1-first displacement Sensors, F2-second displacement sensor, F3-third displacement sensor, F4-fourth displacement sensor, F5-fifth displacement sensor, F6-sixth displacement sensor, F7-seventh displacement sensor, F8-eighth displacement sensor , F9- ninth displacement sensor, F10- tenth displacement sensor, F11- eleventh displacement sensor, F12- twelfth displacement sensor, YB1.1, YB1.2, YB1.3, YB1.4- servo drive change Direction device, YVH1.1, YVH1.2, YVH1.3, YVH1.4, Y1.1, Y1.2, Y1.3, Y1.4, Y1.5, Y1.6, Y1.7, Y1.8 , Y1.9, Y1.10-electromagnet, Y2.1, Y2.2, Y2.3, Y2.4, Y2.5, Y2.6, Y2.7, Y2.8, Y3.1, Y3. 2. Y3.3, Y3.4-proportional electromagnet.

Detailed ways

In order to make the above objects, features and advantages of the present invention more comprehensible, the present invention will be further described in detail below in conjunction with the accompanying drawings and specific embodiments.

As shown in Figures 1 to 5, the present invention provides a hydraulic pressing system for super-large axial cross wedge rolling mills that are applicable to two-machine linkage, including: the hydraulic pressing system of the first rolling mill, the hydraulic pressing system of the second rolling mill and the constant Pressure oil source; the first rolling mill hydraulic pressing system includes the first rolling mill pressing device, the first rolling mill roll balance hydraulic device, the first rolling mill prestressing hydraulic device; the second rolling mill hydraulic pressing system includes the second rolling mill pressing device, The second rolling mill roll balancing hydraulic device, the second rolling mill prestressing hydraulic device. The first rolling mill pressing device and the second rolling mill pressing device form the pressing device 1, the first rolling mill roll balance hydraulic device and the second rolling mill roll balancing hydraulic device form the balancing device 2, the first rolling mill prestressing hydraulic device and the second rolling mill The prestressing hydraulic device constitutes the prestressing device 5; the pressing device 1 is distributed on the archway 7 and the upper bearing seat 4, the balance device 2 is distributed at both ends of the pressing device 1, and is connected with the balance beam 3, and the prestressing device 5 is distributed Between the upper bearing seat 4 and the lower bearing seat 6.

The constant pressure oil source includes a first constant pressure oil source 1.1 and a second constant pressure oil source 1.2, wherein the first constant pressure oil source 1.1 supplies oil to the first rolling mill hydraulic pressing system, and the second constant pressure oil source 1.2 supplies oil to the second Rolling mill hydraulic pressing system. One end of the first two-position two-way electromagnetic reversing valve 11.1 is connected to the oil outlet of the first accumulator 10.1 through an oil pipe, and the other end is connected to the main pressure oil pipe P of the hydraulic pressing system of the first rolling mill through an oil pipe. The oil return port of the device 10.1 is connected to the oil return tank 15 through the oil pipe; one end of the second two-position two-way electromagnetic reversing valve 11.2 is connected to the oil outlet of the second accumulator 10.2 through the oil pipe, and the other end is connected to the hydraulic pressure of the second rolling mill through the oil pipe. The main pressure oil pipe P of the depressing system is connected, and the oil return port of the second accumulator 10.2 is connected to the oil return tank 15 through the oil pipe.

A first accumulator 10.1 and a second accumulator 10.2 are arranged at the oil outlets of the first constant pressure oil source 1.1 and the second constant pressure oil source 1.2 to absorb the first constant pressure oil source 1.1 and the second constant pressure The pressure and flow pulsation generated by the hydraulic pump in the oil source 1.2 maintains the working pressure of the pressing device when it is working, and absorbs the hydraulic impact force generated when the roll balancing device and the prestressing hydraulic device are working, so as to ensure the stability of the system.

Since the hydraulic schematic diagram of the hydraulic pressing system of the first rolling mill is the same as that of the hydraulic pressing system of the second rolling mill, but the force and energy parameters of the two rolling mills are different, the rolling mill force and energy parameters of the hydraulic pressing system of the first rolling mill are as follows: the normal rolling force is 3300KN, the maximum rolling force is 4950KN; the rolling mill force parameters of the hydraulic pressure reduction system of the second rolling mill are as follows: the normal rolling force is 3600KN, and the maximum rolling force is 5400KN. Therefore, only the hydraulic principle diagram of the hydraulic pressing system of the first rolling mill will be described in detail.

The first rolling mill depressing device includes a first transmission side depressing device and a first operation side depressing device; the first rolling mill roll balance hydraulic device includes a first transmission side roll balance hydraulic device and a first operation side roll balance hydraulic device ; The first rolling mill prestressing hydraulic device includes the first driving side prestressing hydraulic device and the first operating side prestressing hydraulic device.

The first transmission side depressing device includes a first servo valve 2.1, a first cartridge valve 4.1, a second cartridge valve 4.2, a first proportional overflow valve 5.1, a first electromagnetic ball valve 14.1, a first displacement sensor F1, The first transmission side depresses the oil cylinder C1 and the first pressure sensor 9.1; the P port of the first servo valve 2.1 is connected to the main pressure oil pipe P through the oil pipe, and the A port of the first servo valve 2.1 is connected to the first plug through the oil pipe. On the A port of the installed valve 4.1, the B port of the first servo valve 2.1 is connected to the A port of the second cartridge valve 4.2 through the oil pipe, and the B port of the first cartridge valve 4.1 and the B port of the second cartridge valve 4.2 respectively pass through The oil pipe is connected to the rod chamber and the rodless chamber of the first transmission side depressing oil cylinder C1, the T port of the first servo valve 2.1 is connected with the main oil return pipe T; the X port of the first cartridge valve 4.1 and the second cartridge valve 4.2 The X port of the first cartridge valve 4.1 is connected to the A port of the first electromagnetic ball valve 14.1 through the oil pipe, the Y port of the first cartridge valve 4.1 and the Y port of the second cartridge valve 4.2 are connected to the main oil return pipe T through the oil pipe, and the first electromagnetic ball valve 14.1 The P port and T port of the oil pipe are respectively connected with the main pressure oil pipe P and the main oil return pipe T.

The piston movement speed of the first transmission side depressing oil cylinder C1 is controlled by the servo-driven reversing device YB1.1 of the first servo valve 2.1. The larger the opening of the spool, the more oil flows into the rodless cavity of the first transmission side depressing cylinder C1, and the faster the piston of the first transmission side depressing cylinder C1 moves; on the contrary, the servo drives the reversing device YB1. 1 The smaller the current passed, the smaller the opening of the spool of the first servo valve 2.1, the less oil flows into the rodless chamber of the first transmission side depressing cylinder C1, and the piston of the first transmission side depressing cylinder C1 moves The slower the speed is; by controlling the YB1.1 current of the servo-driven reversing device, the flow into the cylinder can be controlled, thereby controlling the displacement of the cylinder piston. During specific work, when it is necessary to press down the cylinder C1 on the first transmission side, the electromagnet YVH1.1, the servo drive reversing device YB1.1, the electromagnet Y1.3, and the electromagnet Y1.4 are energized at the same time, and the oil Through the P-A channel of the first servo valve 2.1 and the A-B channel of the first cartridge valve 4.1, it flows into the rodless cavity of the first transmission side depressing cylinder C1, and at the same time, the fluid in the rod cavity of the first transmission side depressing cylinder C1 The oil flows into the main oil return pipe through the B-A channel of the second cartridge valve 4.2 and the B-T channel of the first servo valve 2.1, thereby driving the piston of the first transmission side depressing cylinder C1 to move downward.

In order to protect the first transmission side depressing device, a first proportional relief valve 5.1 is connected in parallel to the oil pipe between the rodless chamber of the first transmission side depressing oil cylinder C1 and the port B of the second cartridge valve 4.2.

When it is necessary to stop in an emergency, the first proportional overflow valve 5.1 can be used to depress the rodless chamber of the first transmission side cylinder C1 to realize shock-free unloading braking.

The first displacement sensor F1 is installed in the piston rod of the first transmission side depressing cylinder C1, and the position control accuracy of the piston of the first transmission side depressing cylinder C1 is guaranteed by the position closed loop formed by the first displacement sensor F1 and the first servo valve 2.1 The first pressure sensor 9.1 is connected to the P2 port of the first transmission side depressing cylinder C1, and the control accuracy of the working pressure of the first transmission side depressing cylinder C1 is achieved by forming a pressure closed loop with the first pressure sensor 9.1 and the first servo valve 2.1. ensure.

Similarly, the first operating side depressing device includes a second servo valve 2.2, a third cartridge valve 4.3, a fourth cartridge valve 4.4, a second proportional overflow valve 5.2, a second electromagnetic ball valve 14.2, and a second displacement valve. Sensor F2, first operating side depressing oil cylinder C2, second pressure sensor 9.2; the P port of the second servo valve 2.2 is connected to the main pressure oil pipe P through the oil pipe, and the A port of the second servo valve 2.2 is connected to the main pressure oil pipe P through the oil pipe. On the A port of the third cartridge valve 4.3, the B port of the second servo valve 2.2 is connected to the A port of the fourth cartridge valve 4.4 through the oil pipe, and the B port of the third cartridge valve 4.3 and the B port of the fourth cartridge valve 4.4 Ports are respectively connected to the rod chamber and rodless chamber of the first operating side depressing oil cylinder C2 through the oil pipe, the T port of the second servo valve 2.2 is connected with the main oil return pipe T; the X port of the third cartridge valve 4.3 is inserted into the fourth port The X port of the valve 4.4 is jointly connected to the A port of the second electromagnetic ball valve 14.2 through the oil pipe, the Y port of the third cartridge valve 4.3 is connected to the main oil return pipe T through the oil pipe, and the Y port of the third cartridge valve 4.3 is connected to the main oil return pipe T through the oil pipe. The P port and the T port of the electromagnetic ball valve 14.2 are respectively connected with the main pressure oil pipe P and the main oil return pipe T through oil pipes.

The piston movement speed of the first operating side depresses the oil cylinder C2 is controlled by the servo-driven reversing device YB1.2 of the second servo valve 2.2, the larger the current passing through the servo-driven reversing device YB1.2, the second servo valve 2.2 The larger the opening of the spool, the more oil flows into the rodless chamber of the first operating side depressing cylinder C2, and the faster the piston of the first operating side depressing cylinder C2 moves; on the contrary, the servo drives the reversing device YB1 .2 The smaller the passing current, the smaller the opening of the spool of the second servo valve 2.2, and the less oil flows into the rodless chamber of the first operating side depressing cylinder C2, and the first operating side depresses the cylinder C2 piston The slower the movement speed is; by controlling the YB1.2 current of the servo-driven reversing device, the flow into the cylinder can be controlled, thereby controlling the displacement of the cylinder piston.

During specific work, when the first operating side is required to press down the oil cylinder C2, the electromagnet YVH1.2, the servo drive reversing device YB1.2, the electromagnet Y1.5, and the electromagnet Y1.6 are energized at the same time, and the oil Through the P-A channel of the second servo valve 2.2 and the A-B channel of the third cartridge valve 4.3, it flows into the rodless chamber of the first operating side depressing cylinder C2, and at the same time, the rod chamber of the first operating side depressing cylinder C2 The oil flows into the main oil return pipe through the B-A channel of the fourth cartridge valve 4.4 and the B-T channel of the second servo valve 2.2, thereby driving the piston of the first operating side depressing cylinder C2 to move downward.

In order to protect the first operating side depressing device, a second proportional relief valve 5.2 is connected in parallel on the oil pipe between the rodless cavity of the first operating side depressing oil cylinder C2 and the port B of the fourth cartridge valve 4.4.

When it is necessary to shut down in an emergency, the rodless cavity of the first operating side depressing oil cylinder C2 can be realized through the second proportional relief valve 5.2 to realize non-shock unloading braking.

The second displacement sensor F2 is installed in the piston rod of the first operating side depressing cylinder C2, and the position control accuracy of the piston of the first operating side depressing cylinder C2 is guaranteed by the position closed loop formed by the second displacement sensor F2 and the second servo valve 2.2 The P2 port of the first operating side depressing oil cylinder C2 is connected with a second pressure sensor 9.2, and the control accuracy of the working pressure of the first operating side depressing oil cylinder C2 is achieved by forming a pressure closed loop with the second pressure sensor 9.2 and the second servo valve 2.2. ensure.

The coordinated control of the position closed-loop and pressure closed-loop of the first drive-side depressing device and the first operation-side depressing device ensures the control accuracy of the depressing device.

The first drive-side pressing device and the first operation-side pressing device adopt the combined throttling and speed-regulating circuit of the solenoid ball valve to control the cartridge valve instead of the traditional throttling and speed-regulating circuit, so that the pressing devices are combined and integrated; at the same time, the The combination has the characteristics of large flow capacity and small pressure loss, making it more suitable for the hydraulic pressing system of super large shaft cross wedge rolling mills with high pressure and large flow; and the cartridge valve circuit has good control characteristics and is easy to maintain; the cartridge valve has Strong anti-pollution ability, reliable performance, long life, small leakage, small valve group and other advantages can ensure the efficient and stable operation of the pressing device.

The first driving side roll balancing hydraulic device includes a first two-position four-way proportional reversing valve 3.1, a second two-position four-way proportional reversing valve 3.2, a first hydraulic control check valve 7.1, a first proportional pressure reducing valve 8.1, the third pressure sensor 9.3, the third accumulator 10.3, the first overflow valve 12.1, the first one-way valve 13.1, the first balance hydraulic cylinder C3, the third displacement sensor F3; the first proportional pressure reducing valve Port A of 8.1 is connected to the main pressure oil pipe P through the oil pipe. The P port of the two-two-position four-way proportional reversing valve 3.2 is connected, and the A port of the first two-position four-way proportional reversing valve 3.1 is connected with the A port of the first hydraulic control check valve 7.1 through the oil pipe. The B port of the directional valve 7.1 is connected to the rodless chamber of the first balance hydraulic cylinder C3 through the oil pipe, and the A port of the second two-position four-way proportional reversing valve 3.2 is respectively connected to the Y port of the first hydraulic control check valve 7.1 through the oil pipe. Port and the rod cavity of the first balance hydraulic cylinder C3. The T port of the first two-position four-way proportional reversing valve 3.1 and the T port of the second two-position four-way proportional reversing valve 3.2 are connected to the main oil return pipe T through oil pipes. The oil outlet of the third accumulator 10.3 is connected to the P port of the first two-position four-way proportional reversing valve 3.1 and the P port of the second two-position four-way proportional reversing valve 3.2 through the oil pipe, and the third accumulator 10.3 The oil return port of the oil tank is connected with the main oil return pipe T through the oil pipe. The oil outlet of the first one-way valve 13.1 is connected with a first overflow valve 12.1.

During specific work, the third accumulator 10.3, the first two-position four-way proportional reversing valve 3.1, the second two-position four-way proportional reversing valve 3.2, the first hydraulic control check valve 7.1 and the first balance hydraulic cylinder C3 A communicator is formed between the oil chambers; the pressure oil is supplied to the communicator only when the leakage of the communicator exceeds a certain value, and the rest of the time is mainly supplied through the third accumulator 10.3; when the roll is balanced, Proportional electromagnet Y2.1 and proportional electromagnet Y2.2 are not energized, the oil mainly flows out from the third accumulator 10.3, on the one hand, it passes through the P-A channel of the first two-position four-way proportional reversing valve 3.1, the first fluid The A-B channel of the control check valve 7.1 flows into the rodless chamber of the first balance hydraulic cylinder C3, and on the other hand flows into the rod chamber of the first balance hydraulic cylinder C3 through the P-A channel of the second two-position four-way proportional reversing valve 3.2 Inside, a differential connection is formed. Due to the existence of the area difference between the two chambers of the first balance hydraulic cylinder C3, the first balance hydraulic cylinder C3 generates a thrust to the rod chamber, which plays the role of balancing the roll; when the first transmission When the side depressing device is depressing, when the piston rod of the first balance hydraulic cylinder C3 is retracted under pressure, the oil discharged from the rodless chamber of the first balance hydraulic cylinder C3 passes through the B-A channel of the first hydraulic control check valve 7.1, On the one hand, the A-P channel of the first two-position four-way proportional directional control valve 3.1 flows into the rod cavity of the first balance hydraulic cylinder C3 through the P-A channel of the second two-position four-way proportional directional control valve 3.2; The storage takes place in the third accumulator 10.3.

During the roll changing operation, when the first balance hydraulic cylinder C3 needs to rise, the proportional electromagnet Y2.1 will not be energized, and the proportional electromagnet Y2.2 will be energized; when the first balance hydraulic cylinder C3 needs to be lowered, the proportional electromagnet Y2. .1 is energized, the proportional electromagnet Y2.2 is not energized; when the first balance hydraulic cylinder C3 needs to stop, the proportional electromagnet Y2.1 is energized, and the proportional electromagnet Y2.2 is energized.

A third displacement sensor F3 is installed in the piston rod of the first balance hydraulic cylinder C3, and the position control accuracy of the piston of the first balance hydraulic cylinder C3 is connected by the third displacement sensor F3 and the first two-position four-way proportional reversing valve 3.1 and the second The two-position four-way proportional reversing valve 3.2 forms a closed loop to ensure the position; the P2 port of the first balance hydraulic cylinder C3 is connected to the third pressure sensor 9.3, and the control accuracy of the working pressure of the first balance hydraulic cylinder C3 is controlled by the third pressure sensor 9.3 It is ensured by forming a pressure closed loop with the first proportional pressure reducing valve 8.1.

Similarly, the roll balance hydraulic device on the first operation side includes a third two-position four-way proportional reversing valve 3.3, a fourth two-position four-way proportional reversing valve 3.4, a second hydraulic control check valve 7.2, and a second proportional reversing valve. Pressure reducing valve 8.2, fourth pressure sensor 9.4, third accumulator 10.3, second overflow valve 12.2, second one-way valve 13.2, second balance hydraulic cylinder C4, fourth displacement sensor F4; the second ratio The A port of the pressure reducing valve 8.2 is connected to the main pressure oil pipe P through the oil pipe. 3.3 is connected to port P of the fourth two-position four-way proportional directional control valve 3.4, port A of the third two-position four-way proportional directional control valve 3.3 is connected to port A of the second hydraulic control check valve 7.2 through the oil pipe, and the second The port B of the hydraulic control check valve 7.2 is connected to the rodless chamber of the second balance hydraulic cylinder C4 through the oil pipe, and the A port of the fourth two-position four-way proportional reversing valve 3.4 is respectively connected to the second hydraulic control check valve through the oil pipe The Y port of 7.2 and the rod cavity of the second balance hydraulic cylinder C4. The T port of the third two-position four-way proportional reversing valve 3.3 and the T port of the fourth two-position four-way proportional reversing valve 3.4 are connected to the main oil return pipe T through oil pipes. The oil outlet of the third accumulator 10.3 is connected to the P port of the third two-position four-way proportional reversing valve 3.3 and the P port of the fourth two-position four-way proportional reversing valve 3.4 through the oil pipe, and the third accumulator 10.3 The oil return port of the oil tank is connected with the main oil return pipe T through the oil pipe. The oil outlet of the second one-way valve 13.2 is connected with a second overflow valve 12.2.

During specific work, the third accumulator 10.3, the third two-position four-way proportional reversing valve 3.3, the fourth two-position four-way proportional reversing valve 3.4, the second hydraulic control check valve 7.2 and the second balance hydraulic cylinder C4 A communicator is formed between the oil chambers; the pressure oil is supplied to the communicator only when the leakage of the communicator exceeds a certain value, and the rest of the time is mainly supplied through the third accumulator 10.3; when the roll is balanced, Proportional electromagnet Y2.3 and proportional electromagnet Y2.4 are not energized, the oil mainly flows out from the third accumulator 10.3, on the one hand, it passes through the P-A channel of the third two-position four-way proportional reversing valve 3.3, the second liquid The A-B channel of the control check valve 7.2 flows into the rodless chamber of the second balance hydraulic cylinder C4, and on the other hand flows into the rod chamber of the second balance hydraulic cylinder C4 through the P-A channel of the fourth two-position four-way proportional reversing valve 3.4 Inside, a differential connection is formed. Due to the existence of the area difference between the two chambers of the second balance hydraulic cylinder C4, the second balance hydraulic cylinder C4 generates a thrust to the rod chamber to play the role of balancing the roll; when the first operation When the side depressing device is depressing, when the piston rod of the second balance hydraulic cylinder C4 is retracted under pressure, the oil discharged from the rodless chamber of the second balance hydraulic cylinder C4 passes through the B-A channel of the second hydraulic control check valve 7.2, On the one hand, the A-P channel of the third two-position four-way proportional directional control valve 3.3 flows into the rod chamber of the second balance hydraulic cylinder C4 through the P-A channel of the fourth two-position four-way proportional directional control valve 3.4; The storage takes place in the third accumulator 10.3.

During the roll changing operation, when the second balance hydraulic cylinder C4 is required to rise, the proportional electromagnet Y2.3 is not energized, and the proportional electromagnet Y2.4 is energized; when the second balance hydraulic cylinder C4 is required to be lowered, the proportional electromagnet Y2. .3 is energized, and the proportional electromagnet Y2.4 is not energized; when the second balance hydraulic cylinder C4 needs to be stopped, the proportional electromagnet Y2.3 is energized, and the proportional electromagnet Y2.4 is energized.

The fourth displacement sensor F4 is installed in the piston rod of the second balance hydraulic cylinder C4, and the position control accuracy of the piston of the second balance hydraulic cylinder C4 is controlled by the fourth displacement sensor F4 and the third two-position four-way proportional reversing valve 3.3 and the fourth Two-position four-way proportional reversing valve 3.4 forms a position closed loop to ensure; the P2 port of the second balance hydraulic cylinder C4 is connected with a fourth pressure sensor 9.4, and the control accuracy of the working pressure of the second balance hydraulic cylinder C4 is controlled by the fourth pressure sensor 9.4 It is ensured by forming a pressure closed loop with the second proportional pressure reducing valve 8.2.

The coordinated control of the position closed-loop and pressure closed-loop of the roll balance hydraulic device on the first transmission side and the roll balance hydraulic device on the first operation side ensures the control accuracy of the roll balance hydraulic device.

The first transmission side roll balance hydraulic device and the first operation side roll balance hydraulic device adopt differential control technology, which improves the response speed of the device; the device is convenient for roll changing operation, and it has two working states of force control and position control Switching selection; the circuit is simple and practical, and has the characteristics of stable balance force. When the device is working, it generally relies on the accumulator for oil supply. When the piston rod of the balance hydraulic cylinder is retracted under the action of the rolling mill pressing device, the excess oil in the rodless chamber is sent back to the accumulator for storage, avoiding energy loss. , The energy-saving effect is remarkable.

The first transmission side prestressed hydraulic device includes a first three-position four-way proportional reversing valve 6.1, a third hydraulic control check valve 7.3, a fourth hydraulic control check valve 7.4, a third proportional pressure reducing valve 8.3, a Five pressure sensors 9.5, the first prestressed hydraulic cylinder C5, the second prestressed hydraulic cylinder C6, the fifth displacement sensor F5; the A port of the third proportional pressure reducing valve 8.3 is connected to the main pressure oil pipe P through the oil pipe, and the first The B port of the three-proportional pressure reducing valve 8.3 is connected with the P port of the first three-position four-way proportional reversing valve 6.1 through the oil pipe, the A port of the third hydraulic control check valve 7.3 and the A port of the fourth hydraulic control check valve 7.4 The ports are respectively connected to the A port and the B port of the first three-position four-way proportional reversing valve 6.1 through the oil pipe, and the B port of the third hydraulic control check valve 7.3 and the B port of the fourth hydraulic control check valve 7.4 are respectively connected through the oil pipe Connected to the rod chamber and the rodless chamber of the first prestressed hydraulic cylinder C5 and the second prestressed hydraulic cylinder C6, the Y port of the third hydraulic control check valve 7.3 and the Y port of the fourth hydraulic control check valve 7.4 are respectively It is connected to port B and port A of the first three-position four-way proportional reversing valve 6.1 through the oil pipe, and the T port of the first three-position four-way proportional reversing valve 6.1 is connected to the main oil return pipe T.

During specific work, the proportional electromagnet Y3.1 is energized, and the oil passes through the A-B channel of the third proportional pressure reducing valve 8.3, the P-A channel of the first three-position four-way proportional reversing valve 6.1, and the third hydraulic control check valve 7.3 The A-B channel flows into the rodless cavity of the first prestressed hydraulic cylinder C5 and the second prestressed hydraulic cylinder C6, at the same time, the oil in the rod cavity of the first prestressed hydraulic cylinder C5 and the second prestressed hydraulic cylinder C6 passes through The B-A channel of the fourth hydraulic control check valve 7.4 and the B-T channel of the first three-position four-way proportional reversing valve 6.1 flow into the main oil return pipe, thereby driving the first prestressed hydraulic cylinder C5 and the second prestressed hydraulic cylinder C6. The piston rod moves upwards.

The fifth displacement sensor F5 is installed in the piston rod of the first prestressed hydraulic cylinder C5, and the position control accuracy of the piston of the first prestressed hydraulic cylinder C5 is composed of the fifth displacement sensor F5 and the first three-position four-way proportional reversing valve 6.1 Position closed loop to ensure; the P2 port of the first prestressed hydraulic cylinder C5 and the second prestressed hydraulic cylinder C6 is connected with the fifth pressure sensor 9.5, the working pressure of the first prestressed hydraulic cylinder C5 and the second prestressed hydraulic cylinder C6 The control accuracy is guaranteed by the pressure closed loop formed by the fifth pressure sensor 9.5 and the third proportional pressure reducing valve 8.3.

Similarly, the first operating side prestressed hydraulic device includes a second three-position four-way proportional reversing valve 6.2, a fifth hydraulic control check valve 7.5, a sixth hydraulic control check valve 7.6, and a fourth proportional pressure reducing valve. 8.4, the sixth pressure sensor 9.6, the third prestressed hydraulic cylinder C7, the fourth prestressed hydraulic cylinder C8, the sixth displacement sensor F6; the A port of the fourth proportional pressure reducing valve 8.4 is connected to the main pressure oil pipe P through the oil pipe Above, port B of the fourth proportional pressure reducing valve 8.4 is connected to port P of the second three-position four-way proportional reversing valve 6.2 through the oil pipe, port A of the fifth hydraulic control check valve 7.5 and the sixth hydraulic control check valve Port A of 7.6 is respectively connected to port A and port B of the second three-position four-way proportional reversing valve 6.2 through oil pipes, port B of the fifth hydraulic control check valve 7.5 and port B of the sixth hydraulic control check valve 7.6 They are respectively connected to the rod chamber and the rodless chamber of the third prestressed hydraulic cylinder C7 and the fourth prestressed hydraulic cylinder C8 through oil pipes, the Y port of the fifth hydraulic control check valve 7.5 and the port of the sixth hydraulic control check valve 7.6 The Y port is connected to the B port and the A port of the second three-position four-way proportional reversing valve 6.2 respectively through oil pipes, and the T port of the second three-position four-way proportional reversing valve 6.2 is connected with the main oil return pipe T.

During specific work, the proportional electromagnet Y3.2 is energized, and the oil passes through the A-B channel of the fourth proportional pressure reducing valve 8.4, the P-A channel of the second three-position four-way proportional reversing valve 6.2, and the fifth hydraulic control check valve 7.5 The A-B channel flows into the rodless cavity of the third prestressed hydraulic cylinder C7 and the fourth prestressed hydraulic cylinder C8, at the same time, the oil in the rod cavity of the third prestressed hydraulic cylinder C7 and the fourth prestressed hydraulic cylinder C8 passes through The B-A channel of the sixth hydraulic control check valve 7.6 and the B-T channel of the second three-position four-way proportional reversing valve 6.2 flow into the main oil return pipe, thereby driving the third prestressed hydraulic cylinder C7 and the fourth prestressed hydraulic cylinder C8 The piston rod moves upwards.

The sixth displacement sensor F6 is installed in the piston rod of the third prestressed hydraulic cylinder C7, and the position control accuracy of the piston of the third prestressed hydraulic cylinder C7 is composed of the sixth displacement sensor F6 and the second three-position four-way proportional reversing valve 6.2 Position closed loop to ensure; the P2 port of the third prestressed hydraulic cylinder C7 and the fourth prestressed hydraulic cylinder C8 is connected with the sixth pressure sensor 9.6, the working pressure of the third prestressed hydraulic cylinder C7 and the fourth prestressed hydraulic cylinder C8 The control accuracy is guaranteed by the pressure closed loop composed of the sixth pressure sensor 9.6 and the fourth proportional pressure reducing valve 8.4.

The coordinated control of the position closed-loop and pressure closed-loop of the prestressed hydraulic device on the first transmission side and the prestressed hydraulic device on the first operating side ensures the control accuracy of the roll balance hydraulic device.

The use of prestressed hydraulic devices to increase the rigidity of the cross wedge rolling mill frame greatly simplifies the equipment structure and reduces the manufacturing cost of the equipment. At the same time, it meets the situation that the rolling force value of the super large shaft type cross wedge rolling mill is relatively large. The required large prestressing requirements. By adjusting the prestress hydraulic cylinder, it can ensure that the prestress of the rolling mill stand is constant during the rolling process, and meet the rolling accuracy requirements of shaft workpieces of different specifications.

The above-mentioned embodiments are only to describe the preferred mode of the present invention, and are not intended to limit the scope of the present invention. Variations and improvements should fall within the scope of protection defined by the claims of the present invention.

Claims (2)

1. A hydraulic pressing system for a super-large axial cross-wedge rolling mill suitable for double-machine linkage, characterized in that it includes: the hydraulic pressing system of the first rolling mill, the hydraulic pressing system of the second rolling mill and a constant pressure oil source; A rolling mill hydraulic pressing system includes: the first rolling mill pressing device, the first rolling mill roll balance hydraulic device, the first rolling mill prestressing hydraulic device; the second rolling mill hydraulic pressing system includes the second rolling mill pressing device, the second rolling mill roll Balance hydraulic device, second rolling mill prestress hydraulic device; Among them, the first rolling mill depressing device and the second rolling mill depressing device form the depressing device, the first rolling mill roll balance hydraulic device and the second rolling mill roll balancing hydraulic device form the balancing device, the first rolling mill prestress hydraulic device and the first rolling mill The prestressing hydraulic device constitutes the prestressing device; the pressing device is distributed on the archway and the upper bearing seat, the balance device is distributed at both ends of the pressing device and connected with the balance beam, and the prestressing device is distributed on the upper bearing seat and the lower bearing seat Between; the constant pressure oil source is used to supply oil to the hydraulic pressing system of the first rolling mill and the hydraulic pressing system of the second rolling mill; The constant pressure oil source includes the first constant pressure oil source and the second constant pressure oil source, the first constant pressure oil source supplies oil to the first rolling mill hydraulic pressing system, and the second constant pressure oil source supplies oil to the second rolling mill hydraulic pressing system ;A first accumulator and a second accumulator are arranged at the oil outlets of the first constant pressure oil source and the second constant pressure oil source to absorb the hydraulic pressure in the first constant pressure oil source and the second constant pressure oil source The pressure and flow pulsation generated by the pump; one end of the first two-position two-way electromagnetic reversing valve is connected to the oil outlet of the first accumulator through the oil pipe, and the other end is connected to the main pressure oil pipe of the hydraulic pressing system of the first rolling mill through the oil pipe , the oil return port of the first accumulator is connected to the oil return tank through the oil pipe; one end of the second two-position two-way electromagnetic reversing valve is connected to the oil outlet of the second accumulator through the oil pipe, and the other end is connected to the second rolling mill through the oil pipe. The main pressure oil pipe of the hydraulic pressing system is connected, and the oil return port of the second accumulator is connected to the oil return tank through the oil pipe; The first rolling mill depressing device includes a first transmission side depressing device and a first operating side depressing device; the first rolling mill roll balance hydraulic device includes a first transmission side roll balance hydraulic device and a first operating side roll balance hydraulic device; A rolling mill prestressing hydraulic device includes a first transmission side prestressing hydraulic device and a first operation side prestressing hydraulic device; wherein, the first transmission side depressing device, the first operation side depressing device, the first transmission side roll balance hydraulic pressure The device, the first operating side roll balancing hydraulic device, the first transmission side prestressing hydraulic device, and the first operating side prestressing hydraulic device are respectively connected to the main pressure oil pipe and the main return oil pipe; The first transmission side depressing device and the first operating side depressing device adopt the combined throttling and speed regulating circuit of the cartridge valve controlled by the electromagnetic ball valve; The roll balance hydraulic device on the first transmission side and the roll balance hydraulic device on the first operation side adopt differential control, and can be switched between force control and position control; Coordinate the position closed-loop and pressure closed-loop control of the first drive-side pressing device and the first operating-side pressing device; coordinate the position closed-loop and pressure closed-loop control of the first transmission-side roll balance hydraulic device and the first operation-side roll balance hydraulic device Control: Coordinated control of the position closed-loop and pressure closed-loop of the prestressed hydraulic device on the first transmission side and the prestressed hydraulic device on the first operating side; A first proportional relief valve is connected in parallel on the oil pipe between the rodless cavity of the first transmission side depressing oil cylinder and the B port of the second cartridge valve; A second proportional relief valve is connected in parallel on the oil pipe between the rodless cavity of the first operating side depressing oil cylinder and the port B of the fourth cartridge valve. 2. the hydraulic pressure reduction system of the super-large shaft type cross wedge rolling mill applicable to double machine linkage as claimed in claim 1, it is characterized in that, the rolling mill power energy parameter of the hydraulic pressure reduction system of the first rolling mill is as follows: the normal rolling force is 3300KN, the maximum rolling force is 4950KN; the rolling mill force parameters of the hydraulic pressure reduction system of the second rolling mill are as follows: the normal rolling force is 3600KN, and the maximum rolling force is 5400KN.

Images