An open-type hydraulic pump-controlled motor-driven rotary forging press

Abstract

The present invention discloses an open-type hydraulic pump-controlled motor-driven rotary forging press, which mainly includes: gears, racks, retaining wheels, balance cylinders, sliders, guide rails, a main machine frame, and an electro-hydraulic system. The electro-hydraulic system further includes: an electro-hydraulic proportional variable hydraulic motor, a make-up oil check valve, a support safety valve, a support electro-hydraulic ball valve, a quick exhaust valve, a forging overflow valve, a back pressure overflow valve, a three-way electro-hydraulic directional valve, a two-way electro-hydraulic directional valve, a system check valve, an electro-hydraulic proportional variable pump, a system overflow valve, a two-way solenoid valve, an accumulator overflow valve, an accumulator bank, etc. The present invention proposes a hybrid drive mode of a press that combines open-type pump-controlled motor hydraulic drive and gear-rack mechanical drive, which not only realizes the high production efficiency of the press but also can complete the automatic stepless adjustment of process parameters such as forging force and forging speed, and has excellent process flexibility.

Description

Technical Field

[0001] The present invention relates to a press, in particular to a rotary forging press, and more particularly to an open-type hydraulic pump-controlled motor-driven rotary forging press. Background Art

[0002] Rotary forging is a relatively complex forging process, which has relatively high requirements for the flexible control of parameters such as the movement and force of the forming equipment - the press; at the same time, rotary forging is a hot forging process, which also has relatively high requirements for the working efficiency of the hydraulic press. Presses can be divided into hydraulic presses and mechanical presses according to the transmission method. The transmission mechanism of the hydraulic press has a large power-volume ratio and is easy to achieve linear transmission, stepless speed regulation, pressure regulation and maintenance, etc. However, the working efficiency of the hydraulic press is low, and the system of the high-speed hydraulic press is very complex; the mechanical press has a high working efficiency, but it cannot output a constant pressing force within a large stroke range, and the flexible adjustment of the parameters of the mechanical press and the performance of maintaining pressure for a long time also require a very complex structure and system to achieve. How to combine hydraulic transmission and mechanical transmission to develop a new hybrid drive mode with the advantages of both is one of the development directions in the field of press technology. Summary of the Invention

[0003] The purpose of the present invention is to provide an open-type hydraulic pump-controlled motor-driven rotary forging press, which combines the advantages of hydraulic transmission and mechanical transmission, not only has high working efficiency, but also is easy to achieve flexible adjustment of process parameters.

[0004] The technical solution of the present invention is as follows:

[0005] The present invention mainly includes; gears, racks, retaining wheels, balance cylinders, sliders, guide rails, main machine frames, electro-hydraulic systems, etc. The shaft of the gear is installed on the upper plane of the upper crossbeam of the main machine frame; the rack passes through the upper crossbeam of the main machine frame, and the lower end of the rack is fixedly installed on the upper plane of the slider; the gear meshes with the rack, and the slider can move up and down under the drive of the gear; the bearing of the retaining wheel is fixedly installed on the upper plane of the upper crossbeam of the main machine frame, and the cylindrical surface of the retaining wheel forms a friction pair with the plane of the rack, and the retaining wheel is used to balance the lateral force received by the rack; the cylinder body of the balance cylinder is fixedly installed on the upper crossbeam of the main machine frame, and the piston rod of the balance cylinder is fixedly installed on both side brackets of the slider, and the balance cylinder is used to balance the gravity of the slider assembly; the slider is placed in the inner cavity of the main machine frame; the guide rails are fixedly installed on the left and right columns of the main machine frame, and the guide rails and the guide plates of the slider form a plane friction pair, and the guide rails play a role of guiding and supporting the slider; the main machine frame is a closed frame with a certain stiffness; the electro-hydraulic system is mainly used to drive and control the movement of the gear and the balance cylinder.

[0006] Furthermore, the electro-hydraulic system of the present invention further includes: an electro-hydraulic proportional variable hydraulic motor, a make-up oil check valve, a support safety valve, a support electro-hydraulic ball valve, a quick exhaust valve, a pressing overflow valve, a back pressure overflow valve, a three-way electro-hydraulic directional valve, a two-way electro-hydraulic directional valve, a system check valve, an electro-hydraulic proportional variable pump, a system overflow valve, a two-way solenoid valve, an accumulator overflow valve, an accumulator bank, etc. The output shaft of the electro-hydraulic proportional variable hydraulic motor is coaxially connected to the gear; the forward rotation inlet A of the electro-hydraulic proportional variable hydraulic motor is communicated with the outlet of the make-up oil check valve, the inlet of the pressing overflow valve, and the A port of the three-way electro-hydraulic directional valve; the reverse rotation inlet B of the electro-hydraulic proportional variable hydraulic motor is communicated with the inlet of the support safety valve and the A port of the support electro-hydraulic ball valve; the P port of the support electro-hydraulic ball valve is communicated with the A port of the quick exhaust valve, the inlet of the back pressure overflow valve, and the A port of the two-way electro-hydraulic directional valve; the outlet of the system check valve is communicated with the P port of the three-way electro-hydraulic directional valve, the P port of the two-way electro-hydraulic directional valve, the inlet of the system overflow valve, and the P port of the two-way solenoid valve; the outlet of the electro-hydraulic proportional variable pump is communicated with the inlet of the system check valve; the A port of the two-way solenoid valve is communicated with the inlet of the accumulator overflow valve, the oil port of the accumulator bank, and the rod chamber of the balance cylinder; the rodless chamber of the balance cylinder is communicated with the atmosphere; the inlet of the make-up oil check valve, the outlet of the support safety valve, the outlet of the quick exhaust valve, the outlet of the pressing overflow valve, the outlet of the back pressure overflow valve, the T port of the three-way electro-hydraulic directional valve, the suction port of the electro-hydraulic proportional variable pump, the outlet of the system overflow valve, and the outlet of the accumulator overflow valve are communicated with the hydraulic oil tank.

[0007] The beneficial effects of the present invention are as follows:

[0008] 1. The present invention combines the open-loop pump-controlled motor hydraulic drive with the gear-rack mechanical drive, realizing the hybrid drive of the rotary swaging press, capable of completing high-frequency strokes, and the process parameters of the press are easy to be flexibly adjusted.

[0009] 2. The hydraulic drive part of the present invention is an open-loop pump-controlled motor, adopting the form of an electro-hydraulic proportional variable pump matching an electro-hydraulic proportional variable hydraulic motor, with a wide pressing speed adjustment range and various matching forms of pressing force and pressing speed.

[0010] 3. The present invention is equipped with a balance cylinder for balancing the weight of the balance slider assembly, realizing the recycling and reuse of energy, reducing the useless power consumption, and the press runs smoothly with little impact during operation; further cooperating with the hydraulic pump and motor with adjustable displacement, the press has flexible energy consumption management. BRIEF DESCRIPTION OF THE DRAWINGS

[0011] Figure 1 is a structural schematic diagram of the present invention.

[0012] Figure 2 is a hydraulic schematic diagram of the present invention.

[0013] Figure 1In: 1 - gear, 2 - rack, 3 - retaining wheel, 4 - balance cylinder, 5 - slider, 6 - guide rail, 7 - mainframe.

[0014] Figure 2 In: 1 - gear, 4 - balance cylinder, 801 - electro-hydraulic proportional variable hydraulic motor, 802 - make-up check valve, 803 - support safety valve, 804 - support electro-hydraulic ball valve, 805 - quick exhaust valve, 806 - pressing overflow valve, 807 - back pressure overflow valve, 808 - three-way electro-hydraulic directional valve, 809 - two-way electro-hydraulic directional valve, 810 - system check valve, 811 - electro-hydraulic proportional variable pump, 812 - system overflow valve, 813 - two-way solenoid valve, 814 - accumulator overflow valve, 815 - accumulator bank. Detailed implementation mode

[0015] The present invention will be further described below in conjunction with the accompanying drawings.

[0016] See Figure 1 , the present invention includes; gear 1, rack 2, retaining wheel 3, balance cylinder 4, slider 5, guide rail 6, mainframe 7, electro-hydraulic system 8, etc. The shaft of gear 1 is installed on the upper plane of the upper crossbeam of mainframe 7; rack 2 passes through the upper crossbeam of mainframe 7, and the lower end of rack 2 is fixedly installed on the upper plane of slider 5; gear 1 meshes with rack 2, and slider 5 can move up and down driven by gear 1; the bearing of retaining wheel 3 is fixedly installed on the upper plane of the upper crossbeam of mainframe 7, and the cylindrical surface of retaining wheel 3 and the plane of rack 2 form a friction pair, and retaining wheel 3 is used to balance the lateral force received by rack 2; the cylinder body of balance cylinder 4 is fixedly installed on the upper crossbeam of mainframe 7, and the piston rod of balance cylinder 4 is fixedly installed on both side brackets of slider 5, and balance cylinder 4 is used to balance the gravity of the slider 5 assembly; slider 5 is placed in the inner compartment of mainframe 7; guide rail 6 is fixedly installed on the left and right columns of mainframe 7, and guide rail 6 and the guide plate of slider 5 form a plane friction pair, and guide rail 6 plays a guiding and supporting role for slider 5; mainframe 7 is a closed frame with a certain rigidity; electro-hydraulic system 8 is mainly used to drive and control the movement of gear 1 and balance cylinder 4.

[0017] See Figure 2, the electro-hydraulic system 8 of the present invention mainly includes: an electro-hydraulic proportional variable hydraulic motor 801, a make-up oil check valve 802, a support safety valve 803, a support electro-hydraulic ball valve 804, a quick exhaust valve 805, a pressing overflow valve 806, a back pressure overflow valve 807, a three-way electro-hydraulic directional valve 808, a two-way electro-hydraulic directional valve 809, a system check valve 810, an electro-hydraulic proportional variable pump 811, a system overflow valve 812, a two-way solenoid valve 813, an accumulator overflow valve 814, an accumulator bank 815, etc. The output shaft of the electro-hydraulic proportional variable hydraulic motor 801 is coaxially connected to the gear 1; the forward rotation inlet A of the electro-hydraulic proportional variable hydraulic motor 801 is communicated with the outlet of the make-up oil check valve 802, the inlet of the pressing overflow valve 806, and the A port of the three-way electro-hydraulic directional valve 808; the reverse rotation inlet B of the electro-hydraulic proportional variable hydraulic motor 801 is communicated with the inlet of the support safety valve 803 and the A port of the support electro-hydraulic ball valve 804; the P port of the support electro-hydraulic ball valve 804 is communicated with the A port of the quick exhaust valve 805, the inlet of the back pressure overflow valve 807, and the A port of the two-way electro-hydraulic directional valve 809; the outlet of the system check valve 810 is communicated with the P port of the three-way electro-hydraulic directional valve 808, the P port of the two-way electro-hydraulic directional valve 809, the inlet of the system overflow valve 812, and the P port of the two-way solenoid valve 813; the outlet of the electro-hydraulic proportional variable pump 811 is communicated with the inlet of the system check valve 810; the A port of the two-way solenoid valve 813 is communicated with the inlet of the accumulator overflow valve 814, the oil port of the accumulator bank 815, and the rod chamber of the balance cylinder 4; the rodless chamber of the balance cylinder 4 is communicated with the atmosphere; the inlet of the make-up oil check valve 802, the outlet of the support safety valve 803, the outlet of the quick exhaust valve 805, the outlet of the pressing overflow valve 806, the outlet of the back pressure overflow valve 807, the T port of the three-way electro-hydraulic directional valve 808, the suction port of the electro-hydraulic proportional variable pump 811, the outlet of the system overflow valve 812, and the outlet of the accumulator overflow valve 814 are communicated with the hydraulic oil tank.

[0018] In practical applications, the press is driven in parallel by multiple sets of the gear 1 and the rack 2 of the present invention to meet the requirements such as tonnage and structural matching. Correspondingly, the number of the electro-hydraulic proportional variable hydraulic motors 801 configured is the same as that of the gear 1 and the rack 2. The number of the electro-hydraulic proportional variable pumps 811 and the accumulator bank 815 is designed and configured according to the technical specifications of the press.

[0019] Next, the working principle of the present invention will be described by taking a single working cycle of the press as an example:

[0020] 1. The slider of the press moves down quickly

[0021] At this stage, the supporting electro-hydraulic ball valve 804 and the three-way electro-hydraulic directional valve 808 are in the energized state, the two-way electro-hydraulic directional valve 809 and the two-way solenoid valve 813 are in the de-energized state, the electro-hydraulic proportional variable hydraulic motor 801 is set to a small displacement, and the electro-hydraulic proportional variable pump 811 is set to a full displacement; the opening of the quick exhaust valve 805 gradually increases to a certain set value according to the required quick down speed. Under the action of gravity, the press slide block 5 accelerates downward, the rack 2 drives the gear 1 to rotate, thereby driving the coaxial electro-hydraulic proportional variable hydraulic motor 801 to rotate forward. The oil discharged from the reverse oil inlet B of the electro-hydraulic proportional variable hydraulic motor 801 flows back to the oil tank through the supporting electro-hydraulic ball valve 804 and the quick exhaust valve 805 and forms a back pressure at the valve orifice of the quick exhaust valve 805. As the downward speed of the press slide block 5 increases, the back pressure at the valve orifice of the quick exhaust valve 805 rises. When the back pressure reaches a certain value, the press slide block 5 is in force balance and begins to move downward at a constant speed; when the press slide block 5 moves quickly downward, the hydraulic oil output by the electro-hydraulic proportional variable pump 811 enters the forward oil inlet A of the electro-hydraulic proportional variable hydraulic motor 801 through the three-way electro-hydraulic directional valve 808. If the flow rate of the hydraulic oil output by the electro-hydraulic proportional variable pump 811 is not sufficient to fill the rotation requirement of the variable hydraulic motor 801, a negative pressure will be formed at the forward oil inlet A of the electro-hydraulic proportional variable hydraulic motor 801. At this time, the hydraulic oil is sucked into the forward oil inlet A of the electro-hydraulic proportional variable hydraulic motor 801 from the hydraulic oil tank through the oil replenishing check valve 802.

[0022] 2. Quick down of the press slide block to working feed

[0023] At this stage, the supporting electro-hydraulic ball valve 804 and the three-way electro-hydraulic directional valve 808 are in the energized state, the two-way electro-hydraulic directional valve 809 and the two-way solenoid valve 813 are in the de-energized state; the displacement of the electro-hydraulic proportional variable hydraulic motor 801 gradually increases, the opening of the quick exhaust valve 805 gradually decreases, and the back pressure at the valve orifice of the quick exhaust valve 805 gradually increases. Thus, the press slide block 5 decelerates. When the downward speed of the press slide block 5 decreases to the working feed speed, the quick exhaust valve 805 closes; the hydraulic oil output by the electro-hydraulic proportional variable pump 811 enters the forward oil inlet A of the electro-hydraulic proportional variable hydraulic motor 801 through the three-way electro-hydraulic directional valve 808. The electro-hydraulic proportional variable hydraulic motor 801 rotates forward under the drive of the flow rate output by the electro-hydraulic proportional variable pump 811; the oil discharged from the reverse oil inlet B of the electro-hydraulic proportional variable hydraulic motor 801 flows back to the oil tank through the supporting electro-hydraulic ball valve 804 and the back pressure overflow valve 807. Under the regulating action of the back pressure overflow valve 807, the pressure at the reverse oil inlet B of the electro-hydraulic proportional variable hydraulic motor 801 is stable; the working feed speed regulation of the press slide block 5 is achieved by adjusting the displacements of the electro-hydraulic proportional variable hydraulic motor 801 and the electro-hydraulic proportional variable pump 811, and constant speed control or constant power control, etc. can be carried out according to actual process requirements.

[0024] 3. Pressure holding

[0025] When the pressing force reaches the set value, pressure holding control can be carried out. At this stage, the supporting electro-hydraulic ball valve 804 and the three-way electro-hydraulic directional valve 808 are in the energized state, the two-way electro-hydraulic directional valve 809 and the two-way solenoid valve 813 are in the de-energized state, and the quick exhaust valve 805 is in the closed state; the displacement of the electro-hydraulic proportional variable hydraulic motor 801 remains constant, and the pressure at the positive rotation inlet A of the electro-hydraulic proportional variable hydraulic motor 801 is closed-loop controlled by the electro-hydraulic proportional variable pump 811, and the pressure holding time is set according to the process requirements.

[0026] 4. Pressure relief

[0027] When the pressure holding time reaches the set value, at this stage, the three-way electro-hydraulic directional valve 808 is in the energized state, the supporting electro-hydraulic ball valve 804, the two-way electro-hydraulic directional valve 809, and the two-way solenoid valve 813 are in the de-energized state, and the quick exhaust valve 805 is in the closed state; the displacement of the electro-hydraulic proportional variable hydraulic motor 801 remains constant, and under the closed-loop control of the electro-hydraulic proportional variable pump 811, the pressure at the positive rotation inlet A of the electro-hydraulic proportional variable hydraulic motor 801 decreases according to the preset law until it reaches zero.

[0028] 5. Return stroke of the press slide

[0029] After the pressure relief is completed, the two-way electro-hydraulic directional valve 809 is in the energized state, the supporting electro-hydraulic ball valve 804, the three-way electro-hydraulic directional valve 808, and the two-way solenoid valve 813 are in the de-energized state, and the quick exhaust valve 805 is in the closed state; the displacements of the electro-hydraulic proportional variable hydraulic motor 801 and the electro-hydraulic proportional variable pump 811 are matched and adjusted to meet the return speed requirement of the press slide 5. The hydraulic oil output by the electro-hydraulic proportional variable pump 811 enters the reverse rotation inlet B of the electro-hydraulic proportional variable hydraulic motor 801 through the two-way electro-hydraulic directional valve 809 and the supporting electro-hydraulic ball valve 804. The electro-hydraulic proportional variable hydraulic motor 801 rotates in reverse under the drive of the flow rate output by the electro-hydraulic proportional variable pump 811, and the hydraulic oil discharged from the positive rotation inlet A of the electro-hydraulic proportional variable hydraulic motor 801 flows back to the oil tank through the three-way electro-hydraulic directional valve 808; the gear 1 rotates in reverse coaxially with the electro-hydraulic proportional variable hydraulic motor 801, and the press slide 5 is lifted upward through the rack 2.

[0030] During the operation of the press slide 5, part of the gravity of the slide 5 assembly is always offset by the force output by the balance cylinder 4; when the slide 5 moves downward, the hydraulic oil in the rodless cavity of the balance cylinder 4 enters the accumulator group 815, and the pressure in the accumulator group 815 increases, and the gravitational potential energy is converted into hydraulic energy; when the slide 5 moves upward, the hydraulic oil in the accumulator group 815 enters the rodless cavity of the balance cylinder 4, and the pressure in the accumulator group 815 decreases, and the hydraulic energy is converted into gravitational potential energy. Because the leakage of the hydraulic system is inevitable, the pressure in the accumulator group 815 will decrease after long-term use. Energizing the two-way solenoid valve 813 can replenish the pressure of the accumulator group 815.

Claims

1. An open-type hydraulic pump-controlled motor-driven rotary forging press, Characterized in that: It mainly includes: a gear (1), a rack (2), a retaining wheel (3), a balance cylinder (4), a slider (5), a guide rail (6), a mainframe frame (7), and an electro-hydraulic system (8). The shaft of the gear (1) is installed on the upper plane of the upper crossbeam of the mainframe frame (7); the rack (2) passes through the upper crossbeam of the mainframe frame (7), and the lower end of the rack (2) is fixedly installed on the upper plane of the slider (5); the gear (1) meshes with the rack (2), and the slider (5) moves up and down driven by the gear (1); the bearing of the retaining wheel (3) is fixedly installed on the upper plane of the upper crossbeam of the mainframe frame (7), and the cylindrical surface of the retaining wheel (3) forms a friction pair with the plane of the rack (2); the cylinder body of the balance cylinder (4) is fixedly installed on the upper crossbeam of the mainframe frame (7), and the piston rod of the balance cylinder (4) is fixedly installed on the two side brackets of the slider (5); the slider (5) is placed inside the mainframe frame (7); the guide rail (6) is fixedly installed on the left and right columns of the mainframe frame (7), and the guide rail (6) forms a plane friction pair with the guide plate of the slider (5); the mainframe frame (7) is a closed frame; the electro-hydraulic system (8) drives and controls the gear (1) and the balance cylinder (4); the electro-hydraulic system (8) also includes: an electro-hydraulic proportional variable hydraulic motor (801), a make-up oil check valve (802), a support safety valve (803), a support electro-hydraulic ball valve (804), a quick exhaust valve (805), a pressing overflow valve (806), a back pressure overflow valve (807), a three-way electro-hydraulic directional valve (808), a two-way electro-hydraulic directional valve (809), a system check valve (810), an electro-hydraulic proportional variable pump (811), a system overflow valve (812), a two-way solenoid valve (813), an accumulator overflow valve (814), and an accumulator bank (815); the output shaft of the electro-hydraulic proportional variable hydraulic motor (801) is coaxially connected to the gear (1); the forward rotation inlet A of the electro-hydraulic proportional variable hydraulic motor (801) is communicated with the outlet of the make-up oil check valve (802), the inlet of the pressing overflow valve (806), and the A port of the three-way electro-hydraulic directional valve (808); the reverse rotation inlet B of the electro-hydraulic proportional variable hydraulic motor (801) is communicated with the inlet of the support safety valve (803) and the A port of the support electro-hydraulic ball valve (804); the P port of the support electro-hydraulic ball valve (804) is communicated with the A port of the quick exhaust valve (805), the inlet of the back pressure overflow valve (807), and the A port of the two-way electro-hydraulic directional valve (809); the outlet of the system check valve (810) is communicated with the P port of the three-way electro-hydraulic directional valve (808), the P port of the two-way electro-hydraulic directional valve (809), the inlet of the system overflow valve (812), and the P port of the two-way solenoid valve (813); the outlet of the electro-hydraulic proportional variable pump (811) is communicated with the inlet of the system check valve (810); the A port of the two-way solenoid valve (813) is communicated with the inlet of the accumulator overflow valve (814), the oil port of the accumulator bank (815), and the rodless cavity of the balance cylinder (4); the rodless cavity of the balance cylinder (4) is communicated with the atmosphere;The oil inlet of the oil replenishing check valve (802), the oil outlet of the support safety valve (803), the oil outlet of the quick exhaust valve (805), the oil outlet of the pressing overflow valve (806), the oil outlet of the back pressure overflow valve (807), the T port of the three-position electro-hydraulic directional valve (808), the oil suction port of the electro-hydraulic proportional variable pump (811), the oil outlet of the system overflow valve (812), and the oil outlet of the accumulator overflow valve (814) are communicated with the hydraulic oil tank; the said retaining wheel (3) is used to balance the lateral force received by the rack (2); the said balance cylinder (4) is used to balance the gravity of the slider (5) assembly; the said guide rail (6) plays a role of guiding and supporting the slider (5).; 2. The open-type hydraulic pump-controlled motor-driven rotary forging press according to claim 1, Characterized in that: The main machine frame (7) is a closed frame with a certain rigidity.

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