CN109773639B - Descaling hydraulic device for forging - Google Patents
Descaling hydraulic device for forging Download PDFInfo
- Publication number
- CN109773639B CN109773639B CN201910126075.7A CN201910126075A CN109773639B CN 109773639 B CN109773639 B CN 109773639B CN 201910126075 A CN201910126075 A CN 201910126075A CN 109773639 B CN109773639 B CN 109773639B
- Authority
- CN
- China
- Prior art keywords
- valve
- main
- port
- hydraulic
- oil
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000005242 forging Methods 0.000 title claims abstract description 45
- 229910000831 Steel Inorganic materials 0.000 claims abstract description 53
- 239000010959 steel Substances 0.000 claims abstract description 53
- 230000004044 response Effects 0.000 claims description 26
- 230000005540 biological transmission Effects 0.000 claims description 6
- 238000006073 displacement reaction Methods 0.000 claims description 3
- 238000000034 method Methods 0.000 abstract description 6
- 239000002699 waste material Substances 0.000 abstract description 5
- 238000003912 environmental pollution Methods 0.000 abstract description 2
- 238000004519 manufacturing process Methods 0.000 abstract description 2
- 239000003921 oil Substances 0.000 description 241
- 230000008878 coupling Effects 0.000 description 9
- 238000010168 coupling process Methods 0.000 description 9
- 238000005859 coupling reaction Methods 0.000 description 9
- 239000002585 base Substances 0.000 description 8
- 230000006872 improvement Effects 0.000 description 8
- 230000008569 process Effects 0.000 description 4
- 102100037573 Dual specificity protein phosphatase 12 Human genes 0.000 description 3
- 101000881110 Homo sapiens Dual specificity protein phosphatase 12 Proteins 0.000 description 3
- 239000002253 acid Substances 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 239000010720 hydraulic oil Substances 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
- 238000005406 washing Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 239000003513 alkali Substances 0.000 description 1
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 1
- 239000011449 brick Substances 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 229910052760 oxygen Inorganic materials 0.000 description 1
- 239000001301 oxygen Substances 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Images
Landscapes
- Fluid-Pressure Circuits (AREA)
Abstract
The invention belongs to the field of descaling of forging blanks, and particularly relates to a descaling hydraulic device for forging. The hydraulic cylinder device comprises a mechanical part and a hydraulic part, wherein the mechanical part comprises a base, walking steel wheels rotatably arranged at four corners of the bottom of the base, a hydraulic cylinder bracket and a support frame arranged on the upper surface of the base, and an encoder is arranged on each walking steel wheel; the hydraulic part comprises a main system, a first driving system, a second driving system, a third driving system and a fourth driving system, wherein the first driving system, the second driving system, the third driving system and the fourth driving system are identical in structure. The descaling device for forging improves the production efficiency, reduces the labor intensity, avoids resource waste and environmental pollution, and simultaneously improves the automation degree of forging equipment. The method is simple and feasible, is easy to realize, and has certain guiding significance for upgrading and reconstructing other forging equipment.
Description
Technical Field
The invention belongs to the field of descaling of forging blanks, and particularly relates to a descaling hydraulic device for forging.
Background
In the forging process, a layer of oxide skin is generated when the heated forging blank is contacted with oxygen in the air, and if the oxide skin is not removed in time, pits and pits appear on the surface of the forging piece, and even the surface of the forging piece is embedded into the steel billet, so that the quality of the forging piece is adversely affected, and even the forging piece becomes a waste product; the oxide skin has higher hardness, so that not only is the deformation energy consumption increased during forging, but also the abrasion of the forging die is accelerated, and the service life is reduced; the oxide skin has chemical corrosion effect on the refractory bricks during secondary heating, so that the furnace bottom of the heating furnace is damaged too early. Therefore, the scale on the surface of the workpiece needs to be removed in time during the forging process. The existing technology for removing the oxide skin mainly uses acid (alkali) washing, manual work or high-pressure water, and the use of acid washing has influence on the environment; the efficiency of manually removing the oxide skin is low, and an operator needs to wear the thermal insulation suit to work in a high-temperature environment for a long time; the removal by high pressure water reduces the initial forging temperature and affects the quality of the finished product.
Disclosure of Invention
The invention aims to provide a descaling hydraulic device for forging, which can effectively overcome the defects in the prior art.
The invention is realized by the following technical scheme: a descaling hydraulic device for forging comprises a mechanical part and a hydraulic part,
the mechanical part comprises a base, walking steel wheels rotatably arranged at four corners of the bottom of the base, a hydraulic cylinder support and a support frame, wherein the hydraulic cylinder support and the support frame are arranged on the upper surface of the base;
the hydraulic part comprises a main system, a first driving system, a second driving system, a third driving system and a fourth driving system, and the first driving system, the second driving system, the third driving system and the fourth driving system have the same structure;
the main system comprises a main pressure reducing valve of which a port B is connected to a main pressure oil pipe, wherein a port A of the main pressure reducing valve is connected to a port P of a high-frequency response proportional servo valve with pressure difference compensation through an oil pipe;
the first driving system comprises a first pressure reducing valve of which a port B is connected to a main pressure oil pipe, a port A of the first pressure reducing valve is connected to a port P of a first M-type three-position four-way electromagnetic reversing valve through an oil pipe, a port A of the first M-type three-position four-way electromagnetic reversing valve is connected to a working oil cavity of a first five-star hydraulic motor through an oil pipe, a first pressure sensor is installed on the working oil cavity of the first five-star hydraulic motor, an oil discharge cavity of the first five-star hydraulic motor is connected to the port B of the first M-type three-position four-way electromagnetic reversing valve through an oil pipe, a port T of the first M-type three-position four-way electromagnetic reversing valve is connected to a main oil return pipe through an oil pipe, the main oil return pipe is connected to the port A of the first check one-way valve in parallel through an oil pipe, the port B of the first check one-way valve is connected to a working cavity of a first hydraulic brake through an oil pipe, and the end part of a piston rod of, the port B of the first check one-way valve is connected in parallel to the port A of the first two-position two-way electromagnetic directional valve through an oil pipe, the port B of the first two-position two-way electromagnetic directional valve is connected to the main oil return pipe through an oil pipe, and a transmission shaft of the first five-star hydraulic motor is coaxially connected with the first traveling steel wheel.
As a further improvement of the technical scheme of the invention, a second main hydraulic control one-way valve and a third main hydraulic control one-way valve are respectively connected in series between the port A and the port B of the high-frequency response proportional servo valve with the pressure difference compensation and the main hydraulic cylinder, Y ports of the second main hydraulic control one-way valve and the third main hydraulic control one-way valve are connected to a leakage oil pipe, X ports of the second main hydraulic control one-way valve and the third main hydraulic control one-way valve are jointly connected to the port A of the main electromagnetic ball valve, a port P of the main electromagnetic ball valve is connected to a control oil pipe, and a port T of the main electromagnetic ball valve is connected to a main oil return pipe.
As a further improvement of the technical scheme of the invention, a first main hydraulic control one-way valve is connected in series between the port A of the main pressure reducing valve and the port P of the high-frequency response proportional servo valve with pressure difference compensation, the port Y of the first main hydraulic control one-way valve is connected to a leakage oil pipe, and the port X of the first main hydraulic control one-way valve is connected to the port A of the main electromagnetic ball valve.
As a further improvement of the technical scheme of the invention, a main direct-acting overflow valve is connected in parallel between an oil outlet of the second main hydraulic control one-way valve and a rodless cavity of the main hydraulic cylinder, and a T port of the main direct-acting overflow valve is connected to a main oil return pipe.
As a further improvement of the technical scheme of the invention, a main check valve is connected in series between a T port of the high-frequency response proportional servo valve with the pressure difference compensation and a main oil return pipe.
As a further improvement of the technical scheme of the invention, a first hydraulic control one-way valve and a second hydraulic control one-way valve are respectively connected in series on an oil pipe between the first M-type three-position four-way electromagnetic directional valve and the first five-star hydraulic motor, Y ports of the first hydraulic control one-way valve and the second hydraulic control one-way valve are connected to a leakage oil pipe, X ports of the first hydraulic control one-way valve and the second hydraulic control one-way valve are connected to an a port of the first electromagnetic ball valve, a P port of the first electromagnetic ball valve is connected to a control oil pipe, and a T port of the first electromagnetic ball valve is connected to a main oil return pipe.
As a further improvement of the technical scheme of the invention, a first proportional flow valve is connected in series on an oil pipe between the first hydraulic control one-way valve and a working oil cavity of the first five-star hydraulic motor, and a second proportional flow valve is connected in series between the working cavity of the first hydraulic brake and a port B of the first check one-way valve.
As a further improvement of the technical scheme of the invention, a first direct overflow valve is connected in parallel to an oil pipe between the first proportional flow valve and a working oil cavity of the first five-star hydraulic motor, and a T port of the first direct overflow valve is connected to a main oil return pipe.
As a further improvement of the technical scheme of the invention, a first oil return one-way valve is connected in series between a T port of the first M-shaped three-position four-way electromagnetic directional valve and a main oil return pipe.
The invention has the advantages and positive effects that:
1. the descaling device for forging improves the production efficiency, reduces the labor intensity, avoids resource waste and environmental pollution, and simultaneously improves the automation degree of the forging equipment.
2. The method is simple and feasible, is easy to realize, and has certain guiding significance for upgrading and reconstructing other forging equipment.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
Fig. 1 is a schematic view of the arrangement position of the present invention.
FIG. 2 is a schematic view of the descaling mechanism for forging according to the present invention.
FIG. 3 is a schematic diagram of a hydraulic system of the descaling device for forging of the present invention.
In the figure: YVH1, YVH 2.1.1, YVH 2.2.2, YVH 2.3.3, YVH 2.4.4, YVH 3.1.1, YVH 3.2.2, YVH 3.3.3, YVH 3.4.4, YVH 4.1.1, YVH 4.2.2, YVH 4.3.3, YVH 4.4.4, YVH 5.1.1, YVH 5.2.2, YVH 5.3.3, YVH 5.4.4-electromagnets, YB1, YB2, YB3, YB4, YB5, YB6, YB7, YB8, YB9, YB 10-proportional electromagnets, 1-main pressure reducing valve, 2.1-first main check valve, 2.2-second main check valve, 2.3-third main check valve, 3-high frequency response proportional servo valve with pressure difference compensation, 4-main check valve, 5-main pressure reducing valve, 6-main pressure reducing valve, 2.9-second main check valve, 10-second main pressure reducing valve, 10-second electromagnetic directional pressure reducing valve, 10.9-second electromagnetic directional pressure reducing valve, 10-second electromagnetic directional pressure reducing valve, two-third main pressure reducing valve, two-position electromagnetic directional pressure reducing valve, electromagnetic directional valve, 10.3-a third two-position two-way electromagnetic directional valve, 10.4-a fourth two-position two-way electromagnetic directional valve, 11.1-a first electromagnetic ball valve, 11.2-a second electromagnetic ball valve, 11.3-a third electromagnetic ball valve, 11.4-a fourth electromagnetic ball valve, 12.1-a first M-type three-position four-way electromagnetic directional valve, 12.2-a second M-type three-position four-way electromagnetic directional valve, 12.3-a third M-type three-position four-way electromagnetic directional valve, 12.4-a fourth M-type three-position four-way electromagnetic directional valve, 13.1-a first pilot operated check valve, 13.2-a second pilot operated check valve, 13.3-a third pilot operated check valve, 13.4-a fourth pilot operated check valve, 13.5-a fifth pilot operated check valve, 13.6-a sixth pilot operated check valve, 13.7-a seventh pilot operated check valve, 13.8-an eighth pilot operated check valve, 14.1-a first proportional flow valve, 14.2-a second proportional flow valve, 14.3-a third proportional flow valve, 14.4-a fourth proportional flow valve, 14.5-a fifth proportional flow valve, 14.6-a sixth proportional flow valve, 14.7-a seventh proportional flow valve, 14.8-an eighth proportional flow valve, 15.1-a first direct-acting overflow valve, 15.2-a second direct-acting overflow valve, 15.3-a third direct-acting overflow valve, 15.4-a fourth direct-acting overflow valve, 16.1-a fifth-star hydraulic motor, 16.2-a second five-star hydraulic motor, 16.3-a third five-star hydraulic motor, 16.4-a fourth five-star hydraulic motor, 17.1-a first traveling steel wheel, 17.2-a second traveling steel wheel, 17.3-a third traveling steel wheel, 17.4-a fourth traveling steel wheel, 18.1-a first encoder, 18.2-a second encoder, 18.3-a third encoder, 18.4-a fourth encoder, 19.1-a first hydraulic brake, 19.2-a second hydraulic brake, 19.3-a third hydraulic brake, 19.4-a fourth hydraulic brake, 20.1-a first oil return check valve, 20.2-a second oil return check valve, 20.3-a third oil return check valve, 20.4-a fourth oil return check valve, 21.1-a first check valve, 21.2-a second check valve, 21.3-a third check valve, 21.4-a fourth check valve, 22.1-a first pressure sensor, 22.2-a second pressure sensor, 22.3-a third pressure sensor, 22.4-a fourth pressure sensor, P-main pressure oil pipe, T-main oil return pipe, X-control oil pipe, Y-leakage oil pipe, 23-base, 24-hydraulic cylinder bracket, 25-support frame, 26-a first pin, 27-second pin, 28-rocker, 29-bearing block, 30-bearing, 31-fourth pin, 32-third pin, 33-wire brush, 34-forged blank, 35-left manipulator, 36-right manipulator, 37-upper hammer, 38-lower anvil block, 39-running rail.
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 described in detail below. It is to be understood that the described embodiments are merely exemplary of the invention, and not restrictive of the full scope of the invention. All other embodiments, which can be derived by a person skilled in the art from the examples given herein without any inventive step, are within the scope of the present invention.
The technical solution of the present invention will be described in detail below with reference to the accompanying drawings.
A descaling hydraulic device for forging comprises a mechanical part and a hydraulic part,
the mechanical part comprises a base 23, walking steel wheels rotatably mounted at four corners of the bottom of the base 23, a hydraulic cylinder support 24 and a support frame 25 which are arranged on the upper surface of the base 23, the top of the hydraulic cylinder support 24 is rotatably mounted on a cylinder body of the main hydraulic cylinder 7 through a first pin shaft 26, the piston end of the main hydraulic cylinder 7 is rotatably connected with one end of a rocker arm 28 through a second pin shaft 27, two bearing seats 29 are oppositely mounted on the support frame 25, a bearing 30 is respectively mounted on each of the two bearing seats 29, a fourth pin shaft 31 penetrates between the inner circles of the two bearings 30, the end part of the rocker arm 28 close to the second pin shaft 27 penetrates through the fourth pin shaft 31 and is positioned between the two bearings 30, a steel brush 33 is fixedly mounted at the other end of the rocker arm 28 through a third pin shaft 32, and an encoder is mounted on each walking.
The hydraulic part comprises a main system, a first driving system, a second driving system, a third driving system and a fourth driving system, wherein the first driving system, the second driving system, the third driving system and the fourth driving system are identical in structure.
The main system comprises a main pressure reducing valve 1 with a port B connected to a main pressure oil pipe P, the port A of the main pressure reducing valve 1 is connected to the port P of a high-frequency response proportional servo valve 3 with pressure difference compensation through an oil pipe, the port A of the high-frequency response proportional servo valve 3 with pressure difference compensation is connected to a rodless cavity of a main hydraulic cylinder 7 through an oil pipe, a built-in magnetostrictive displacement sensor 8 is installed on the main hydraulic cylinder 7, a rod cavity of the main hydraulic cylinder 7 is connected to the port B of the high-frequency response proportional servo valve 3 with pressure difference compensation through an oil pipe, and a port T of the high-frequency response proportional servo valve 3 with pressure difference compensation is connected to a main oil return pipe T through an oil pipe.
The first driving system comprises a first reducing valve 9.1 of which a port B is connected to a main pressure oil pipe P, the port A of the first reducing valve 9.1 is connected to the port P of a first M-type three-position four-way electromagnetic reversing valve 12.1 through an oil pipe, the port A of the first M-type three-position four-way electromagnetic reversing valve 12.1 is connected to a working oil cavity of a first five-star hydraulic motor 16.1 through an oil pipe, a first pressure sensor 22.1 is installed on the working oil cavity of the first five-star hydraulic motor 16.1, an oil discharge cavity of the first five-star hydraulic motor 16.1 is connected to the port B of the first M-type three-position four-way electromagnetic reversing valve 12.1 through an oil pipe, a port T of the first M-type three-position four-way electromagnetic reversing valve 12.1 is connected to a main oil return pipe T through an oil pipe, the main oil return pipe T is connected to the port A of a first check one-way valve 21.1 through an oil pipe in parallel, and the port B of the first check one-way valve 21.1 is connected to a working cavity of a, the end part of a piston rod of the first hydraulic brake 19.1 is in braking fit with the first five-star hydraulic motor 16.1, a port B of the first check one-way valve 21.1 is connected in parallel to a port A of the first two-position two-way electromagnetic directional valve 10.1 through an oil pipe, a port B of the first two-position two-way electromagnetic directional valve 10.1 is connected to a main oil return pipe T through an oil pipe, and a transmission shaft of the first five-star hydraulic motor 16.1 is coaxially connected with the first traveling steel wheel 17.1.
The second driving system comprises a second reducing valve 9.2 of which a port B is connected to a main pressure oil pipe P, a port A of the second reducing valve 9.2 is connected to a port P of a second M-type three-position four-way electromagnetic reversing valve 12.2 through an oil pipe, a port A of the second M-type three-position four-way electromagnetic reversing valve 12.2 is connected to a working oil cavity of a second five-star hydraulic motor 16.2 through an oil pipe, a second pressure sensor 22.2 is installed on the working oil cavity of the second five-star hydraulic motor 16.2, an oil discharge cavity of the second five-star hydraulic motor 16.2 is connected to a port B of the second M-type three-position four-way electromagnetic reversing valve 12.2 through an oil pipe, a port T of the second M-type three-position four-way electromagnetic reversing valve 12.2 is connected to a main oil return pipe T through an oil pipe, the main oil return pipe T is connected to a port A of a second check one-way valve 21.2 through an oil pipe in parallel, and a port B of the second check one-way valve 21.2 is connected to a working cavity of, the piston rod tip and the second five-star hydraulic motor 16.2 braking cooperation of second hydraulic brake 19.2, the B mouth of second non return check valve 21.2 passes through oil pipe parallel coupling to the A mouth of the two solenoid directional valves 10.2 of second, and the B mouth of the two solenoid directional valves 10.2 of second passes through oil pipe coupling to main oil return pipe T, the transmission shaft and the second walking steel wheel 17.2 coaxial coupling of second five-star hydraulic motor 16.2.
The third driving system comprises a third reducing valve 9.3 of which a port B is connected to a main pressure oil pipe P, a port A of the third reducing valve 9.3 is connected to a port P of a third M-type three-position four-way electromagnetic reversing valve 12.3 through an oil pipe, a port A of the third M-type three-position four-way electromagnetic reversing valve 12.3 is connected to a working oil cavity of a third five-star hydraulic motor 16.3 through an oil pipe, a third pressure sensor 22.3 is installed on the working oil cavity of the third five-star hydraulic motor 16.3, an oil discharge cavity of the third five-star hydraulic motor 16.3 is connected to a port B of the third M-type three-position four-way electromagnetic reversing valve 12.3 through an oil pipe, a port T of the third M-type three-position four-way electromagnetic reversing valve 12.3 is connected to a main oil return pipe T through an oil pipe, the main oil return pipe T is connected to a port A of a third check one-way valve 21.3 through an oil pipe in parallel, and a port B of the third check one-way valve 21.3 is connected to a working cavity, piston rod end and the cooperation of the braking of third five star hydraulic motor 16.3 of third hydraulic brake 19.3, the B mouth of third non return check valve 21.3 passes through oil pipe parallel coupling to the A mouth of the two solenoid directional valves 10.3 of third, and the B mouth of the two solenoid directional valves 10.3 of third passes through oil pipe coupling to main oil return pipe T, the transmission shaft and the third travelling steel wheel 17.3 coaxial coupling of the three five star hydraulic motor 16.3.
The fourth driving system comprises a fourth reducing valve 9.4 of which a port B is connected to a main pressure oil pipe P, a port A of the fourth reducing valve 9.4 is connected to a port P of a fourth M-shaped three-position four-way electromagnetic reversing valve 12.4 through an oil pipe, a port A of the fourth M-shaped three-position four-way electromagnetic reversing valve 12.4 is connected to a working oil cavity of a fourth five-star hydraulic motor 16.4 through an oil pipe, a fourth pressure sensor 22.4 is installed on the working oil cavity of the fourth five-star hydraulic motor 16.4, an oil discharge cavity of the fourth five-star hydraulic motor 16.4 is connected to a port B of the fourth M-shaped three-position four-way electromagnetic reversing valve 12.4 through an oil pipe, a port T of the fourth M-shaped three-position four-way electromagnetic reversing valve 12.4 is connected to a main oil return pipe T through an oil pipe, the main oil return pipe T is connected to a port A of a fourth check one-way valve 21.4 through an oil pipe in parallel, and a port B of the fourth check one-way valve 21.4 is connected to a working cavity of a, piston rod end and the cooperation of fourth five star hydraulic motor 16.4 braking of fourth hydraulic brake 19.4, fourth check valve 21.4's B mouth passes through oil pipe parallel coupling to the A mouth of the two solenoid directional valves 10.4 of fourth, and the two solenoid directional valves 10.4's of fourth B mouth passes through oil pipe coupling to main oil return pipe T, fourth five star hydraulic motor 16.4's transmission shaft and fourth row walk steel wheel 17.4 coaxial coupling.
In practice, as shown in FIG. 1, the present invention is placed under the forging stock 34 between the upper hammer 37 and the lower anvil 38, the traveling steel wheel according to the present invention is in rolling engagement with the traveling rail 39, and the forging stock 34 is held between the jaws of the left and right manipulators 35 and 36. When the device is used specifically, the relative position between the base 23 and the forging blank 34 is adjusted by controlling the first driving system, the second driving system, the third driving system and the fourth driving system, and the main system is controlled to adjust the contact between the wire brush 33 and the forging blank 34.
Furthermore, the position of the steel wire brush 33 is ensured mainly by forming a position closed loop by the high-frequency response proportional servo valve 3 with pressure difference compensation and the main hydraulic cylinder 7 through the built-in magnetostrictive displacement sensor 8 to realize accurate control, and meanwhile, the working pressure of the main hydraulic cylinder 7 can be adjusted. Specifically, the oil inlet pressure of a P port of the high-frequency response proportional servo valve 3 with pressure difference compensation is adjusted through the main pressure reducing valve 1, and then the working pressure of a rodless cavity of the main hydraulic cylinder 7 is adjusted.
Specifically, the driving force of each five-star hydraulic motor can be adjusted. Specifically, the oil inlet pressure of a P port of the first M-shaped three-position four-way electromagnetic directional valve 12.1 is adjusted through a first pressure reducing valve 9.1, and then the driving force of a first five-star hydraulic motor 16.1 is adjusted; the oil inlet pressure of a P port of the second M-shaped three-position four-way electromagnetic directional valve 12.2 is adjusted through a second pressure reducing valve 9.2, and then the driving force of a second five-star hydraulic motor 16.2 is adjusted; the oil inlet pressure of a P port of a third M-shaped three-position four-way electromagnetic directional valve 12.3 is adjusted through a third pressure reducing valve 9.3, and then the driving force of a third five-star hydraulic motor 16.3 is adjusted; the oil inlet pressure of the P port of the fourth M-shaped three-position four-way electromagnetic directional valve 12.4 is adjusted through a fourth pressure reducing valve 9.4, and then the driving force of a fourth five-star hydraulic motor 16.4 is adjusted.
Specifically, a second main hydraulic check valve 2.2 and a third main hydraulic check valve 2.3 are respectively connected in series between an opening a and an opening B of the high-frequency response proportional servo valve 3 with pressure difference compensation and the main hydraulic cylinder 7, openings Y of the second main hydraulic check valve 2.2 and the third main hydraulic check valve 2.3 are connected to a leakage oil pipe Y, openings X of the second main hydraulic check valve 2.2 and the third main hydraulic check valve 2.3 are commonly connected to an opening a of the main electromagnetic ball valve 5, an opening P of the main electromagnetic ball valve 5 is connected to a control oil pipe X, and an opening T of the main electromagnetic ball valve 5 is connected to a main oil return pipe T. When the high-frequency response proportional servo valve 3 with pressure difference compensation is stopped and overhauled, the second main hydraulic control one-way valve 2.2 and the third main hydraulic control one-way valve 2.3 ensure that hydraulic oil in the main hydraulic cylinder 7 cannot flow out, so that resource waste is avoided.
Furthermore, a first main hydraulic control one-way valve 2.1 is connected in series between the port A of the main pressure reducing valve 1 and the port P of the high-frequency response proportional servo valve 3 with pressure difference compensation, the port Y of the first main hydraulic control one-way valve 2.1 is connected to the leakage oil pipe Y, and the port X of the first main hydraulic control one-way valve 2.1 is connected to the port A of the main electromagnetic ball valve 5.
Further, a main direct-acting overflow valve 6 is connected in parallel between an oil outlet of the second main hydraulic control one-way valve 2.2 and a rodless cavity of the main hydraulic cylinder 7, and a T port of the main direct-acting overflow valve 6 is connected to a main oil return pipe T. The main direct-acting relief valve 6 serves as a safety valve for safely protecting the working pressure of the rodless cavity of the main hydraulic cylinder 7, and is unloaded when the working pressure exceeds the set pressure of the main direct-acting relief valve 6.
Preferably, a main check valve 4 is connected in series between the port T of the high-frequency response proportional servo valve 3 with the pressure difference compensation and the main oil return pipe T.
Further, a first hydraulic control one-way valve 13.1 and a second hydraulic control one-way valve 13.2 are respectively connected in series on an oil pipe between the first M-type three-position four-way electromagnetic directional valve 12.1 and the first five-star hydraulic motor 16.1, Y ports of the first hydraulic control one-way valve 13.1 and the second hydraulic control one-way valve 13.2 are connected to the leakage oil pipe Y, X ports of the first hydraulic control one-way valve 13.1 and the second hydraulic control one-way valve 13.2 are connected to an a port of the first electromagnetic ball valve 11.1, a P port of the first electromagnetic ball valve 11.1 is connected to the control oil pipe X, and a T port of the first electromagnetic ball valve 11.1 is connected to the main oil return pipe T. A third hydraulic control one-way valve 13.3 and a fourth hydraulic control one-way valve 13.4 are connected in series on an oil pipe between the second M-type three-position four-way electromagnetic directional valve 12.2 and the second five-star hydraulic motor 16.2 respectively, ports Y of the third hydraulic control one-way valve 13.3 and the fourth hydraulic control one-way valve 13.4 are connected to a leakage oil pipe Y, ports X of the third hydraulic control one-way valve 13.3 and the fourth hydraulic control one-way valve 13.4 are connected to a port a of the second electromagnetic ball valve 11.2, a port P of the second electromagnetic ball valve 11.2 is connected to a control oil pipe X, and a port T of the second electromagnetic ball valve 11.2 is connected to a main oil return pipe T. An oil pipe between the third M-type three-position four-way electromagnetic directional valve 12.3 and the third five-star hydraulic motor 16.3 is connected with a fifth hydraulic control one-way valve 13.5 and a sixth hydraulic control one-way valve 13.6 in series respectively, ports Y of the fifth hydraulic control one-way valve 13.5 and the sixth hydraulic control one-way valve 13.6 are connected to a leakage oil pipe Y, ports X of the fifth hydraulic control one-way valve 13.5 and the sixth hydraulic control one-way valve 13.6 are connected to a port a of the third electromagnetic ball valve 11.3, a port P of the third electromagnetic ball valve 11.3 is connected to a control oil pipe X, and a port T of the third electromagnetic ball valve 11.3 is connected to a main oil return pipe T. A seventh hydraulic control one-way valve 13.7 and an eighth hydraulic control one-way valve 13.8 are respectively connected in series on an oil pipe between the fourth M-type three-position four-way electromagnetic directional valve 12.4 and the fourth five-star hydraulic motor 16.4, ports Y of the seventh hydraulic control one-way valve 13.7 and the eighth hydraulic control one-way valve 13.8 are connected to a leakage oil pipe Y, ports X of the seventh hydraulic control one-way valve 13.7 and the eighth hydraulic control one-way valve 13.8 are connected to a port a of the fourth electromagnetic ball valve 11.4, a port P of the fourth electromagnetic ball valve 11.4 is connected to a control oil pipe X, and a port T of the fourth electromagnetic ball valve 11.4 is connected to a main oil return pipe T. When the machine is stopped to overhaul each M-shaped three-position four-way electromagnetic reversing valve, the hydraulic control one-way valve ensures that hydraulic oil in the five-star hydraulic motor and the middle pipeline cannot flow out, and resource waste is caused.
Further, a first proportional flow valve 14.1 is connected in series on an oil pipe between the first pilot-controlled check valve 13.1 and a working oil chamber of the first five-star hydraulic motor 16.1, and a second proportional flow valve 14.2 is connected in series between the working chamber of the first hydraulic brake 19.1 and a port B of the first check valve 21.1. The position synchronous control of the four traveling steel wheels is mainly controlled by forming a position closed loop by respective proportional flow valves and five-star hydraulic motors through encoders. Specifically, a first proportional flow valve 14.1 and a first five-star hydraulic motor 16.1 form a position closed loop through a first encoder 18.1 to ensure the traveling precision of a first traveling steel wheel 17.1; a third proportional flow valve 14.3 and a second five-star hydraulic motor 16.2 form a position closed loop through a second encoder 18.2 to ensure the traveling precision of a second traveling steel wheel 17.2; a position closed loop is formed by the fifth proportional flow valve 14.5 and the third five-star hydraulic motor 16.3 through a third encoder 18.3 to ensure the traveling precision of a third traveling steel wheel 17.3; the seventh proportional flow valve 14.7 and the fourth five-star hydraulic motor 16.4 form a position closed loop through a fourth encoder 18.4 to ensure the traveling precision of the fourth traveling steel wheel 17.4. The four hydraulic brakes realize flexible braking by controlling the voltage obtained by the proportional electromagnets of the proportional flow valve, and specifically realize flexible braking of the first hydraulic brake 19.1 by controlling the voltage obtained by the proportional electromagnets YB4 of the second proportional flow valve 14.2; flexible braking of the second hydraulic brake 19.2 is realized by controlling the electric voltage of a proportional electromagnet YB6 of the fourth proportional flow valve 14.4; the flexible braking of the third hydraulic brake 19.3 is realized by controlling the electric voltage of a proportional electromagnet YB8 of the sixth proportional flow valve 14.6; the flexible braking of the fourth hydraulic brake 19.4 is realized by controlling the electric voltage of the proportional electromagnet YB10 of the eighth proportional flow valve 14.8.
Further, a first direct overflow valve 15.1 is connected in parallel to an oil pipe between the first proportional flow valve 14.1 and a working oil cavity of the first five-star hydraulic motor 16.1, and a T port of the first direct overflow valve 15.1 is connected to the main oil return pipe T. And a second direct-acting overflow valve 15.2 is connected in parallel to an oil pipe between the second proportional flow valve 14.2 and a working oil cavity of the second five-star hydraulic motor 16.2, and a T port of the second direct-acting overflow valve 15.2 is connected to a main oil return pipe T. And a third direct-acting overflow valve 15.3 is connected in parallel to an oil pipe between the third proportional flow valve 14.3 and a working oil cavity of the third five-star hydraulic motor 16.3, and a T port of the third direct-acting overflow valve 15.3 is connected to a main oil return pipe T. A fourth direct-acting overflow valve 15.4 is connected in parallel to an oil pipe between the fourth proportional flow valve 14.4 and a working oil cavity of the fourth five-star hydraulic motor 16.4, and a T port of the fourth direct-acting overflow valve 15.4 is connected to a main oil return pipe T. The driving force of each five-star hydraulic motor is provided with bypass safety protection. Specifically, the first direct-acting overflow valve 15.1 serves as a safety valve to safely protect the driving force of the first five-star hydraulic motor 16.1, and is unloaded after the set pressure of the first direct-acting overflow valve 15.1 is exceeded; the second direct-acting overflow valve 15.2 is used as a safety valve to perform safety protection on the driving force of the second five-star hydraulic motor 16.2, and unloading is performed after the set pressure of the second direct-acting overflow valve 15.2 is exceeded; the third direct-acting overflow valve 15.3 is used as a safety valve to perform safety protection on the driving force of the third five-star hydraulic motor 16.3, and unloading is performed after the set pressure of the third direct-acting overflow valve 15.3 is exceeded; the fourth direct-acting relief valve 15.4 serves as a safety valve for safety protection of the driving force of the fourth five-star hydraulic motor 16.4, and is unloaded when the set pressure of the fourth direct-acting relief valve 15.4 is exceeded.
Preferably, a first oil return one-way valve 20.1 is connected in series between a port T of the first M-type three-position four-way electromagnetic directional valve 12.1 and the main oil return pipe T.
In particular, the first drive system operates as follows: the electromagnet YVH 3.1.1, the electromagnet YVH 5.1.1 and the proportional electromagnet YB3 are simultaneously electrified, and high-pressure oil of ｃA main pressure oil pipe P flows into ｃA working oil cavity of ｃA first five-star hydraulic motor 16.1 through ｃA first reducing valve 9.1, ｃA P-A channel of ｃA first M-type three-position four-way electromagnetic reversing valve 12.1, an A-B channel of ｃA first hydraulic control one-way valve 13.1 and an A-B channel of ｃA first proportional flow valve 14.1; the first pressure sensor 22.1 detects the pressure of the working oil cavity of the first five-star hydraulic motor 16.1 in real time, when the pressure rises to the point that the first five-star hydraulic motor 16.1 has enough starting torque, the proportional electromagnet YB4 is quickly electrified, high-pressure oil flows into the working oil cavity of the first hydraulic brake 19.1 through the first check one-way valve 21.1 and the second proportional flow valve 14.2, the first hydraulic brake 19.1 is released, and the first five-star hydraulic motor 16.1 starts to drive the first traveling steel wheel 17.1 to travel. Meanwhile, oil in the oil discharge cavity of the first five-star hydraulic motor 16.1 flows into the main oil return pipe T through an oil port B of the first five-star hydraulic motor 16.1, a B-A channel of the second hydraulic control one-way valve 13.2, a B-T channel of the first M-shaped three-position four-way electromagnetic directional valve 12.1 and an A-B channel of the first oil return one-way valve 20.1.
Likewise, the second drive system operates as follows: the electromagnet YVH 3.2.2, the electromagnet YVH 5.2.2 and the proportional electromagnet YB5 are simultaneously electrified, and high-pressure oil of the main pressure oil pipe P flows into ｃA working oil cavity of the second five-star hydraulic motor 16.2 through the second pressure reducing valve 9.2, ｃA P-A channel of the second M-shaped three-position four-way electromagnetic reversing valve 12.2, an A-B channel of the third hydraulic control one-way valve 13.3 and an A-B channel of the third proportional flow valve 14.3; the second pressure sensor 22.2 detects the pressure of the working oil cavity of the second five-star hydraulic motor 16.2 in real time, when the pressure rises to the point that the second five-star hydraulic motor 16.2 has enough starting torque, the proportional electromagnet YB6 is quickly powered on, high-pressure oil flows into the working oil cavity of the second hydraulic brake 19.2 through the second check one-way valve 21.2 and the fourth proportional flow valve 14.4, the second hydraulic brake 19.2 is released, and the second five-star hydraulic motor 16.2 starts to drive the second traveling steel wheel 17.2 to travel. Meanwhile, oil in the oil discharge cavity of the second five-star hydraulic motor 16.2 flows into the main oil return pipe T through an oil port B of the second five-star hydraulic motor 16.2, a B-A channel of the fourth hydraulic control one-way valve 13.4, a B-T channel of the second M-type three-position four-way electromagnetic reversing valve 12.2 and an A-B channel of the second oil return one-way valve 20.2.
Likewise, the third drive system operates as follows: the electromagnet YVH 3.3.3, the electromagnet YVH 5.3.3 and the proportional electromagnet YB7 are simultaneously electrified, and high-pressure oil of the main pressure oil pipe P flows into ｃA working oil cavity of ｃA third five-star hydraulic motor 16.3 through ｃA third pressure reducing valve 9.3, ｃA P-A channel of ｃA third M-shaped three-position four-way electromagnetic reversing valve 12.3, an A-B channel of ｃA fifth hydraulic control one-way valve 13.5 and an A-B channel of ｃA fifth proportional flow valve 14.5; the third pressure sensor 22.3 detects the pressure of the working oil cavity of the third five-star hydraulic motor 16.3 in real time, when the pressure rises to the point that the third five-star hydraulic motor 16.3 has enough starting torque, the proportional electromagnet YB8 is quickly electrified, high-pressure oil flows into the working oil cavity of the third hydraulic brake 19.3 through the third non-return one-way valve 21.3 and the sixth proportional flow valve 14.6, the third hydraulic brake 19.3 is released, and the third five-star hydraulic motor 16.3 starts to drive the third traveling steel wheel 17.3 to travel. Meanwhile, oil in the oil discharge cavity of the third five-star hydraulic motor 16.3 flows into the main oil return pipe T through an oil port B of the third five-star hydraulic motor 16.3, a B-A channel of the sixth hydraulic control one-way valve 13.6, a B-T channel of the third M-type three-position four-way electromagnetic directional valve 12.3 and an A-B channel of the third oil return one-way valve 20.3.
Likewise, the fourth drive system operates as follows: the electromagnet YVH 3.4.4, the electromagnet YVH 5.4.4 and the proportional electromagnet YB9 are simultaneously electrified, and high-pressure oil of the main pressure oil pipe P flows into ｃA working oil cavity of ｃA fourth five-star hydraulic motor 16.4 through ｃA fourth reducing valve 9.4, ｃA P-A channel of ｃA fourth M-shaped three-position four-way electromagnetic reversing valve 12.4, an A-B channel of ｃA seventh hydraulic control one-way valve 13.7 and an A-B channel of ｃA seventh proportional flow valve 14.7; the fourth pressure sensor 22.4 detects the pressure of the working oil cavity of the fourth five-star hydraulic motor 16.4 in real time, when the pressure rises to the point that the fourth five-star hydraulic motor 16.4 has enough starting torque, the proportional electromagnet YB10 is quickly powered on, high-pressure oil flows into the working oil cavity of the fourth hydraulic brake 19.4 through the fourth check one-way valve 21.4 and the eighth proportional flow valve 14.8, the fourth hydraulic brake 19.4 is released, and the fourth five-star hydraulic motor 16.4 starts to drive the fourth traveling steel wheel 17.4 to travel. Meanwhile, oil in the oil discharge cavity of the fourth five-star hydraulic motor 16.4 flows into the main oil return pipe T through an oil port B of the fourth five-star hydraulic motor 16.4, a B-A channel of the eighth hydraulic control one-way valve 13.8, a B-T channel of the fourth M-type three-position four-way electromagnetic directional valve 12.4 and an A-B channel of the fourth oil return one-way valve 20.4.
After the first traveling steel wheel 17.1, the second traveling steel wheel 17.2, the third traveling steel wheel 17.3 and the fourth traveling steel wheel 17.4 travel to target positions simultaneously, the electromagnet YVH1 and the proportional electromagnet YB2 are electrified simultaneously, high-pressure oil of ｃA main pressure oil pipe P flows into ｃA rodless cavity of the main hydraulic cylinder 7 through the main pressure reducing valve 1, ｃA B-A channel of the first main hydraulic check valve 2.1, ｃA P-A channel of the high-frequency response proportional servo valve 3 with pressure difference compensation and an A-B channel of the second main hydraulic check valve 2.2, the rocker arm is driven to ascend, and the steel wire brush starts to remove oxide skin from ｃA workpiece; meanwhile, oil in a rod cavity of the main hydraulic cylinder 7 flows into the main oil return pipe T through a B-A channel of the third main hydraulic control one-way valve 2.3, a B-T channel of the high-frequency response proportional servo valve 3 with pressure difference compensation and an A-B channel of the main one-way valve 4.
The further descaling process of the present invention can be divided into three types:
the first and the second traveling steel wheels 17.1, 17.2, 17.3 and 17.4 travel back and forth on the traveling rail 39 at the same time without moving the forging blank 34, so as to remove the oxide skin on the surface of the forging blank 34;
secondly, after the rocker arm 28 rises to a specified position, the first traveling steel wheel 17.1, the second traveling steel wheel 17.2, the third traveling steel wheel 17.3 and the fourth traveling steel wheel 17.4 are kept still, and the scales are removed by moving left and right operation machines 35 and 36 back and forth (in the same direction as that shown in fig. 1) and driving the forged blank 34 to rotate for 360 degrees by a clamp, wherein under the working condition, the first M-type three-position four-way electromagnetic reversing valve 12.1, the second M-type three-position four-way electromagnetic reversing valve 12.2, the third M-type three-position four-way electromagnetic reversing valve 12.3 and the fourth M-type three-position four-way electromagnetic reversing valve 12.4 are in a middle unloading state;
in the process that the third traveling steel wheel 17.1, the second traveling steel wheel 17.2, the third traveling steel wheel 17.3 and the fourth traveling steel wheel 17.4 travel simultaneously, the left and right operating machines 35 and 36 drive the forging blank 34 to move left and right relatively, and meanwhile, the clamp drives the forging blank 34 to rotate 360 degrees.
After oxide skin is removed, the electromagnet YVH1 and the proportional electromagnet YB1 are powered on simultaneously, high-pressure oil of a main pressure oil pipe P flows into a rod cavity of the main hydraulic cylinder 7 through the main pressure reducing valve 1, a B-A channel of the first main hydraulic check valve 2.1, a P-B channel of the high-frequency response proportional servo valve 3 with pressure difference compensation and an A-B channel of the third main hydraulic check valve 2.3, a piston rod of the main hydraulic cylinder 7 contracts to drive the upper end of the rocker arm 28 to descend, and the steel brush 33 is separated from the surface of the forging blank 34; meanwhile, oil in a rodless cavity of the main hydraulic cylinder 7 flows into the main oil return pipe T through a B-A channel of the second main hydraulic control one-way valve 2.2, an A-T channel of the high-frequency response proportional servo valve 3 with pressure difference compensation and an A-B channel of the main one-way valve 4.
Furthermore, an electromagnet YVH 3.1.1, an electromagnet YVH 4.1.1 and a proportional electromagnet YB3 of the first driving system are simultaneously electrified, and high-pressure oil of a main pressure oil pipe P flows into a working oil cavity of the first five-star hydraulic motor 16.1 through a first pressure reducing valve 9.1, a P-B channel of the first M-shaped three-position four-way electromagnetic reversing valve 12.1 and an A-B channel of the second hydraulic control one-way valve 13.2, so that the first traveling steel wheel 17.1 is driven to return; meanwhile, oil in an oil discharge cavity of the first five-star hydraulic motor 16.1 flows into the main oil return pipe T through an oil outlet A of the first five-star hydraulic motor 16.1, a B-A channel of the first proportional flow valve 14.1, a B-A channel of the first hydraulic control one-way valve 13.1, an A-T channel of the first M-type three-position four-way electromagnetic reversing valve 12.1 and an A-B channel of the first oil return one-way valve 20.1.
Similarly, an electromagnet YVH 3.2.2, an electromagnet YVH 4.2.2 and a proportional electromagnet YB5 of the second driving system are simultaneously electrified, and high-pressure oil of a main pressure oil pipe P flows into a working oil cavity of a second five-star hydraulic motor 16.2 through a second pressure reducing valve 9.2, a P-B channel of a second M-shaped three-position four-way electromagnetic reversing valve 12.2 and an A-B channel of a fourth hydraulic control one-way valve 13.4, so that a second traveling steel wheel 17.2 is driven to return; meanwhile, oil in an oil discharge cavity of the second five-star hydraulic motor 16.2 flows into the main oil return pipe T through an oil outlet A of the second five-star hydraulic motor 16.2, a B-A channel of a third proportional flow valve 14.3, a B-A channel of a third hydraulic control one-way valve 13.3, an A-T channel of a second M-type three-position four-way electromagnetic reversing valve 12.2 and an A-B channel of a second oil return one-way valve 20.2.
Similarly, an electromagnet YVH 3.3.3, an electromagnet YVH 4.3.3 and a proportional electromagnet YB7 of the third driving system are simultaneously electrified, and high-pressure oil of a main pressure oil pipe P flows into a working oil cavity of a third five-star hydraulic motor 16.3 through a third pressure reducing valve 9.3, a P-B channel of a third M-shaped three-position four-way electromagnetic reversing valve 12.3 and an A-B channel of a sixth hydraulic control one-way valve 13.6, so that the third traveling steel wheel 17.3 is driven to return; meanwhile, oil in an oil discharge cavity of the third five-star hydraulic motor 16.3 flows into the main oil return pipe T through an oil outlet A of the third five-star hydraulic motor 16.3, a B-A channel of a fifth proportional flow valve 14.5, a B-A channel of a fifth hydraulic control one-way valve 13.5, an A-T channel of a third M-type three-position four-way electromagnetic reversing valve 12.3 and an A-B channel of a third oil return one-way valve 20.3.
Similarly, an electromagnet YVH 3.4.4, an electromagnet YVH 4.4.4 and a proportional electromagnet YB9 of the fourth driving system are simultaneously electrified, and high-pressure oil of a main pressure oil pipe P flows into a working oil cavity of a fourth five-star hydraulic motor 16.4 through a fourth reducing valve 9.4, a P-B channel of a fourth M-shaped three-position four-way electromagnetic reversing valve 12.4 and an A-B channel of an eighth hydraulic control one-way valve 13.8, so that a fourth traveling steel wheel 17.4 is driven to return; meanwhile, oil in an oil discharge cavity of the fourth five-star hydraulic motor 16.4 flows into the main oil return pipe T through an oil outlet A of the fourth five-star hydraulic motor 16.4, a B-A channel of the seventh proportional flow valve 14.7, a B-A channel of the seventh hydraulic control one-way valve 13.7, an A-T channel of the fourth M-type three-position four-way electromagnetic reversing valve 12.4 and an A-B channel of the fourth oil return one-way valve 20.4.
After the first traveling steel wheel 17.1, the second traveling steel wheel 17.2, the third traveling steel wheel 17.3 and the fourth traveling steel wheel 17.4 return to the original positions at the same time, the electromagnets YVH 3.1.1, the electromagnets YVH 4.1.1 and the proportional electromagnet YB3 of the first driving system are powered off at the same time, the electromagnet YVH 2.1.1 is powered on at the same time, oil in the working chamber of the first hydraulic brake 19.1 flows into the main oil return pipe T through the B-A channel of the second proportional flow valve 14.2 and the A-B channel of the first two-position two-way electromagnetic reversing valve 10.1, the magnitude of the power-on voltage of the proportional electromagnet YB4 is adjusted, the opening degree of the valve core of the second proportional flow valve 14.2 can be controlled, and the flexible braking of the first hydraulic brake 19.1 is realized.
Similarly, the electromagnet YVH 3.2.2, the electromagnet YVH 4.2.2 and the proportional electromagnet YB5 of the second driving system are powered off at the same time, the electromagnet YVH 2.2.2 is powered on at the same time, oil in the working chamber of the second hydraulic brake 19.2 flows into the main oil return pipe T through the B-a channel of the fourth proportional flow valve 14.4 and the a-B channel of the second two-position two-way electromagnetic directional valve 10.2, the magnitude of the power-on voltage of the proportional electromagnet YB6 is adjusted, the opening degree of the valve element of the fourth proportional flow valve 14.4 can be controlled, and therefore flexible braking of the second hydraulic brake 19.2 is achieved.
Similarly, the electromagnet YVH 3.3.3, the electromagnet YVH 4.3.3 and the proportional electromagnet YB7 of the third driving system are powered off at the same time, the electromagnet YVH 2.3.3 is powered on at the same time, oil in the working chamber of the third hydraulic brake 19.3 flows into the main oil return pipe T through the B-a channel of the sixth proportional flow valve 14.6 and the a-B channel of the third two-position two-way electromagnetic directional valve 10.3, the magnitude of the power-on voltage of the proportional electromagnet YB8 is adjusted, and the opening degree of the valve core of the sixth proportional flow valve 14.6 can be controlled, so that the flexible braking of the third hydraulic brake 19.3 is realized.
Similarly, the electromagnet YVH 3.4.4, the electromagnet YVH 4.4.4 and the proportional electromagnet YB9 of the fourth driving system are powered off at the same time, the electromagnet YVH 2.4.4 is powered on at the same time, oil in the working chamber of the fourth hydraulic brake 19.4 flows into the main oil return pipe T through the B-a channel of the eighth proportional flow valve 14.8 and the a-B channel of the fourth two-position two-way electromagnetic directional valve 10.4, the magnitude of the power-on voltage of the proportional electromagnet YB10 is adjusted, the opening degree of the valve element of the eighth proportional flow valve 14.8 can be controlled, and therefore flexible braking of the fourth hydraulic brake 19.4 is achieved.
The above description is only for the specific embodiments of the present invention, but the scope of the present invention is not limited thereto, and any person skilled in the art can easily conceive of the changes or substitutions within the technical scope of the present invention, and all the changes or substitutions should be covered within the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the appended claims.
Claims (9)
1. A descaling hydraulic device for forging comprises a mechanical part and a hydraulic part, wherein the mechanical part comprises a base (23),
the mechanical part also comprises traveling steel wheels rotatably arranged at four corners of the bottom of the base (23), a hydraulic cylinder bracket (24) and a support frame (25) which are arranged on the upper surface of the base (23), the top of the hydraulic cylinder bracket (24) is rotatably arranged on a cylinder body of the main hydraulic cylinder (7) through a first pin shaft (26), the piston end of the main hydraulic cylinder (7) is rotatably connected with one end of a rocker arm (28) through a second pin shaft (27), the support frame (25) is oppositely provided with two bearing seats (29), the two bearing seats (29) are respectively provided with a bearing (30), a fourth pin shaft (31) penetrates between inner circles of the two bearings (30), the end part of the rocker arm (28) close to the second pin shaft (27) penetrates through the fourth pin shaft (31) and is positioned between the two bearings (30), and the other end of the rocker arm (28) is fixedly provided with a steel wire brush (33) through a third pin shaft (32), each walking steel wheel is provided with an encoder;
the hydraulic part comprises a main system, a first driving system, a second driving system, a third driving system and a fourth driving system, and the first driving system, the second driving system, the third driving system and the fourth driving system have the same structure;
the main system comprises a main pressure reducing valve (1) with a port B connected to a main pressure oil pipe (P), wherein the port A of the main pressure reducing valve (1) is connected to the port P of a high-frequency response proportional servo valve (3) with pressure difference compensation through an oil pipe, the port A of the high-frequency response proportional servo valve (3) with pressure difference compensation is connected to a rodless cavity of a main hydraulic cylinder (7) through an oil pipe, a built-in magnetostrictive displacement sensor (8) is installed on the main hydraulic cylinder (7), a rod cavity of the main hydraulic cylinder (7) is connected to the port B of the high-frequency response proportional servo valve (3) with pressure difference compensation through an oil pipe, and a port T of the high-frequency response proportional servo valve (3) with pressure difference compensation is connected to a main oil return pipe (T) through an oil pipe;
the first driving system comprises a first reducing valve (9.1) with a port B connected to a main pressure oil pipe (P), the port A of the first reducing valve (9.1) is connected to the port P of a first M-type three-position four-way electromagnetic reversing valve (12.1) through an oil pipe, the port A of the first M-type three-position four-way electromagnetic reversing valve (12.1) is connected to a working oil cavity of a first five-star hydraulic motor (16.1) through an oil pipe, a first pressure sensor (22.1) is installed on the working oil cavity of the first five-star hydraulic motor (16.1), an oil discharge cavity of the first five-star hydraulic motor (16.1) is connected to the port B of the first M-type three-position four-way electromagnetic reversing valve (12.1) through an oil pipe, a port T of the first M-type three-position four-way electromagnetic reversing valve (12.1) is connected to a main oil pipe (T) through an oil return pipe, and the main oil return pipe (T) is connected to a port A of a first oil return pipe (21.1) through an oil return pipe in parallel, a port B of the first check one-way valve (21.1) is connected to a working cavity of the first hydraulic brake (19.1) through an oil pipe, the end part of a piston rod of the first hydraulic brake (19.1) is in brake fit with the first five-star hydraulic motor (16.1), the port B of the first check one-way valve (21.1) is connected to a port A of the first two-position two-way electromagnetic reversing valve (10.1) in parallel through the oil pipe, the port B of the first two-position two-way electromagnetic reversing valve (10.1) is connected to a main oil return pipe (T) through the oil pipe, and a transmission shaft of the first five-star hydraulic motor (16.1) is coaxially connected with the first traveling steel wheel (17.1).
2. The hydraulic descaling device for forging according to claim 1, wherein a second main check valve (2.2) and a third main check valve (2.3) are respectively connected in series between the port A and the port B of the high-frequency response proportional servo valve (3) with differential pressure compensation and the main hydraulic cylinder (7), the ports Y of the second main check valve (2.2) and the third main check valve (2.3) are connected to a leakage oil pipe (Y), the ports X of the second main check valve (2.2) and the third main check valve (2.3) are connected to the port A of the main electromagnetic ball valve (5), the port P of the main electromagnetic ball valve (5) is connected to a control oil pipe (X), and the port T of the main electromagnetic ball valve (5) is connected to a main oil return pipe (T).
3. The hydraulic descaling device for forging of claim 2, wherein a first main hydraulic check valve (2.1) is connected in series between the port A of the main pressure reducing valve (1) and the port P of the high-frequency response proportional servo valve (3) with pressure difference compensation, the port Y of the first main hydraulic check valve (2.1) is connected to a leakage oil pipe (Y), and the port X of the first main hydraulic check valve (2.1) is connected to the port A of the main electromagnetic ball valve (5).
4. A descaling hydraulic device for forging according to claim 2, characterized in that a main direct-acting overflow valve (6) is connected in parallel between the oil outlet of the second main hydraulic check valve (2.2) and the rodless cavity of the main hydraulic cylinder (7), and the T-port of the main direct-acting overflow valve (6) is connected to the main oil return pipe (T).
5. A descaling hydraulic device for forging according to claim 4, characterized in that a main check valve (4) is connected in series between the T port of the high-frequency-response proportional servo valve (3) with pressure difference compensation and the main oil return pipe (T).
6. The descaling hydraulic device for forging of the claim 1, 2, 3, 4 or 5, wherein a first hydraulic control one-way valve (13.1) and a second hydraulic control one-way valve (13.2) are respectively connected in series on an oil pipe between the first M-type three-position four-way electromagnetic directional valve (12.1) and the first five-star hydraulic motor (16.1), the Y ports of the first hydraulic control one-way valve (13.1) and the second hydraulic control one-way valve (13.2) are connected to a leakage oil pipe (Y), the X ports of the first hydraulic control one-way valve (13.1) and the second hydraulic control one-way valve (13.2) are connected to the A port of the first electromagnetic ball valve (11.1), the P port of the first electromagnetic ball valve (11.1) is connected to a control oil pipe (X), and the T port of the first electromagnetic ball valve (11.1) is connected to a main oil return pipe (T).
7. A descaling hydraulic device for forging according to claim 6, characterized in that a first proportional flow valve (14.1) is connected in series on an oil pipe between the first pilot-operated check valve (13.1) and the working oil chamber of the first five-star hydraulic motor (16.1), and a second proportional flow valve (14.2) is connected in series between the working chamber of the first hydraulic brake (19.1) and the port B of the first check valve (21.1).
8. The hydraulic descaling device for forging according to claim 7, wherein a first direct overflow valve (15.1) is connected in parallel to an oil pipe between the first proportional flow valve (14.1) and a working oil chamber of the first five-star hydraulic motor (16.1), and a T port of the first direct overflow valve (15.1) is connected to a main oil return pipe (T).
9. A descaling hydraulic device for forging according to claim 6, characterized in that a first oil return check valve (20.1) is connected in series between the T port of the first M-shaped three-position four-way electromagnetic directional valve (12.1) and the main oil return pipe (T).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910126075.7A CN109773639B (en) | 2019-02-20 | 2019-02-20 | Descaling hydraulic device for forging |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910126075.7A CN109773639B (en) | 2019-02-20 | 2019-02-20 | Descaling hydraulic device for forging |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109773639A CN109773639A (en) | 2019-05-21 |
| CN109773639B true CN109773639B (en) | 2020-04-07 |
Family
ID=66504677
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910126075.7A Active CN109773639B (en) | 2019-02-20 | 2019-02-20 | Descaling hydraulic device for forging |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109773639B (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111375718B (en) * | 2020-03-09 | 2021-08-03 | 太原理工大学 | Intermediate support hydraulic device for forging |
| CN111843781B (en) * | 2020-07-15 | 2021-04-27 | 太原理工大学 | Robot is clear away on line to hard and soft coupling driven super large axle class forging cinder |
| CN113787095B (en) * | 2021-09-03 | 2024-05-03 | 太原理工大学 | Metal composite plate rolling device capable of applying horizontal vibration |
| CN113857248A (en) * | 2021-10-22 | 2021-12-31 | 太原理工大学 | Equipment for controlling warping of bimetal composite board plate shape by utilizing hydraulic speed regulation |
| CN114932186A (en) * | 2022-07-26 | 2022-08-23 | 南通大鹏光电有限公司 | Anti-cracking rapid forging equipment for processing photovoltaic panel support and implementation method |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4248019A (en) * | 1977-11-28 | 1981-02-03 | Western Gear Corporation | Workpiece conditioning grinder control system |
| CN201645300U (en) * | 2010-04-30 | 2010-11-24 | 湖北省电力建设第一工程公司 | Derusting machine for steel strands |
| CN102229090A (en) * | 2011-06-30 | 2011-11-02 | 陕西火石咀煤矿有限责任公司 | Outer derusting machine for single hydraulic prop |
| CN205874551U (en) * | 2016-08-21 | 2017-01-11 | 浙江洲隆机器制造有限公司 | Stainless steel forges with high -efficient even flake device |
| CN107745319A (en) * | 2017-11-29 | 2018-03-02 | 四川大黄河钢结构工程有限公司 | Tubulose steelframe derusting device |
| CN207771530U (en) * | 2017-12-05 | 2018-08-28 | 西安嘉特电气设备有限公司 | A kind of bridge pier cast reinforcing bar Rapid rust cleaning device |
| CN108637867B (en) * | 2018-05-10 | 2020-10-13 | 北京石油化工学院 | Underwater pipeline polishing device |
-
2019
- 2019-02-20 CN CN201910126075.7A patent/CN109773639B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN109773639A (en) | 2019-05-21 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN109773639B (en) | Descaling hydraulic device for forging | |
| CN201411331Y (en) | Full-automatic pipe blank transferring device | |
| CN109807177B (en) | Hydraulic pressing corrugated roller mill of special-shaped supporting roller | |
| CN103047390B (en) | Variable pressure angle cam contour line design method applicable to sudden variable load | |
| CN201096120Y (en) | Heating stove walking beam speed regulating device | |
| CN201627983U (en) | Combined type multidirectional pneumatic control valve | |
| CN203062791U (en) | Automatic gripper of transfer robot | |
| CN101653798B (en) | System for processing curved face of plate material | |
| CN105782154A (en) | Hydraulic machining machine, hydraulic system thereof and control method of hydraulic system | |
| CN203021651U (en) | Seamless steel tube core rod surface strengthening device | |
| CN102335698B (en) | A kind of high-temperature steel plate grabbing mechanical hand with heat insulation function | |
| CN111375718B (en) | Intermediate support hydraulic device for forging | |
| CN215879684U (en) | Direct-drive forging press | |
| CN109604341A (en) | Punch and its big lid lifting locking control system | |
| CN216107079U (en) | Quenching furnace sealing cover plate | |
| CN212225639U (en) | Hydraulic circuit system for rapid and accurate braking of hydraulic motor | |
| CN110552917B (en) | Hydraulic servo system based on extremely thin steel sheet roll-in formula quenching machine | |
| CN109058197B (en) | Novel overflow collection device and method for energy-saving rapid forging machine | |
| CN202967390U (en) | Position limiting device for ball mill lining plate mounting and dismounting transfer trolley | |
| CN205870545U (en) | Nut thermal treatment automatic handling equipment control system | |
| CN206860564U (en) | A kind of closed-loop control system of sharpening machine for copper billet figuring of surface | |
| CN205496282U (en) | Cold bed air -balance device of raising to higher plane of principle | |
| CN206083721U (en) | C -frame hydraulic press servo with forge function soon | |
| CN111140558A (en) | Hydraulic system of heat treatment manipulator and control method thereof | |
| CN214698540U (en) | Nearly free fall formula is from closing lid quenching oil groove hydraulic system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20240109 Address after: 034000 Shen Shan Xiang Wei Cun, Dingxiang County, Xinzhou City, Shanxi Province Patentee after: Shanxi baolongda Forging Co.,Ltd. Address before: 030024 No. 79 West Main Street, Taiyuan, Shanxi, Yingze Patentee before: Taiyuan University of Technology |
|
| TR01 | Transfer of patent right |