NL2029082B1 - Energy-saving high-efficiency low-noise press hydraulic system - Google Patents

Energy-saving high-efficiency low-noise press hydraulic system Download PDF

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Publication number
NL2029082B1
NL2029082B1 NL2029082A NL2029082A NL2029082B1 NL 2029082 B1 NL2029082 B1 NL 2029082B1 NL 2029082 A NL2029082 A NL 2029082A NL 2029082 A NL2029082 A NL 2029082A NL 2029082 B1 NL2029082 B1 NL 2029082B1
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Netherlands
Prior art keywords
valve
way
hydraulic cylinder
oil
hydraulic
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NL2029082A
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Dutch (nl)
Inventor
Li Zhibo
Qi Zhentao
Wang Shoujun
Zou Bingyan
Liu Feng
Liu Guodong
Liu Ze
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Tianjinsino German Univ Of Applied Sciences
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6654—Flow rate control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7114—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators
    • F15B2211/7128—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators the chambers being connected in parallel
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P70/00—Climate change mitigation technologies in the production process for final industrial or consumer products
    • Y02P70/10—Greenhouse gas [GHG] capture, material saving, heat recovery or other energy efficient measures, e.g. motor control, characterised by manufacturing processes, e.g. for rolling metal or metal working

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Presses (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

An energy-saving high-efficiency low-noise press hydraulic system, including an oil tank, a first and second oil-absorbing oil-filtering device, a first and second directly operated type relief valve, a first and second pressure sensor, a 5 three-position four-way electro-hydraulic directional valve, a first, second and third check valve, a first and second two-position two-way electromagnetic ball valve, an externally controlled one-way balance valve, a first and second orifice, a movable plate driven long-stroke hydraulic cylinder, a movable plate driven hydraulic cylinder, a first and second pressure gauge, an internal gear pump, an 10 alternating-current servo motor and a first and second coupler, a three-phase asynchronous motor, a constant-pressure variable piston pump, an electromagnetic relief valve, a three-position four-way electromagnetic directional valve, a two/one-way throttle valve, a bidirectional hydraulic lock, and a short-stroke pressurizing hydraulic cylinder. 15 Fig.1

Description

DESCRIPTION ENERGY-SAVING HIGH-EFFICIENCY LOW-NOISE PRESS
HYDRAULIC SYSTEM Technical Field The disclosure belongs to the technical field of hydraulic drive and control, and relates to a hydraulic system of a press, particularly to an energy-saving high-efficiency low-noise press hydraulic system. Background At present, a hydraulic technology has been widely applied to various fields of national economy, such as aviation, aerospace, shipbuilding, transportation, machinery manufacturing, furthermore, standardization, serialization and universalization of hydraulic elements have been reached, which is greatly convenient for people to select. A press is ordinarily composed of upper and lower fixed plates, a middle movable plate, a guide pillar and other components. Since the press needs a large output force, the upper and lower drive of the movable plate is generally achieved by a hydraulic system. The hydraulic system of the traditional press generally uses a piston pump as a power source due to high working pressure. The piston pump has large noise when in high-pressure working. The movable plate moves up and down, and generally has two speeds, that is, quick speed and slow speed. If a quantitative piston pump is used, a lot of hydraulic oil returns to an oil tank via a relief valve when movement is conducted at the slow speed. The system is low in efficiency and many in heat; the variable piston pump is used, so the cost is high. How to improve the efficiency of the system and reduce the operation noise of the system when the movable plate of the press moves at the slow speed is a technical problem to be urgently solved by those skilled in the art. Summary of the Invention The objective of the disclosure is to provide an energy-saving high-efficiency low-noise press hydraulic system, which is rational in design, high in working efficiency and low in manufacturing cost, in order to overcome the defects of the prior art.
The actual problem to be solved by the disclosure is achieved by adopting the following technical solution: Provided is an energy-saving high-efficiency low-noise press hydraulic system, comprising: an oil tank 1, a first oil-absorbing oil-filtering device 2, a first directly operated type relief valve 3, a first pressure sensor 4, a three-position four-way electro-hydraulic directional valve 5, a first check valve 6, a first two-position two-way electromagnetic ball valve 7, an externally controlled one-way balance valve 8, a first orifice 9, a movable plate driven long-stroke hydraulic cylinder 10, a movable plate driven hydraulic cylinder 11, a second check valve 15, a first pressure gauge 16, an internal gear pump 17, an alternating-current servo motor 18 and a first coupler 19; the internal gear pump 17 being driven by the alternating-current servo motor 18 via the first coupler 19 and used for supplying pressure oil to the system; the oil absorbing port of the internal gear pump 17 being connected with the oil tank 1 through the first oil-absorbing oil-filtering device 2; the oil tank 1 being used for storing, purifying and cooling oil, and the oil-absorbing oil-filtering device 2 being used for filtering the oil; the oil discharge port of the internal gear pump 17 being respectively connected with the first pressure gauge 16, the first pressure sensor 4, the oil inlet port of the first directly operated type relief valve 3,
the oil inlet port of the three-position four-way electro-hydraulic directional valve
5, the ball end of the first check valve 6 and the tip end of the second check valve 15, the first pressure gauge 16 being used for displaying the working pressure of the internal gear pump, the first pressure sensor 4 converting a pressure signal into an electrical signal, and the first directly operated type relief valve 3 being used for setting the maximum working pressure of the internal gear pump 17; the oil outlet port of the first directly operated type relief valve 3 being connected with the oil tank 1; the oil return port of the three-position four-way electro-hydraulic directional valve 5 being connected with the oil tank, the left output port of the three-position four-way electro-hydraulic directional valve 5 being connected with the input port of the first two-position two-way electromagnetic ball valve 7, the output port of the first two-position two-way electromagnetic ball valve 7 being respectively connected with the tip end of the first check valve 6 and the lower port of the externally controlled one-way balance valve 8, the three-position four-way electro-hydraulic directional valve 5, the first two-way electromagnetic ball valve 7 and the first check valve 6 being used for achieving the differential control of the movable plate driven long-stroke hydraulic cylinder 10 and the movable plate driven hydraulic cylinder 11; the upper port of the externally controlled one-way balance valve 8 being respectively connected with rod cavities of the movable plate driven long-stroke hydraulic cylinder 10 and the movable plate driven hydraulic cylinder 11, the rodless cavities of the movable plate driven long-stroke hydraulic cylinder 10 and the movable plate driven hydraulic cylinder 11 being connected with the right output port of the three-position four-way electro-hydraulic directional valve 5 and connected with the externally controlled port of the externally controlled one-way balance valve 8 through the first orifice 9, and the externally controlled one-way balance valve 8 being used for controlling the movable plate driven long-stroke hydraulic cylinder 10 and the movable plate driven hydraulic cylinder 11 to stably descend.
Furthermore, provided is an energy-saving high-efficiency low-noise press hydraulic system, also comprising: a second pressure sensor 12, a second orifice 13, a second two-position two-way electromagnetic ball valve 14, a second oil-absorbing oil-filtering device 20, a three-phase asynchronous motor 21, a second coupler 22, a constant-pressure variable piston pump 23, a second pressure gauge 24, an electromagnetic relief valve 25, a third check valve 26, a three-position four-way electromagnetic directional valve 27, a two/one-way throttle valve 28, a bidirectional hydraulic lock 29, a second directly operated type relief valve 30 and a short-stroke pressurizing hydraulic cylinder 31; the constant-pressure variable piston pump 23 being driven by the three-phase asynchronous motor 21 via the second coupler 22 to supply oil for the pressurizing hydraulic cylinder 31; the oil absorbing port of the constant-pressure variable piston pump 23 being connected with the oil tank 1 via the second oil-absorbing oil-filtering device 20, and the oil-absorbing oil-filtering device 20 being used for filtering oil; the oil discharge port of the constant-pressure variable piston pump 23 being respectively connected with the second pressure gauge 24, the oil inlet port of the electromagnetic relief valve 25 and the tip end of the third check valve 26, the second pressure gauge 24 being used for displaying the working pressure of the system; the oil return port of the electromagnetic relief valve 25 being connected with the oil tank, and the electromagnetic relief valve 25 being used for setting the maximum working pressure of the pressurizing hydraulic cylinder 31, if necessary, achieving the unloading of the system; the ball end of the third check valve 26 being respectively connected with the ball end of the second check valve 15 and the oil inlet port of the three-position four-way electromagnetic directional valve 27; the oil return port of the three-position four-way electromagnetic directional valve 27 being connected with the oil tank 1, and the left and right output ports of the three-position four-way electromagnetic directional valve 27 being respectively connected with the left and right input ports of the two/one-way throttle valve 28 in an oil-return throttling manner, the three-position four-way electromagnetic directional valve 27 being used for controlling up and down movement of the short-stroke pressurizing hydraulic cylinder 31; the left and right output ports of the two/one-way throttle valve 28 being connected with oil ports at the left and right tip ends of the bidirectional hydraulic lock 29, the two/one-way throttle valve 28 being used for controlling the movement speed of the short-stroke pressurizing hydraulic cylinder 31, the bidirectional hydraulic lock being used for the pressure holding of the pressurizing hydraulic cylinder 31, the left output port of the bidirectional hydraulic lock 29 being respectively connected with the second pressure sensor 12,
the rodless cavity of the short-stroke pressurizing hydraulic cylinder 31 and the second orifice 13, the second orifice 13 being also connected with the input port at the ball end of the second two-position two-way electromagnetic ball valve 14, the output port at the tip end of the second two-position two-way electromagnetic ball valve 14 being connected with the oil tank 1, the second orifice 13 and the second two-position two-way electromagnetic ball valve 14 being used for depressurization of the rodless cavity of the short-stroke pressurizing hydraulic cylinder 31; the right output port of the bidirectional hydraulic lock 29 being respectively connected with the rod cavity of the short-stroke pressurizing hydraulic cylinder 31 and the oil input port of the second directly operated type relief valve 30, the oil return port of the second directly operated type relief valve 30 being connected with the oil tank 1, and the second directly operated type relief valve 30 being used for preventing the overloading of the pressurizing cavity of the pressurizing hydraulic cylinder 31.
In the disclosure, terms “first” and “second” are only used for describing the purposes but cannot be understood as indicating or hinting relative importance. Terms “linking”, “connection”, “fixing” and the like are all broadly understood, for example, “connect” can be fixed connection, or detachable connection, or integrated connection, “linking” can be direct linking, or linking through an intermediate medium. For those skilled in the art, the meanings of the above terms in the disclosure can be understood according to specific situations.
In the description of the disclosure, it is understood that terms “upper”, “lower” , “left, “right”, “front” ‚ “rear” and other indicated orientation and position relationships are orientation or position relationships as shown in figures, which are only for conveniently describing the disclosure and simplifying the description, but not indicating or hinting that the specified device or unit must have specific direction or configuration and operation in a specific orientation.
The disclosure has the advantages and beneficial effects:
1. When the system of the disclosure is on standby, although the internal gear pump is a quantitative pump and is driven by the alternating-current servo motor, and the minimum stable rotation speed is only 50 rpm; the constant-pressure variable piston pump is driven by the three-phase asynchronous motor, at this moment, the electromagnetic relief valve is in an unloading state, the power consumption is very low, the heat is low, and the noise is low.
2. According to the disclosure, through cooperation among the internal gear pump, the three-position four-way electro-hydraulic directional valve, the first two-position two-way electromagnetic ball valve and the externally controlled one-way balance valve, in the rapid descending process of the movable plate, the movable plate driven long-stroke hydraulic cylinder realizes differential connection and rapidly extends, and the movable plate stably descends under the action of the externally controlled one-way balance valve; in the slow descending process of the movable plate, the first two-position two-way electromagnetic ball valve electromagnet is electrified, the valve is turned on, the piston rod of the movable plate driven long-stroke hydraulic cylinder slowly extends, and the extension speed can be adjusted by controlling the rotation speed of the alternating-current servo motor; in the rising process of the movable plate, the piston rod of the movable plate driven long-stroke hydraulic cylinder returns, and the return speed can be adjusted by controlling the rotation speed of the alternating-current servo motor; in the rapid descending, slow descending and rising processes of the movable plate, the oil supply amount of the internal gear pump is always matched with the working speed of the hydraulic cylinder without excessive flow, and therefore only a small-displacement directly operated type relief valve is arranged at the oil discharge port of the internal gear pump. The system is high in efficiency and low in heat. When the rotation speed of the internal gear pump does not exceed 2000 rpm, the noise is low.
3. According to the disclosure, in the pressurization process of the short-stroke pressurizing hydraulic cylinder, the three-position four-way electromagnetic directional valve is in the left position, the electromagnetic relief valve 1s electrified, the electromagnet of the second two-position two-way electromagnetic ball valve is not electrified, oil supplied from the constant-pressure variable piston pump is supplied to the rodless cavity of the short-stroke pressurizing hydraulic cylinder via the third check valve, the three-position four-way electromagnetic directional valve, the two/one-way throttle valve and the bidirectional hydraulie lock, the oil returns to the rod cavity and then to the oil tank via the bidirectional hydraulic lock, the two/one-way throttle valve, the three-position four-way electromagnetic directional valve, and the second directly operated type relief valve is used for preventing the overloading of the rod cavity of the hydraulic cylinder.
4. According to the disclosure, in the depressurizing process of the short-stroke pressurizing hydraulic cylinder, the electromagnet of the second two-position two-way electromagnetic ball valve is electrified, and the pressure of the rodless cavity of the short-stroke pressurizing hydraulic cylinder returns to the oil tank via the second orifice and the second two-position two-way valve. Because the orifice is small, when the hydraulic cylinder returns again after pressure relief, the vibration and nose are reduced.
5. According to the disclosure, a locking device is added on the mechanical structure, and therefore the stroke length of the movable plate driven long-stroke hydraulic cylinder meets movable plate movement requirements, while the stroke of the pressurizing hydraulic cylinder is only 25 mm which is only used for pressurization; to meet the output force requirement, the diameter of the pressurizing hydraulic cylinder is large, generally 300 mm-1000 mm; the stroke is shortened, thereby effectively reducing the manufacturing difficulty and greatly decreasing the manufacturing cost.
Brief Description of Drawings Embodiments of the disclosure will be described in detail in combination with accompanying drawing.
An energy-saving high-efficiency low-noise press hydraulic system, as shown in Fig 1, includes: an oil tank 1, a first oil-absorbing oil-filtering device 2, a first directly operated type relief valve 3, a first pressure sensor 4, a three-position four-way electro-hydraulic directional valve 5, a first check valve 6, a first two-position two-way electromagnetic ball valve 7, an externally controlled one-way balance valve 8, a first orifice 9, a movable plate driven long-stroke hydraulic cylinder 10, a movable plate driven hydraulic cylinder 11, a second check valve 15, a first pressure gauge 16, an internal gear pump 17, an alternating-current servo motor 18, a first coupler 19, a second oil-absorbing oil-filtering device 20, a three-phase asynchronous motor 21, a second coupler 22, a constant-pressure variable piston pump 23, a second pressure gauge 24, an electromagnetic relief valve 25, a third check valve 26, a three-position four-way electromagnetic directional valve 27, a two/one-way throttle valve 28, a bidirectional hydraulic lock 29, a second directly operated type relief valve 30, a short-stroke pressurizing hydraulic cylinder 31. The internal gear pump 17 is driven by the alternating-current servo motor 18 via the first coupler 19 and used for supplying pressure oil to the system; the oil absorbing port of the internal gear pump 17 is connected with the oil tank 1 through the first oil-absorbing oil-filtering device 2; the oil tank 1 is used for storing, purifying and cooling oil, and the oil-absorbing oil-filtering device 2 is used for filtering the oil; the oil discharge port of the internal gear pump 17 is respectively connected with the first pressure gauge 16, the first pressure sensor 4, the oil inlet port of the first directly operated type relief valve 3, the oil inlet port of the three-position four-way electro-hydraulic directional valve 5, the ball end of the first check valve 6 and the tip end of the second check valve 15, the first pressure gauge 16 is used for displaying the working pressure of the internal gear pump, the first pressure sensor 4 converts a pressure signal into an electrical signal, and the first directly operated type relief valve 3 is used for setting the maximum working pressure of the internal gear pump 17; the oil outlet port of the first directly operated type relief valve 3 is connected with the oil tank 1; the oil return port of the three-position four-way electro-hydraulic directional valve 5 is connected with the oil tank, the left output port of the three-position four-way electro-hydraulic directional valve 5 is connected with the input port of the first two-position two-way electromagnetic ball valve 7, the output port of the first two-position two-way electromagnetic ball valve 7 is respectively connected with the tip end of the first check valve 6 and the lower port of the externally controlled one-way balance valve 8, the three-position four-way electro-hydraulic directional valve 5, the first two-way electromagnetic ball valve 7 and the first check valve 6 are used for achieving the differential control of the movable plate driven long-stroke hydraulic cylinder 10 and the movable plate driven hydraulic cylinder 11; the upper port of the externally controlled one-way balance valve 8 is respectively connected with rod cavities of the movable plate driven long-stroke hydraulic cylinder 10 and the movable plate driven hydraulic cylinder 11, the rodless cavities of the movable plate driven long-stroke hydraulic cylinder 10 and the movable plate driven hydraulic cylinder 11 are connected with the right output port of the three-position four-way electro-hydraulic directional valve 5 and connected with the externally controlled port of the externally controlled one-way balance valve 8 through the first orifice 9, and the externally controlled one-way balance valve 8 is used for controlling the movable plate driven long-stroke hydraulic cylinder 10 and the movable plate driven hydraulic cylinder 11 to stably descend.
The constant-pressure variable piston pump 23 is driven by the three-phase asynchronous motor 21 via the second coupler 22 to supply oil for the pressurizing hydraulic cylinder 31; the oil absorbing port of the constant-pressure variable piston pump 23 is connected with the oil tank 1 via the second oil-absorbing oil-filtering device 20, and the oil-absorbing oil-filtering device 20 is used for filtering oil; the oil discharge port of the constant-pressure variable piston pump 23 is respectively connected with the second pressure gauge 24, the oil inlet port of the electromagnetic relief valve 25 and the tip end of the third check valve 26, and the second pressure gauge 24 is used for displaying the working pressure of the system; the oil return port of the electromagnetic relief valve 25 is connected with the oil tank, and the electromagnetic relief valve 25 is used for setting the maximum working pressure of the pressurizing hydraulic cylinder 31, if necessary, achieving the unloading of the system; the ball end of the third check valve 26 is respectively connected with the ball end of the second check valve 15 and the oil inlet port of the three-position four-way electromagnetic directional valve 27; the oil return port of the three-position four-way electromagnetic directional valve 27 is connected with the oil tank 1,
and the left and right output ports of the three-position four-way electromagnetic directional valve 27 are respectively connected with the left and right input ports of the two/one-way throttle valve 28 in an oil-return throttling manner, the three-position four-way electromagnetic directional valve 27 is used for controlling up and down movement of the short-stroke pressurizing hydraulic cylinder 31; the left and right output ports of the two/one-way throttle valve 28 are respectively connected with oil ports at the left and right tip ends of the bidirectional hydraulic lock 29, the two/one-way throttle valve 28 is used for controlling the movement speed of the short-stroke pressurizing hydraulic cylinder 31, the bidirectional hydraulic lock is used for the pressure holding of the pressurizing hydraulic cylinder 31, the left output port of the bidirectional hydraulic lock 29 is respectively connected with the second pressure sensor 12, the rodless cavity of the short-stroke pressurizing hydraulic cylinder 31 and the second orifice 13, the second orifice 13 is also connected with the input port at the ball end of the second two-position two-way electromagnetic ball valve 14, the output port at the tip end of the second two-position two-way electromagnetic ball valve 14 is connected with the oil tank 1, and the second orifice 13 and the second two-position two-way electromagnetic ball valve 14 are used for depressurization of the rodless cavity of the short-stroke pressurizing hydraulic cylinder 31; the right output port of the bidirectional hydraulic lock 29 is respectively connected with the rod cavity of the short-stroke pressurizing hydraulic cylinder 31 and the oil input port of the second directly operated type relief valve 30, the oil return port of the second directly operated type relief valve 30 is connected with the oil tank 1, and the second directly operated type relief valve 30 is used for preventing the overloading of the pressurizing cavity of the pressurizing hydraulic cylinder
31. The working principle of the disclosure is as follows: When the system is on standby, the alternating-current servo motor 18 drives the internal gear pump 17, and the minimum stable rotation speed is only 50 rpm; the three-phase asynchronous motor 21 drives the constant pressure variable piston pump 23, at this moment, the electromagnetic relief valve 25 is in the unloading state, so power consumption is extremely low, heat is few and noise is low. The quick descending of a movable plate: with the increase in the rotation speed of the alternating-current servo motor 18, the internal gear pump 17 outputs larger flow, the three-position four-way electro-hydraulic directional valve 5 is in the right position, and the electromagnet of the first two-position two-way electromagnetic ball valve 7 is not electrified, the flow output from the internal gear pump 17 is delivered to the rodless cavities of the movable plate driven long-stroke hydraulic cylinder 10 and the movable plate driven hydraulic cylinder 11 via the three-position four-way electro-hydraulic directional valve 5; oil returns to the rod cavities of the movable plate driven long-stroke hydraulic cylinder 10 and the movable plate driven hydraulic cylinder 11 and are connected with the oil inlet port of the three-position four-way electro-hydraulic directional valve 5 via the externally controlled one-way balance valve 8 and the first check valve 6, the movable plate driven long-stroke hydraulic cylinder realizes the differential connection, the piston rod rapidly extends, and the movable plate stably descends under the action of the externally controlled one-way balance valve 8. The slow descending of a movable plate: the three-position four-way electro-hydraulic directional valve 5 is in the right position, the electromagnet of the first two-position two-way electromagnetic ball valve 7 is electrified, the flow output from the internal gear pump 17 is delivered to the rodless cavities of the movable plate driven long-stroke hydraulic cylinder 10 and the movable plate driven hydraulic cylinder 11 via the three-position four-way electro-hydraulic directional valve 5; oil returns to the rod cavities of the movable plate driven long-stroke hydraulic cylinder 10 and the movable plate driven hydraulic cylinder 11 and then to the oil tank via the externally controlled one-way balance valve 8, the first two-position two-way electromagnetic ball valve 7 and the three-position four-way electro-hydraulic valve 5, the piston rods of the movable plate driven long-stroke hydraulic cylinder 10 and the movable plate driven hydraulic cylinder
11 slowly extend, the extension speed can be adjusted by controlling the rotation speed of the alternating-current servo motor 18. The ascending of a movable plate: the three-position four-way electro-hydraulic directional valve 5 is in the left position, the electromagnet of the first two-position two-way electromagnetic ball valve 7 is not electrified, the flow output from the internal gear pump 17 is delivered to the rod cavities of the movable plate driven long-stroke hydraulic cylinder 10 and the movable plate driven hydraulic cylinder 11 via the three-position four-way electro-hydraulic directional valve 5 and the check valve of the externally controlled one-way balance valve 8; the rodless cavities of the movable plate driven long-stroke hydraulic cylinder 10 and the movable plate driven hydraulic cylinder 11 return to the oil tank, the piston rods of the movable plate driven long-stroke hydraulic cylinder 10 and the movable plate driven hydraulic cylinder 11 return, and the return speed can be adjusted by controlling the rotation speed of the alternating-current servo motor.
In the above working processes, the oil supply amount of the internal gear pump is always matched with the working speed of the hydraulic cylinder without excessive flow, and therefore only a small-displacement directly operated type relief valve is arranged at the oil discharge port of the internal gear pump. The system is high in efficiency and little in heat. When the rotation speed of the internal gear pump does not exceed 2000 rpm, the noise is low.
Pressurization of a short-stroke pressurizing hydraulic cylinder: the three-position four-way electromagnetic directional valve 27 is in the left position, the electromagnet of the electromagnetic relief valve 25 is electrified, the electromagnet of the second two-position two-way electromagnetic ball valve 14 is not electrified, the oil supplied from the constant-pressure variable piston pump
23 is supplied to the rodless cavity of the short-stroke pressurizing hydraulic cylinder 31 via the check valve 26, the three-position four-way electromagnetic directional valve 27, the two/one-way throttle valve 28 and the bidirectional hydraulic lock 29, the oil returns to the rod cavity and then to the oil tank 1 via the bidirectional hydraulic lock 29, the two/one-way throttle valve 28 and the three-position four-way electromagnetic directional valve 27, and the second directly operated type relief valve 30 is used for preventing the overloading of the rod cavity of the short-stroke pressurizing hydraulic cylinder 31. Depressurization of a short-stroke pressurizing hydraulic cylinder: the electromagnet of the second two-position two-way electromagnetic ball valve 14 is electrified, the pressure of the rodless cavity of the short-stroke pressurizing hydraulic cylinder 31 returns to the oil tank through the second orifice 13 and the second two-position two-way electromagnetic ball valve 14. Because the orifice is small, when the piston rod of the short-stroke pressurizing hydraulic cylinder returns after depressurizing, the vibration and noise are reduced.
Returning of a short-stroke pressurizing hydraulic cylinder: the three-position four-way electromagnetic directional valve 27 is in the right position, the electromagnet of the electromagnetic relief valve 25 is electrified, the electromagnet of the second two-position two-way electromagnetic ball valve 14 is not electrified, the oil supplied from the constant-pressure variable piston pump 23 is supplied to the rod cavity of the short-stroke pressurizing hydraulic cylinder 31 via the third check valve 26, the three-position four-way electromagnetic directional valve 27, the two/one-way throttle valve 28 and the bidirectional hydraulic lock 29, and oil returns to the rodless cavity and then to the oil tank via the bidirectional hydraulic lock 29, the two/one-way throttle valve 28 and the three-position four-way electromagnetic directional valve 27. The action of the bidirectional hydraulic lock 29 is to achieve the pressure holding of the two cavities of the short-stroke pressurizing hydraulic cylinder. Since the locking device is added on the mechanical structure, the stroke length of the movable plate driven long-stroke hydraulic cylinder meets the movement movable plate movement requirement, while the stroke of the pressurizing hydraulic cylinder is only 25 mm which is only used for pressurization; to meet the output force requirement, the diameter of the pressurizing hydraulic cylinder is large, generally 300 mm-1000 mm; the stroke is shortened, so as to effectively reduce the manufacturing difficulty; the stroke is short, a few of supplied oil is desired when pressurization, the diameters of the relevant hydraulic valves for controlling the movement of the pressurizing hydraulic cylinder are small, thereby greatly decreasing the manufacturing cost, reducing the weight of the apparatus and lowering the occupied area. It is noted that embodiments of the disclosure are illustrative but not limiting, and thus the disclosure includes but is not limited to examples in specific embodiments, other embodiments made by those skilled in the art according to the technical solution of the disclosure are all included within the protective scope of the disclosure.
PREFERRED EMBODIMENTS
1. An energy-saving high-efficiency low-noise press hydraulic system, comprising: an oil tank, a first oil-absorbing oil-filtering device, a first directly operated type relief valve, a first pressure sensor, a three-position four-way electro-hydraulic directional valve, a first check valve, a first two-position two-way electromagnetic ball valve, an externally controlled one-way balance valve, a first orifice, a movable plate driven long-stroke hydraulic cylinder, a movable plate driven hydraulic cylinder, a second check valve, a first pressure gauge, an internal gear pump, an alternating-current servo motor and a first coupler; the internal gear pump being driven by the alternating-current servo motor via the first coupler and used for supplying pressure oil to the system; the oil absorbing port of the internal gear pump being connected with the oil tank through the first oil-absorbing oil-filtering device; the oil tank being used for storing, purifying and cooling oil, and the oil-absorbing oil-filtering device being used for filtering the oil; the oil discharge port of the internal gear pump being respectively connected with the first pressure gauge, the first pressure sensor, the oil inlet port of the first directly operated type relief valve, the oil inlet port of the three-position four-way electro-hydraulic directional valve, the ball end of the first check valve and the tip end of the second check valve, the first pressure gauge being used for displaying the working pressure of the internal gear pump, the first pressure sensor converting a pressure signal into an electrical signal, and the first directly operated type relief valve being used for setting the maximum working pressure of the internal gear pump; the oil outlet port of the first directly operated type relief valve being connected with the oil tank; the oil return port of the three-position four-way electro-hydraulic directional valve being connected with the oil tank, the left output port of the three-position four-way electro-hydraulic directional valve being connected with the input port of the first two-position two-way electromagnetic ball valve, the output port of the first two-position two-way electromagnetic ball valve being respectively connected with the tip end of the first check valve and the lower port of the externally controlled one-way balance valve, and the three-position four-way electro-hydraulic directional valve, the first two-way electromagnetic ball valve and the first check valve being used for achieving the differential control of the movable plate driven long-stroke hydraulic cylinder and the movable plate driven hydraulic cylinder; the upper port of the externally controlled one-way balance valve being respectively connected with rod cavities of the movable plate driven long-stroke hydraulic cylinder and the movable plate driven hydraulic cylinder, the rodless cavities of the movable plate driven long-stroke hydraulic cylinder and the movable plate driven hydraulic cylinder being connected with the right output port of the three-position four-way electro-hydraulic directional valve and connected with the externally controlled port of the externally controlled one-way balance valve through the first orifice, and the externally controlled one-way balance valve being used for controlling the movable plate driven long-stroke hydraulic cylinder and the movable plate driven hydraulic cylinder to stably descend.
2. The energy-saving high-efficiency low-noise press hydraulic system according to embodiment 1, the energy-saving high-efficiency low-noise press hydraulic system also comprising: a second pressure sensor, a second orifice, a second two-position two-way electromagnetic ball valve, a second oil-absorbing oil-filtering device, a three-phase asynchronous motor, a second coupler, a constant-pressure variable piston pump, a second pressure gauge, an electromagnetic relief valve, a third check valve, a three-position four-way electromagnetic directional valve, a two/one-way throttle valve, a bidirectional hydraulic lock, a second directly operated type relief valve and a short-stroke pressurizing hydraulic cylinder; the constant-pressure variable piston pump being driven by the three-phase asynchronous motor via the second coupler and used for supplying oil to the pressurizing hydraulic cylinder; the oil absorbing port of the constant-pressure variable piston pump being connected with the oil tank via the second oil-absorbing oil-filtering device, and the oil-absorbing oil-filtering device being used for filtering oil; the oil discharge port of the constant-pressure variable piston pump being respectively connected with the second pressure gauge, the oil inlet port of the electromagnetic relief valve and the tip end of the third check valve, and the second pressure gauge being used for displaying the working pressure of the system; the oil return port of the electromagnetic relief valve being connected with the oil tank, and the electromagnetic relief valve being used for setting the maximum working pressure of the pressurizing hydraulic cylinder, if necessary, achieving the unloading of the system; the ball end of the third check valve being respectively connected with the ball end of the second check valve and the oil inlet port of the three-position four-way electromagnetic directional valve; the oil return port of the three-position four-way electromagnetic directional valve being connected with the oil tank, and the left and right output ports of the three-position four-way electromagnetic directional valve being respectively connected with the left and right input ports of the two/one-way throttle valve in an oil-return throttling manner, the three-position four-way electromagnetic directional valve being used for controlling up and down movement of the short-stroke pressurizing hydraulic cylinder; the left and right output ports of the two/one-way throttle valve being respectively connected with oil ports at the left and right tip ends of the bidirectional hydraulic lock, the two/one-way throttle valve being used for controlling the movement speed of the short-stroke pressurizing hydraulic cylinder, the bidirectional hydraulic lock being used for the pressure holding of the pressurizing hydraulic cylinder, the left output port of the bidirectional hydraulic lock being respectively connected with the second pressure sensor, the rodless cavity of the short-stroke pressurizing hydraulic cylinder and the second orifice, the second orifice being also connected with the input port at the ball end of the second two-position two-way electromagnetic ball valve, the output port at the tip end of the second two-position two-way electromagnetic ball valve being connected with the oil tank, the second orifice and the second two-position two-way electromagnetic ball valve being used for depressurization of the rodless cavity of the short-stroke pressurizing hydraulic cylinder; the right output port of the bidirectional hydraulic lock being respectively connected with the rod cavity of the short-stroke pressurizing hydraulic cylinder and the oil inlet port of the second directly operated type relief valve, the oil return port of the second directly operated type relief valve being connected with the oil tank, and the second directly operated type relief valve being used for preventing the overloading of the pressurizing cavity of the pressurizing hydraulic cylinder.

Claims (2)

CONCLUSIESCONCLUSIONS 1. Een energiebesparend, hoogefficiënt en geluidsarm hydraulisch systeem voor persen, gekenmerkt doordat het bestaat uit: een olietank, een eerste olieabsorberend filter, een eerste continu werkende overdrukklep, een eerste druksensor, een 3-positie 4-weg elektrohydraulische keerklep, een eerste terugslagklep, een eerste 2-positie 2-weg elektromagnetische kogelklep, een extern gestuurde eenweg balanceerklep, een eerste smooropening, een door een bewegende plaat aangedreven hydraulische cilinder met lange slag, een door een bewegende plaat aangedreven hydraulische cilinder, een tweede terugslagklep, een eerste manometer, een inwendig bekrachtigde tandwielpomp, een AC-servomotor en een eerste koppeling; de genoemde interne tandwielpomp wordt aangedreven door de AC-servomotor via de eerste koppeling voor het leveren van olie onder druk aan het system; de aanzuigopening van deze interne tandwielpomp is verbonden met de olietank via het eerste olieaanzuigfilter; de olietank wordt gebruikt voor het opslaan, zuiveren en koelen van de olie, en het olieaanzuigfilter wordt gebruikt voor het filteren van de olie; de uitlaatopening van deze interne tandwielpomp is verbonden met de eerste manometer, de eerste druksensor, de olie-inlaat van de eerste ontlastklep met open uiteinde, de olie-inlaat van de 3-positie 4- weg klep, de olie-inlaat van de eerste ontlastklep met open uiteinde en de olie-inlaat van de eerste ontlastklep met open uiteinde; de eerste manometer wordt gebruikt om de werkdruk van de interne tandwielpomp aan te geven, de eerste druksensor zet het druksignaal om in een elektrisch signaal, en de eerste ontlastklep met open uiteinde wordt gebruikt om de maximale werkdruk van de interne tandwielpomp in te stellen; de uitlaatopening van bovengenoemde ontlastklep met open uiteinde wordt aangesloten op de olietank; de retouropening van bovengenoemde 3-positie1. An energy-saving, high-efficiency and low-noise hydraulic system for presses, characterized in that it consists of: an oil tank, a first oil-absorbing filter, a first continuously operating pressure relief valve, a first pressure sensor, a 3-position 4-way electro-hydraulic check valve, a first check valve , a first 2-position 2-way solenoid ball valve, an externally controlled one-way balancing valve, a first throttle orifice, a moving plate actuated long stroke hydraulic cylinder, a moving plate actuated hydraulic cylinder, a second check valve, a first pressure gauge , an internally excited gear pump, an AC servo motor and a first clutch; said internal gear pump is driven by the AC servo motor through the first clutch for supplying pressurized oil to the system; the suction port of this internal gear pump is connected to the oil tank through the first oil suction filter; the oil tank is used for storing, purifying and cooling the oil, and the oil suction filter is used for filtering the oil; the outlet port of this internal gear pump is connected to the first pressure gauge, the first pressure sensor, the oil inlet of the first open-ended relief valve, the oil inlet of the 3-position 4-way valve, the oil inlet of the first open-ended relief valve and the oil inlet of the first open-ended relief valve; the first pressure gauge is used to indicate the working pressure of the internal gear pump, the first pressure sensor converts the pressure signal into an electrical signal, and the first open-ended relief valve is used to set the maximum working pressure of the internal gear pump; the outlet port of the above-mentioned open-ended relief valve is connected to the oil tank; the return opening of the above 3 position 4-weg elektrohydraulische klep wordt aangesloten op de olietank, de linkeruitgangsopening van de 3-positie 4-weg elektrohydraulische keerklep is verbonden met de ingangsopening van de eerste 2-positie 2-weg magneetkogelklep, de uitgangsopening van de eerste 2-positie 2-weg magneetkogelklep is verbonden respectievelijk met het uiteinde van de eerste terugslagklep en de benedenoepning van de extern gestuurde eenweg tegengewichtsklep, de 3-positie 4-weg elektrohydraulische keerklep, de eerste tweeweg magneetkogelklep en de eerste terugslagklep worden gebruikt om differentiële besturing van de door de bewegende plaat aangedreven hydraulische cilinder met lange slag en de door de bewegende plaat aangedreven hydraulische cilinder te bewerkstelligen; de bovenopening van de externe eenweg klep, die in evenwicht brengt, wordt verbonden respectievelijk met de staafkamer van door de bewegende plaat gedreven hydraulische cilinder met lange slag en door de bewegende plaat gedreven hydraulische cylinder; de staafloze kamer van door de bewegende plaat gedreven hydraulische cilinder met lange slag en door de bewegende plaat gedreven hydraulische cilinder worden verbonden met de output aan de rechterhand van de 3-positie 4-weg elektrohydraulische omkeerklep, en verbonden met de externe controleopening van de externe eenweg klep, die in evenwicht brengt, door het eerste gasgat, de externe eenweg-balansklep wordt gebruikt om de hydraulische cilinder met lange slag te controleren, die door de bewegende plaat wordt gedreven.4-way electro-hydraulic valve is connected to the oil tank, the left output port of the 3-position 4-way electro-hydraulic check valve is connected to the input port of the first 2-position 2-way solenoid ball valve, the output port of the first 2-position 2-way solenoid ball valve is connected respectively with the end of the first check valve and the bottom opening of the externally controlled one-way counterweight valve, the 3-position 4-way electro-hydraulic check valve, the first two-way solenoid ball valve and the first check valve are used to provide differential control of the moving plate long stroke driven hydraulic cylinder and the moving plate driven hydraulic cylinder; the top opening of the external one-way balancing valve is respectively connected with the rod chamber of moving plate driven long stroke hydraulic cylinder and moving plate driven hydraulic cylinder; the rodless chamber of long stroke moving plate driven hydraulic cylinder and moving plate driven hydraulic cylinder are connected to the right hand output of 3 position 4 way electro-hydraulic reversing valve, and connected to the external control port of the external one-way valve, which balances, through the first gas hole, the external one-way balance valve is used to control the long-stroke hydraulic cylinder, which is driven by the moving plate. 2. Een energie-efficiënt en met geringe geluidssterkte pers hydraulisch systeem volgens aanvraag 1, gekenmerkt in die zin dat: het energie-efficiént en met geringe geluidssterkte pers hydraulisch systeem verder omvat: een tweede druksensor, een tweede smoorklep, een tweede 2-positie 2-weg elektromagneetkogelklep, een tweede olieaanzuigfilter, een asynchrone driefasenmotor, een tweede koppeling, een constante druk variabele zuigerpomp, een tweede manometer, een elektromagnetische ontlastklep, een derde terugslagklep, een 3-positie 4-weg elektromagnetische keerklep, een dubbele een-weg gasklep, een tweeweg hydraulisch slot, een tweede direct werkende ontlastklep en een korte slag onder druk gezette hydraulische cilinder;2. An energy-efficient and low-noise press hydraulic system according to claim 1, characterized in that: the energy-efficient and low-noise press hydraulic system further comprises: a second pressure sensor, a second throttle valve, a second 2-position 2-way solenoid ball valve, a second oil suction filter, a three-phase asynchronous motor, a second clutch, a constant pressure variable piston pump, a second pressure gauge, an electromagnetic relief valve, a third check valve, a 3-position 4-way electromagnetic check valve, a double one-way throttle valve, a two-way hydraulic lock, a second direct-acting relief valve and a short-stroke pressurized hydraulic cylinder; de zuigerpomp met constante druk wordt aangedreven door een asynchrone driefasenmotor via een tweede koppeling voor de toevoer van olie naar de onder druk staande hydraulische cylinder; de aanzuigopening van deze pomp met constante druk is verbonden met de olietank via een tweede olieaanzuigfilter, dat wordt gebruikt voor het filteren van de olie; de uitlaatopening van deze pomp met constante druk is verbonden respectievelijk met een tweede manometer, de olie-inlaat van de elektromagnetische overdrukklep en het uiteinde van de derde keerklep; de genoemde tweede manometer wordt gebruikt om de werkdruk van het systeem aan te geven, de bovengenoemde elektromagnetische afblaasklep retouropening is verbonden met de olietank, de elektromagnetische afblaasklep wordt gebruikt om de maximale werkdruk van de onder druk gezette hydraulische cilinder in te stellen, indien nodig, om het systeem te lossen; het bovengenoemde derde kogeleinde van de keerklep is verbonden respectievelijk met het tweede kogeleinde van de keerklep, en de 3-positie 4-weg elektromagnetische keerklep; deze retouropening van de 3-positie 4-weg elektromagnetische keerklep is verbonden met de olietank; die uitgangsopeningen aan de linker- en rechterkant van deze 3-positie 4-weg elektromagnetische keerklep zijn verbonden met de dubbele een-weg smoorklep aan de linker- en rechterkant; de 3-positie 4-weg elektromagnetische keerklep wordt gebruikt om de op- en neergaande beweging van hydraulische cilinders met korte slag onder druk te controleren; deze output aan de linker- en rechterkant van dubbele een-weg smoorklep wordt verbonden met die uiteinden aan de linker- en rechterkant van het hydraulische slot met twee richtingen; de dubbele een-weg smoorklep wordt gebruikt om de bewegingssnelheid van de hydraulische cilinder met korte slag te controleren; het hydraulische slot met twee richtingen wordt gebruikt om druk in de hydraulische cilinder te handhaven; de output aan de linkerkant van het hydraulische slot met twee richtingen wordt verbonden met de tweede druksensor, de staafloze kamer van de hydraulische cilinder met korte slag en de output aan de linkerkant van het hydraulische slot met twee richtingen; de tweede gashendel wordt ook verbonden met de input van het kogeleind van de 2-positie 2-weg elektromagnetische kogelklep; de uiteindeoutput van de 2-positie 2-weg elektromagnetische kogelklep wordt verbonden met de olietank; de tweede gashendel en de 2-positie 2-weg elektromagnetische kogelklep worden gebruikt voor drukvermindering van de staafloze kamer van de korte slag onder druk gezette hydraulische cylinder; de output aan de rechterkant van het bovengenoemde hydraulische slot met twee richtingen wordt verbonden respectievelijk met de met de korte slag onder druk gezette hydraulische cilinder en de olie-inlaat van de tweede direct werkende ontlastklep; de retouropening van de tweede direct werkende ontlastklep is verbonden met de olietank en de tweede direct werkende ontlastklep wordt gebruikt om overbelasting van de drukkamer van de onder druk staande hydraulische cilinder te voorkomen.the constant-pressure piston pump is driven by a three-phase asynchronous motor through a second coupling for supplying oil to the pressurized hydraulic cylinder; the suction port of this constant pressure pump is connected to the oil tank through a second oil suction filter, which is used for filtering the oil; the outlet port of this constant pressure pump is respectively connected to a second pressure gauge, the oil inlet of the solenoid pressure relief valve and the end of the third check valve; the said second pressure gauge is used to indicate the working pressure of the system, the above solenoid relief valve return port is connected to the oil tank, the solenoid relief valve is used to set the maximum working pressure of the pressurized hydraulic cylinder, if necessary, to fix the system; the aforementioned third ball end of the check valve is respectively connected to the second ball end of the check valve, and the 3-position 4-way solenoid check valve; this return port of the 3 position 4 way solenoid check valve is connected with the oil tank; those exit ports on the left and right sides of this 3 position 4 way solenoid check valve are connected to the dual one way throttle valve on the left and right sides; the 3-position 4-way solenoid check valve is used to control the up and down movement of pressurized short-stroke hydraulic cylinders; this output on the left and right side of double one-way throttle valve will be connected to those ends on the left and right side of two-way hydraulic lock; the double one-way throttle valve is used to control the moving speed of the short-stroke hydraulic cylinder; the two-way hydraulic lock is used to maintain pressure in the hydraulic cylinder; the output on the left side of the two-way hydraulic lock is connected to the second pressure sensor, the rodless chamber of the short-stroke hydraulic cylinder, and the output on the left side of the two-way hydraulic lock; the second throttle is also connected to the ball end input of the 2-position 2-way solenoid ball valve; the end output of the 2-position 2-way electromagnetic ball valve is connected to the oil tank; the second throttle lever and the 2-position 2-way solenoid ball valve are used for pressure reduction of the rodless chamber of the short-stroke pressurized hydraulic cylinder; the output on the right side of the above-mentioned two-way hydraulic lock is connected to the short-stroke pressurized hydraulic cylinder and the oil inlet of the second direct acting relief valve respectively; the return port of the second direct-acting relief valve is connected to the oil tank, and the second direct-acting relief valve is used to prevent overloading of the pressure chamber of the pressurized hydraulic cylinder.
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