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GB2592220A - Linear actuator assembly control unit - Google Patents

Linear actuator assembly control unit Download PDF

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Publication number
GB2592220A
GB2592220A GB2002301.6A GB202002301A GB2592220A GB 2592220 A GB2592220 A GB 2592220A GB 202002301 A GB202002301 A GB 202002301A GB 2592220 A GB2592220 A GB 2592220A
Authority
GB
United Kingdom
Prior art keywords
control unit
valve
port
unit according
linear actuator
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.)
Granted
Application number
GB2002301.6A
Other versions
GB202002301D0 (en
GB2592220B (en
Inventor
John Pegram Christopher
Terance Hynes Paul
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
METROL SPRINGS Ltd
Original Assignee
METROL SPRINGS Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by METROL SPRINGS Ltd filed Critical METROL SPRINGS Ltd
Priority to GB2002301.6A priority Critical patent/GB2592220B/en
Publication of GB202002301D0 publication Critical patent/GB202002301D0/en
Publication of GB2592220A publication Critical patent/GB2592220A/en
Application granted granted Critical
Publication of GB2592220B publication Critical patent/GB2592220B/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/021—Installations or systems with accumulators used for damping
    • 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
    • B30B15/163—Control arrangements for fluid-driven presses for accumulator-driven presses
    • 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
    • B30B15/166—Electrical control arrangements
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/027—Installations or systems with accumulators having accumulator charging devices
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/027—Installations or systems with accumulators having accumulator charging devices
    • F15B1/0275—Installations or systems with accumulators having accumulator charging devices with two or more pilot valves, e.g. for independent setting of the cut-in and cut-out pressures
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/027—Installations or systems with accumulators having accumulator charging devices
    • F15B1/033—Installations or systems with accumulators having accumulator charging devices with electrical control means
    • 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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/50—Monitoring, detection and testing means for accumulators
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/50—Monitoring, detection and testing means for accumulators
    • F15B2201/505—Testing of accumulators, e.g. for testing tightness
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/50—Monitoring, detection and testing means for accumulators
    • F15B2201/51—Pressure detection
    • 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
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • 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
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • 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
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief 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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/526—Pressure control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid 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
    • F15B2211/50—Pressure control
    • F15B2211/575—Pilot pressure control
    • F15B2211/5756—Pilot pressure control for opening a valve
    • 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
    • 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
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load 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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6343—Electronic controllers using input signals representing a temperature
    • 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
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • 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
    • F15B2211/6653—Pressure 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/67—Methods for controlling pilot 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
    • F15B2211/70—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
    • 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
    • F15B2211/7052—Single-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

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

Abstract

A control unit 140 for a hydraulic type linear actuator assembly is provided. The control unit 140 comprises: first and second ports (1121, 1122 Figure 2) for respectively connecting the control unit 140 to an accumulator 160, and a manifold block 120. A fluid passageway connects the first port to the second port, the fluid passageway including first and second flow channels. A force generator valve (1200, Figure 2) is associated with the first flow channel of the fluid passageway, the force generator valve configured to control the flow of fluid from the manifold block 120 of into the accumulator 160 via the control unit 140, and arranged to be actuated when a pressure force in the first flow channel reaches a pre-set value. A solenoid valve 143 is associated with the second flow channel of the fluid passageway, the solenoid valve 143 configured to control the flow of fluid from the accumulator 160 to the manifold block 120 via the control unit 140. The control unit 140 further comprises an electronic controller, remotely operable and configured to select the pre-set value from one of a plurality of different stored pressure force values.

Description

Linear Actuator Assembly Control Unit
Field of the Invention
The present invention relates to a linear actuator control unit, and in particular to a control unit for a linear actuator assembly incorporating hydraulic cylinders. More particularly, the present invention relates to a control unit for a hydraulic cylinder actuator assembly for use in a metal pressing process.
Description of the Related Art
Linear actuators are mechanisms that produce linear forces. Linear actuators have utility in a wide range of applications, notably in industrial machinery, for automated movement of components of the machinery or for damping such components. Two types of linear actuator of particular interest are hydraulic cylinders and pneumatic cylinders. Hydraulic and pneumatic cylinders use a working fluid, in the case of a hydraulic cylinder typically a hydraulic oil and in the case of a pneumatic cylinder typically an inert gas, to control the movement of a piston either outwardly (or inwardly) of a cylinder portion.
One particular use of a hydraulic or pneumatic cylinder is in metal-pressing/stamping machinery. In such a use, a 'spring' type pneumatic cylinder is typically referred to as a 'gas spring'.
In a typical mechanical press used in a metal pressing process, the ram drives the upper die part of a press tool downwardly towards the lower die part of the press tool, and the workpiece, or 'blank', is supported therebetween by the blank-holder.
The function of the blank-holder is generally to hold the workpiece in place during the pressing operation and to auto-lift the pressed workpiece from the lower die following pressing. The blank-holder typically takes the form of a clamp about the perimeter of the workpiece. 2 -
Whilst the position of the lower die is generally fixed, the blank-holder is usually configured to be movable so as to allow the upper die to engage the workpiece at a position a short distance above the lower die, and to allow the workpiece to then travel downwardly with the upper die before contacting the lower die. A 'press-cushion' (also called a 'die' or 'bed' cushion) is conventionally provided under the blank-holder. The primary function of the press cushion is to provide a flexible, controlled, blank-holder force, to control material flow of the workpiece during the pressing operation.
Typically, such a press-cushion comprises of a single motor unit, often an air-bag, equipped with a plurality of cushion pins for engaging the blank-holder at different locations. As will be appreciated, it is often the case that a single press machine may be used for pressing of different parts, and so the cushion pins may be moved to engage the blank-holder at different locations to facilitate localized control of the blank-holder force to optimise material flow to suit the particular shape of the pressing. Although such conventional press cushions are generally effective, they incur certain practical disadvantages, and so in certain applications it may be desirable to replace such a press cushion with an array of hydraulic cylinders or gas springs.
The replacement of such press cushions with hydraulic cylinders or gas springs overcomes many of the problems encountered with conventional press cushions and it is known that hydraulic cylinders/gas springs function effectively in substitute of a conventional press cushion.
The linear actuator assembly generally includes a control unit configured to control the rate of retraction of the pistons of the hydraulic/pneumatic cylinders, and the delayed return of the pistons of the hydraulic/pneumatic cylinders from a retracted position during a pressing or stamping process. 3 -
In linear actuator assemblies utilising hydraulic cylinders, the control unit sometimes employs a pressure valve and a solenoid valve to control the reciprocating motion of the pistons of the hydraulic cylinders.
Known control units for linear actuator assemblies of the hydraulic type are limited in their functionality, simply only being able to be used to control the rate of retraction, the amount of delay in a retracted state before return of a piston back to its extended position, and/or the return rate of a piston back to its extended position.
Furthermore, known control units are configured to function with a single tool or specific arrangement of linear actuators in linear actuator assembly arrangement. This leads to the requirement for a different control unit for a tool change or in cases where the same control unit is to be used, reconfiguration of the control unit for the new tool or new arrangement of the linear actuators. This can lead to severe down time while the system is being reconfigured and/or set-up for the new application.
It is desirable therefore to provide a control unit for a hydraulic type linear actuator assembly which is configured to be used with a plurality of different tool configurations and/or linear actuator arrangements, and which allows for easy and convenient changes in the settings of the reciprocating motion of the pistons of the hydraulic cylinders when a tool change or change in the arrangement of the linear actuators required.
It is also desirable to provide a control unit for a hydraulic type linear actuator assembly which allows other properties of the linear actuator assembly, apart from the control rate of retraction of the pistons, to be monitored, controlled and/or adjusted. 4 -
Brief Summary of the Invention
According to an aspect of the invention, there is provided a control unit for a hydraulic type linear actuator assembly, the control unit comprising: a first port for connecting the control unit to an accumulator; a second port for connecting the control unit to a manifold; a fluid passageway connecting the first port to the second port, said fluid passageway comprising first and second flow channels; a force generator valve associated with the first flow channel of the fluid passageway, said force generator valve configured to control the flow of fluid from a manifold block of a linear actuator assembly into an accumulator of said linear actuator via the control unit, and arranged to be actuated when a pressure force in the first flow channel reaches a preset value; and a solenoid valve associated with the second flow channel of the fluid passageway, said solenoid valve configure to control the flow of fluid from said accumulator to said manifold block via the control unit; wherein the control unit further comprises an electronic controller configured to select said preset value from one of a plurality of different stored pressure force values.
The control unit in accordance with the invention may be used with a plurality of different tools and/or linear actuator configurations. The electronic controller allows for the required pressure force to actuate the force generator valve to be easily selected and set for a given tool or linear actuator configuration.
Preferably, the electronic controller is configured to change a selected preset value to a different preset value from one of said plurality of stored pressure force values.
Preferably, the electronic controller comprises a programmable logic controller.
Preferably, the control unit further comprises a pilot operated valve assembly in fluid communication with the fluid passageway and associated with the electronic controller. The pilot operated valve assembly allows for a variation in the tolerable pressure range within the first flow channel before reaching a value capable of actuating the force generator valve.
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Preferably, the pilot operated valve assembly comprises a pilot-operated, balanced piston relief main stage with integral T-8A control cavity, and a 24 VDC coil with ISO/DIN 43650, Form A connector with TVS Diode.
Preferably, the control unit further comprises a check valve arranged to protect the solenoid valve from pressure transients.
Preferably, the control unit further comprises a check cartridge associated with the check valve, the check cartridge positioned between the check valve and the solenoid valve.
Preferably, the control unit further comprises a shuttle valve in fluid communication with the fluid passageway.
Preferably, the shuttle valve is a single ball shuttle valve with a signal at port 3 of the valve.
Preferably, the control unit further comprises a relief valve in fluid communication with the fluid passageway and a check cartridge associated with the relief valve.
Preferably, the first port and the second port are positioned on perpendicular faces of the control unit.
Preferably, the control unit further comprises a third port in fluid communication with the fluid passageway, said third port configured to facilitate connection of the control unit to a tank containing working fluid for the linear actuator assembly Preferably, the control unit further comprises a fourth port in fluid communication with the fluid passageway, said fourth port configured to facilitate connection of the control unit to a pressure valve.
Preferably, the control unit further comprises a fifth port, said fifth port configured to facilitate connection of the control unit to a tank sensor for monitoring the volume of working fluid within the linear actuator assembly in use. 6 -
Preferably, the control unit further comprises one or more auxiliary ports for facilitating connection of one or more auxiliary valves and/or sensors to the control unit.
Preferably, the control unit further comprises a plurality of fasteners configured to facilitate the mounting of the control unit onto a surface.
Preferably, the plurality of fasteners are eyebolt type fasteners.
Other aspects of the invention are as set out in the claims herein.
Brief Description of the Drawings
For a better understanding of the invention and to show how the same may be carried into effect, there will now be described by way of example only, specific embodiments, methods and processes according to the present invention with reference to the accompanying drawings in which: Fig. 1 shows an arrangement of a linear actuator assembly in which the control unit in accordance with the invention may be used.
Fig. 2 shows an embodiment of a control unit in accordance with the invention; Fig. 3 is a view from the front of the control unit of Fig. 2; Fig. 4 is a view from above of the control unit of Fig. 2; Fig. 5 is a view from behind of the control unit of Fig. 2; Fig. 6 is a view from below of the control unit of Fig. 2; Fig. 7 is a view from a first side of the control unit of Fig. 2; Fig. 8 is a view from a second side of the control unit of Fig. 2; and 7 -
Detailed Description of the Embodiments
There will now be described by way of example a specific mode contemplated by the inventors. In the following description numerous specific details are set forth in order to provide a thorough understanding. It will be apparent however, to one skilled in the art, that the present invention may be practiced without limitation to these specific details. In other instances, well known methods and structures have not been described in detail so as not to unnecessarily obscure the description.
Aspects of the present invention relate to a control unit for a linear actuator assembly. The control unit of the invention is specifically adapted for use with a linear actuator assembly which incorporates linear actuators in the form of a hydraulic cylinder.
One use for such a linear actuator assembly that is of particular interest to the present applicant is an assembly for supporting a blank-holder in a metal-pressing machine (herein after referred to as a metal press). Thus, in the specific embodiment described herein, the control unit is described in relation to a linear actuator assembly which incorporates a hydraulic cylinder suitable for exerting a force on a blank-holder resting thereon in a metal press. It will of course be appreciated however that, although the control unit of the invention described herein is for a linear actuator assembly that incorporates a hydraulic cylinder suitable for exerting a force on a blank-holder resting thereon in a metal press, the invention could alternatively be used in an assembly incorporating alternative types of linear actuators for a different application, for example, a hydraulic tam' cylinder.
Moreover, it will be appreciated that hydraulic cylinders, and linear actuators more generally, have utility in a number of different applications other than for supporting a blank-holder in a metal press, and it should be understood that the invention is not limited in this regard to any one particular intended application rather has broader utility. 8 -
Referring to Fig. 1, an arrangement of a linear actuator assembly 100 in which a control unit in accordance with the invention may be utilised is shown.
The linear actuator assembly 100 comprises a plurality of linear actuators in the form of hydraulic cylinders 110. As known in the art, each of the hydraulic cylinders comprises piston and a chamber. The chamber is filled with a working fluid in the form of oil. The piston of each hydraulic cylinder 110 is arranged such that it can slide into and out of the chamber while maintaining a seal such that the oil within the chamber does not leak out via the piston.
The plurality of hydraulic cylinders 110 are configured for use in substitute of a press cushion in metal pressing machinery. Thus, in the example arrangement, the function of the plurality of hydraulic cylinders 110 is to exert a retarding and restorative force on a blank-holder, supported on said hydraulic cylinders 110, in order to control the flow of a workpiece (typically a flat metal sheet) held by the blank-holder during a pressing operation.
The hydraulic cylinders 110 are each connected to a manifold block 120 of the linear actuator assembly 100 by a hose 130. The hose 130 is configured to fluidly connect an associated hydraulic cylinder 110 to the manifold block 120.
A control unit 140 is connected to the manifold block 120 such that it is in fluid communication with the manifold block 120. In this way, the control unit 140 is in fluid communication with the hydraulic cylinders 110 via said manifold block 120.
The control unit 140 may be connected to the manifold block 120 by suitable means known in the art. For example, as shown in Fig. 1, the control unit 140 may be connected to the manifold block 120 by a hose 150.
The control unit 140 comprises a fluid passageway (not shown) having first and second flow channels (not shown). The control unit 140 includes a first valve means 142 in the form of a force generator valve and a second valve means 143 in the form of a solenoid valve. 9 -
The force generator valve 142 is arranged to control the flow of fluid from the manifold block 120 into an accumulator 160 via the control unit 140. The solenoid valve 143 is arranged to control the flow of fluid from the accumulator 160 into the manifold block 120 via the control unit 140.
The control unit 140 also includes a pressure valve 144 which is configured to set and/or adjust the predetermined/default value Po of the force required to actuate the force generator valve 142. The pressure valve 144 is connected to a main body of the control unit 140 by a pipe 145.
The accumulator 160 is positioned in fluid communication with the control unit 140, and is coupled to the control unit 140. The accumulator 160 may be connected to the control unit 140 by any suitable means, for example by a hose or other fluid connector.
The accumulator 160 of the linear actuator assembly 100 is generally in the form of a compressed gas/hydro-pneumatic accumulator having a first chamber adapted to receive the working fluid, and a second sealed chamber filled with a compressible gas, for example nitrogen.
The control unit 140 is configured for use with a specific tool or arrangement of linear actuators, and the predetermined/default value Po is set on setup of the metal pressing process for optimal functionality of the linear actuator assembly depending on the tool or linear actuator arrangement being used. Reconfiguration of the whole system is required if the tool or linear actuator arrangement is changed.
Referring to Figs. 2 to 8, an embodiment of a control unit 1000 in accordance with the invention is shown.
The control unit 1000 is intended to substituted for the previously described control unit 140 in the linear actuator assembly.
Similarly to the previously described control unit, the control unit 1000 of the invention comprises a first valve means 1200 in the form of a force generator valve -10 -arranged to control the flow of fluid from the manifold block into the accumulator via the control unit 1000; a second valve means 1300 in the form of a solenoid valve arranged to control the flow of fluid from the accumulator into the manifold block via the control unit 1000.
The control unit 1000 of the invention differs from the earlier described control unit 140, in that it further comprises an electronic controller configured to set or select the pressure force required to actuate the force generator valve to/from one of a plurality of different stored pressure force values. Moreover, incorporation of the electronic controller provides the control unit 1000 with remote operation capabilities. Remote operation thereby obviates the need to stop machining, manually adjusting the equipment and restarting machining. Remote operation of said electronic controller can be conducted by way of an electronic device (such as a laptop, or other remote operable hardware) either on the premises of the apparatus connected to said controller or from an entirely different site, provided appropriate connection and feedback loops are incorporated.
The structure of the embodiment of the control unit 1000 will now be described. It would be understood that the control unit 1000 may be of a different structure while still providing the benefits and advantages of the invention.
The control unit 1000 comprises a housing 1100, which in the embodiment shown, is substantially cuboid in shape. The housing 1100 has a first face 1111 (Fig. 3), a second face 1112 (Fig. 4), a third face 1113 (Fig. 5), a fourth face 1114 (Fig. 6), a fifth face 1115 (Fig. 7), and a sixth face 1116 (Fig. 8).
A first port 1121 is positioned on the first face 1111 of the housing 1100 and a second port 1122 is positioned on the second face 1112 of the housing 1100. In the embodiment shown, the first port 1121 and second port 1122 are located on perpendicular faces of the housing 1100, however, it would be understood that the first port 1121 and second port 1122 could be located on opposite faces of the housing 1100.
A fluid passageway (not shown) having first and second flow channels is contained within the housing 1100, with the first port 1121 positioned at a first end of the fluid passageway and the second port 1122 positioned at a second end of the fluid passageway.
The force generator valve 1200 is associated with the first flow channel, the first flow channel providing the pathway for the flow of fluid from the manifold block to the accumulator via the control unit 1000. The force generator valve 1200 will be actuated when the pressure force in the first flow channel reaches a preset value. The preset value corresponding to a set or selected pressure force from one of the different stored pressure force values of the electronic controller.
The solenoid valve 1300 is associated with the second flow channel, the second flow channel proving the pathway for the flow of fluid from the accumulator to the manifold block via the control unit 1000.
The manifold block forming part of the linear actuator assembly is fluidly connected to the control unit 1000 via the first port 1121. In the embodiment shown, this is achieved by means of a 1.500 code 62 four bolt flange connector tube type fitting. It would be understood that other suitable means may be utilized to fluidly connect the manifold block to the control unit.
The accumulator forming part of the linear actuator assembly is fluidly connected to the control unit 1000 via the second port 1122. In the embodiment shown, this is achieved by means of a 1.500 code 62 four bolt flange connector tube type fitting. It would be understood that other suitable means may be utilized to fluidly connect the manifold block to the control unit.
A third port 1123 is located on the first face 1111 of the housing 1100 for facilitating connection of the control unit 1000 to a tank containing working fluid i.e. oil for priming the linear actuator assembly prior to use. In the embodiment shown, the third port 1123 is a SAE size 20 threaded port. It would be understood that the third port may be of a different configuration.
A fourth port 1124 is located on the second face 1112 of the housing 1100 for receiving the pipe configured to connect a pressure sensor to the housing 1100.
The fourth port 1124 may instead be used to connect a pressure valve to the -12 -housing 1100 in a similar way as in the previously described control unit. In the embodiment shown, the fourth port 1124 is a BSPP 0.250-19 threaded port. Said pressure sensor is then operatively connected to a Programmable Logic Controller (not shown). Said PLC allows the user to: monitor rate of cylinder return (duration the check valve remains open to return springs); monitor cylinder pressure (pressure that the force generator valve 142 sets the relief valve to open at); monitor nitrogen pressure (pressure in the accumulator 160 and the pressure at which the springs are returned); monitor system temperature (by way of a temperature sensor (not shown), monitoring the oil temperature of the system); monitor system pressure (the oil pressure of the system); monitor the oil level within the accumulator 160; and to control the force curve during the downward stroke of the piston during machining.
A fifth port 1125 is located on the second face 1112 of the housing 1100. The fifth port 1125 is configured to be connected to a temperature sensor. In the embodiment shown, the fourth port 1124 is a BSPP 0.500-14 threaded port Sensor connection ports 1126, 1127, 1128 are provided on the second face 1112 of the housing 1100 to facilitate connection of one or more sensors to the control unit 1100. Such sensors include pressure and temperature sensors, or a tank sensor (not shown). The tank sensor is used to monitor the volume of working fluid within the linear actuator assembly. In particular, port 1128 facilitates the connection of a flow restrictor for the regulation of oil flow to the proportional valve.
Two eyebolts 1400 are provided on the second face 1112, with the eyebolts 1400 positioned on opposing sides of the second face 1112 The eyebolts 1400 facilitate the mounting of the control unit 1000 to a surface.
A shuttle valve 1600 is positioned on the third face 1113 of the housing 1100 (see Fig. 5). The shuttle valve 1600 is a single ball shuttle valve with a signal at port 3 of the valve. The third face 1115 includes a 1-11A line mount cavity for facilitating connection of the shuttle valve 1600 to the housing 1100.
A relief valve (not shown) is positioned on the third face side of the housing and a check cartridge 1700 is associated with the relief valve.
-13 -The relief valve is a relief cartridge type valve of the flat nose variety.
The check cartridge 1700 is a direct-acting relief cartridge which is normally in a closed state. The check cartridge 1700 and associated relief valve act as a pressure-limiting means used to protect the hydraulic components of the control unit and the linear actuator assembly from pressure transients.
The relief valve is connected to the housing 1100 by a DIN 40 U fastener and the third face 1113 comprises a DIN 40 U port to receive the fastener.
A sensor connection port 1129 is provided on the third face 1113 of the housing 1100 to facilitate connection of a sensor to the control unit 1100.
The fourth face 1114 of the housing 1100 includes an auxiliary port, which in the embodiment shown is closed off by a plug 1800.
The force generator valve 1200 is positioned on the fifth face 1115 of the housing 1100 (see Fig. 7), and the solenoid valve 1300 is positioned on the sixth face 1116 of the housing 1100 (see Fig 8).
The force generator valve 1200 is direct-acting pressure relief type valve.
The pressure valve 144 responsible for controlling the pressure relief valve 1200 is a proportional valve 144.
A pilot operated valve assembly 1500 is also position on the fifth face 1115 of the housing. The pilot operated valve assembly 1500 is associated with the electronic controller. In the embodiment shown, the pilot operated valve assembly comprises a pilot-operated, balanced piston relief main stage with integral T-8A control cavity indicated by reference numeral 1510 and a 24 VDC coil with ISO/DIN 43650, Form A connector with TVS Diode indicated by reference numeral 1520.
The fifth face 1115 includes a T-10A line mount cavity for facilitating connection of the pilot operated valve assembly 1500 to the housing 1100.
-14 -A plurality of auxiliary ports in fluid communication with the fluid passageway are included on the fifth face 1114 of the housing 1100. The auxiliary ports are shown closed off by a plug 1800.
The solenoid valve 1300 is a spool type, direct operated solenoid valve.
A check valve (not shown) is positioned on the sixth face side of the housing 1100. The check valve is arranged to protect the solenoid valve from pressure transients.
The check valve is directional cartridge type valve.
A check cartridge 1900 associated with the check valve is positioned between the check valve and the solenoid valve 1300.
The control unit 1000 in accordance with the invention provides a multi-functional control unit which is capable of more than just controlling the retraction, delay, and return of a piston of a hydraulic cylinder.
The control unit 1000 in accordance with the invention allows for the remote control of the force generator valve 1200, which allows the control unit 1000 to be utilized for different tools and linear actuator arrangements.
This is accomplished in the embodiment shown by means of the electronic controller and pilot operated valve assembly. The electronic controller and pilot operated valve assembly allow for a change in the amount of fluid receivable from the manifold block into the control unit and hence the pressure build up within the first flow channel.
The electronic controller may be connected to a user interface on the press tool assembly thus facilitating a user to select one of the plurality of stored pressure force values depending on the tool or linear actuator arrangement being used for the pressing process.
-15 -Alternatively, the electronic controller may be connected to a user interface remote from the press tool assembly or metal press.
Being able to remotely control and adjust the generation of force required to actuate the force generator valve has a number of advantages, in particular it reduces the down time of a metal press during tool change as the required pressure force to actuate the force generator valve does not need to manually set. Manual setting of the pressure force can be time consuming and also lead to discrepancies between the newly set value and the value for optimal performance of the linear actuator assembly.
The electronic controller can be pre-programmed for use with different tools and/or linear actuator configurations. In this way, a user can simply select the already determined optimal pressure force value stored within the electronic controller for the desired tool or linear actuator configuration.
The electronic controller is also preferably configured to store new pressure force values in addition to those already stored on the electronic controller. The allows the control unit to be adapted for use with different tools and/or linear actuator configurations than those it was initially configured to be used with.
The control unit 1000 in accordance with the invention can be configured to function as a diagnostic system for the press tool and/or linear actuator assembly. The numerous ports provided allow it to be connected to appropriate sensors to measure one or more characteristics of the linear actuator assembly.
For example, temperature and/or heat generation during the pressing process can be closely monitored.
The control unit 1000 can be arranged to monitor the gas pressure in the accumulator. A change in the gas pressure in the accumulator would indicate that a corresponding change in the oil pressure in the accumulator has occurred. An unwanted change in gas pressure would indicate that an oil leak is present in the system.
-16 -A key feature of the control unit in accordance with the present invention is that it allows for the generation of the pressure force required to actuate the force generator valve to be easily changed from one tool to another or linear actuator configuration to another without manual adjustment of the force generator valve.

Claims (16)

  1. -17 -Claims 1. A control unit for a hydraulic type linear actuator assembly, the control unit comprising: a first port for connecting the control unit to an accumulator; a second port for connecting the control unit to a manifold; a fluid passageway connecting the first port to the second port, said fluid passageway comprising first and second flow channels; a force generator valve associated with the first flow channel of the fluid passageway, said force generator valve configured to control the flow of fluid from a manifold block of a linear actuator assembly into an accumulator of said linear actuator via the control unit, and arranged to be actuated when a pressure force in the first flow channel reaches a preset value; and a solenoid valve associated with the second flow channel of the fluid passageway, said solenoid valve configured to control the flow of fluid from said accumulator to said manifold block via the control unit; wherein the control unit further comprises an electronic controller, remotely operable and configured to select said preset value from one of a plurality of different stored pressure force values.
  2. 2. A control unit according to claim 1, wherein the electronic controller is further configured to change a selected preset value to a different preset value from one of said plurality of different stored pressure force values.
  3. 3. A control unit according to either claim 1 or claim 2, wherein the electronic controller is configured to facilitate adjustment of the force curve generated by a piston during machining.
  4. 4. A control unit according to any preceding claim, wherein the electronic controller comprises a programmable logic controller.
  5. 5. A control unit according to any one of the preceding claims, further comprising a pilot operated valve assembly in fluid communication with the fluid passageway and associated with the electronic controller.
  6. -18 - 6. A control unit according to claim 5, wherein the pilot operated valve assembly comprises a pilot-operated, balanced piston relief main stage with integral T-8A control cavity, and a 24 VDC coil with ISO/DIN 43650, Form A connector with TVS Diode.
  7. 7. A control unit according to any one of the preceding claims, further comprising a check valve arranged to protect the solenoid valve from pressure transients.
  8. 8. A control unit according to claim 7, further comprising a check cartridge associated with the check valve, the check cartridge positioned between the check valve and the solenoid valve.
  9. 9. A control unit according to any one of the preceding claims, further comprising a shuttle valve in fluid communication with the fluid passageway.
  10. 10. A control unit according to claim 9, wherein the shuttle valve is a single ball shuttle valve with a signal at port 3 of the valve.
  11. 11. A control unit according to any one of the preceding claims, further comprising a relief valve in fluid communication with the fluid passageway and a check cartridge associated with the relief valve.
  12. 12. A control unit according to any one of the preceding claims, further comprising a third port in fluid communication with the fluid passageway, said third port configured to facilitate connection of the control unit to a tank containing working fluid for the linear actuator assembly
  13. 13. A control unit according to claim 12, further comprising a fourth port in fluid communication with the fluid passageway, said fourth port configured to facilitate connection of the control unit to a pressure valve.
  14. 14. A control unit according to claim 13, further comprising a fifth port, said fifth port configured to facilitate connection of the control unit to a tank sensor for monitoring the volume of working fluid within the linear actuator assembly in use.-19 -
  15. 15. A control unit according to any one of claims 10 to 12, further comprising one or more auxiliary ports for facilitating connection of one or more auxiliary valves and/or sensors to the control unit.
  16. 16. A control unit according to any one of the preceding claims, further comprising a plurality of fasteners configured to facilitate the mounting of the control unit onto a surface.
GB2002301.6A 2020-02-19 2020-02-19 Linear actuator assembly control unit Expired - Fee Related GB2592220B (en)

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN203214470U (en) * 2013-05-02 2013-09-25 北京精海仪机电设备有限公司 Hydraulic manifold lifting control valve bank for hopper of heavy truck
WO2014143795A1 (en) * 2013-03-15 2014-09-18 Eaton Corporation Hydraulic power system
CN109764020A (en) * 2019-02-15 2019-05-17 徽瑞智能装备（黄山）有限责任公司 A servo hydraulic valve controller

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014143795A1 (en) * 2013-03-15 2014-09-18 Eaton Corporation Hydraulic power system
CN203214470U (en) * 2013-05-02 2013-09-25 北京精海仪机电设备有限公司 Hydraulic manifold lifting control valve bank for hopper of heavy truck
CN109764020A (en) * 2019-02-15 2019-05-17 徽瑞智能装备（黄山）有限责任公司 A servo hydraulic valve controller

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