US10385884B2 - Control valve compensation system - Google Patents

Control valve compensation system Download PDF

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Publication number
US10385884B2
US10385884B2 US15/268,777 US201615268777A US10385884B2 US 10385884 B2 US10385884 B2 US 10385884B2 US 201615268777 A US201615268777 A US 201615268777A US 10385884 B2 US10385884 B2 US 10385884B2
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Prior art keywords
compensation
post
valve
control valve
compensated
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US15/268,777
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US20170082122A1 (en
Inventor
Alvin Stanley Rost
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Rost Innovation LLC
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Rost Innovation LLC
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Priority to US15/268,777 priority Critical patent/US10385884B2/en
Priority to PCT/US2016/052473 priority patent/WO2017049281A1/en
Assigned to Rost Innovation LLC reassignment Rost Innovation LLC ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ROST, ALVIN STANLEY
Publication of US20170082122A1 publication Critical patent/US20170082122A1/en
Priority to US16/541,908 priority patent/US10989232B2/en
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Publication of US10385884B2 publication Critical patent/US10385884B2/en
Priority to US17/236,380 priority patent/US20210239140A1/en
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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
    • 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F15B13/0418—Load sensing elements sliding within a hollow main valve spool
    • 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
    • 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
    • F15B13/026—Pressure compensating 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
    • 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
    • F16K31/124—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston servo actuated
    • 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
    • F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
    • 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
    • F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
    • F15B2013/006—Modular components with multiple uses, e.g. kits for either normally-open or normally-closed valves, interchangeable or reprogrammable manifolds
    • 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
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/3054—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and output member
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/5109—Convertible
    • Y10T137/5283—Units interchangeable between alternate locations

Definitions

  • Example embodiments in general relate to a Control Valve Compensation System for producing both a pre-compensated and a post-compensated load sensing hydraulic directional control valve module, wherein both configurations use the same components except for a sliding compensating component.
  • Hydraulic directional control valves are generally constructed to comprise either a pre-compensated configuration or a post-compensated configuration. In a pre-compensated configuration, module priority is provided by the control valve. In a post-compensated configuration, multiple modules are utilized to share the pump flow proportionally. Other desired functionality is accomplished by adding control components or logic controls adapted to control the sliding main component of the module.
  • An example embodiment of the present invention is directed to a Control Valve Compensation System for producing both a pre-compensated and a post-compensated load sensing hydraulic directional control valve module, wherein both configurations use the same components except for a sliding compensating component.
  • Such configurations allow manufacturers of such valves to reduce costs, such as manufacturing tooling costs and manufacturing testing costs.
  • the present invention also aids with increasing inventory turn numbers.
  • Each of the control valve systems disclosed herein are adapted to covert from pre-compensated to post-compensated, or vice versa, by simply changing a sliding compensating component.
  • FIG. 1 is a sectional view of a first embodiment of a pre-compensated configuration of the present invention.
  • FIG. 2 is a sectional view of a first embodiment of a post-compensated configuration of the present invention.
  • FIG. 3 is a sectional view of a first embodiment of a pre-compensated configuration of the present invention in a working position.
  • FIG. 4 is a sectional view of a first embodiment of a post-compensated configuration of the present invention in a working position.
  • FIG. 5 is a sectional view of a second embodiment of a pre-compensated configuration of the present invention.
  • FIG. 6 is a sectional view of a second embodiment of a post-compensated configuration of the present invention.
  • FIGS. 1 through 6 illustrate a Control Valve Compensation System 10 , which comprises a hydraulic directional control valve housing 11 , 12 which is adapted to be easily-interchangeable between a load sensing pre-compensated pressure configuration and a load sensing post-compensated pressure configuration by simply removing and replacing a different compensator assembly within the housing.
  • the compensator assembly is adapted to direct oil flow through the housing 11 , 12 while simultaneously providing compensation for the valve function.
  • Directional valve assemblies may be provided, with the valve assemblies functioning to provide post-compensated functions, pre-compensated functions, and mixed pre- and post-compensated functions. These directional valve functions can be re-configured in the field by simply swapping the compensator assemblies to produce the desired functionality of the end-user at that particular time.
  • FIGS. 1, 3, and 5 illustrate different embodiments of the present invention configured for pre-compensation.
  • FIG. 1 illustrates the pre-compensation configuration.
  • FIG. 3 illustrates the pre-compensation configuration in a work position.
  • FIG. 5 illustrates an alternate embodiment of the pre-compensation configuration in which the compensator is positioned perpendicular with respect to the main control unit.
  • the pre-compensated configuration comprises a valve body 14 with a plurality of internal flow passageways 20 , 21 , 22 , 23 , 24 , 26 , 27 .
  • the number, configuration, orientation, and types of passageways 20 , 21 , 22 , 23 , 24 , 26 , 27 utilized may vary in different embodiments of the present invention. In the exemplary embodiment shown in the figures, these include a power passageway 20 , a first intermediate passageway 21 , a second intermediate passageway 22 , a loop passage 23 , one or more return passages 24 , and a plurality of work ports 26 , 27 .
  • the pre-compensated configuration further comprises a selectable valve spool 13 .
  • a selectable valve spool 13 may include a plurality of control notches 29 .
  • a pre-compensator piston 17 is provided which may include a compensating aperture 28 .
  • the spring 16 shown in the figures is generally biased to be normally open in the pre-compensated configuration.
  • fluid When the selectable valve spool 13 is positioned toward a first side of the housing 11 (i.e. to the right side as shown in the figures), fluid will flow from the power passage 20 across the compensator piston 17 and pre-compensator control aperture 28 into the first intermediate passage 21 . After the first intermediate passage 21 , the fluid will continue onward to the selectable valve spool 13 and across the selectable valve spool notches 29 into the second intermediate passage 22 . From the second intermediate passage 22 , the fluid flows by the compensator piston 17 at undercut 34 and into the loop passage 23 , where the selectable valve spool 13 directs fluid through a passage into the powered work port 26 .
  • the compensator piston 17 ends 30 , 31 are adapted to sense pressure, such as power passageway 20 pressure on end 31 through a sensing compensator passage internally. Power passage pressure on end 31 is measured internally through the compensator 17 and reduced pressure on end 30 is measure internally through the compensator 17 from the artificial pressure passage 25 .
  • fine metering may be provided for the selectable valve spool 13 and control notches 29 .
  • FIGS. 2, 4, and 6 illustrate different embodiments of the present invention configured for post-compensation.
  • FIG. 1 illustrates the post-compensation configuration.
  • FIG. 3 illustrates post pre-compensation configuration in a work position.
  • FIG. 6 illustrates an alternate embodiment of the post-compensation configuration in which the compensator is positioned perpendicular with respect to the main control unit.
  • the post-compensated configuration 12 comprises a valve body 14 with a plurality of internal flow passageways 20 , 21 , 22 , 23 , 24 , 26 , 27 .
  • the number, configuration, orientation, and types of passageways 20 , 21 , 22 , 23 , 24 , 26 , 27 utilized may vary in different embodiments of the present invention. In the exemplary embodiment shown in the figures, these include a power passageway 20 , a first intermediate passageway 21 , a second intermediate passageway 22 , a loop passage 23 , one or more return passages 24 , and a plurality of work ports 26 , 27 .
  • the post-compensated configuration 12 further comprises a selectable valve spool 13 .
  • a selectable valve spool 13 may include a plurality of control notches 29 .
  • a post-compensator piston 18 is provided which may include a post-compensator control aperture 32 .
  • the spring 16 shown in the figures is generally biased to be normally closed in the post-compensated configuration 12 .
  • fluid flows from the power passage 20 , across the compensator piston 18 at undercut 35 and into the first intermediate passage 21 . From there, the fluid flows onto the selectable valve spool 13 and across the selectable valve spool notches 29 into the second intermediate passage 22 . From the second intermediate passage 22 , the fluid flows by the compensator piston 18 and compensating aperture 32 into the loop passage 23 , where the selectable valve spool 13 directs fluid into a passageway to the powered work port 26 .
  • the compensator 18 piston ends 30 , 31 sense multiple pressures. Power passage pressure on end 31 is measured internally through the compensator 18 and reduced pressure on end 30 is measure internally through the compensator 18 from an artificial pressure passage 25 .
  • fine metering may be provided for the selectable valve spool 13 and control notches 29 .
  • Returning fluid from the working function enters work port 27 , through an interconnected passageway 27 , and flow across the control notches to the body return passage 24 . Reversing the position of the selectable valve spool 13 toward the second side of the housing (i.e. to the left side as shown in the figures) reverses the flows inside the present invention powering the opposite work port 27 and returning to the opposite work port 26 .
  • actuators may be utilized to control the sliding directional control component 13 of the modules.
  • the actuators may be controlled in various manners, including electrically, hydraulically, pneumatically, or by computer logic to have the modules function in desired modes.
  • FIGS. 5 and 6 illustrate an alternate embodiment of both the pre-compensated configuration 11 and the post-compensated configuration 12 . While FIGS. 1-4 illustrate an embodiment in which the compensator is parallel to the main control component, FIGS. 5-6 illustrate an embodiment in which the compensator is perpendicular to the main control component. In the latter embodiment, the compensator controls only one set of metering orifices and does not bypass any flow in the flow stream. The post-compensator controls the upstream metering orifices and the pre-compensator controls the downstream orifices. In such an embodiment, the compensator assemblies are still interchangeable for desired module functionality.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Multiple-Way Valves (AREA)
US15/268,777 2015-09-18 2016-09-19 Control valve compensation system Active 2037-07-02 US10385884B2 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US15/268,777 US10385884B2 (en) 2015-09-18 2016-09-19 Control valve compensation system
PCT/US2016/052473 WO2017049281A1 (en) 2015-09-18 2016-09-19 Control valve compensation system
US16/541,908 US10989232B2 (en) 2015-09-18 2019-08-15 Control valve compensation system
US17/236,380 US20210239140A1 (en) 2015-09-18 2021-04-21 Control Valve Compensation System

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201562220350P 2015-09-18 2015-09-18
US15/268,777 US10385884B2 (en) 2015-09-18 2016-09-19 Control valve compensation system

Related Child Applications (2)

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US16/541,908 Continuation-In-Part US10989232B2 (en) 2015-09-18 2019-08-15 Control valve compensation system
US16/541,908 Continuation US10989232B2 (en) 2015-09-18 2019-08-15 Control valve compensation system

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US20170082122A1 US20170082122A1 (en) 2017-03-23
US10385884B2 true US10385884B2 (en) 2019-08-20

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EP (1) EP3347531B8 (de)
WO (1) WO2017049281A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20190368518A1 (en) * 2015-09-18 2019-12-05 Rost Innovation LLC Control Valve Compensation System

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112879366B (zh) * 2020-12-31 2022-02-15 华中科技大学 一种多功能全海深电控集成阀组
CN115163588B (zh) * 2022-08-03 2025-09-23 中核四川环保工程有限责任公司 一种用于核设施退役的液压控制系统
CN119163661B (zh) * 2024-11-11 2025-04-25 上海强田液压股份有限公司 一种高精度同步阀组

Citations (18)

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US4519420A (en) * 1982-09-29 1985-05-28 Commercial Shearing, Inc. Hydraulic valves
US4693272A (en) * 1984-02-13 1987-09-15 Husco International, Inc. Post pressure compensated unitary hydraulic valve
US5025625A (en) 1988-11-10 1991-06-25 Hitachi Construction Machinery Co., Ltd. Commonly housed directional and pressure compensation valves for load sensing control system
US5279121A (en) 1993-01-19 1994-01-18 Eaton Corporation Flow control valve with pilot operation and pressure compensation
US5305789A (en) 1992-04-06 1994-04-26 Rexroth-Sigma Hydraulic directional control valve combining pressure compensation and maximum pressure selection for controlling a feed pump, and multiple hydraulic control apparatus including a plurality of such valves
US5466064A (en) 1995-05-23 1995-11-14 Enrj Ltd. Fuel homogenization system with dual compensating homogenization valves
US6119967A (en) 1995-05-02 2000-09-19 Komatsu Ltd. Control circuit of transportable crusher
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US7182097B2 (en) 2004-08-17 2007-02-27 Walvoil S.P.A. Anti-saturation directional control valve composed of two or more sections with pressure selector compensators
US7770592B2 (en) 2006-07-13 2010-08-10 Parker-Hannifin Corporation Valve with freeze-proof heated valve seat
US7770596B2 (en) 2006-12-20 2010-08-10 Sauer-Danfoss Aps Hydraulic valve arrangement
US7818966B2 (en) 2008-01-09 2010-10-26 Husco International, Inc. Hydraulic control valve system with isolated pressure compensation
US7854115B2 (en) * 2008-04-25 2010-12-21 Husco International, Inc. Post-pressure compensated hydraulic control valve with load sense pressure limiting
US8191579B2 (en) 2006-02-24 2012-06-05 Robert Bosch Gmbh Directional or flow control valve
US8381757B2 (en) * 2007-12-24 2013-02-26 Hydac Electronic Gmbh Valve device
US20130112297A1 (en) 2011-09-30 2013-05-09 Eaton Corporation Pre- and post- compensational valve arrangement
US8479768B2 (en) 2009-07-27 2013-07-09 Robert Bosch Gmbh Directional control valve arrangement
US20140026985A1 (en) 2011-03-22 2014-01-30 Parker-Hannifin Corporation Electro-proportional pilot operated poppet valve with pressure compensation

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US4693272A (en) * 1984-02-13 1987-09-15 Husco International, Inc. Post pressure compensated unitary hydraulic valve
US5025625A (en) 1988-11-10 1991-06-25 Hitachi Construction Machinery Co., Ltd. Commonly housed directional and pressure compensation valves for load sensing control system
US5305789A (en) 1992-04-06 1994-04-26 Rexroth-Sigma Hydraulic directional control valve combining pressure compensation and maximum pressure selection for controlling a feed pump, and multiple hydraulic control apparatus including a plurality of such valves
US5279121A (en) 1993-01-19 1994-01-18 Eaton Corporation Flow control valve with pilot operation and pressure compensation
US6119967A (en) 1995-05-02 2000-09-19 Komatsu Ltd. Control circuit of transportable crusher
US5466064A (en) 1995-05-23 1995-11-14 Enrj Ltd. Fuel homogenization system with dual compensating homogenization valves
US6895852B2 (en) 2003-05-02 2005-05-24 Husco International, Inc. Apparatus and method for providing reduced hydraulic flow to a plurality of actuatable devices in a pressure compensated hydraulic system
US7182097B2 (en) 2004-08-17 2007-02-27 Walvoil S.P.A. Anti-saturation directional control valve composed of two or more sections with pressure selector compensators
US8191579B2 (en) 2006-02-24 2012-06-05 Robert Bosch Gmbh Directional or flow control valve
US7770592B2 (en) 2006-07-13 2010-08-10 Parker-Hannifin Corporation Valve with freeze-proof heated valve seat
US7770596B2 (en) 2006-12-20 2010-08-10 Sauer-Danfoss Aps Hydraulic valve arrangement
US8381757B2 (en) * 2007-12-24 2013-02-26 Hydac Electronic Gmbh Valve device
US7818966B2 (en) 2008-01-09 2010-10-26 Husco International, Inc. Hydraulic control valve system with isolated pressure compensation
US7854115B2 (en) * 2008-04-25 2010-12-21 Husco International, Inc. Post-pressure compensated hydraulic control valve with load sense pressure limiting
US8479768B2 (en) 2009-07-27 2013-07-09 Robert Bosch Gmbh Directional control valve arrangement
US20140026985A1 (en) 2011-03-22 2014-01-30 Parker-Hannifin Corporation Electro-proportional pilot operated poppet valve with pressure compensation
US20130112297A1 (en) 2011-09-30 2013-05-09 Eaton Corporation Pre- and post- compensational valve arrangement
US9200647B2 (en) * 2011-09-30 2015-12-01 Eaton Corporation Pre- and post- compensational valve arrangement

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PCT Search Report and Written Opinion Received from the International Searching Authority; Received and Printed Dec. 12, 2016.

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20190368518A1 (en) * 2015-09-18 2019-12-05 Rost Innovation LLC Control Valve Compensation System
US10989232B2 (en) * 2015-09-18 2021-04-27 Rost Innovation LLC Control valve compensation system

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Publication number Publication date
US20170082122A1 (en) 2017-03-23
EP3347531B1 (de) 2021-03-17
EP3347531A1 (de) 2018-07-18
EP3347531A4 (de) 2019-07-03
WO2017049281A1 (en) 2017-03-23
EP3347531B8 (de) 2021-04-28

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