US20110114304A1 - Method for the hydraulic compensation and control of a heating or cooling system and compensation and control valve therefor - Google Patents

Method for the hydraulic compensation and control of a heating or cooling system and compensation and control valve therefor Download PDF

Info

Publication number
US20110114304A1
US20110114304A1 US13/003,211 US200913003211A US2011114304A1 US 20110114304 A1 US20110114304 A1 US 20110114304A1 US 200913003211 A US200913003211 A US 200913003211A US 2011114304 A1 US2011114304 A1 US 2011114304A1
Authority
US
United States
Prior art keywords
balancing
valve
range
regulating
regulating valve
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.)
Abandoned
Application number
US13/003,211
Other languages
English (en)
Inventor
Urs Keller
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.)
Belimo Holding AG
Original Assignee
Belimo Holding AG
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=40029328&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=US20110114304(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Belimo Holding AG filed Critical Belimo Holding AG
Assigned to BELIMO HOLDING AG reassignment BELIMO HOLDING AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KELLER, URS
Publication of US20110114304A1 publication Critical patent/US20110114304A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1009—Arrangement or mounting of control or safety devices for water heating systems for central heating
    • F24D19/1015—Arrangement or mounting of control or safety devices for water heating systems for central heating using a valve or valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2220/00—Components of central heating installations excluding heat sources
    • F24D2220/02—Fluid distribution means
    • F24D2220/0264—Hydraulic balancing valves

Definitions

  • the present invention relates to a balancing and regulating valve for a heating or cooling system and to a method for the hydraulic balancing of such a balancing and regulating valve in a branch of a heating or cooling system.
  • the hydraulic balancing of a heating or cooling system is carried out before the system is transferred to the customer.
  • the system must be fully installed and be in operation.
  • the aim is to distribute, as required, the medium delivered from the central pump to the various zones of the system. Balancing is usually carried out only at one operating point, to be precise under full load. This means, for such a system, that all the regulating valves are opened to a maximum.
  • the rotational speed of the pump and the position of balancing throttles or balancing valves, which precede or follow the actual regulating valves are set such that the throughflow values stipulated by the planner are achieved in each branch.
  • the rotational speed of the pump is in this case to be set as low as possible, but sufficiently high to achieve all the throughflows required.
  • a differential pressure measuring instrument is often used for throughflow measurement. The pressure loss is measured across a known resistance, for example a measuring diaphragm or heat exchanger.
  • a mobile ultrasonic throughflow meter may also be used, which can be mounted on the pipework on the outside.
  • EP 0 301 568 discloses an autocalibration method for a regulating valve, in which the effective actuating travel of the valve is established and the regulating range is limited to this effective actuating travel.
  • the effective actuating travel is in this case defined as the range of the total actuating travel between 5% and 95% of maximum throughflow. This document is not concerned with the set object of hydraulic balancing.
  • the invention is based on the recognition that said setting of the hydraulic balancing according to the prior art is carried out only when the regulating valves are open, in order to establish the minimum necessary pump delivery rate required under full load so as to achieve all the required throughflows in the individual branches.
  • a relatively large part of the operating range of the regulating valve is lost.
  • the overall characteristic curve (k V —throughflow characteristic value) of the branch is flattened in the range of a relatively pronounced opening of the regulating valve, that is to say in its upper operating range.
  • the overall characteristic curve is steeper. This deformation of the characteristic curve is detrimental to the regulating behavior for this line, because, on the one hand, resolution is poorer in the lower regulating range and, on the other hand, the overall circuit amplification is not constant over the operating range. Variable circuit amplification actually necessitates variable control parameters. This makes it difficult to tune the controller, especially since variable parameters are mostly not provided in the controllers used.
  • An object of the present invention is to overcome this disadvantage of the prior art and to combine hydraulic balancing and regulating in a simple way adjustably in control terms.
  • an object of the present invention is to configure the overall characteristic curve, that is to say the characteristic curve of the regulating valve with a folded characteristic curve of the connected load, for example a heat exchanger, so as to be improved for the purpose of simpler and better regulation.
  • a balancing valve brake regulating valve
  • the operating range of the actual regulating valve is restricted.
  • the valve control is also advised of this, so that the signal range can be mapped automatically onto the new operating range. In this way, a 100% dynamic range remains for the control.
  • a method for the hydraulic balancing of a balancing and regulating valve in a branch of a heating or cooling system can be employed when such a balancing and regulating valve and a load are provided.
  • a medium flows through a branch of the heating or cooling system.
  • a setpoint value for the balancing and regulating valve is determined, at which a predetermined throughflow value of the medium, which is lower than the maximum throughflow value, is reached in the branch. This setpoint value is defined and set as the “maximum setpoint value”.
  • the operating range of the balancing and regulating valve is then defined as the range between the set “maximum setpoint value” and the position with the balancing and regulating valve closed.
  • the original signal regulating range of the balancing and regulating valve is then mapped onto the newly defined operating range. This then gives rise to full dynamics with reduced maximum setpoint value.
  • the valve characteristic curve is an equal-percentage characteristic curve in order, in interaction with a connected heat exchanger, to generate a linear dependence.
  • a valve characteristic curve which is equal-percentage in the case of 100% operating range and is also equal-percentage in the balanced state, that is to say with a smaller operating range, for example 60%. This applies over the widest range of the restricted operating range.
  • a predetermined lower regulating range may be configured linearly, in order to ensure better regulation of the small valve openings.
  • This division of the regulating range in two via a continuously differentiable transition makes it possible to combine the advantageous equal-percentage valve characteristic curve in the large opening range, in order to avoid a flattening of the gradient in the case of high control deflections, with the linear flat characteristic curve in a predetermined lower regulating range.
  • the setting of the “maximum setpoint value”, which can be set, for example, in the form of a limit angle, may be carried out manually directly on the control unit or else electrically via the actuating signal which is also used in regulating mode.
  • the storage of the “maximum setpoint value”, that is to say of the determined and set position of the valve as a new maximum value, may be carried out by pressing a key directly on the drive or else electronically by sending a bus command. This command may be sent either by a service tool or from the building management system.
  • FIG. 1 shows a graph which shows diagrammatically a characteristic curve of a conventional regulating valve, which is connected in series with a balancing valve, and a characteristic curve of a balancing and regulating valve according to the invention.
  • FIG. 2 shows a graph which shows diagrammatically a characteristic curve of a heat exchanger as the load, a characteristic curve of a balancing and regulating valve according to the invention and the overall characteristic curve of a branch.
  • FIG. 1 shows diagrammatically a characteristic curve 10 of a conventional regulating valve which is connected in series with a balancing valve, and a characteristic curve 20 of a balancing and regulating valve according to the invention.
  • the gradient 11 of the characteristic curve 10 of the conventional regulating valve is very much steeper in the lower regulating range, that is to say at values of, for example, 10 to 20%, than the gradient 21 of the characteristic curve 20 of a balancing and regulating valve according to the invention in the range of between 0% and 30%.
  • the gradient 11 or 21 is also associated with a range 13 without a gradient, also called a dead angle or dead zone, here at 0% to 10%.
  • the gradient 12 of the characteristic curve 10 of the conventional regulating valve flattens greatly in the upper regulating range, here from 80% of the operating range, and, for example here, approaches a percentage k V value of 25% which is predetermined as the maximum value by the preceding or following balancing valve.
  • k V value of 25% which is predetermined as the maximum value by the preceding or following balancing valve.
  • the characteristic curve 20 of a balancing and regulating valve for this method and device is equal-percentage.
  • identical input variable changes cause identical percentage output variable changes over the entire regulating range.
  • FIG. 2 shows a graph showing diagrammatically a characteristic curve of a heat exchanger 30 as the load, a characteristic curve 20 of a balancing and regulating valve according to the invention and the overall characteristic curve 40 of a branch.
  • the resulting control characteristic curve 40 of a branch remains essentially linear or can be considered as such by a control unit.
  • the equal-percentage characteristic curve 20 referred to here is modified.
  • n gl (often called n ep ) is a measure of how sharply the characteristic curve is curved. Since exponential functions never cross the zero point, this definition of the characteristic curve is replaced in the lower range 21 by linear. The transition from the linear to the exponential part is continuously differentiable and is predetermined by the reciprocal value of n gl .
  • the overall characteristic curve is called “equal-percentage” (sometimes “modified equal-percentage”).
  • n gl 4.5.
  • the greater curvature, as compared with n gl 2 to 4 of the prior art, is advantageous for the balancing function by means of an equal-percentage valve.
  • Equal-percentage valves with a value of n gl of 4.5 to 6 or 7 are advantageous. Consequently, the region of transition of the curve into the linear part is likewise shifted toward lower
  • Such a heating or cooling system comprises at least one pump and a multiplicity of branches which each have a balancing and regulating valve and a load, the valve and load being connected one behind the other in series.
  • the load is usually a heat exchanger.
  • a maximum setpoint value is then set for each of the balancing and regulating valves, so that predetermined throughflow values are reached in each branch.
  • the operating range of each balancing and regulating valve is defined as the range between the set maximum setpoint value and the position when the balancing and regulating valve is closed.
  • the signal regulating range of each balancing and regulating valve is then mapped onto the newly defined operating range in the control circuit of the heating or cooling system, so that the full signal regulating width of 100% is available again and is applied to a reduced operating range.
  • the mapping of the signal regulating range of each balancing and regulating valve onto the newly defined operating range makes it possible to ensure that there is a reasonably regulatable range for low manipulated variables, since the gradient of the linear range remains flat and, because the curve for high operating ranges then rises exponentially toward the maximum, no control saturation occurs.
  • the maximum setpoint values of the individual balancing and regulating valves can be stored in said electronic control unit and can then, after being stored in this way, be transmitted as setting signals to the balancing and regulating valve in order to fix the maximum value of the valve opening.
  • the design of the heating or cooling system advantageously makes use of balancing and regulating valves and elements acting as the load, which in each case have a specific characteristic curve, so that the overall characteristic curve of a branch which arises from the load and from the balancing and regulating valve is essentially linear. Since the load characteristic curve mostly has a form like that of the characteristic curve 30 in FIG. 2 , it is advantageous to use in each case balancing and regulating valves which have an equal-percentage valve characteristic curve and, even more preferably, a characteristic curve with an n gl of 4.5.
  • the balancing and regulating valve can also expediently be used on its own.
  • a maximum setpoint value is then still set for this balancing and regulating valve, this setting being carried out by means of a setting knob, for example potentiometrically. It is advantageous that the maximum setpoint value is not just a limit stop, but a maximum settable angle or other manipulated variable of the valve, so that a predetermined maximum throughflow value in the branch of this valve is achieved.
  • This maximum value can also be stored, for example, in a nonvolatile memory of an activation and control circuit of the valve.
  • the operating range is defined in this activation and control circuit as the range between the set maximum setpoint value and the position when the balancing and regulating valve is closed.
  • the signal regulating range of this balancing and regulating valve can then continue to be addressed over the full signal regulating width of 100% in the control circuit of the heating or cooling system, whereas this range is then actually applied to an operating range reduced in the valve. Mapping onto the newly defined operating range can thus take place solely in the balancing and regulating valve, thus making it possible to replace individual valve combinations of a branch valve and regulating valve in an older heating or cooling system with a balancing and regulating valve according to the invention, if the response of the control circuit is compatible.
  • the signal regulating range is to be understood as meaning the range of input signals (digital or analog) for the balancing and regulating valve, with which a control unit can address this valve to maximum, this usually corresponding to values between 0% and a 100% maximum opening of the valve.
  • this maximum signal regulating range can address the full reduced operating range of the balancing and regulating valve, and no interval in the signal regulating range is lost.
  • Such a balancing and regulating valve can operate independently in a branch if it is subjected by a conventional control unit of a heating or cooling system to an activation signal of between 0 and 100%. According to another exemplary embodiment of the invention, however, it can also operate with a control unit of a heating or cooling system in which the balancing and regulating valve does not itself know or store a maximum threshold value, but instead, these maximum setpoint values are stored in this control unit and then the activation signal for a balancing and regulating valve does not have a signal value of between 0 and 100%, but covers only a range predetermined by the maximum setpoint value, then, however, with a signal value resolution of 100%.
  • FIG. 1 An example is depicted in FIG. 1 .
  • the maximum setpoint value is fixed at 75% in a branch, for which purpose the reference symbol S 75 has been used.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Control Of Temperature (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Steam Or Hot-Water Central Heating Systems (AREA)
US13/003,211 2008-07-25 2009-07-21 Method for the hydraulic compensation and control of a heating or cooling system and compensation and control valve therefor Abandoned US20110114304A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP08161224.4 2008-07-25
EP08161224 2008-07-25
PCT/EP2009/059367 WO2010010092A2 (de) 2008-07-25 2009-07-21 Verfahren für den hydraulischen abgleich und regelung einer heizungs- oder kühlanlage und abgleich- und regelventil dafür

Publications (1)

Publication Number Publication Date
US20110114304A1 true US20110114304A1 (en) 2011-05-19

Family

ID=40029328

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/003,211 Abandoned US20110114304A1 (en) 2008-07-25 2009-07-21 Method for the hydraulic compensation and control of a heating or cooling system and compensation and control valve therefor

Country Status (5)

Country Link
US (1) US20110114304A1 (de)
EP (1) EP2304325B1 (de)
CN (1) CN102216691B (de)
CA (1) CA2727779A1 (de)
WO (1) WO2010010092A2 (de)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170328493A1 (en) * 2013-12-20 2017-11-16 Imi Hydronic Engineering International Sa Valve and a method of operating a valve
US9890870B2 (en) 2011-12-29 2018-02-13 Schneider Electric Buildings Llc Valve flow control optimization via customization of an intelligent actuator
US11092354B2 (en) 2019-06-20 2021-08-17 Johnson Controls Tyco IP Holdings LLP Systems and methods for flow control in an HVAC system
US11149976B2 (en) 2019-06-20 2021-10-19 Johnson Controls Tyco IP Holdings LLP Systems and methods for flow control in an HVAC system
US11391480B2 (en) 2019-12-04 2022-07-19 Johnson Controls Tyco IP Holdings LLP Systems and methods for freeze protection of a coil in an HVAC system
US11519631B2 (en) 2020-01-10 2022-12-06 Johnson Controls Tyco IP Holdings LLP HVAC control system with adaptive flow limit heat exchanger control
US11614757B2 (en) 2020-07-15 2023-03-28 Siemens Schweiz Ag Estimating a maximum flow through a heat exchanger
US11624524B2 (en) 2019-12-30 2023-04-11 Johnson Controls Tyco IP Holdings LLP Systems and methods for expedited flow sensor calibration
US11828384B2 (en) 2018-10-29 2023-11-28 Siemens Schweiz Ag Method for operating a valve, associated electronic control unit, and valve drive

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PT2307938E (pt) * 2008-06-26 2013-12-17 Belparts Sistema de controlo de fluxo
DE102010034769A1 (de) * 2010-08-18 2012-02-23 Ista International Gmbh Verfahren und System zur Durchführung eines hydraulischen Abgleichs in einem Heizungssystem
DE102011018698A1 (de) * 2011-04-26 2012-10-31 Rwe Effizienz Gmbh Verfahren und System zum automatischen hydraulischen Abgleichen von Heizkörpern
US20210148589A1 (en) * 2017-07-26 2021-05-20 Belimo Holding Ag Method and system for controlling a valve in an hvac system
DE202018001783U1 (de) 2018-04-05 2018-05-09 Siemens Schweiz Ag Charakteristiken von Ventilen
SE543008C2 (sv) * 2018-11-22 2020-09-22 Stockholm Exergi Ab Förfarande och system för balansering av massflöde under produktionsstörning eller -brist i ett fjärrvärmenät
EP3702872A1 (de) 2019-02-27 2020-09-02 Siemens Schweiz AG Druckunabhängiges regelventil
CN110701361A (zh) * 2019-10-28 2020-01-17 上海庄生机电工程设备有限公司 一种利用等百分比阀门特性曲线解决水力平衡的方法
WO2023110361A1 (en) * 2021-12-14 2023-06-22 Danfoss A/S Heating system with automatic differential pressure setting

Citations (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4951224A (en) * 1987-07-30 1990-08-21 Jiri Hokynar Control device for fluid flow
US5218984A (en) * 1992-05-29 1993-06-15 Allen Ernest E Means and method for noise and cavitation attenuation in ball-type valves
US5549137A (en) * 1993-08-25 1996-08-27 Rosemount Inc. Valve positioner with pressure feedback, dynamic correction and diagnostics
US5950668A (en) * 1996-10-09 1999-09-14 Fisher Controls International, Inc. Control valve positioners having improved operating characteristics
US6058955A (en) * 1993-12-23 2000-05-09 Flowcon International A/S Differential pressure valve for controlling a system having a heat carrying medium
US6234144B1 (en) * 1999-01-14 2001-05-22 Nissan Motor Co., Ltd. Intake-air quantity control apparatus for internal combustion engine with variable valve timing system
US6247456B1 (en) * 1996-11-07 2001-06-19 Siemens Canada Ltd Canister purge system having improved purge valve control
US6260524B1 (en) * 1999-11-30 2001-07-17 Mitsubishi Denki Kabushiki Kaisha Valve timing control system for internal combustion engine
US20010037159A1 (en) * 1997-07-23 2001-11-01 Henry Boger Valve positioner system
US6318163B1 (en) * 1998-11-19 2001-11-20 Bayerische Motoren Werke Aktiengesellschaft Method and apparatus for determining the throttle valve angle
US6415779B1 (en) * 1998-02-25 2002-07-09 Magneti Marelli France Method and device for fast automatic adaptation of richness for internal combustion engine
US6435207B1 (en) * 1996-12-21 2002-08-20 Ksb Aktiengesellschaft Flow regulation fitting
US20040182443A1 (en) * 2003-03-21 2004-09-23 Douglas Mclntosh Dual purpose valve
US20050115786A1 (en) * 2003-12-01 2005-06-02 Zf Friedrichshafen Ag Damping valve assembly with a progressive damping force characteristic
US20050198979A1 (en) * 2004-03-03 2005-09-15 Jean-Jacques Robin Expansion valve and method for controlling it
US20060162792A1 (en) * 2005-01-26 2006-07-27 Invensys Building Systems, Inc. Flow characterization in a flowpath
US7096093B1 (en) * 2000-02-14 2006-08-22 Invensys Systems, Inc. Intelligent valve flow linearization
US20070000302A1 (en) * 2003-03-19 2007-01-04 Thomas Gramkow Method for testing the function of a hydraulic valve and a test bench for carrying out said method
US20090082944A1 (en) * 2007-09-21 2009-03-26 Holger Frank Process for controlling an internal combustion engine
US20090240376A1 (en) * 2008-03-19 2009-09-24 Moustafa Elshafei System and method for controlling flow characteristics

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4263091A (en) 1980-01-25 1981-04-21 Phillips Petroleum Company Fluid flow control
US4434746A (en) 1983-03-04 1984-03-06 Phillips Petroleum Company Control of a system for supplying heat
DE4019503A1 (de) 1990-06-19 1992-01-02 Heimeier Gmbh Metall Theodor Einrichtung zur steuerung des stellventiles einer zentralheizungsanlage
DE4221725A1 (de) * 1992-07-02 1994-01-05 Buderus Heiztechnik Gmbh Verfahren zum automatischen Erzielen eines hydraulischen Abgleichs in einer Heizungsanlage
DE19724447A1 (de) * 1997-06-10 1998-12-17 Buerkert Werke Gmbh & Co Verfahren zum Herstellen eines digitalen Proportionalventils und Proportionalventil
CN2336144Y (zh) * 1997-09-15 1999-09-01 张国瑞 水力平衡调节阀
US6352106B1 (en) 1999-05-07 2002-03-05 Thomas B. Hartman High-efficiency pumping and distribution system incorporating a self-balancing, modulating control valve
US6363958B1 (en) 1999-05-10 2002-04-02 Parker-Hannifin Corporation Flow control of process gas in semiconductor manufacturing
US20050039797A1 (en) 2002-02-14 2005-02-24 Carlson Bengt A. Pressure independent control valve
SE528703C2 (sv) * 2004-09-15 2007-01-30 Tour & Andersson Ab Anordning för flödesreglering av ett medium i ett värme-och kylsystem
CA2607763A1 (en) 2005-05-06 2006-11-16 Belimo Holding Ag A field adjustable control valve assembly and field adjustment module
CN2919080Y (zh) * 2006-03-22 2007-07-04 北京紫御湾科技有限公司 供暖管网的水力平衡系统
PT2307938E (pt) 2008-06-26 2013-12-17 Belparts Sistema de controlo de fluxo

Patent Citations (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4951224A (en) * 1987-07-30 1990-08-21 Jiri Hokynar Control device for fluid flow
US5218984A (en) * 1992-05-29 1993-06-15 Allen Ernest E Means and method for noise and cavitation attenuation in ball-type valves
US5549137A (en) * 1993-08-25 1996-08-27 Rosemount Inc. Valve positioner with pressure feedback, dynamic correction and diagnostics
US5573032A (en) * 1993-08-25 1996-11-12 Rosemount Inc. Valve positioner with pressure feedback, dynamic correction and diagnostics
US6058955A (en) * 1993-12-23 2000-05-09 Flowcon International A/S Differential pressure valve for controlling a system having a heat carrying medium
US5950668A (en) * 1996-10-09 1999-09-14 Fisher Controls International, Inc. Control valve positioners having improved operating characteristics
US6247456B1 (en) * 1996-11-07 2001-06-19 Siemens Canada Ltd Canister purge system having improved purge valve control
US6435207B1 (en) * 1996-12-21 2002-08-20 Ksb Aktiengesellschaft Flow regulation fitting
US20010037159A1 (en) * 1997-07-23 2001-11-01 Henry Boger Valve positioner system
US6415779B1 (en) * 1998-02-25 2002-07-09 Magneti Marelli France Method and device for fast automatic adaptation of richness for internal combustion engine
US6318163B1 (en) * 1998-11-19 2001-11-20 Bayerische Motoren Werke Aktiengesellschaft Method and apparatus for determining the throttle valve angle
US6234144B1 (en) * 1999-01-14 2001-05-22 Nissan Motor Co., Ltd. Intake-air quantity control apparatus for internal combustion engine with variable valve timing system
US6260524B1 (en) * 1999-11-30 2001-07-17 Mitsubishi Denki Kabushiki Kaisha Valve timing control system for internal combustion engine
US7096093B1 (en) * 2000-02-14 2006-08-22 Invensys Systems, Inc. Intelligent valve flow linearization
US20070000302A1 (en) * 2003-03-19 2007-01-04 Thomas Gramkow Method for testing the function of a hydraulic valve and a test bench for carrying out said method
US20040182443A1 (en) * 2003-03-21 2004-09-23 Douglas Mclntosh Dual purpose valve
US20050115786A1 (en) * 2003-12-01 2005-06-02 Zf Friedrichshafen Ag Damping valve assembly with a progressive damping force characteristic
US20050198979A1 (en) * 2004-03-03 2005-09-15 Jean-Jacques Robin Expansion valve and method for controlling it
US20060162792A1 (en) * 2005-01-26 2006-07-27 Invensys Building Systems, Inc. Flow characterization in a flowpath
US20090082944A1 (en) * 2007-09-21 2009-03-26 Holger Frank Process for controlling an internal combustion engine
US20090240376A1 (en) * 2008-03-19 2009-09-24 Moustafa Elshafei System and method for controlling flow characteristics
US7769493B2 (en) * 2008-03-19 2010-08-03 King Fahd University Of Petroleum And Minerals System and method for controlling flow characteristics

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10527187B2 (en) 2011-12-29 2020-01-07 Schneider Electric Buildings Llc Valve flow control optimization via customization of an intelligent actuator
US10527186B2 (en) 2011-12-29 2020-01-07 Schneider Electric Buildings Llc Valve flow control optimization via customization of an intelligent actuator
US9890870B2 (en) 2011-12-29 2018-02-13 Schneider Electric Buildings Llc Valve flow control optimization via customization of an intelligent actuator
EP3489557B1 (de) 2013-12-20 2020-04-22 IMI Hydronic Engineering International SA Ventil und verfahren zur betätigung eines ventils
EP2886916B1 (de) * 2013-12-20 2019-02-20 IMI Hydronic Engineering International SA Ventil und Verfahren zur Betätigung eines Ventils
US9822904B2 (en) 2013-12-20 2017-11-21 Imi Hydronic Engineering International Sa Valve and a method of operating a valve
US10619761B2 (en) 2013-12-20 2020-04-14 Imi Hydronic Engineering International Sa Valve and a method of operating a valve
US20170328493A1 (en) * 2013-12-20 2017-11-16 Imi Hydronic Engineering International Sa Valve and a method of operating a valve
EP3702873A1 (de) * 2013-12-20 2020-09-02 IMI Hydronic Engineering International SA Ventil und verfahren zur betätigung eines ventils
EP3489557A1 (de) * 2013-12-20 2019-05-29 IMI Hydronic Engineering International SA Ventil und verfahren zur betätigung eines ventils
US11828384B2 (en) 2018-10-29 2023-11-28 Siemens Schweiz Ag Method for operating a valve, associated electronic control unit, and valve drive
US11092354B2 (en) 2019-06-20 2021-08-17 Johnson Controls Tyco IP Holdings LLP Systems and methods for flow control in an HVAC system
US11644215B2 (en) 2019-06-20 2023-05-09 Johnson Controls Tyco IP Holdings LLP Systems and methods for flow control in an HVAC system
US11149976B2 (en) 2019-06-20 2021-10-19 Johnson Controls Tyco IP Holdings LLP Systems and methods for flow control in an HVAC system
US11391480B2 (en) 2019-12-04 2022-07-19 Johnson Controls Tyco IP Holdings LLP Systems and methods for freeze protection of a coil in an HVAC system
US11624524B2 (en) 2019-12-30 2023-04-11 Johnson Controls Tyco IP Holdings LLP Systems and methods for expedited flow sensor calibration
US11519631B2 (en) 2020-01-10 2022-12-06 Johnson Controls Tyco IP Holdings LLP HVAC control system with adaptive flow limit heat exchanger control
US11614757B2 (en) 2020-07-15 2023-03-28 Siemens Schweiz Ag Estimating a maximum flow through a heat exchanger

Also Published As

Publication number Publication date
CA2727779A1 (en) 2010-01-28
EP2304325A2 (de) 2011-04-06
CN102216691B (zh) 2014-07-16
EP2304325B1 (de) 2017-04-05
CN102216691A (zh) 2011-10-12
WO2010010092A2 (de) 2010-01-28
WO2010010092A3 (de) 2011-11-10

Similar Documents

Publication Publication Date Title
US20110114304A1 (en) Method for the hydraulic compensation and control of a heating or cooling system and compensation and control valve therefor
US9874880B2 (en) Device and method for controlling opening of a valve in an HVAC system
EP3428767B1 (de) Steuerungsverstärkungsautomatisierung
US9631831B2 (en) Method for controlling the opening of an HVAC valve based on the energy-per-flow gradient
US11175039B2 (en) Regulating turbulent flows
AU2005230524B2 (en) Cooling and/or heating device
CN109764243B (zh) 用于控制通过阀的流体流动的方法
US7775865B2 (en) Set and forget exhaust controller
US5179330A (en) Control circuit for an electrically controlled servo device
US7684947B2 (en) Method for matching the actual characteristic curve of a hydrodynamic component to a predefined set characteristics curve during the final test of the hydrodynamic component
US10183599B2 (en) Device and method for adjusting a contour of a vehicle seat with contour adjustment
RU2613474C2 (ru) Способ регулирования для насосного агрегата
EP0540079A1 (de) Steuerung des Stellgliedes eines Durchflussventiles mittels seiner Durchfluss-Kennlinie
RU2557150C2 (ru) Уравнительный вентиль
US20210396418A1 (en) Device and method for controlling an orifice of a valve in an hvac system
KR101785247B1 (ko) 자동 온수 조절 장치 및 그 조절 방법
CN112127987A (zh) 特种车辆独立散热系统温度控制方法
CN112127986A (zh) 特种车辆独立散热系统温度控制系统
EP3309465A1 (de) Fehlerdetektion einer ventilanordnung
EP4141608A1 (de) Ventilanordnung und verfahren zum betrieb des ventils
CN110986332B (zh) 一种自动判别冷媒三通阀调节死区及自动跳过死区的控制方法
US3951337A (en) Arrangement, in a weather-dependent advance controller of temperature of a heating installation, for facilitating adjustment of controller characteristics to heating characteristics
Hittle Controlling variable-volume systems
JPS6069448A (ja) 空気調和装置
JPS5813725B2 (ja) タ−ビンベンセイギ゛ソウチ

Legal Events

Date Code Title Description
AS Assignment

Owner name: BELIMO HOLDING AG, SWITZERLAND

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:KELLER, URS;REEL/FRAME:025621/0091

Effective date: 20101108

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION