WO2005015068A1 - Vanne de regulation et systeme d'echangeur de chaleur - Google Patents

Vanne de regulation et systeme d'echangeur de chaleur Download PDF

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Publication number
WO2005015068A1
WO2005015068A1 PCT/DK2004/000524 DK2004000524W WO2005015068A1 WO 2005015068 A1 WO2005015068 A1 WO 2005015068A1 DK 2004000524 W DK2004000524 W DK 2004000524W WO 2005015068 A1 WO2005015068 A1 WO 2005015068A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
drive
heat exchanger
control valve
valve element
Prior art date
Application number
PCT/DK2004/000524
Other languages
German (de)
English (en)
Inventor
Jan Eric Thorsen
Niels Peter Graversen
Original Assignee
Danfoss A/S
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 Danfoss A/S filed Critical Danfoss A/S
Publication of WO2005015068A1 publication Critical patent/WO2005015068A1/fr

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Classifications

    • 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
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise
    • F16K47/023—Means in valves for absorbing fluid energy for preventing water-hammer or noise for preventing water-hammer, e.g. damping of the valve movement
    • 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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats

Definitions

  • the invention relates to a control valve with a valve seat, a valve element interacting with the valve seat and a drive device acting on the valve element.
  • a control valve of this type is usually used to control a liquid flow as a function of one or two influencing variables.
  • An example in which the invention is applicable is a heat exchanger arrangement.
  • the drive arrangement is e.g. regulated as a function of a flow on the primary side of the heat exchanger and as a function of the temperature on the secondary side of the heat exchanger.
  • Operation can become unstable, i.e. the control valve can start to oscillate.
  • the invention has for its object to improve the control behavior with small flow rates.
  • the drive device preferably has a first drive and a second drive with a fixed signal-path relationship, the second drive acting on the valve element via the spring element.
  • a control valve provided with such a drive device is also referred to as an engine valve, because a signal that acts on the second drive causes a change in position of the output of the second drive that is directly related to the signal. This change in position does not depend on external forces.
  • An example of the second drive is a thermostatic element with a non-compressible filling, for example a wax filling or a liquid filling, which expands and contracts depending on the temperature. This will give the control signal to the second Actuator works, not converted directly into a position or change of position, but into a force.
  • the second drive acts on the valve element via the spring element.
  • the spring element can now react to external forces, for example to reaction forces that act back from the valve element.
  • the first drive and the second drive are preferably arranged in series with the spring element interposed.
  • the second drive thus acts on the valve element via the first drive, the spring element being arranged between the two drives.
  • the spring element is then given another task: it prevents the second drive from overstressing the first drive.
  • the first drive is preferably formed by a membrane which is arranged between a first pressure chamber and a second pressure chamber.
  • the two pressure chambers can now be supplied with different pressures, for example, which can be removed on two sides of a throttle point.
  • the flow of a fluid through the throttling point can be regulated in this way.
  • the preload of the membrane can be specified via the second drive.
  • the valve element can preferably be moved in the direction of the valve seat against the force of an opening spring.
  • the two drives must therefore overcome the force of the opening spring to close the valve. In principle, this results in a stable control behavior, but this can still be improved if the second drive is allowed to act on the valve element via a spring element. This also enables the element to be readjusted, that is, an adjustment of the set point.
  • At least one of the two parts valve element and valve seat preferably has a pre-contact zone in which contact between the valve seat and valve element is restricted to a predetermined partial area of a closing area, which has a predetermined deformation behavior and opposes a predetermined counterforce when the valve element and valve seat approach each other ,
  • This pre-contact zone then forms, so to speak, the damping spring arrangement, which generates an increasingly greater counterforce as the valve element approaches the valve seat, but only when the valve element and valve seat touch.
  • the pre-contact zone is preferably formed by at least one projection on at least one of the parts of the valve seat and valve element, which protrudes in the direction of the other part of the valve element or valve seat.
  • the projection In order to achieve a closing or at least a sufficiently close approach of the valve element to the valve seat, either the projection must be deformed or a material must be deformed into which the projection penetrates. Appropriate forces are required for these material deformations.
  • the projection is made of the same material as the part carrying it.
  • the projection can be formed on an elastomeric element which is arranged on the valve element. Such an elastomeric element is usually present to allow the valve to be closed tightly. If the protrusion is also formed from the elastomeric material, then the protrusion is deformed. But you can also form the projection on the valve seat.
  • the valve seat is usually made of a harder material, for example a metal. If the projection is formed from metal, it penetrates into the elastomeric material on the valve element and deforms it until a sealing contact of the valve element with the valve seat is achieved. This is also a way to achieve the desired counterforce when closing the valve.
  • the projection preferably tapers towards its tip.
  • the counterforce which is generated by the compression of the projection or the pressing of the projection into the elastomer increases sharply as the valve element approaches the valve seat. The closer the valve element approaches the valve seat, the more material has to be compressed or displaced.
  • the pre-contact zone preferably has a plurality of projections which are arranged symmetrically to a drive axis of the valve element. In this case, avoidance of the valve element being skewed when it is placed against the valve seat and thus increased wear when driving the valve element.
  • the invention also relates to a heat exchanger arrangement with a control valve of the type described, in which the first drive is controlled as a function of a differential pressure via a throttle on a primary side of the heat exchanger and the second drive as a function of a variable on a secondary side of the heat exchanger.
  • the first drive thus controls the flow of a heat transfer fluid to the primary side of the heat exchanger.
  • the second drive specifies a pretension for the first drive, but this is influenced by the secondary side of the heat exchanger.
  • the first drive can be controlled as a function of a differential pressure via a throttle on a secondary side of the heat exchanger and the second drive can be controlled by a variable on the secondary side of the heat exchanger. It is also possible that the first drive is controlled as a function of a differential pressure via a throttle on a secondary side of the heat exchanger and the second drive is controlled by a variable on the primary side of the heat exchanger. Both alternatives control the secondary side, here preferably the inflow on the secondary side.
  • the size on the secondary side is a temperature. You can then regulate the temperature on the secondary side very stably with the control valve.
  • control valve is arranged as a pilot valve for an actuator of an adjustable throttle.
  • the control valve is therefore not used directly to control the flow. Rather, the control valve is used as an auxiliary device for controlling an adjustable throttle.
  • Such a solution is particularly useful when larger amounts of fluid have to be regulated.
  • control valve is arranged in a secondary flow path parallel to the adjustable throttle and pressures are present on different sides of the actuator on both sides of the control valve.
  • the actuator for the adjustable throttle can then be actuated, for example, proportional to the flow through the control valve, so that there is a fixed assignment of the flow rate through the adjustable throttle and through the control valve.
  • valve element 5 shows a first embodiment of a pairing of valve element and valve seat
  • FIG. 6 is a sectional view of the valve element of FIG. 5,
  • FIG. 7 shows an alternative embodiment of a pairing of valve element and valve seat
  • Fig. 8 shows a second alternative heat exchanger arrangement
  • Fig. 9 shows a third alternative heat exchanger arrangement.
  • FIG. 1 shows a heat exchanger arrangement 1 with a heat exchanger 2, which is supplied with a heat transfer medium, for example hot water from a district heating system, via a primary side 3, which has a flow 4 and a return 5.
  • a secondary side 6 has an extraction line 7 and an inflow line 8. Heated service water can be withdrawn via the discharge line 7, which is supplied via the inflow line 8 and heated in the heat exchanger 2.
  • a control valve 9 which has a closing device 10, which is explained in more detail in connection with FIG. 2, is arranged on the primary side 3 in the flow line 4.
  • the closing device 10 more or less releases a flow cross section through the flow 4.
  • the closing device 10 has a valve seat 11 and a valve element 12 cooperating therewith.
  • the valve element 12 is biased in the opening direction by an opening spring 13.
  • the valve element 12 is connected to a tappet 14 which is connected to a first drive 15.
  • the first drive 15 has a membrane 16 which is arranged between a first pressure chamber 17 and a second pressure chamber 18.
  • the plunger 14 is connected to the membrane 16.
  • the first pressure chamber 17 is connected to the flow 4 at a position in the flow direction in front of an adjustable throttle 19 and the second pressure chamber 18 is connected to the flow 4 at a position in the flow direction behind the throttle 19. Accordingly, there is a pressure difference across the membrane 16, which corresponds to the pressure drop across the throttle 19 corresponds.
  • the flow resistance of the throttle 19 can optionally be changed via a handle 20.
  • the first drive 15 regulates the flow through the flow 4 so that the pressure drop across the throttle 19 is constant.
  • the position of the valve element 12 relative to the valve seat is also influenced by a second drive 21.
  • the second drive 21 is identified here by an "M", i.e. it is a motor drive in which the position of a drive element 22 changes as a function of an input signal E. Motors can therefore be used as the drive 21, both rotary motors and linear motors.
  • M motor drive
  • a thermostat element that is filled with a non-compressible filling, for example a wax cartridge.
  • a wax cartridge changes its length depending on the temperature. External forces play practically no role here.
  • the spring element 23 for example a helical compression spring, which is arranged in a tube 24, does not immediately indicate a change in position of the drive member 22 Valve element 12 further, but the change in position of the valve element 12 depends on other factors, in particular the other forces that act on the valve element 12.
  • the spring element 23 has the advantage that it can prevent the drive 21 from being overloaded. If the valve element 12 is already in its end position on the valve seat 11, then the drive 21 cannot be damaged, even if it moves the drive member 22 further in the direction of the valve seat 11. With the help of the spring element 23, the drive 21 can thus change the pretension against which the first drive 15 must work. The setting point of the differential pressure regulator formed by the first drive 15 can thus be changed from the outside, namely via the signal E.
  • a controller 25 is provided, to which a temperature setpoint TSET on the one hand and the temperature in the extraction line 7 on the other hand is supplied. From the difference between these two temperatures, the controller 25 forms the signal E, which is fed to the drive 21. If the temperature is too low, the drive member 22 is moved away from the valve seat 11. The spring element 23 relaxes and the spring force acting on the first drive 15 is reduced. Accordingly, a lower closing force acts on the valve element 12 and more heat transfer fluid can flow on the primary side 3 of the heat exchanger 2. Conversely, the spring force of the spring element 23 is increased if the temperature of the process water in the extraction line 7 is too high.
  • a progressive valve characteristic curve is provided, which is shown in FIG. 4.
  • the flow amount Q that is passed between the valve seat 11 and the valve element 12 depends non-linearly on the signal E. As will be described in the following, this non-linearity is automatically set as a function of the position of the valve element 12 relative to the valve seat 11.
  • a damping spring 40 is shown, which is prevented from further expansion by a stop 41 fixed to the housing, but can be compressed by an actuating element 42 arranged on the tappet 14 if the actuating element 42 is attached to the blow 41 is moved past.
  • the stop 41 can also be omitted if the length of the damping spring 40 is short enough in the relaxed state. The damping spring therefore only acts when the valve element 12 is relatively close to the valve seat 11.
  • valve seat 11 and valve element 12 are provided.
  • a line 26 indicates a limit at which the valve seat 11 abuts when the valve is closed.
  • the valve element 12 has four projections 27 distributed in the circumferential direction, between which there are gaps 28.
  • the projections 27 are distributed symmetrically about an axis 29.
  • the axis 29 is the central axis of the plunger 14.
  • valve element 12 When the valve element 12 approaches the valve seat 11, the projections 27 first come into contact with the valve seat 11.
  • the valve element 12 is formed from a core 30 which carries an elastomeric coating 31. It is also possible to use a separate elastomeric element which is connected to the core 30 in another way.
  • the projections 27 are integrally connected to the elastomer 31.
  • the valve seat 11, on the other hand, is formed from a harder material, for example a metal.
  • valve element 12 with the projections 27 comes to rest on the valve seat 11, then a further movement of the valve element 12 on the valve seat 11 is opposed to an increasingly greater resistance. This resistance is due to the fact that the projections 27 have to be deformed until the valve element 12 finally lies tight against the valve seat 11.
  • the control valve 9 shown in FIG. 2 it is often not important to be able to completely interrupt the flow 4. You want to be able to influence the flow through the flow line 4 only so that a desired pressure drop across the throttle 19 is achieved.
  • the protrusions 27 taper towards their tip, i.e. to the position closest to the valve seat 11. This produces an even greater increase in the counterforce that is required when the valve element 12 approaches the valve seat 11.
  • projections 32 on the valve seat 11 can also be used, as shown in FIG. 7. Parts which correspond to those in FIG. 5 are provided with deleted reference numerals. Again, this is the case Valve element 12 'provided with an elastomeric element, at least in the area that the Valve seat 11 'is opposite.
  • the projections 32 are made of the same material as the valve seat 11 ', that is, for example, of metal.
  • the projections 32 press into the elastomeric element on the valve element 12 'and thereby also cause a counterforce which is required to displace material. This material displacement is necessary to make room for the projections 32. The projections thus take over the function of the damping spring 40.
  • FIG. 8 shows an embodiment of a heat exchanger arrangement modified compared to FIG. 1. The same and corresponding parts are provided with the same reference numerals as in Fig. 1.
  • a tap 43 for warm water is arranged in the extraction line 7 on the secondary side 6 of the heat exchanger 2.
  • the controller 25 now regulates the flow Q by actuating the closing device 10 on the primary side 3 of the heat exchanger 2.
  • the closing device 10 is arranged in the return 5 of the primary side 3.
  • the first drive 15 is determined by a difference between two pressures P
  • the throttle 19 is arranged in the inflow line 8 of the secondary side 6. In the embodiment shown, it is not adjustable, but is designed as a fixed throttle. The drive 15 is therefore regulated by the pressure difference that arises when the liquid flows through on the secondary side 6.
  • An electrical actuating device normally acts directly on the plunger 14. At a high primary temperature and high primary differential pressure stability problems can arise. At the start and the end of the tap, the reaction speed is normally limited by the speed of the drive device and the conditions around the temperature sensor.
  • thermostatic adjustment element is replaced by a spring and a motor.
  • the drive element driven by the drive 21 does not serve as a position transmitter for the plunger 14, but is part of the balance of forces which ultimately determines the position of the plunger. Via the membrane 16 there is a "feed-forward" member that has a quick response. The action of the damping spring assembly 40 is used to achieve stable control.
  • FIG. 9 shows a further embodiment of a heat exchanger arrangement in which parts which correspond to those in FIGS. 1 to 8 are provided with the same reference symbols.
  • control valve 9 is arranged on the secondary side 6 of the heat exchanger 2, specifically in the inflow line 8.
  • the inflow line 8 just as in the embodiment according to FIG. 8, there is a throttle 19 which generates a pressure difference. This pressure difference is used to control the first drive 15.
  • a temperature T from the flow 4 of the primary side 3 of the heat exchanger is used to control the second drive 21, possibly via a controller 25.
  • the two drives 15, 21 are therefore on the one hand of the temperature on the primary side 3 of the heat exchanger 2 and others controlled by the consumption on the secondary side 6 of the heat exchanger 2.
  • the control valve 9 serves here rather as a pilot valve for an adjustable throttle 50.
  • the adjustable throttle 50 is actuated via an actuator 51.
  • the actuating drive 51 has a membrane 52, which is actuated in the other direction by a pressure in a first pressure chamber 53 and by a pressure in a second pressure chamber 54 and a spring 55.
  • the pressure in the pressure chamber 53 corresponds to the pressure in front of the closing element 10 of the control valve 9.
  • the pressure in the second pressure chamber 54 corresponds to the pressure behind the closing element 10 of the control valve 9, which is arranged in a secondary flow path 56 to the adjustable throttle 50.
  • the adjustable throttle 50 is thus controlled via the pressure drop at the closing device 10 of the control valve 9.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Temperature-Responsive Valves (AREA)

Abstract

L'invention concerne une vanne de régulation comportant un siège de soupape (11), un élément de soupape (12) coopérant avec le siège de soupape (11) et un dispositif d'entraînement agissant sur l'élément de soupape. L'invention vise à améliorer le comportement en régulation dans le cas de débits réduits. A cet effet, il est prévu que le dispositif d'entraînement agisse sur l'élément de soupape (12) par l'intermédiaire d'un élément à effet ressort (23), un dispositif d'amortissement étant prévu. Ledit dispositif d'amortissement n'agit sur l'élément de soupape qu'en cas de dépassement d'un seuil inférieur d'un écart prédéterminé entre le siège de soupape (11) et l'élément de soupape (12).
PCT/DK2004/000524 2003-08-07 2004-08-05 Vanne de regulation et systeme d'echangeur de chaleur WO2005015068A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10336916.3A DE10336916B4 (de) 2003-08-07 2003-08-07 Regelventil und Wärmetauscheranordnung
DE10336916.3 2003-08-07

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Publication Number Publication Date
WO2005015068A1 true WO2005015068A1 (fr) 2005-02-17

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PCT/DK2004/000524 WO2005015068A1 (fr) 2003-08-07 2004-08-05 Vanne de regulation et systeme d'echangeur de chaleur

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WO (1) WO2005015068A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007098880A1 (fr) * 2006-02-24 2007-09-07 Deutz Power Systems Gmbh Procédé et dispositif pour améliorer le comportement instable de moteurs à gaz à mélange pauvre

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006005411A1 (de) * 2006-01-30 2007-08-09 Danfoss A/S Ventil

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1709747U (de) * 1955-08-17 1955-10-27 Kuehnle Kopp Kausch Ag Servomotor fuer regulierventile.
EP0027933A1 (fr) * 1979-10-12 1981-05-06 Honeywell-Braukmann GmbH Soupape thermostatique, notamment soupape thermostatique pour radiateur de chauffage
EP0827057A1 (fr) * 1996-08-31 1998-03-04 Deutsches Zentrum für Luft- und Raumfahrt e.V. Vanne thermostatique
US5904292A (en) * 1996-12-04 1999-05-18 Mcintosh; Douglas S. Modulating fluid control device
GB2341223A (en) * 1998-09-02 2000-03-08 Danfoss As Stroke-action valve
WO2002090382A2 (fr) * 2001-05-04 2002-11-14 Commissariat A L'energie Atomique Melange de peptides issus des proteines e6 et/ou e7 de papillomavirus et leurs applications

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Publication number Priority date Publication date Assignee Title
FR1554857A (fr) * 1967-12-11 1969-01-24
FR2437546A2 (fr) * 1978-09-29 1980-04-25 Guilbert & Fils Leon Dispositif obturateur en particulier pour robinets
DE3149839A1 (de) * 1981-12-16 1983-06-23 Motoren-Werke Mannheim AG, vorm. Benz Abt. stat. Motorenbau, 6800 Mannheim Ausregel-vorrichtung fuer einen aufgeladenen gasmotor
GB2158616A (en) * 1984-05-10 1985-11-13 Anthony Charles Robert Johnson Hydraulic operated pressure reducing valve
DE4427846C2 (de) * 1994-08-05 1997-07-31 Danfoss As Regeleinrichtung für die Temperatur des aus einer Wasserleitung entnommenen Wassers
DE19800882C2 (de) * 1998-01-13 1999-11-18 Baelz Gmbh Helmut Wärmeübertragungssystem und Verfahren zum Betrieb desselben
AT408689B (de) * 1998-12-09 2002-02-25 Seebacher Theodor Vorrichtung zum steuern eines wärmetauschers

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1709747U (de) * 1955-08-17 1955-10-27 Kuehnle Kopp Kausch Ag Servomotor fuer regulierventile.
EP0027933A1 (fr) * 1979-10-12 1981-05-06 Honeywell-Braukmann GmbH Soupape thermostatique, notamment soupape thermostatique pour radiateur de chauffage
EP0827057A1 (fr) * 1996-08-31 1998-03-04 Deutsches Zentrum für Luft- und Raumfahrt e.V. Vanne thermostatique
US5904292A (en) * 1996-12-04 1999-05-18 Mcintosh; Douglas S. Modulating fluid control device
GB2341223A (en) * 1998-09-02 2000-03-08 Danfoss As Stroke-action valve
WO2002090382A2 (fr) * 2001-05-04 2002-11-14 Commissariat A L'energie Atomique Melange de peptides issus des proteines e6 et/ou e7 de papillomavirus et leurs applications

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007098880A1 (fr) * 2006-02-24 2007-09-07 Deutz Power Systems Gmbh Procédé et dispositif pour améliorer le comportement instable de moteurs à gaz à mélange pauvre

Also Published As

Publication number Publication date
DE10336916B4 (de) 2015-02-19
DE10336916A1 (de) 2005-03-03

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