DK179689B1 - Control valve for heating and/or cooling system - Google Patents

Control valve for heating and/or cooling system Download PDF

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Publication number
DK179689B1
DK179689B1 DKPA201870152A DKPA201870152A DK179689B1 DK 179689 B1 DK179689 B1 DK 179689B1 DK PA201870152 A DKPA201870152 A DK PA201870152A DK PA201870152 A DKPA201870152 A DK PA201870152A DK 179689 B1 DK179689 B1 DK 179689B1
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DK
Denmark
Prior art keywords
annular body
control valve
pressure
valve
axial
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DKPA201870152A
Other languages
Danish (da)
Inventor
Enøe Møller Carsten
Original Assignee
Flowcon International Aps
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Priority claimed from DKPA201770612A external-priority patent/DK179688B1/en
Application filed by Flowcon International Aps filed Critical Flowcon International Aps
Priority to DKPA201870152A priority Critical patent/DK179689B1/en
Publication of DK201870152A1 publication Critical patent/DK201870152A1/en
Application granted granted Critical
Publication of DK179689B1 publication Critical patent/DK179689B1/en

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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
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/30—Details
    • F16K3/32—Means for additional adjustment of the rate of flow
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D7/00—Control of flow
    • G05D7/01—Control of flow without auxiliary power

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Fluid Pressure (AREA)

Abstract

A control valve (1) for controlling flow of liquid in a heating and/or cooling installation, the control valve (1) comprising an elongated, preferably rotation symmetric, valve body (2,4) with opposite first- and second longitudinal ends, the first longitudinal end being provided with an inlet opening (9), a pressure regulating arrangement configured for maintaining a substantially constant differential pressure between a first pressure (P1) in the control valve (1) and a second pressure (P2) in the control valve (1), the pressure regulating arrangement comprises a movable throttle member (16) that is urged by the first pressure (P1) to increase the flow resistance posed by the pressure regulating arrangement and that is urged by a resilient member (20) and by the second pressure (P2) to decrease the flow resistance posed by the pressure regulating arrangement, the movable throttle member comprising a rolling diaphragm (16) that interacts with a plurality of exit openings (18), the rolling diaphragm (16) having a circular circumference attached to an annular body (11), the plurality of exit openings (18)being formed radially through the annular body (11), and the annular body (11) being slidably disposed in a cylindrical portion (4) of the valve housing (2) for allowing axial movement and rotational movement of the annular body (11) relative to the valve housing (2).

Description

CONTROL VALVE FOR HEATING AND/OR COOLING SYSTEM
TECHNICAL FIELD
The disclosure relates to a control valves that includes a differential pressure control function, in particular to control valves for control of fluid in a heating and/or cooling installation of e.g. a building, a ship or a plant.
BACKGROUND
This type of control valve is used for hydraulic balancing in a system that comprises a large number of individual heating circuits. These control valves are used to control the flow of heating or cooling fluids through individual circuits in the system, and thus ensure that each individual heating circuit is provided with a desired flow of heating or cooling liquid so that the whole system is balanced. An individual heating circuit can be a section of a floor heating, of a ceiling cooling system, a space heating radiator or a group of several space heating radiators.
This type of control valve is provided with a differential pressure control function that includes a movable throttling element that is affected on one side by a first pressure P1 and on the other side by second pressure P2 and a resilient force, for example from a helical spring. The second pressure P2 is lower than the first pressure P1 and the characteristics of the resilient force determine the pressure differential that is maintained. Thus, a stiffer spring results in a higher differential pressure. Such a differential pressure control function is e.g. used to maintain a constant differential pressure over an adjustable size opening. With a constant differential pressure over the adjustable size opening the flow can be accurately regulated by adjusting the adjustable size opening. The adjustable size opening can be manually adjusted or be adjusted using an actuator, such as an electric actuator. The adjustment can be automatic by an electronic control unit or be in response to a control signal. Typically, the typically, adjustment is manual and the control valves are arranged in the return line.
However, there are other ways to use a differential pressure function in a control valve that do not relate to an adjustable size opening.
WO2008052553 discloses a control valve with a rolling membrane as the throttling member and the resilient force comes from a helical spring acting on the rolling membrane. The first higher pressure P1 and the second low pressure P2 originate both on one of the same side of the rolling membrane. Therefore, a pressure communication channel is provided in a central shaft that extends through the rolling membrane for communicating the first high pressure P1 to the opposite side of the rolling membrane. The central shaft extends through a collar in a central opening in the rolling membrane. The collar fits slidingly over the central shaft since the rolling membrane must be allowed to move freely in response to the first pressures P1 on its one side and the second pressure P2 and the helical spring on its other side. The rolling membrane must therefore be free move relative to the central shaft. A small clearance is needed between the collar and the central shaft to ensure free movement of the rolling membrane. However, such a clearance will always form a leak path and consequently, it is not possible to avoid small amount of leakage even if the valve of WO2008052553 is in its fully closed position. Though small, such leakage may over time accrue and form a substantial energy loss for the system in which is used.
Consequently, there is a need for a control valve that overcomes or at least reduces the problems indicated above.
SUMMARY
The foregoing and other objects are achieved by the features of the independent claims. Further implementation forms are apparent from the dependent claims, the description and the figures.
According to a first aspect, there is provided a control valve for controlling flow of liquid in a heating and/or cooling installation, the control valve comprising an elongated, preferably rotation symmetric, valve body with opposite first- and second longitudinal ends, the first longitudinal end being provided with an inlet opening, a pressure regulating arrangement configured for maintaining a substantially constant differential pressure between a first pressure P1 in the control valve and a second pressure P2 in the control valve, the pressure regulating arrangement comprises a movable throttle member that is urged by the first pressure P1 to increase the flow resistance posed by the pressure regulating arrangement and that is urged by a resilient member and by the second pressure P2 to decrease the flow resistance posed by the pressure regulating arrangement, the movable throttle member comprising a rolling diaphragm that interacts with a plurality of exit openings, the rolling diaphragm having a circular circumference attached to an annular body, the plurality of exit openings being formed radially through the annular body, the annular body being slidably disposed in a cylindrical portion of the valve housing for allowing axial movement and rotational movement of the annular body relative to the valve housing.
By providing a control valve in which the differential pressure regulation function is included in a separate body that can move axially and rotationally relative to the valve body, it is possible to provide a differential control valve with improved possibilities for controlling flow and reducing leakage.
According to a possible implementation of the first aspect the annular body fits sealingly inside the cylindrical portion.
In a possible implementation of the first aspect the control valve comprises a closing member arranged to move axially in unison with the annular body, the closing member being configured to sealingly close the inlet opening in a first axial portion of the annular body and to allow fluid passage through the inlet opening in a second axial position of the annular body.
According to a possible implementation of the first aspect the closing member comprises a cylindrical part extending axially from the annular body towards the inlet opening.
According to a possible implementation of the first aspect the annular body has two opposite axial ends, wherein the axial end of the annular body closest to inlet opening comprises a disk-shaped element provided with at least one first regulation opening.
According to a possible implementation of the first aspect the disk-shaped element forms a bottom of the annular body.
According to a possible implementation of the first aspect the control valve comprises a plate member with at least one second regulation opening for interacting with the first regulation opening, one side of the plate member being in contact with the side of the disk shaped element closest to the inlet opening, the plate member, being arranged to move axially in unison with the annular body and the plate member being rotationally immovable relative to the cylindrical portion of the valve body, whereby a greater or smaller overlap may be established between the at least one first regulation opening and the at least one second regulation opening by the rotation of the annular body relative to the valve body.
According to a possible implementation of the first aspect the cylindrical portion is connected to the plate member.
According to a possible implementation of the first aspect the control valve comprises a membrane support member for supporting and engaging a central portion of the rolling membrane, and a helical spring, the helical spring acting on the support member to urge the rolling membrane in a direction that reduces the throttling effect of the rolling membrane.
According to a possible implementation of the first aspect the control valve comprises a mechanism connected to the annular body for adjusting the rotational position of the annular body relative to the valve body, the mechanism being configured for adjusting the rotational position manually or with an actuator.
According to a possible implementation of the first aspect the control valve comprises a mechanism connected to the annular body for adjusting the axial position of the annular body relative to the valve housing, the mechanism being configured for adjusting the axial position manually or with an actuator.
According to a possible implementation of the first aspect the annular body comprises least one pressure communication channel extending in the annular body for communicating the first pressure P1 from a first location in the control valve on one axial side of the rolling diaphragm to a second location in the control valve on the other axial side of the rolling diaphragm.
These and other aspects will be apparent from and the embodiment(s) described below.
BRIEF DESCRIPTION OF THE DRAWINGS
In the following detailed portion of the present disclosure, the aspects, embodiments and implementations will be explained in more detail with reference to the example embodiments shown in the drawings, in which:
Figs. 1 and 2 are different side views of a control valve, Figs 3,4 and 6 are longitudinal-sectional views of the control valve of Figs. 1 and 2,
Fig. 5 is a cross-sectional view of the control valve of Figs. 1 and 2,
Fig. 7 is a longitudinal-sectional view of a functional element of Figs. 1 and 2, the functional element including a constant pressure differential function and a flow area adjustment function,
Fig. 8 is an enlarged detail of Fig. 7,
Fig. 9 is an exploded view of the valve of Figs. 1 and 2, Fig. 10 is an enlarged longitudinal-sectional view of the valve of Figs. 1 and 2 in an open position, but with internal thread instead of external threat for coupling an actuator to the control valve,
Fig. 11 is an enlarged longitudinal-sectional view of the valve of Fig. 10 in a closed position,
Figs. 12 and 13 show a plurality of control valves in a manifold of a floor heating or ceiling cooling system, and Figs. 14 and 15 show the manifold and control valves of Figs. 12 and 13 in cross-sectional and longitudinalsectional view, respectively.
DETAILED DESCRIPTION
A control valve is described with reference to Figs. 1 to 15. The control valve 1 comprises a valve body 2. The valve body 2 is generally rotation symmetric and comprises a part with a hexagonal outer contour and a cylindrical part 4. It should though be noted that the part with the hexagonal order does not need to have a hexagonal outer shape, the skilled person is familiar with other suitable shapes, such as e.g. a simple cylindrical shape.
The valve body 2 is at or near one of its longitudinal ends provided with thread for coupling with a linear actuator provided with corresponding thread, such as an electric actuator (not shown). The valve body 2 is also provided with thread for engaging thread of a housing or body, such as a manifold 40. Both the cylindrical part 4 and the part with the hexagonal outer have a hollow interior in which most of the components of the control valve 1 are arranged.
An axially movable activator 6 protrudes from the longitudinal end of the valve body 2 where the thread for coupling to an actuator is provided. The activator 6 protrudes from the valve body 2 for engaging an actuator (not shown). The activator 6 is arranged in to parts with a helical spring 38 therebetween in order to avoid application of excessive force to the components in control valve 1 by an actuator.
The opposite longitudinal end is part of the cylindrical part 4. The opposite longitudinal end is provided with an axial inlet opening 9. The cylindrical part 4 is provided with one or more radial outlet openings 7. The control valve 1 controls the flow from the axial inlet opening 9 to the radial outlet opening(s) 7.
Hereto, the control valve 1 comprises an arrangement for maintaining a constant differential pressure and an arrangement for adjusting the size of an adjustable size opening. In an embodiment the arrangement for maintaining the constant differential pressure maintains a constant differential pressure over the adjustable size opening.
An annular body 11 is disposed slidably inside the cylindrical portion 4 of the valve body 2, such that the annular body can rotate relative to the valve body 2 and move in the axial direction relative to the valve body 2. The fit between the annular body 11 and the cylindrical portion 4 is such that it is substantially sealing.
The differential pressure control function comprises a throttling member in the form of a rolling diaphragm 16. The rolling diaphragm 16 has a circular outer circumference that is secured to the annular body 11. The rolling diaphragm is supported by a diaphragm support member 14. A helical spring 20 acts on the diaphragm support member 14 and urges the rolling diaphragm 16 in a direction that reduces the throttling effect of the rolling diaphragm 16.
The annular body 11 is provided with a plurality of exit openings 18. The exit openings 18 extend radially through the annular body 11. The exit openings 18 can be formed as longitudinal slits that extend axially. The exit openings 18 are preferably circumferentially evenly distributed over the annular body 11.
The axial end of the annular body 11 closest to the axial inlet opening 9 is closed off by a bottom in the form of a disc member 15. The disc member 15 is provided with one or more first regulation openings 26.
The axial end of the annular body 11 furthest from the axial inlet opening is provided with a cover 12. The cover 12 is provided with a number of through going openings for pressure equalization.
The bottom with the disc member 15 is rigidly connected to annular body 11 and can be formed as an integral part of the annular body 11. The cover 12 is rigidly connected to the annular body 11.
A central cylindrical portion extends from the disc member 15 and is in an embodiment and integral part of the annular body 11. The central cylindrical portion serves as a shaft for a cylindrical part 22. The cylindrical part 22 moves axially in unison with the annular body 11 and is rotatably suspended from the annular body 11. The cylindrical part 22 is provided with a closing member 29. The closing member 29 is configured to be able sealingly close the axial inlet opening 9. Hereto, the closing member 29 is advantageously the provided with an O-ring. The closing member 29 essentially consists of a cylindrical body that sealingly fits in the circular outline of the axial inlet opening 9.
The cylindrical part 22 can move axially relative to the valve body 2. However, the cylindrical part 22 it is prevented from a rotational movement relative to the valve body 2.
Thus, the annular body 11 and the cylindrical part 22 form together an axially movable unit 10. Figs. 7 and 8 show the unit 10 in detail. Fig. 10 shows the axially movable unit 10 in a position where the closing member 29 does not close the axial inlet opening 9 and Fig. 11 shows the axially movable unit 10 in a position where the closing member 29 sealingly closes the inlet opening 9. Thus, in the position shown in Fig. 11 the control valve is completely closed and does not have any leakage.
The unit 10 is biased to the open position by a helical spring 32. The unit 10 can be moved against the bias of the helical spring 32 by applying force to the activator 6 (e.g. by using an actuator). The force of the activator 6 is transmitted to the cover 12 of the unit 10 by a central shaft 8. The central shaft 8 is sealed by an O-ring against an insert 37.
The cylindrical part 22 supports a plate member 25. The plate member 25 is urged onto the disc member 15 by the helical spring 32. Thus, the side furthest from the inlet opening 9 of the plate member 25 is pressed onto the side closest to the inlet opening 9 of the disc shaped member 15. The plate member 25 is provided with at least one second regulation opening 24 for interacting with the first regulation opening 26. One side of the plate member 25 is in contact with the side of said disk shaped element 25 closest to said inlet opening 9. The plate element 25 is arranged to move axially in unison with the annular body 11 and the plate element 25 is rotationally immovable relative to the cylindrical portion 4 of the valve body 2. Rotation of the annular body 11 relative to the valve body 2 and thus relative to the plate member 25 establishes a greater or smaller overlap between the at least one first regulation opening 26 and the at least one second regulation opening 24.
Thus, greater or smaller overlap may be established between the at least one first regulation opening 26 and the at least one second regulation opening 24 by the rotation of the annular body 11 relative to the valve body 2. The size of the overlap can be used to determine the flow area of the adjustable opening through which the liquid that flows through the control valve one needs to pass. The differential pressure regulation function ensures that the pressure differential over the adjustable size opening is constant, thereby allowing very precise control of the flow.
Fig. 10 illustrates the areas in the valve where the first pressure P1 resides and the area in the valve where the second pressure P2 resides. Pressure P1 resides in the inlet area of the control valve. Pressure P2 is established through a pressure drop over the adjustable size opening and acts on the same side of the rolling diaphragm 16 as the helical spring 20. Pressure P3 is the pressure at the outlet 7 of the control valve 1 and is established by a pressure drop from the second pressure P2 over the exit openings 18. The threat for coupling the control valve 1 shown in Figs. 10 to 15 to an actuator is than external threat, whereas the threat for coupling the control valve 1 shown in Figs. 1 to 9 is an internal threat. Both types of threat and other coupling means can be used interchangeably for coupling actuator to the control valve
1.
Pressure P1 needs to be communicated to the side of the rolling diaphragm 16 furthest from the axial inlet opening 9. At least one pressure communication channel 28 is provided in the annular body 11 for communicating the first pressure P1 from a position on the axial extremity of the annular body 11 closest to the longitudinal end of the control valve 1 with the inlet opening 9 to a position on the other side of the rolling diaphragm 16. Hereto, at least one pressure communication channel 28 extends substantially axially through the annular body 11. In an embodiment, a pressure communication channel 28 extends axially between two axially extending exit openings 18. The at least one pressure communication channel 28 opens to the axial extremity of the annular body 11 closest to the inlet opening 9, i.e. to the chamber with the first pressure P1.
Thus, liquid can flow from the chamber with the first pressure P1 in the cylindrical portion of 4 and from there into the pressure communication channels 28, regardless of the relative rotational position between the plate member 25 and the annular body 11 and via the communication channel to the opposite side of the rolling diaphragm 16, without the need for any opening in the rolling diaphragm 16. Thus, the rolling diaphragm 16 can be made from a single piece of material without any through going hole in it.
A handle 5 for manual adjustment of the rotational position of the annular body 11 protrudes through a circumferentially extending slot in the valve body 2. The handle 5 engages an interconnecting cylindrical member 3 that is arranged to rotatably move relative to the valve body 2. The interconnecting cylindrical member 3 is sealed against an insert 37 by means of O-rings. The insert 37 is statically disposed in the valve body 2 and sealed against the valve body 2 by an O-ring. The insert 37 is provided with a central bore through which the interconnecting cylindrical member 3 passes with a sealing fit provided by O-rings. This allows the interconnecting cylindrical member 3 to move rotationally relative to the valve body 2 in a sealing manner. The interconnecting cylindrical member 3 is connected to a cover 12 of the annular body 11. The cover 12 is rigidly connected to the annular body 11. Rotational movement of the handle 5 is transmitted to the annular body 11 via the interconnecting cylindrical member 3 and the cover 12. The position of the handle 5 is secured against unintentional change of position by a locking member 34.
The central shaft 8 extends through a central bore in the interconnecting cylindric member 3. The central shaft 8 extends axially between the activator 6 and the cover 12 and thus transmits axial force from the activator to the annular body 11. This axial force, that can originate form an electric or other type actuator urges the annular body 11 axially in the direction of the axial inlet opening 9 against the action of the helical spring 32. When sufficient axial force is applied to the activator 6, the annular body 11 together with the cylindrical part 22 with its closing member 29 are pushed towards the axial inlet opening 9 until the closing member 9 engages the inlet opening, thereby closing the inlet opening sealingly. This closed position of the control valve 1 is illustrated in Fig 11. The open position of the control valve 1 where no force is applied to the activator 6 is shown in Fig. 10. The actuator can therefore be a simple on/off type linear actuator that either applies a force or does not, although a more sophisticated type of linear actuator that can be commanded to move to a desired position can also be used.
When the control valve 1 is open, the size of the adjustable size opening is adjusted by rotation of the annular body 11 relative to the valve body 2 and thus relative to the plate member 25 so that the overlap between the first regulation opening 26 and the second regulation opening 24 changes.
The pressure drop from the first (inlet) pressure P1 to the second (intermediate) pressure P2 is kept constant by the rolling diaphragm 16 that finds its position under the balance of the pressures and the spring force acting on the rolling diaphragm 16. The flow though the exit openings 18 is restricted to a degree depending on the position of the rolling diaphragm 16 and causes the pressure drop from the second (intermediate) pressure P2 to the third (outlet) pressure P3.
The control valve 1 is suitable for use in a manifold 40, such as for example a manifold for a floor heating system. Hereto, the control valve 1 is installed in the manifold using the outer thread on the valve body 2 that engages corresponding thread in the manifold 40. The manifold 40 is preferably provided with fittings 42 that engage the longitudinal end of the valve body 2 with the axial inlet opening 9. Thus, the supply of the first pressure P1 can take place through a manifold 42.
In the shown embodiments, the rotational position of the annular body 11 is adjusted manually using the handle 5. However, the rotational position of the annular body 11 may in not shown embodiments be adjusted by an actuator or the like, e.g. under control from an electronic control unit.
The various aspects and implementations has been described in conjunction with various embodiments herein. However, other variations to the disclosed embodiments can be understood and effected by those skilled in the art in practicing the claimed subject-matter, from a study of the drawings, the disclosure, and the appended claims. In the claims, the word comprising does not exclude other elements or steps, and the indefinite article a or an does not exclude a plurality. The mere fact that certain measures are recited in mutually different dependent claims does not indicate that a combination of these measured cannot be used to advantage. The reference signs used in the claims shall not be construed as limiting the scope.

Claims (12)

PATENTKRAV 1. Styreventil (1) til styring af væskestrøm i et varme- og/eller køleanlæg, hvilken styreventil (1) omfatter:Control valve (1) for controlling liquid flow in a heating and / or cooling system, which control valve (1) comprises: et aflangt, fortrinsvis rotationssymmetrisk, ventillegeme (2, 4) med modstående første og anden længdeender, hvor den første længdeende er forsynet med en indgangsåbning (9), et trykregulerende arrangement, der er udformet til at opretholde et i alt væsentligt konstant differenstryk mellem et første tryk (P1) i styreventilen (1) og et andet tryk (P2) i styreventilen (1), det trykregulerende arrangement omfatter et bevægeligt droslingselement (16), der tvinges af det første tryk (P1) til at øge strømningsmodstanden frembudt af det trykregulerende arrangement, og som tvinges af et elastisk element (20) og af det andet tryk (P2) til at reducere strømningsmodstanden frembudt af det trykregulerende arrangement, hvor det bevægelige droslingselement omfatter en rullemembran (16), der interagerer med en flerhed af udgangsåbninger (18), hvor rullemembranen (16) har en ringformet periferi, der er forbundet med et ringformet legeme (11), hvor flerheden af udgangsåbninger (18) er dannet radialt gennem det ringformede legeme (11), kendetegnet ved, at det ringformede legeme (11) er glidende placeret i en cylindrisk del (4) af ventillegemet (2) for at muliggøre aksial bevægelse og rotationsbevægelse af det ringformede legeme (11) i forhold til ventillegemet (2).an elongate, preferably rotationally symmetrical, valve body (2, 4) having opposite first and second longitudinal ends, the first longitudinal end being provided with an inlet opening (9), a pressure regulating arrangement designed to maintain a substantially constant differential pressure between a first pressure (P1) in the control valve (1) and a second pressure (P2) in the control valve (1), the pressure regulating arrangement comprises a movable throttling element (16) forced by the first pressure (P1) to increase the flow resistance offered by the pressure regulating arrangement, which is forced by an elastic member (20) and by the second pressure (P2) to reduce the flow resistance offered by the pressure regulating arrangement, the movable throttling element comprising a roller diaphragm (16) interacting with a plurality of outlet openings ( 18), wherein the roller diaphragm (16) has an annular periphery connected to an annular body (11), the plurality of exit openings (18) being formed radially. The annular body (11), characterized in that the annular body (11) is slidably located in a cylindrical part (4) of the valve body (2) to enable axial movement and rotational movement of the annular body (11) relative to valve body (2). 2. Styreventil (1) ifølge krav 1, hvor det ringformede legeme (11) passer tætnende ind i den cylindriske del (4).The control valve (1) according to claim 1, wherein the annular body (11) fits sealingly into the cylindrical part (4). 3. Styreventil (1) ifølge krav 1 eller 2, der omfatter et lukkeelement (29), der er indrettet til at bevæge sig aksialt sammen med det ringformede legeme (11), hvilket lukkeelement (29) er udformet til tætnende at lukke indgangsåbningen (9) i en første aksial del af det ringformede legeme (11) og til at muliggøre fluidpassage gennem indgangsåbningen (9) i en anden aksial position af det ringformede legeme (11).Control valve (1) according to claim 1 or 2, comprising a closing element (29) adapted to move axially with the annular body (11), which closing element (29) is designed to seal the inlet opening ( 9) in a first axial part of the annular body (11) and to enable fluid passage through the inlet opening (9) in a second axial position of the annular body (11). 4. Styreventil (1) ifølge krav 3, hvor lukkeelementet (29) omfatter en cylindrisk del (22), der strækker sig aksialt fra det ringformede legeme (11) mod indgangsåbningen (9).The control valve (1) according to claim 3, wherein the closing element (29) comprises a cylindrical part (22) extending axially from the annular body (11) towards the inlet opening (9). 5. Styreventil (1) ifølge et hvilket som helst af kravene 1 til 4, hvor det ringformede legeme (11) har to modstående aksiale ender, hvor den aksiale ende af det ringformede legeme (11) tættest på indgangsåbningen (9) omfatter et skiveformet element (15), der er forsynet med mindst én første reguleringsåbning (26).A control valve (1) according to any one of claims 1 to 4, wherein the annular body (11) has two opposite axial ends, the axial end of the annular body (11) closest to the inlet opening (9) comprising a disc-shaped element (15) provided with at least one first control opening (26). 6. Styreventil (1) ifølge krav 5, hvor det skiveformede element (15) danner en bund af det ringformede legeme (11).The control valve (1) according to claim 5, wherein the disc-shaped element (15) forms a bottom of the annular body (11). 7. Styreventil (1) ifølge krav 5 eller 6, der omfatter et pladeelement (25) med mindst én anden reguleringsåbning (24) til at interagere med den første reguleringsåbning (26), hvor én side af pladeelementet (25) er i kontakt med siden af det skiveformede element (25) tættest på indgangsåbningen (9), hvor pladeelementet (25) er indrettet til at bevæge sig aksialt sammen med det ringformede legeme (11), og hvor pladeelementet (25) rotationsmæssigt er ubevægeligt i forhold til ventillegemets (2) cylindriske del (4), hvorved der kan etableres en større eller mindre overlapning mellem den mindst ene første reguleringsåbning (26) og den mindst ene anden reguleringsåbning (24) ved rotation af det ringformede legeme (11) i forhold til ventillegemet (2).Control valve (1) according to claim 5 or 6, comprising a plate element (25) with at least one second control opening (24) for interacting with the first control opening (26), one side of the plate element (25) being in contact with the side of the disc-shaped element (25) closest to the inlet opening (9), where the plate element (25) is arranged to move axially together with the annular body (11), and where the plate element (25) is rotationally immovable relative to the valve body ( 2) cylindrical part (4), whereby a greater or lesser overlap can be established between the at least one first control opening (26) and the at least one second control opening (24) by rotating the annular body (11) relative to the valve body (2). ). 8. Styreventil (1) ifølge krav 6 eller 7, hvor den cylindriske del (22) er forbundet med pladeelementet (25).Control valve (1) according to claim 6 or 7, wherein the cylindrical part (22) is connected to the plate element (25). 9. Styreventil (1) ifølge et hvilket som helst af kravene 1 til 8, der omfatter et membranbæreelement (14) til at støtte og gå i indgreb med en central del af rullemembranen (16), og en spiralfjeder (20), hvilken spiralfjeder (20) indvirker på bæreelementet (14) for at tvinge rullemembranen (16) i en retning, der reducerer rullemembranens (16) droslingseffekt.A control valve (1) according to any one of claims 1 to 8, comprising a diaphragm support member (14) for supporting and engaging a central portion of the roller diaphragm (16), and a coil spring (20), said coil spring (20) acts on the support member (14) to force the roller diaphragm (16) in a direction which reduces the throttling effect of the roller diaphragm (16). 10. Styreventil (1) ifølge et hvilket som helst af kravene 1 tilControl valve (1) according to any one of claims 1 to 9, der omfatter en mekanisme forbundet med det ringformede legeme (11) til justering af det ringformede legemes (11) rotationsposition i forhold til ventillegemet (2), hvilken mekanisme er udformet til at justere rotationspositionen manuelt eller med en aktuator.9, comprising a mechanism connected to the annular body (11) for adjusting the rotational position of the annular body (11) relative to the valve body (2), which mechanism is designed to adjust the rotational position manually or with an actuator. 11. Styreventil (1) ifølge et hvilket som helst af kravene 1 tilControl valve (1) according to any one of claims 1 to 10, der omfatter en mekanisme forbundet med det ringformede legeme (11) til justering af det ringformede legemes (11) aksiale position i forhold til ventillegemet (2), hvilken mekanisme er udformet til at justere den aksiale position manuelt eller med en aktuator.10, comprising a mechanism connected to the annular body (11) for adjusting the axial position of the annular body (11) relative to the valve body (2), which mechanism is designed to adjust the axial position manually or with an actuator. 12. Styreventil (1) ifølge et hvilket som helst af kravene 1 tilControl valve (1) according to any one of claims 1 to 11, hvor det ringformede legeme (11) omfatter mindst én trykforbindelseskanal (28), der strækker sig i det ringformede legeme (11) for at forbinde det første tryk (P1) fra et første sted i styreventilen (1) på én aksial side af rullemembranen (16) med et andet sted i styreventilen (1) på den anden aksiale side af rullemembranen (16).11, wherein the annular body (11) comprises at least one pressure connection channel (28) extending in the annular body (11) to connect the first pressure (P1) from a first location in the control valve (1) on one axial side of the roller diaphragm (16) with another location in the control valve (1) on the other axial side of the roller diaphragm (16).
DKPA201870152A 2017-08-14 2018-03-12 Control valve for heating and/or cooling system DK179689B1 (en)

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DKPA201770612A DK179688B1 (en) 2017-08-14 2017-08-14 Control valve for heating and/or cooling system
DKPA201870152A DK179689B1 (en) 2017-08-14 2018-03-12 Control valve for heating and/or cooling system

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DK201870152A1 DK201870152A1 (en) 2019-03-20
DK179689B1 true DK179689B1 (en) 2019-03-26

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