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EP3456984B1 - Soupape de commutation d'un flux de fluide - Google Patents

Soupape de commutation d'un flux de fluide Download PDF

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Publication number
EP3456984B1
EP3456984B1 EP18194426.5A EP18194426A EP3456984B1 EP 3456984 B1 EP3456984 B1 EP 3456984B1 EP 18194426 A EP18194426 A EP 18194426A EP 3456984 B1 EP3456984 B1 EP 3456984B1
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EP
European Patent Office
Prior art keywords
valve
control
units
flow
flow direction
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.)
Active
Application number
EP18194426.5A
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German (de)
English (en)
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EP3456984A1 (fr
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.)
A&K Mueller GmbH and Co KG
Original Assignee
A&K Mueller GmbH and Co KG
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Filing date
Publication date
Application filed by A&K Mueller GmbH and Co KG filed Critical A&K Mueller GmbH and Co KG
Publication of EP3456984A1 publication Critical patent/EP3456984A1/fr
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Publication of EP3456984B1 publication Critical patent/EP3456984B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F15B11/0426—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling the number of pumps or parallel valves switched on
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F15B2211/40592—Assemblies of multiple valves with multiple valves in parallel flow paths
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/411—Flow control characterised by the positions of the valve element the positions being discrete

Definitions

  • the present invention relates to a valve for switching a fluid flow with a valve inlet and a valve outlet, through which the fluid flow can flow axially along a main flow direction.
  • Valves are used to switch fluid flows, which can be liquids and gases.
  • the fluid flow enters the valve via a valve inlet.
  • the valve In a closed switching position, the valve is impermeable and blocks the fluid flow. The fluid cannot escape from the valve again. In an open switching position, however, the fluid flow is released. The valve makes this possible Fluid flow exits the valve again through valve outlets. In this way, the fluid flow can be switched by changing the switching position of the valve, ie it can be released or blocked by the valve.
  • Valves that are used along a fluid line, such as a pipeline, have a valve inlet and a valve outlet through which they are connected to the fluid line.
  • the valve inlet and the valve outlet can be arranged relative to one another in such a way that the fluid flow flows through the valve axially along a main flow direction.
  • a valve according to the preamble of claim 1 is off US 4,019,533 A known.
  • the object of the present invention is therefore to provide a compact valve with which different quantities of fluid can be switched.
  • each valve unit can release or block a subset of the fluid flow. If all valve units assume an open switching position, the valve is fully opened and the fluid flow can be released as a whole. If all valve units assume a closed switching position, the valve is closed and the fluid flow can be blocked as a whole. If some valve units assume a closed switching position and the remaining valve units assume an open switching position, only subsets of the fluid flow are blocked while others are released.
  • the valve as a whole can assume an intermediate switching position between the closed and open switching positions. Depending on the number of valve units, there can be a different number of intermediate switching positions of the valve. With two valve units, for example, there can be four switching positions, two of which are intermediate switching positions.
  • the number of intermediate switching positions can also depend on the control of the valve units.
  • the individual valve units can be connected in parallel or individually. With parallel control, interconnected valve units can be operated simultaneously and thereby switch a subset of the fluid flow, which results from the individual subsets that can be switched by the interconnected valve units. If the valve units are controlled individually, each valve unit can be operated separately. The largest number of intermediate switching positions of the valve can be achieved through individual control. Individual or all of the above controls of the valve units can also be combined with one another.
  • the valve units can be arranged in such a way that a symmetrically constructed valve results, in particular a rotationally symmetrical valve.
  • a symmetrical valve can simplify valve installation.
  • the valve units can also be arranged in such a way that an asymmetrical valve results.
  • An asymmetrical valve can be used The installation space available for installing the valve can be better utilized.
  • valve inlet and the valve outlet are arranged coaxially to one another.
  • valve inlet and valve outlet Through a coaxial arrangement of the valve inlet and valve outlet, the valve can be easily integrated into a straight section of a fluid line without resulting in a lateral offset of the flow in front of and behind the valve.
  • valve units are arranged such that the flow direction of the valve units runs transversely to the main flow direction. In this way, the valve units can be arranged radially to the main flow direction. By arranging the valve units radially, the valve can be kept compact in a structurally advantageous manner transversely to the main flow direction.
  • valve chamber is arranged between the valve inlet and the valve outlet, in which the valve units are at least partially arranged.
  • a valve chamber can enable the valve units to be arranged between the valve inlet and the valve outlet in a simple manner in terms of manufacturing technology. By partially arranging the valve units in the valve chamber The valve units can also be accessible from outside the valve chamber. One or more of the valve units can be exchanged in a simple manner.
  • the valve chamber has a flow direction reversal compared to the main flow direction.
  • the flow direction reversal enables the valve units to be arranged along a flow direction that deviates from the main flow direction. A more efficient and compact design of the valve can be achieved in this way.
  • the valve units preferably each have a valve seat and a closing element which interacts with the valve seat for switching the subsets of the fluid flow.
  • the closing element that interacts with the valve seat can block or release the subset of the fluid flow that can be switched by the valve unit in a structurally simple manner.
  • the closing element for switching the partial quantity is actuated by a pilot valve. In this way, the subsets of the fluid flow can be switched using little energy.
  • a further embodiment of the invention provides that the valve seats of the valve units are fluidly connected to the valve outlet on the downstream side. The portions of the fluid flow released by the valve units can be directed to the valve outlet via the outflow side of the valve seat.
  • valve seats of the valve units are preferably each fluidly connected to the valve outlet via an angular outlet.
  • an angular outlet By means of an angular outlet, a flow connection between the valve seat and the valve outlet can be established in a simple manner in terms of production technology. Especially in one of the main flow directions If the flow direction of the valve units deviates, the subset of the fluid flow can be easily redirected along the main flow direction through an angular outlet.
  • valve units have different flow cross sections. Differently sized subsets of the fluid flow can be switched by the valve units due to different flow cross sections.
  • the intermediate switching positions of the valve can differ from each other due to different flow cross sections of the valve units.
  • the flow cross sections can be specified in particular by the diameter of the valve seats.
  • valve inlet and the valve outlet and preferably the valve seats are integrally formed on a common valve body.
  • a one-piece molding onto the common valve body can reduce the number of components and the production time in a constructively advantageous manner.
  • the valve body is designed in the manner of a tube, the tube ends of which are formed by the valve inlet and the valve outlet, the valve units each having an actuating device which is arranged on the tube jacket.
  • the valve body By designing the valve body in the manner of a tube, the tube ends of which are formed by the valve inlet and the valve outlet, the valve can be integrated in a simple and compact manner as a component in a fluid line, in particular in a pipe or a pipeline.
  • the actuating device can actuate the valve unit and thus change the switching positions of the valve unit.
  • the arrangement of the actuating device on the tubular jacket of the valve body can enable a compact design that is flat in the radial direction.
  • the actuating devices particularly preferably have coils that extend parallel to the valve body.
  • the valve units can be switched by energizing the coils.
  • energizing a coil can move the valve unit into an open switching position and de-energizing the coil can lead to the valve unit closing.
  • the energization of the coil transfers the valve unit into a closed switching position.
  • a one-time energization of the coil could cause bistable switching between the closed and open switching positions.
  • the coils can be parts of pilot control valves, which act as actuators of the valve units.
  • the valve units are designed as servo valves that can be actuated by their own medium. By designing them as servo valves that can be actuated by their own medium, the valve units can be switched with little energy expenditure.
  • a further embodiment of the invention provides that at least one valve unit is equipped with a quantity regulator.
  • the amount of the subset of the fluid stream flowing through the valve unit can be regulated in a simple manner using a volume regulator.
  • the quantity regulator for independent quantity control of a fluid flow comprises at least two mutually movable control elements delimiting a control gap, the gap width of the control gap being adjustable in a pressure-dependent manner via a relative movement of the control elements and the control elements being designed as dimensionally stable inflow bodies.
  • the quantity control with control elements designed as dimensionally stable inflow bodies is less susceptible to influences of the fluid and in particular changes in the temperature of the fluid.
  • Dimensionally stable inflow bodies are characterized by an inelastic, solid shape. They can be produced, for example, by an injection molding process, by plastic molding or by machining. The dimensionally stable inflow bodies therefore retain their shapes under the pressure of the fluid flow on the inflow side through the quantity regulator.
  • the gap width of the control gap can be adjusted by a relative movement, but not by a temperature-dependent deformation of the control elements.
  • the dimensionally stable inflow bodies advantageously consist of temperature-resistant material, such as hard plastic, metal, thermoset, ceramic or glass. Temperature changes in the fluid cannot affect dimensionally stable inflow bodies made of temperature-resistant material. Any influence on the quantity control caused by changing temperatures of the fluid can be easily counteracted.
  • dimensionally stable inflow bodies made of metal, ceramic or glass can be resistant to a chemically reactive fluid.
  • a flow regulator with control elements made of metal, ceramic or glass can be used to control chemically reactive fluids.
  • control elements are relatively movable in the direction of a flow direction.
  • Control elements that are relatively movable in the direction of flow can be moved in a particularly simple manner for independent quantity control by the pressure of the fluid flow on the inflow side through the quantity regulator become.
  • At least one first control element has a varying cross-section with a cross-sectional profile running along the direction of flow, in particular in the manner of a pyramid, a cone, a truncated pyramid, a truncated cone and/or a wedge.
  • the gap width of the control gap can be changed during the relative movement of the control elements.
  • the gap width can be predetermined by the cross-sectional shape along the flow direction.
  • the gap width can be changed on one side or on several sides of the first control element.
  • a cross-sectional course in the manner of a pyramid, a cone, a truncated pyramid or a truncated cone can change the gap width of the control gap on several sides of the first control element and in particular over the entire circumference.
  • a cross-sectional course in the manner of a wedge, in which at least one side of the cross-section runs essentially parallel to the direction of flow, can change the gap width of the control gap on one side or on several sides of the first control element.
  • the cross-sectional course can in particular be the course of the cross-section of the material of the first control element.
  • Complementary cross-sections, in which material recesses of the first control element run according to the types mentioned can also be cross-sectional courses.
  • several cross-sectional courses, in particular of the types described can be combined into one cross-sectional course.
  • the cross-sectional course has step-shaped, in particular different, cross-sectional jumps.
  • the gap width can be adjusted in a structurally simple manner to suit several pressure ranges. Different cross-sectional jumps can cause the relative changes in the Make the gap width different for adjacent pressure areas.
  • a further embodiment provides that the cross-sectional course is essentially continuous, in particular curved. Due to a substantially continuous cross-sectional progression, the gap width of the control gap can be adjusted substantially continuously during a relative movement of the control elements. Cross-sectional jumps, which lead to an abrupt change in the cross-section, are not present when the cross-section is essentially continuous.
  • the quantity control can particularly well compensate for the pressure dependence of the quantity of fluid flow through the quantity regulator by constantly adjusting the gap width.
  • a curved cross-sectional shape can enable the gap width to be changed differently in individual pressure areas. The curved cross-sectional shape can additionally or alternatively enable a continuous transition when adjusting the gap width of the control gap between different pressure ranges.
  • first control element is fixed and a second control element is movable.
  • a relative movement of the two control elements can take place in a structurally simple manner with a fixed first control element and a movable second control element.
  • Guided storage for the first control element can be omitted. The number of moving components can be reduced.
  • control elements can be moved towards one another by the pressure of the fluid flow, in particular against a restoring force.
  • the pressure of the fluid flow can move the control elements towards one another in a particularly simple manner.
  • the gap width can be reduced by the pressure of the fluid flow to regulate the amount of fluid flow passing through the flow regulator.
  • a restoring force directed against the pressure of the fluid flow can move the control elements away from one another when the pressure decreases.
  • a restoring element exerts a restoring force for moving the control elements into their starting positions on at least one control element, in particular in the case of control elements moving towards one another.
  • the restoring element can move the control elements into their starting positions, which they assume without pressure from the fluid on the inflow side, by means of the restoring force, in particular directed against the direction of flow.
  • the restoring force can be of different strength, in particular depending on the relative movement of the two control elements. As the relative movement of the control elements towards one another increases, the restoring force can increase and compensate for the pressure of the fluid.
  • the restoring element can be particularly advantageously designed as a spring.
  • a spring can store energy applied by the inflow-side pressure of the fluid for the relative movement of the control elements and, when the pressure of the fluid flow decreases, can retrieve this energy, at least in part, in order to move the control elements in the direction of their initial positions.
  • a control element is designed as a control diaphragm, in particular as an annular control diaphragm, with a through-hole.
  • the control gap can be limited in a structurally simple manner through the passage recess of a control diaphragm.
  • an annular control diaphragm can represent an advantageous embodiment in terms of production technology.
  • the control aperture can preferably be designed in the manner of a second control element. Nevertheless, the control aperture can also be designed in the manner of a first control element.
  • a peg-shaped control element enters the passage recess to adjust the gap width of the control gap a.
  • the peg-shaped control element can be longer along the fluid flow through the quantity regulator than it is wide across the fluid flow.
  • the base area of the peg-shaped control element can be polygonal, in particular rectangular or square, or round, in particular circular or oval.
  • the shape of the base surface of the peg-shaped control element can be adapted to the shape of the passage recess in the control panel.
  • the peg-shaped control element can preferably be designed in the manner of a first control element. Nevertheless, the peg-shaped control element can also be designed in the manner of a second control element.
  • control orifice is mounted floating along the direction of flow.
  • a floating control orifice can have play in the radial direction. The play can prevent mechanical tensioning of the control panel.
  • a further embodiment provides that one of the control elements includes a bypass.
  • a bypass can lead part of the fluid flow through the quantity regulator past the control gap. With a closed control gap with a gap width equal to zero, part of the fluid flow can still pass through the quantity regulator via the bypass.
  • control elements are arranged in a control housing and a control element is fixed relative to the control housing.
  • the quantity regulator can be easily installed as a unit.
  • a control element that is fixed relative to the control housing can be arranged in the control housing in a simple manner in terms of production technology. The number of moving parts can be reduced.
  • the fixed control element can be formed in one piece with the control housing be.
  • an inner wall of the control housing guides the movement of a control element. Guiding the movement of a control element can prevent the control element from being misunderstood. By guiding through the inner wall of the control housing, a guide element can be saved in a cost-saving manner.
  • valve 1 according to the invention will be discussed below, before quantity regulators 100 according to the invention are then described.
  • FIG 1 a schematic circuit diagram of a valve 1 is shown.
  • a fluid flow F enters the valve chamber 6 along a main flow direction H via a valve inlet 2.
  • the fluid flow F is divided in the valve chamber 6 and is directed to two valve units 4, 5 connected in parallel. Both valve units 4, 5 have two switching positions, one closed and one open.
  • the valve 1 can also have further valve units and/or a different arrangement of the valve units 4, 5.
  • Each valve unit 4, 5 does not switch the entire fluid flow F, but only a subset F1, F2 of the fluid flow F. Depending on the switching positions and the nominal widths of the valve units 4, 5, the flow results from the valve chamber 6 on the downstream side via a valve outlet 3 amount of fluid emerging.
  • both valve units 4, 5 When the valve 1 is open, in which both valve units 4, 5 release the subsets F1, F2 in their open switching positions, both subsets F1, F2 exit the valve outlet 3 together along the main flow direction H. If both valve units 4, 5 assume their closed switching positions, they block both subsets F1, F2. The valve 1 is closed and no fluid comes out of the valve outlet 3. In the remaining combinations of the switching positions of the valve units 4, 5, the valve 1 is partially open and assumes an intermediate switching position. Either the subset F1 or the subset F2 emerges from the valve outlet 3.
  • the schematic diagram of the valve 1 in Fig. 2 differs from that in Fig. 1 circuit shown by a quantity regulator in the valve units 4, 5. In the respective open switching position of the valve units 4, 5, this quantity regulator regulates the quantity of fluid flowing through the valve units 4, 5. The subsets F1, F2 are thereby limited.
  • the quantity regulator shown is a non-adjustable quantity regulator, which forms a predetermined narrow point of the flow cross section along the flow direction of the fluid through the valve unit 4, 5. Otherwise, this corresponds to Fig. 2
  • Valve 1 shown corresponds to valve 1 in terms of its components and their properties Fig. 1 .
  • the Fig. 3 shows another schematic circuit diagram of a valve 1, which has an adjustable quantity regulator 100 in the valve units 4, 5.
  • the adjustable flow regulator 100 makes it possible to adjust the narrow point along the flow direction of the fluid. This adjustability makes it possible to compensate for influences on the quantities of fluid flowing through the valve units 4, 5, such as changing pressures of the fluid flow F.
  • the adjustable quantity regulator 100 is preferably a quantity regulator 100 for independent quantity control of the fluid flow. The design of this quantity regulator 100 will be discussed separately below.
  • FIGS. 4 and 5 show schematic sections along the main flow direction H through a valve body 7 or a valve 1 with differently designed valve bodies 7.
  • the fluid flow F enters the valve 1 via the valve inlet 2 and can leave the valve again through the valve outlet 3.
  • the fluid flow F flows through the valve 1 axially along the main flow direction H.
  • the valve inlet 2 and the valve outlet 3 are arranged parallel to one another and lie coaxially on the main flow direction H.
  • the valve chamber 6 is located between the valve inlet 2 and the valve outlet 3.
  • the valve units 4, 5 are at least partially arranged in it.
  • the valve chamber 6 includes the valve seats 4.1, 5.1, the outlets 4.3, 5.3 and the quantity regulators 100 of the valve units 4, 5.
  • the valve chamber 6 is delimited transversely to the main flow direction by the valve body 7.
  • the fluid flow F flowing into the valve chamber 6 along the main flow direction H is changed in the valve chamber 6 by a flow direction reversal deflected in such a way that the flow runs transversely to the main flow direction H.
  • the flow direction reversal occurs essentially at right angles to the main flow direction H.
  • the fluid flow F flows against a part of the valve housing 7 that is oriented transversely to the main flow direction H and is deflected by it to the valve units 4, 5.
  • a flow direction through the valve units 4, 5 arranged in this way is achieved transversely to the main flow direction H.
  • the flow direction is essentially changed by 180°.
  • the flow direction on the outflow side of the valve units 4, 5 is opposite to the flow direction on the upflow side.
  • the flow directions through the valve units 4, 5 run opposite to one another.
  • the flow directions through the valve units 4, 5 are directed radially inwards.
  • the valve units 4, 5 include, in addition to the valve seats 4.1, 5.1, closing elements of 4.2, 5.2 that interact with them.
  • the closing elements 4.2, 5.2 are arranged outside the valve chamber 6 and close it in the radial direction, as in Fig. 5 shown. Likewise, the closing elements 4.2, 5.2 can be arranged in the valve chamber 6.
  • the closing element 4.2, 5.2 closes the valve seat 4.1, 5.1.
  • the closing element 4.2, 5.2 comprises a preferably elastic part, which rests on the valve seat 4.1, 5.1 in the closed switching position, and an inelastic part, which supports the closing element 4.2, 5.2.
  • the subset F1, F2 cannot flow through the valve seat 4.1, 5.1 in this closed switching position.
  • the valve unit 4, 5 When the valve unit 4, 5 is actuated, it lifts Closing element 4.2, 5.2 from the valve seat 4.1, 5.1.
  • the subset F1, F2 of the fluid flow F can flow through the valve 1 via the valve seat 4.1, 5.1 which is flow-connected to the valve outlet 3 on the downstream side.
  • the connection between the valve seat 4.1, 5.1 and the valve outlet 3 is established by an angular outlet 4.3, 5.3.
  • the angular outlet 4.3, 5.3 deflects the flow direction of the subset F1, F2 of the fluid flow F passing through the valve unit 4, 5 so that it emerges from the outlet 3 along the main flow direction H.
  • the outlets 4.3, 5.3 are designed so that they run parallel on the valve outlet side.
  • the subsets F1, F2 of the fluid stream F flowing through the valve units 4, 5 are brought together in parallel flow. Turbulence in the fluid flow F, which would arise when subsets F1, F2 flow toward one another, is thus avoided in a structurally simple manner.
  • the cross sections of the outlets 4.3 and 5.3 differ. The same pressure is achieved in both outlets 4.3, 5.3 with different subsets F1, F2.
  • valve units 4, 5 In the case of identical valve units 4, 5, the two subsets F1, F2 of the fluid flow F do not differ from one another.
  • the partially open switching positions of the valve units 4, 5 lead to identical controls of the fluid flow F.
  • the flow cross sections of the valve units 4, 5 differ from one another.
  • a different flow cross section, even with otherwise identical valve units 4, 5, is achieved by a different cross section of the valve seat 4.1, 5.1.
  • quantity regulators 100 arranged in the valve units 4, 5 can lead to different flow cross sections of the valve units 4, 5. Particularly in the case of independently regulating quantity regulators 100, quantity regulators 100 can have different control behavior be used. Such quantity regulators 100 will be discussed in more detail below.
  • valve unit 2 the valve outlet 3 and the valve seats 4.1, 5.1 are each integrally formed on a common valve body 7.
  • the quantity regulators 100 are also partially integrally formed on the valve body 7.
  • control elements 101 and control housing 104 are designed in one piece as parts of the valve body 7.
  • valve bodies 7 shown are designed in the manner of a tube, the ends of which are formed by the valve inlet 2 and the valve outlet 3.
  • Valve body 7 shown is designed as a T-shaped injection molded body asymmetrically along the main flow direction H.
  • the valve inlet 2 merges directly into the valve chamber 6, while the connection between the valve chamber 6 and the valve outlet 3 is formed by a comparatively long piece of pipe.
  • the valve body 7 Transverse to the main flow direction, the valve body 7 has flange-like connections.
  • the parts of the valve units 4, 5 that are not arranged in the valve chamber 6 can be connected to the valve body 7 via these connections.
  • valve 1 shown is essentially symmetrical along the main flow direction H.
  • a pipe section of essentially the same length extends between the valve inlet 2 and the valve chamber 6 and between the valve chamber 6 and the valve outlet 3.
  • the valve units 4, 5 are arranged on the valve body 7 by means of flange-like connections.
  • the closing elements 4.2, 5.2 are arranged between the valve body 7 and the housings of the valve units 4, 5, which are formed in one piece with the housings of the actuating devices 4.4, 5.4.
  • the locking elements 4.2, 5.2 also serve as a seal for these connection points to the outside of the chamber.
  • the closing elements 4.2, 5.2 and the housings of the valve units 4, 5 enclose in Fig. 5 Control rooms 4.6, 5.6 of the valve units 4, 5 outside the valve chamber 6.
  • Actuating devices 4.4, 5.4 of the valve units 4, 5 are arranged on the tube jacket of the valve body 7 in the exemplary embodiment Fig. 5 Actuating devices 4.4, 5.4 of the valve units 4, 5 are arranged.
  • the actuating devices 4.4, 5.4 have coils 4.5, 5.5 extending parallel to the valve body 7 and parallel to the main flow direction H. Due to the alignment of the coils 4.5, 5.5 parallel to the valve body 7, the actuating devices 4.4, 5.4 can rest flat on the valve body 7 compared to coils protruding from the valve body 7. This results in a small radial dimension of the valve 1.
  • the closing element 4.2, 5.2 of the valve unit 4, 5 is actuated by means of the coils 4.5, 5.5.
  • Valve units 4, 5 shown are designed in the manner of self-medium-operated servo valves with a pilot valve as an actuating device 4.4, 5.4. By utilizing the applied fluid pressure, they can be operated with little effort and energy saving.
  • a pilot control valve (not shown) of the respective valve unit 4, 5 opens or closes.
  • the pilot control valve When the pilot control valve is open, the fluid in the control chamber 4.6, 5.6 can be discharged via a relief channel 4.7, 5.7 in the direction of the valve outlet 3 become.
  • the relief channel 4.7, 5.7 extends as a closable connection between the pilot control valve and the valve outlet 3 through the valve body 7.
  • a quantity regulator 100 is shown, which is flowed against from the flow direction S by a fluid stream F and in particular a subset F1, F2 of the fluid stream F.
  • the quantity regulator 100 comprises 2 control elements 101, 102 which can be moved relative to one another and which limit a control gap 103. Through a relative movement of the control elements 101, 102, the gap width W of the control gap 103 extending between the control elements 101, 102 is adjusted depending on the pressure of the fluid flow F on the inflow side.
  • Both control elements 101, 102 are designed as dimensionally stable inflow bodies, the shape of which is not changed by the inflowing fluid.
  • the dimensionally stable inflow bodies are made of temperature-resistant materials, such as hard plastic, metal, thermoset, ceramic, thermoplastic or glass.
  • the control elements 101, 102 can be moved relative to one another along the flow direction S.
  • the first control element 101 has a varying cross section with a cross section 105 running along the flow direction S in the manner of a pyramid.
  • the cross-sectional course 105 includes an angle ⁇ transverse to the flow direction S. Preferably this angle ⁇ is in an angular range between 0 and 180°.
  • the distance between the two control elements can be changed transversely to the flow direction S between a maximum distance A max and a minimum distance A 0 .
  • the minimum distance A 0 preferably corresponds to a value of 0 mm.
  • the first control element 101 is fixed and its position is not changed by the fluid flow F flowing along the flow direction S. It is arranged on another element with a cuboid cross-section.
  • the second control element 102 is arranged to be movable relative to the first control element 101. Due to the pressure of a fluid flow F on the inflow side, its position changes along the flow direction S. The control elements 101, 102 can be moved towards one another due to the pressure of the fluid flow F.
  • a restoring element 107 extends between the two control elements 101, 102 and exerts a restoring force between them.
  • the restoring element 107 acts on the control element 102 with a restoring force, which is directed in the direction of the starting position of the control element 102. If the pressure of the fluid flow F moving the control element 102 drops, the restoring force of the restoring element 107 moves the control element 102 away from the control element 101.
  • the starting position of the control element 102 is in the Figures 6 and 7 shown. If the pressure of the fluid flow F is not sufficient to move the control element 102 against the restoring force of the restoring element 107, the control element 102 assumes or remains in its initial position.
  • the second control element 102 is designed as a control diaphragm with a through hole 102.1.
  • the peg-shaped first control element 101 enters this through hole 102.1 to adjust the gap width W of the control gap.
  • Both control elements 101, 102 are arranged coaxially to one another.
  • the relative movement of the control orifice 102 along the flow direction S leads to a deeper entry of the pin-shaped control element 101 into the through hole 102.1.
  • the gap width W is thereby reduced.
  • the control orifice 102 is mounted floating along the flow direction S. This storage means that the control panel 102 can be prevented from tilting. Since tilting would prevent movement of the control panel 102 and thus also the quantity control, the floating bearing improves the reliability of the quantity regulator 100.
  • a quantity regulator 100 is shown, the control element 101 of which includes a bypass 106.
  • the bypass 106 Through the bypass 106, part of the fluid flow F flows through the quantity regulator 100, even with a closed control gap 103.
  • the bypass 106 forms a direct, in particular straight connection between the inflow side and the outflow side of the quantity regulator 100.
  • the control elements 101, 102 are arranged in a control housing 104.
  • the control housing 104 can be a part of the valve body 107 or an independent component.
  • the control element 101 is fixed relative to the control housing 104. It can also be integrally formed on the control housing 104.
  • the inner wall 104.1 of the control housing 104 guides the movement of the control element 102.
  • a projection 104.2 of the control housing 104 acts as a one-sided stop of the control element 102 against the flow direction S.
  • the projection 104.2 determines the starting position of the control unit 102 shown in the figure.
  • the wall thickness of the control housing 104 is greater on the upstream side than on the downstream side.
  • a projection 101.1 of the control element 101 supports the restoring element 107 along the flow direction S.
  • the restoring element 107 is designed as a spiral spring, which is arranged between the projection 101.1 and the control element 102.
  • the control element 101 has a cross-sectional shape 105 in the manner of a cone.
  • the control aperture 102 is annular.
  • the injection molded flow regulator 100 in Fig. 9 Essentially corresponds to the 100 in. flow regulator Fig. 8 .
  • the control element 101 has a substantially pistol-spherical cross-sectional profile 105.
  • a quantity regulator 100 is shown with a further cross-sectional profile 105 of the control element 101.
  • the cross-sectional course 105 is designed in the manner of a step-shaped truncated cone. It has step-shaped cross-sectional jumps 105.1.
  • the cross-sectional jumps 105.1 differ each other. They are at different distances from each other along the flow direction S. They also differ in their jump height, the difference in cross-section in front of and behind the cross-section jump 105.1.
  • the Fig. 11 shows another cross-sectional profile 105.
  • the control element 101 has a comparatively complicated and essentially wedge-shaped cross-sectional profile 105.
  • the cross-sectional course 105 runs continuously, without cross-sectional jumps 105.1. Areas of the control element 101 with different cross-sections are connected to one another by the curved cross-sectional profile 105.
  • the gap width W of the control gap 103 can be adjusted essentially continuously during a relative movement of the control elements 101, 102.
  • the control elements 101 can also have other cross-sectional profiles 105. So are the cross-sectional courses 105 in Fig. 4
  • the quantity regulator 100 shown is wedge-shaped. The distance between the control elements 101, 102 and thus the gap width W of the control gap 103 only changes on one side of the control element 101 when the control elements 101, 102 move relative to each other.
  • control elements 101 of the quantity regulator 100 in Fig. 5 have cross-sectional shapes 105 in the manner of truncated cones. These are followed by additional, even more cylindrical cross-sectional profiles 105 in the lower region of the truncated cone-shaped cross-sectional profiles 105.
  • control element 102 can alternatively or additionally have a varying cross section with a cross section 105 running along the flow direction S. It would also be conceivable for the peg-shaped control element 101 to be movable while the control aperture 102 is fixed.
  • the valve 1 described above allows a compact design of a valve with which different quantities of fluid can be switched.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Multiple-Way Valves (AREA)

Claims (12)

  1. Soupape de commutation d'un courant de fluide (F) avec une entrée de soupape (2) et une sortie de soupape (3), qui sont formées d'un seul tenant sur un corps de soupape commun (7) et qui peuvent être traversées axialement par le courant de fluide (F) le long d'une direction d'écoulement principale (H) et sont agencées coaxialement l'une par rapport à l'autre, au moins deux unités de soupape (4, 5) pouvant être actionnées séparément, réalisées sous forme de servo-soupapes pouvant être actionnées par leur propre fluide, étant agencées entre l'entrée de soupape (2) et la sortie de soupape (3) pour la commutation de quantités partielles (F1, F2) du courant de fluide (F), le corps de soupape (7) étant réalisé à la manière d'un tube dont les extrémités de tube sont formées par l'entrée de soupape (2) et la sortie de soupape (3), les unités de soupape (4, 5) présentant chacune un dispositif d'actionnement (4.4, 5.4) qui est agencé sur l'enveloppe tubulaire du corps de soupape (7), caractérisée en ce que les dispositifs d'actionnement (4.4, 5.4) présentent des bobines (4.5, 5.5) qui s'étendent parallèlement à la direction d'écoulement principale (H).
  2. Soupape selon la revendication 1, caractérisée en ce que les unités de soupape (4, 5) sont agencées de telle sorte que la direction d'écoulement des unités de soupape (4, 5) s'étend transversalement à la direction d'écoulement principale (H).
  3. Soupape selon la revendication 2, caractérisée en ce que les directions d'écoulement de deux unités de soupape (4, 5) s'étendent de manière opposée.
  4. Soupape selon l'une quelconque des revendications précédentes, caractérisée en ce qu'une chambre de soupape (6) est agencée entre l'entrée de soupape (2) et la sortie de soupape (3), dans laquelle les unités de soupape (4, 5) sont agencées au moins partiellement.
  5. Soupape selon la revendication 4, caractérisée en ce que la chambre de soupape (6) présente une inversion de la direction d'écoulement par rapport à la direction d'écoulement principale (H).
  6. Soupape selon l'une quelconque des revendications précédentes, caractérisée en ce que les unités de soupape (4, 5) présentent chacune un siège de soupape (4.1, 5.1) et un élément de fermeture (4.2, 5.2) coopérant avec le siège de soupape (4.1, 5.1) pour la commutation des quantités partielles (F1, F2) du courant de fluide (F).
  7. Soupape selon la revendication 6, caractérisée en ce que les sièges de soupape (4.1, 5.1) des unités de soupape (4, 5) sont reliés fluidiquement en aval à la sortie de soupape (3).
  8. Soupape selon la revendication 7, caractérisée en ce que les sièges de soupape (4.1, 5.1) des unités de soupape (4, 5) sont reliés fluidiquement à la sortie de soupape (3) par l'intermédiaire d'une sortie à angle (4.3, 5.3).
  9. Soupape selon l'une quelconque des revendications précédentes, caractérisée en ce que les unités de soupape (4, 5) présentent des sections transversale d'écoulement différentes.
  10. Soupape selon l'une quelconque des revendications précédentes, caractérisée en ce que les sièges de soupape (4.1, 5.1) sont formés d'un seul tenant sur le corps de soupape commun (7).
  11. Soupape selon la revendication 1, caractérisée en ce que les bobines (4.5, 5.5) s'étendent parallèlement au corps de soupape (7).
  12. Soupape selon l'une quelconque des revendications précédentes, caractérisée en ce qu'au moins une unité de soupape (4, 5) est équipée d'un régulateur de débit (10).
EP18194426.5A 2017-09-19 2018-09-14 Soupape de commutation d'un flux de fluide Active EP3456984B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102017121704.5A DE102017121704A1 (de) 2017-09-19 2017-09-19 Ventil zum Schalten eines Fluidstroms

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EP3456984A1 EP3456984A1 (fr) 2019-03-20
EP3456984B1 true EP3456984B1 (fr) 2023-11-08

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EP (1) EP3456984B1 (fr)
DE (1) DE102017121704A1 (fr)
DK (1) DK3456984T3 (fr)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4019533A (en) * 1975-07-17 1977-04-26 Digital Dynamics, Inc. Digital valve assembly

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4244396A (en) * 1971-08-09 1981-01-13 Powell Industries, Inc. Digital fluid flow control system
US4170245A (en) * 1978-03-03 1979-10-09 Fmc Corporation Digital control valve

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4019533A (en) * 1975-07-17 1977-04-26 Digital Dynamics, Inc. Digital valve assembly

Also Published As

Publication number Publication date
EP3456984A1 (fr) 2019-03-20
DK3456984T3 (da) 2024-01-08
DE102017121704A1 (de) 2019-03-21

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