WO2018046555A1

WO2018046555A1 - Filling valve having a main valve

Info

Publication number: WO2018046555A1
Application number: PCT/EP2017/072379
Authority: WO
Inventors: Wolfgang Seidel
Original assignee: Tece Gmbh
Priority date: 2016-09-06
Filing date: 2017-09-06
Publication date: 2018-03-15
Also published as: CN110741194A; CN110741194B

Abstract

The invention relates to a filling valve (1) for filling a flush tank with a fluid, in particular with water, having a hydrostatically controllable main valve (2), which is provided with a flow channel (31). Said main valve has a valve main body having a flow channel (31) and has a flow body (41), which protrudes into the flow channel (31). In order to at least reduce the development of noise when the main valve (2) is closed, the flow body (41) is tapered in the flow direction (s). The flow body (41) has at least three radially extending planar wings (54), which are tapered in the flow direction (s) at least in an end region lying at the rear in the flow direction (s), in such a way that the distance between the lateral surfaces (47) of the wings decreases.

Description

Filling valve with main valve

The invention relates to a filling valve for filling a cistern with a fluid, in particular water, having a flow channel provided with a hydrostatically controllable main valve having a flow channel having a valve main body, a projecting into the flow channel flow body in or on the flow channel guided valve plate and comprising a valve disposed between the valve main body and the valve body in a closed position membrane. At least in the closed position, the flow body is arranged at least in sections in the flow channel. As a rule, such a filling valve has a pilot valve or pilot valve for its hydrostatic control. The pilot valve is usually closed, for example via a water level control or a water level measurement, whereby the hydrostatic pressure increases in front of the valve plate and the diaphragm of the main valve and this membrane and valve disc are brought into the closed position. At this moment of movement, the valve disc also has the opportunity to strike by a tumbling movement transversely to the flow direction against the housing wall of the valve main body. This in turn generates a short closing noise.

An object of the invention is therefore to provide a filling valve Provide main valve of the type mentioned, in which the noise when closing the main valve is at least reduced.

The stated object is achieved by the features of claim 1. Advantageous developments are described in the subclaims. The stated object is already achieved in that, in order to reduce turbulence and / or pressure fluctuations with respect to a flow direction of the fluid through the flow channel and / or in the amount of the flow body, the flow body is preferably formed continuously tapering in the flow direction.

With the preferably continuous taper of the flow body in the flow direction, a flow favorable shape of the flow body is achieved.

Generally, a fluid-flowed body at its leeward side, i. downstream, a flow separation, which can lead to turbulence in the form of vortex or vortex entrainment to form a turbulence zone. In the swirl zone, the flow may be opposite to the main flow direction. By the flow separation in general a noise development, here in particular a noise development under tumbling here of the flow body in the flow channel occur and thereby constantly changing touching / knocking out of the flow body at the valve main body.

With the tapering of the flow body, in the case of a laminar inflow of the fluid into the main valve, a gradual detachment of the fluid from the flow body can take place, at least largely avoiding vortex formation and thus substantially maintaining the laminar flow. With the taper of the flow body in the flow direction, a favorable shape for the flow of the flow body is achieved, whereby at least a pronounced reduction of the Verwirbelungszone and thus a reduction in noise can be achieved. The taper is suitably provided in a corresponding effective range of the flow body. Particularly preferred for this purpose is the taper steadily. The rejuvenation can for this purpose be continuous in the strict mathematical sense or approximately steadily. Depending on the embodiment, the flow body can taper in the flow direction over a specifically selected length or a specifically selected section along the flow direction. In particular, the flow body converges in the direction of flow while forming an edge. In particular, the flow body tapers in sections continuously in the flow direction. In particular, the flow body tapers continuously over its entire extension along the flow direction. In particular, the flow body tapers in the flow direction in its section, with which it is arranged in the closed position in the flow channel. In particular, the flow body tapers in a section with which it terminates with respect to the flow direction in the closed position in the flow channel, and thus in its flow direction rear portion in the flow direction continuously, in particular this rear portion at least a quarter, in particular at least one third , in particular occupies at least half of the portion of the flow body along the flow direction, with which the flow body is arranged in the closed position in the flow channel.

The flow body may have at least three, preferably four radially extending wings, on which the flow body is arranged radially outwardly in the flow channel, in particular guided on the inner wall of the flow channel. Thus, between the wings, the fluid may flow through the flow channel in the open position. The wings are preferably formed continuously tapering in the flow direction. The wings are preferably tapered over a portion of the flow body along the flow direction, as generally described above with respect to the taper of the flow body. The wings therefore do not necessarily have to taper over their entire extent along the flow direction in the flow direction.

The flow body can have a carrier, for example in the form of a flow-extending projection, from which the vanes can extend radially and / or axially. In particular, the flow body ends axially in the flow direction to form the wings. The wings are preferably circumferentially equidistantly spaced.

The wings can each be plate-like. The wings may each have a respect to the flow direction in the radial direction outwards, that is perpendicular to the flow direction, facing outer narrow side, also referred to as wing outer side, over which the flow body is guided out in the flow channel. In addition, they can each have two peripherally facing circumferential in relation to the narrow sides large side surfaces.

In order to avoid the formation of vortices, the wings can be designed to taper continuously in the flow direction at least in a rear end region in the flow direction. In particular, the wings may each be formed in a wedge-like manner in the flow direction to form an end edge. The wings may have a rear narrow side pointing in the axial direction, that is to say in the flow direction, on which the side surfaces are preferably designed to converge in a wedge-like manner in each case in the flow direction. This can be done, for example, in extension of a conventional flow body on the wings. The each located at the free end of the wing rear narrow side can perpendicular to the flow direction, but also beveled so that it forms an angle equal to or less than 90 ° with this. The wedge-like taper may be symmetrical with respect to a central mirror symmetry plane parallel to the larger side surfaces.

An end wedge angle may be less than or equal to 60 °, preferably less than / equal to 30 or less than / equal to 20 °. Preferably, the transitions between the larger side surface and the wedge-like taper are edgeless.

In a further development of the filling valve can be provided that at least the surfaces of the flow body and / or the inner wall of the flow channel, on which or over which the fluid flows in the open position of the main valve, at least partially with shallow trough-like depressions and / or with a fine Surface structure are formed coated. Preferably, at least the surfaces of the flow body facing the inner wall of the flow channel are formed with shallow trough-like depressions and / or coated with a surface structure.

In particular, the vanes of the flow body may each be coated with shallow trough-like depressions at least on their circumferentially facing circumferential side surfaces and / or may have the fine surface structure.

The surface structure may preferably have grooves, of which in particular some, in particular the majority, in particular all, run parallel to one another or at least approximately parallel. In the present case, roughly parallel means that they form an angle to one another of less than 30 °, preferably less than 20 °, preferably less than 10 °. In particular, at least some of the grooves, in particular at least one group, may be arranged to extend in the direction of flow in parallel or at least approximately parallel grooves. In addition or instead, at least some of the grooves, in particular at least one group, may be arranged running transversely to the direction of flow at mutually parallel or at least approximately parallel grooves. In particular, the majority of the grooves run parallel and / or at least approximately parallel and / or transversely and / or at least approximately transversely to the flow direction. In particular, the grooves can all extend transversely to or in the direction of flow. The surface structure may also be isotropic, that is to say that it is the same and non-directional with respect to the surface. In particular, it is proposed that the grooves run on the circumferential side surfaces in or approximately in the flow direction.

When the grooves are in the flow direction, these resistances reduce the flow of fluid. This can be justified by the fact that the fluid is guided in the direction of flow grooves and that a transverse movement perpendicular to the flow direction, as occurs for example in a vortex formation impeded and thus advantageously a low-noise laminar flow are favored. Furthermore, the grooves may be formed like a nozzle. As a result, the fluid can be accelerated.

These two effects described above can be dependent on the speed and the viscosity of the respective fluid. Therefore, the groove geometry can be adapted to the expected speed and the viscosity of the fluid. Furthermore, the grooves can act like a nozzle, in that the fluid can be accelerated. The surface structure may also have instead of the grooves or in addition to the same in the flow direction extending ribs, in particular so-called riblets. These riblets may be fine ribs, preferably ending on both sides in a sharp rib tip. The riblets may preferably extend in directions as explained with respect to the grooves.

In particular, by means of the surface structure, depending on their predominant orientation or anisotropy, the local flow velocity can be slowed down or accelerated, and in particular the transverse movement to the flow direction can be at least reduced.

Due to the design, the radially outwardly pointing narrow sides can be completely surrounded by the fluid. According to the energy equation of Bernoulli is the

Flow rate higher, the lower the respective partial pressure. If, in particular at the circumferentially equally spaced wings of the case, two opposite wing outer edges are flowed around at different speeds of the fluid, different partial pressures arise at the wing outer edges. This in turn can cause a movement of the valve disc transversely to the flow direction against the housing wall of the flow channel of the valve main body, whereby at this point the fluid flow is at least severely restricted. Thus, the pressure conditions are reversed, which generates a movement in the opposite direction. Thus, the valve disk can be placed in a tumbling vibration with stops against the housing wall, whereby a closing noise is generated. This effect is greater, the higher the flow velocity of the fluid. It therefore occurs in particular in the last phase of closing of the main valve, in which the flow velocity due to the reduced flow cross section particularly strong rises.

In order to reduce the closing noise, it is proposed that the grooves on the outer side surfaces extend at least approximately transversely to the flow direction.

At least approximately transversely here means at an angle of at least 45 °, preferably at least 60 °, preferably at least 80 °.

This has the advantage that the fluid flowing over the outer side surfaces is decelerated across the grooves to a certain extent. That is, the local flow velocity is reduced, producing a slightly higher partial pressure. These dynamic processes are subject to a particular inertia, e.g., depending on the viscosity of the fluid. this partial increase in pressure has a dampening effect on the overall system, which delays the wobbling motion and thus the noise can be reduced.

In a further embodiment of the filling valve, the surfaces may have or be coated with a multiplicity of shallow trough-like depressions.

These depressions may also be generally referred to as dents, dimples or dimples. You can usually have a kugelkalottenartigen interior. Such shallow trough-like depressions may in particular be characterized in that they macroscopically have a smooth shape course without any structural measures or discontinuities or discontinuities in the shape course, such as heels, points or elevations.

These trough-like depressions may preferably be slightly spaced apart from each other or in particular adjacent to each other. These dimples or depressions can be arranged adjacent to one another, for example as on the surface of golf balls. In general, such a surface is also referred to as a dulled surface. With the fluid flowing over the dimples, which is an extension of the fluid space, a negative pressure can be exerted on the fluid, making the fluid closer to the surface and making the fluid flow more laminar and hence quieter. Thus, a volume of a swirling zone of the fluid flow in the flow direction during the demolition of the flow from the flow body can be at least reduced.

The present invention will be described below with reference to several embodiments shown in a drawing of the

Guide explained in more detail, but without limiting the invention thereto. In the drawing show:

FIG. 1 is a longitudinal sectional view of a filling valve with

Main valve,

FIG. FIG. 2 shows an enlarged detail II according to FIG. 1 with the main valve having a valve disk, FIG.

FIG. 3 is a perspective view of the individual

Valve discs with wings in the direction of flow,

FIG. 4a is a side view on a narrow side of a

Wing according to the prior art,

FIG. 4b is a side view on a narrow side of one of the wings shown in Figure 3,

FIG. FIG. 5 shows a detail enlargement V according to FIG. 3 and FIG

FIGURES 6a and 6b respectively an enlarged detail Via or Vlb according to Figure 3.

1 shows a longitudinal sectional view of a filling valve 1 for filling a rinse water, not shown here with fluid, not shown here, in particular with water, shown. The filling valve 1 has a hydrostatically controllable main valve 2, which, in particular Figure 2 removable, with a flow channel 31 having a valve main body 3, a projecting into the flow passage 31 flow body 41 on the flow channel 31 guided valve disk 4 and an intermediate

Valve main body 3 and valve plate 4 is provided in a closing position not shown here sealingly effective membrane 5. The main valve 2 is shown in Figures 1 and 2 in an open position, in which the flow channel 31 is released by the passage of fluid. In a closed position, the membrane 5 is sealingly against the

Opening edge 32 of the flow direction s front opening 33 of the flow channel 31 at. The flow body 41 extends in the flow direction s of the valve disk 4 in the flow channel 31, in which it is arranged axially displaceably guided with a clear radial play. This play is necessary so that a slight axial displaceability of the valve disk 4 is ensured via the flow body 41 to the flow channel 31 in the flowing fluid.

The flow body 41 has an annular groove 43, in which the membrane 5 engages, so that this, following an axial movement of the valve disk 4, correspondingly axially stretched or compressed. As in particular Figure 3, a

perspective individual representation of the valve disk 4, removable, extend under the immediate axial boundary of the annular groove 43 axially from the same four

plate-like formed in the axial and radial direction extending wings 45 which are circumferentially equally spaced and centrally connected to each other.

These wings 45 are in the installation position of the valve disk 4 with radial clearance on the inside of the flow channel 31 at

(Figure 3). Thus, the fluid between the wings 45 flow through the flow channel 31 as long as the front opening 33 is not closed by conditioning the membrane 5 at the front opening edge 32.

The plate-like wings 45 each have a respect to the flow direction s in the radial direction r to the outside, that is perpendicular to the flow direction s, facing outer narrow side 46, which also as

Wing outside is called, on, at the

Flow body 4 is guided in the flow channel 3.

In addition, the wings 45 each have two circumferentially u-facing circumferential and in relation to the narrow sides 46 large side surfaces 47.

Figure 4a shows a side view of the outer narrow side 46 ^Λ one of the wings 45 ^λ one here not further

illustrated valve head of a conventional main valve, wherein the associated reference numerals for identifying the invention are marked with a raised apostrophe. Can be clearly seen that the vane rear blunt ends in the flow direction 45 ^λ s ¹ *, that is, its rear in the flow direction Ξ narrow side 48 is ^Λ

unrestrained formed and arranged at right angles to its other sides 46 48 ^Λ . As a result of these geometries, a flow separation of the fluid takes place, producing vortices W shown purely schematically in FIG. 4a in a turbulence zone Z. This is not the case here

shown valve plate vibrated, which, as described above, especially in the last phase of closing the main valve generates a short closing noise. In Figure 4b is a side view of the outer

Narrow side 46 of one of the wings 45 of the filling valve 1 according to the invention shown, in which case the wing 45 in

Flow direction is formed end streamlined, whereby the above-described noise largely can be avoided. For this purpose, the rear narrow side 48 is formed extended to a tapered edge 44. Here, the transition from the larger side surfaces 47 to the tapered edge 44 toward no edges or other discontinuities. The flow body 4, in the present case its wings 45, thereby taper continuously in the flow direction in the rear portion of the flow body 4 in the flow direction. The transition takes place in a flow favorable steady, here smoothed profile profile. Further measures to eliminate noise when operating the main valve 2 are based on the

Extensions enlargements in Figures 5 and 6 explained, the representations in the detail enlargements are purely schematic. In addition, the illustrated

Although proportions are realistic, but should not

Limiting the scope of protection.

Although at least the surfaces of the flow body and the flow channel, on which or over which the fluid flows in the open position of the main valve, at least

may be formed partially covered with shallow trough - like depressions and / or with a fine surface structure, this is limited to two essential locations in the embodiments of the filling valve shown in the figures:. On the one hand, it is provided that the outer narrow sides 46 of the wings 45 of the flow body 41 are each provided with a directed surface structure in the form of narrow parallel grooves 491 extending transversely to the flow direction s.

By means of the grooves, as explained above, the local flow velocity of the fluid can be reduced and thus a slightly higher partial pressure can be generated at this point. Since this partial increase in pressure depends on the level of local velocity, the narrowing of the Flow cross-section increases, this affects one

Oscillation of the flow body 41 across the

Direction of flow, with which the flow cross-section is narrowed with radial abutment of the flow body 41 accordingly. Thus, this partial pressure increase dampens the pendulum movement of the flow body 41 in the flow channel 31, whereby the noise is reduced.

On the other hand, it is provided that the vanes 45 of the flow body 41 are each formed on their circumferentially facing circumferential side surfaces 47 having a surface structure with grooves 491 running in the direction of flow s (FIG. 6a).

As described in more detail above, by means of the grooves 491, the flow of the fluid can be guided more strongly and the risk of a transverse flow transversely to the flow direction and thus a noise-generating vortex formation can be reduced.

Furthermore, it is provided here that the circumferential

Side surfaces 47 in addition to the grooves 591 with shallow trough-like recesses 492, so-called dimples,

are coated, wherein the recesses 492 are shown separately in Figure 6b.

As also described in more detail above, depressions 492 may be dependent upon

Flow rate and viscosity of the over

Wells 492 flowing fluid, the swirling zone Z in the flow direction s behind the flow body 41 and thus the noise are at least reduced. It is provided that the opening edges of the

Recesses 492 are rounded. To its hydrostatic control of the main valve 2 is a commonly referred to as a pilot valve conventional pilot valve 6 upstream of the passage opening 61 via a with a float 62 connected to the water level detection lever 63 is closed, whereby the hydrostatic pressure in a front of the valve plate 4 arranged and increased by the same limited antechamber 34, which in turn the valve plate 4 is pressed with the diaphragm 5 sealingly against the opening 33 of the flow channel 31 ,

Filling valve with main valve

LIST OF REFERENCE NUMBERS

filling valve

main valve

Valve main body

flow channel

opening edge

opening

antechamber

valve disc

flow body

head Start

ring groove

edge

, 45 ^Λ wings

, 46 ^Λ outer narrow side

, 47 side surface

, 48 'rear narrow side

1 groove

2 deepening

membrane

pilot valve

Through opening

swimmer

lever r radial direction s flow direction u circumferential direction W vortex

Z swirl zone

Claims

Filling valve with main valve claims

1. filling valve (1) for filling a cistern with a fluid, in particular with water, having a with a flow channel (31) provided hydrostatically controllable main valve (2) having a one

Flow channel (31) having valve main body, one via a in the flow channel (31)

protruding flow body (41) in or on the flow channel (31) guided valve disc (4) and between the valve main body and valve body (3) in a closed position sealingly arranged membrane (5) wherein to reduce turbulence and pressure fluctuations with respect to a flow direction (s) of the fluid through the flow channel (31) to and / or in the amount of the flow body (41) this in

Flow direction (s) is tapered, as you rchge ke nnzeic hn et that the flow body (41) has at least three radially extending plate-like wings (45), each at the free end a rear narrow side (48), one in radial Direction lateral narrow side (46) and two circumferentially facing, in relation to the narrow sides (46, 48) large side surfaces (47) have, and the flow body (41) is guided on the wings radially outward in the flow channel (31), wherein the wings (45) at least in one in

Flow direction rear end in

Direction of flow (s) are formed tapered such that the distance between the side surfaces (47) is reduced.

2. filling valve (1) according to claim 1, characterized in that the rear narrow side (48) is wedge-shaped.

3. filling valve (1) according to claim 2, d a du r ch

The transition between the larger side surface and the wedge-like taper is edgeless.

4. Filling valve (1) according to one of the preceding claims, d a c h e c e s n e c e s, d a s s

at least some, especially all of the

Inner wall of the flow channel (41) facing

Surface portions of the flow body (4) are formed with shallow trough-like depressions (492) and / or coated with a surface structure.

5. filling valve (1) according to claim 4, d a du r c h

There is no such thing as the

Surface structure parallel or at least approximately parallel grooves (491) and / or riblets, of which in particular at least some in

Flow direction (s) run and / or at least some transverse to the flow direction (s).

6. filling valve (1) according to one of claims 4 to 5,

as you can see from the fact that the shallow trough-like depressions (492) adjoin one another or at a distance smaller than one average diameter of the recesses (492)

are arranged spaced from each other.

7. filling valve (1) according to one of claims 1 to 6,

as you can see, the wings (45) are plate - shaped, each with in

Circumferentially (u) facing larger side surfaces (47) and with a radially outwardly facing, the inner wall of the flow channel (41) facing outer narrow side (46) are formed, which connects the larger side surfaces (47) with each other.

8. filling valve (l) according to claim 7 and according to one of

Claims 4 to 6, d a du r ch

The wings (45) of the flow body (41) are each coated with the trough-like depressions (492) at least at their side surfaces (47) pointing in the circumferential direction (u) and / or have the surface structure.

9. filling valve (1) according to claim 8, since you r c h

The flow body (41) on the outer narrow sides (46) is arranged so as to be axially displaceable radially outward under play on the inner wall of the flow channel (31).

10. filling valve (1) according to any one of claims 8 or 9,

Since this is because the surface structure extends beyond the outer narrow sides (46) of the vanes (45).