WO2007098630A1

WO2007098630A1 - Valve for throughflow regulation, and method for eliminating vibrations

Info

Publication number: WO2007098630A1
Application number: PCT/CH2007/000104
Authority: WO
Inventors: Urs Keller; Giuseppe Pulli; Marc Thuillard
Original assignee: Belimo Holding Ag
Priority date: 2006-03-01
Filing date: 2007-03-01
Publication date: 2007-09-07

Abstract

A valve (66) for liquid and/or gaseous, flowing media (38), having a valve housing (44), has a valve chamber which is provided with at least in each case one inlet (43) and outlet (45). A throttle body (10) which is moveable and positionable in said valve chamber serves to regulate the throughflow cross section (78). The throttle body (10), as it moves in the valve chamber, alternatively forms at least two different characteristic curves. The throttle body (10) has at least two separate setting regions (I, II, III), which can be selected by means of at least one drive motor, with different throughflow openings (18, 20, 22, 32, 34, 36, 47, 49). According to one variant, the throttle body (10) has a throughflow opening (16, 18, 74, 76) with at least two setting regions (I, II, III) which can be selected by means of a drive motor. Vibrations (S) in a regulating loop are eliminated by means of the valve (66) by virtue of the throttle body (10) being autonomously guided, in order to select the operating point, into another setting region (I, II, III) by means of the process-controlled drive motor, and the appropriate characteristic curve (K) is set in a motor-driven fashion.

Description

Valve for flow regulation and method for vibration elimination

Technical area

The invention relates to a valve for liquid and / or gaseous, flowing media, with a valve housing, which forms a valve chamber provided with at least one inlet and one outlet, and a movable therein and positionable throttle body for controlling the hydraulic cross section, wherein at least one flow path is formed. Furthermore, the invention relates to a method for eliminating vibrations in a control loop with this valve. State of the art

In industry and for the infrastructure of residential areas, media are transported in pipelines, which are exposed to extremely changing pressures, flow rates and temperatures. Regulators, such as gate valves, valves or valves, are used to control the flow rates in the piping to ensure optimum operating conditions and environmental safety. Generic valves are used in particular in the field heating-ventilation-climate, short HVAC.

In the regulation of the flow rate, the installation of a suitable valve plays an essential role. If the flow opening of the valve is too small, can be extremely high

Flow requirement can not be met. If the flow opening of the valve is too large, the flow rate can not be regulated precisely enough and / or control oscillations occur if the flow rate is low. All these effects are undesirable.

For example, in district heating the energy demand in winter is much higher than in summer. The control quality can be improved with the arrangement of different sized valves for summer and winter.

Fig. 1 shows a progressively increasing characteristic K of a known rotary valve. Each valve has characteristic curves K, with the abscissa representing the setting angle or the linear displacement, and the ordinate the percentage of the maximum flow rate. Within an angle α of 90 °, the flow is increased from 0 to 100% of the maximum flow through the valve. In practice, one works with operating points on the present characteristic curve K according to FIG. 1, in particular in the lower region. If the flow rate is low, it may be necessary to switch to a parallel-connected valve with a lower maximum flow rate.

In US 4,391,265 A (Chen), a three-way gas valve having an inlet and two outlets is described. To adjust the gas flow is integrated in the housing of the valve cylinder or a throttle body, which has several radial punctures has used. A servomotor rotates the throttle body so that the inlet and a first outlet of the valve are connected by one of the punctures in the cylinder. Due to the different diameter of the punctures different discrete flow cross sections can be adjusted. However, such valves are only very bad for the dynamic control of flow rates, since no continuous control ranges are available, which allow a continuous change in the flow rates. This results in unwanted control vibrations, which in particular make it difficult to precisely regulate small flow rates.

DE 29 47 229 A1 (Hansa Metallwerke AG) discloses a continuously adjustable control disk valve, in particular for the sanitary sector. In this case, a fixed mounted fixed disk and a rotatable control disk lying on it and mounted in a valve body with two outlets and two inlets. The fixed and the control disc both have a plurality of superimposed, differently shaped openings, which are partially connected to each other. With a rotation of the control disc, so different flow openings, which are connected in series with each other in the valve. This defines a single adjustment range, which allows the mixing of cold and hot water. However, low flow rates can not be set or regulated precisely with this type of valve.

US 5,983,937 A (Makihara et al.) Proposes a three-way valve with two inlets and one outlet for the controlled mixing of cold and hot water streams. In the valve housing while a rotatable hollow cylinder is mounted with different and separate flow openings on the lateral surface. To control the flow cross sections of the two inlets, the various flow openings of the hollow cylinder can be aligned with a motor relative to the inlets. Due to an increasing in the direction of rotation flow opening the flow area can be controlled continuously in a single control range. The other flow openings are either completely open or completely closed and are intermittently opened and closed for fine adjustment. However, a continuous control of the flow rate through actual control ranges is not possible. Such valves are therefore only of limited suitability, in particular for low flow rates to regulate precisely. The fine adjustment through digital "Aύf-Zu" cycles leads to a discontinuous flow of fluid flows through the valve, which in turn leads to control oscillations.

If a valve of known design does not have the optimum control range, then an imprecise setting or switching to another valve with a different characteristic K must be accepted.

Presentation of the invention

The present invention is therefore an object of the invention to provide a valve of the type mentioned and a method for its operation, which eliminate the disadvantages mentioned.

With regard to the valve, the object is achieved according to the invention in that, when moving in the valve chamber, the throttle body alternatively forms at least two different characteristic curves per flow path.

With the invention, a valve is provided which can be used for a wide variety of applications or for a wide variety of control circuits. By at least two different characteristics are integrated in the valve and can be switched between them, the more advantageous characteristic can be selected in the context of the specific application. The characteristic curve is preferably selected automatically (by an intelligent controller). By switching between the two characteristics during operation, e.g. a control oscillation eliminated or at least mitigated. The unwanted vibrations can z. B. be suppressed by the method which is known from WO 2006 / 105677A2 (Belimo). It is also possible to actuate the valve with a cost-effective drive, because the fine control in various flow areas is substantially facilitated by the proper or adapted characteristic curve.

The characteristic curve is determined by the valve design (design of the movable throttle body and interaction with the static flow openings of the housing). defined functional dependence of the flow cross-section or hydraulic cross-section of the valve of the position (eg., Angular graduation, position) of the throttle body understood. A valve whose cross section is either open or closed, that is, the flow "digital" on and off, forms no characteristic in the spirit of the invention. No gain (see below) can be assigned to such a valve. Differences in the characteristic arise when z. B. the maximum flow cross sections are different sizes or if z. B. the course or gradient of the characteristics is not identical. It is readily within the scope of the invention (but less preferred), when the curves are equal in areas.

For the user, the valve according to the invention is a module which he uses as part of his control circuit. So z. For example, the temperature is measured at a location of the HVAC system and the system control circuit determines a system control signal V _HVAC (eg as an analog voltage value, as a pulse sequence, as a digital value) which serves as input for the valve according to the invention , Due to this system control signal, the position x of the throttle body is adjusted. It is in the inventive valve (as mentioned above) possible, the appropriate characteristic K; so that the gain G is optimal:

OX

Where F (K |, x) is the hydraulic cross section or effective flow and x is the position (eg the angular position) of the throttle body. The position x can be varied per characteristic within a lower and an upper limit x _u or X ₀ , whereby the areas belonging to different characteristic lines completely, partially or not overlap depending on the construction of the valve. It is understood that G ≠ O must be in order for a regulation is possible.

Because the at least two characteristic curves per flow path act alternatively, two (or more) alternative gains G (i = 1, x) and G (i = 2, x) can be produced in a desired control range for a specific system control _value V _HLK and a selected cross-sectional value ) etc. exist. In that regard, there is a clear difference to the known mixing valves, in which different characteristics can be applicable to the hot water path and the cold water path, but these always act simultaneously on the parallel water paths, so that for a given system control signal (mixing ratio) effectively only one gain is possible.

A flow path in the sense of the invention is a path that the medium (when used as intended) in the valve can take from the inlet to the outlet if the path is not blocked due to the position of the throttle body. For example, in the case of a mixing valve, there are two flow paths, one for the warm medium and one for the cold medium, with the flow paths falling together on the output side of the valve.

With the invention, continuous control (as opposed to on / off control) is enabled within different control ranges. In other words, the valve has control ranges (I, II, III) with different flow openings. The position x of the throttle body is selected by means of at least one drive motor connected to the valve.

In contrast to the prior art, this allows the flow rate through the valve in all control ranges continuously adjusted and controlled continuously from 0 - 100%. Precise control is also achieved in low flow control ranges, without the need for the valve to be limited to small flow rates. It suffices a single usable for all control ranges drive motor. Compared with valves according to the known state of the art, this leads in particular to a significant reduction of control oscillations, which so far can only be suppressed by using several valves connected in parallel with different control ranges. The valves according to the invention are therefore more cost-effective to produce, since expensive precision components, additional valves connected in parallel and complex controls can be dispensed with.

The throttle body of the valve according to the invention has at least two (eg separate) control ranges, the control range being different for each control range. A setting range in the sense of the invention allows the continuous adjustment of the flow rate (controlled variable) between zero and a range-specific maximum value. value (u ⁰ A) which is less than or equal to the maximum possible flow rate (100%) through the valve. In other words, the valve according to the invention has two or more control ranges of the throttle body, which operate optimally for different flow rates. At low flow rates, the throttle body can be positioned so that the smaller flow port is in use. If the flow rates increase, the drive motor autonomously moves the throttle body into a different setting range, which is created for larger flow rates. Within this and the other control ranges, the fine adjustment is preferably carried out by means of the same drive motor, but it can also be used two drive motors. This results in different characteristics for the different control ranges with the same movement of the throttle body. This has the advantage that with a conventional valve drive an extremely precise regulation of the flow rate is achieved without several different valves must be installed in parallel. It is essential that, unlike a conventional valve, an unchangeable throttle body be moved by a motor over a 0 to 100% range. The preferred throttle body according to the invention with at least two selectable separate and substantially equal control ranges with different flow openings allows the position of the throttle body, ie the flow cross-section, to be optimally adapted to the flow rate.

In practice, the valve according to the invention can be realized in various embodiments, for example by

a combination of a fixed and a freely rotatable, motor-driven disc, which sealing, even full-surface sealing, each other. The solid disc may be part of the housing. The one disc has at least one passage opening, the other disc has at least two different sizes

Through openings, which are preferably designed to be the same length in a direction of movement. The apertures of the two discs must overlap appropriately.

- A combination of a fixed or integrated in the housing plate and a longitudinally and / or transversely displaceable sealingly resting, motor-driven plate. The one plate has at least one flow opening, the other plate at least two different sized flow openings.

- One in a valve housing in the longitudinal direction displaceable and freely rotatable cylindrical throttle body with different sized passage openings.

- A freely rotatable in a valve housing ball with at least two substantially wedge-shaped, different sized throttle gaps or two substantially prismatic holes through the ball center, which are angled to each other.

Examples of the aforementioned embodiments of the inventive valve are explained in more detail in the drawing description.

Depending on the area of application of the valve are usually usually two control ranges for. the flow rate provided. In a first setting range, the flow cross-section can be set with 0 to 100% of the largest flow opening. The flow cross section is formed by the flow opening and the corresponding counterpart in the valve. A second, smaller flow opening allows only a flow area of 0 to u% of the largest flow opening, where u <100. Preferably u is in the range of 1 to 50. On the other hand, in practice hardly any applications are conceivable which make a setting range of less than 1% of the larger flow opening required. It may be useful according to a variant of the invention to use two flow openings with the same or similar maximum value, which have a different characteristic shape.

In the case of a valve with three setting ranges, the first setting range can again be set to a flow cross section from 0 to 100% of the largest flow opening. In a second adjustment range, the flow cross-section is 0 to v% of the largest flow opening, with a third control range 0 to w% of the largest flow opening, ie always related to the first control range, v is preferably in the range of 30 to 60, w in the range from 1 to 20. A throttle body with three actuator An optimal control is possible, but the entire valve is correspondingly more complicated. This is especially true for valves with more than three control ranges, which theoretically allow an even more differentiated control, but in practice increasingly encounter difficulties of a constructive nature. ,

Switching to different setting ranges can be done automatically, according to given data, but also manually. In the case of a non-optimal setting range, control oscillations can occur which are sensitive to normal operation and must be eliminated.

According to the invention, these control oscillations are eliminated by autonomously guiding the throttle body to a different control range for selecting the operating point by the process-controlled drive motor and adjusting the appropriate characteristic curve by motor.

Preferably, the control circuit is designed so that the throttle body is guided by the drive motor autonomously in a lower control range, z. B. by a frequency analysis such as wavelet, Fourier or Min / Max analysis an oscillation is detected.

Specific and further developing embodiments of the method are the subject of dependent claims.

Each setting range of a throttle body has a characteristic curve, as mentioned, depending on the operating point, the appropriate characteristic is selected, for example, the large or small at two control ranges or the large, medium or small at three control ranges:

- The positioning time from 0 to the corresponding 100% remains the same, even if the flow rate is greater or smaller.

- The shapes of the curves can be set independently within certain limits, these are in particular straight or progressive increasing. The choice of the appropriate characteristic at a given operating point is preferably carried out programmatically, in particular by an external controller or a control. Particularly suitable are ASIC (Application Specific Integrated Circuits) or μP (microprocessor). The changeover from one setting range to another is triggered, for example, by control oscillations. If, during a certain predetermined period of time Δt, the position setpoint value of the valve does not exceed a predetermined first setpoint value and a minimum number of oscillations have preferably occurred during this time, the throttle body is autonomously guided by the drive motor into a lower setting range where the throttle body has a smaller flow opening , It should therefore be detected an oscillation before switching to another setting range.

- If the position setpoint of the valve exceeds a specified second setpoint, the drive motor immediately switches autonomously to the higher one

Range.

The object with respect to the device according to a variant is achieved in that the throttle body has a single flow opening with at least two selectable by means of a drive motor control ranges.

The throttle body consists for example of a valve disc fixed to the housing or integrated first disc and a sealingly resting, motor-freely rotatable second disc. A preferably cross-sectionally round, elliptical or rectangular puncture penetrates both panes. The second disc is not only rotatable but also displaceable in the radial direction. Similarly, a valve housing may have two or more actuator ranges on two plates with a single flow port. This variant includes - if they can be used - all in the dependent claims and the drawings illustrated embodiments of the valve.

A valve with the throttle body according to the invention, also called a multi-range valve, has a wide range of uses, for example Femheizung

Heating / cooling in change over systems Cooling / dehumidifying in cold water circuits

Changes to a building (reconstruction, renovation, tenant development) - High / low pressure differences, eg. B. long supply lines between different zones of a plant.

In summary, multi-range valves according to the invention can be advantageously used everywhere where greatly varying demands are placed on the valves.

From the following detailed description and the totality of the claims, further advantageous embodiments and feature combinations of the invention result.

Brief description of the drawings

The invention will be explained in more detail with reference to embodiments shown in the drawing, which are also the subject of dependent claims. They show schematically:

1 shows a characteristic curve according to the prior art,

2 shows a fixed and a freely rotatable disc of a two-way valve,

3 shows the characteristics of the valve according to FIG. 2,

4a shows a fixed and a freely rotatable disc of a three-way valve,

Fig. 4b, a three-way valve

5 shows the characteristics of the valve according to FIG. 4,

6a shows a cylindrical throttle body,

Fig. 6b shows a variant according to Fig. 6a with a connecting channel 7 shows a spherical, semi-open throttle body,

8 shows a section through a spherical throttle body with two prismatic punctures,

9 is a schematic of a district heating with a dual-range valve,

10 is a diagram of a Stellbereichswechsels large - small,

1 1 is a diagram of a Stellbereichswechsels small - large,

12 shows a fixed and one displaceable in the x- and y-direction plate, each with a congruent opening,

13 shows the x-direction shifted openings,

FIG. 14 shows the openings shifted in the x and y directions, FIG.

Fig. 15 shows a circuit arrangement with a valve according to the invention, and

Fig. 16a-e another embodiment of a spherical throttle body in three mutually rotated 90 ° positions, in the equatorial section and in a perspective view.

Basically, the same parts are provided with the same reference numerals in the figures.

Ways to carry out the invention

The already mentioned in the introduction, Fig. 1 shows a characteristic K for a valve according to the prior art.

Fig. 2 shows some details of a throttle body 10, which consists of two in a valve chamber surface sealingly superposed discs 12, 14. The first disc 12 is fixedly mounted in a valve chamber of known type or integrated into the valve housing (44 in Figure 7). It is recessed a substantially trapezoidal flow opening 16, which extends in the present case over an angle of about 20 °. The in the Valve chamber coaxially on the first disc 12 lying freely rotatable second disc 14 has in the same peripheral region three arranged in each circle sector of 90 ° differently sized flow openings 18, 20, 22. Thus, the boundaries of the flow openings 18, 20, 22 directed towards the center of the second disk 14 are in the direction of rotation or in a tangential direction of the disk. 14 of equal length. The disc 14 is connected via a shaft to a drive motor, not shown, which can rotate the disc 14 positionable clockwise and counterclockwise. Of course, the second disc 14 may be fixedly mounted or integrated and the first disc 12 may be rotatable.

The flow openings 18, 20, 22 of the second disc 14 extend in the same peripheral region as the flow opening 16 of the first disc 12. All three flow openings 18, 20, 22 extend in a tangential direction counterclockwise, continuously or stepwise, according to the grid of the flow opening 16 of the fixed disc 12. If the second disc 14 is placed coaxially on the first disc 12 and rotated in a clockwise direction, the flow opening formed by both discs extends disproportionately. Obviously, with the flow opening 18, the largest flow cross sections 78 (FIGS. 13, 14) can be achieved, with the flow opening 22 being the smallest. The mentioned drive motor rotates the disc 14 autonomously so that the optimum setting range I, II or III results.

In Fig. 3, the characteristics of the three control ranges I, II, III of the disc 14 are recorded when the flow opening 18, 20 or 22 moves on the flow opening 16 of the first disc 12. The value 100% for the flow cross-section 78 corresponds to the maximum possible flow rate when the largest portion of the flow opening 18 is in the region of the flow opening 16. With the characteristic K ₁₈ can be achieved by turning the disc 14 by an angle α of 90 °, a flow rate of 0 - 100%. The characteristic K ₂₀ shows that with the flow opening 20 with a rotation by an angle α of 90 °, a flow rate of only 40% of the maximum possible flow cross section 78 can be achieved in the adjustment range of the flow opening 22 by an angle α of 90 ° only a flow rate of almost 20% of the maximum flow cross section 78. Thus, a valve with three is the same large adjustment ranges (rotation of the disc 14 by 90 ° in each case) realized, wherein all adjustment ranges continuously adjustable and different control ranges for the flow rate (I: 0 - 100%, II: 0 - have 40% and III: 0 - 20%).

If in the control range I a small flow with the characteristic K ₁₈ can not be controlled fine enough, the drive motor autonomously selects the operating point on the matching curve K ₂₀ and rotates the disc 14 in the corresponding adjustment range II of the flow opening 20 or III of the flow opening 22nd

In practice, the discs 12, 14 suitably made of a ceramic or a mechanically strong plastic, such as Teflon. Essential is a good lubricity and the sealing of the flat superimposed discs 12, 14th

Fig. 2 shows the discs 12, 14 of a two-way valve, in Fig. 4a, those of a three-way valve are shown. The three-way valve 15 according to FIG. 4b has two inputs A and B and an output AB. Other, not shown arrangements are also possible. Inputs A and B open and close in opposite directions, ie when input A is closed, input B is fully open and vice versa. In all intermediate positions, the media flowing through inputs A and B are mixedly directed to output AB.

The fixed disc 12 according to FIG. 4a for a three-way valve has a first flow opening 16 and a second flow opening 24, which is offset by an angle of 120 ° - 150 °. The rotatable disc 14 is designed so that two adjustment ranges I and II result. As shown in FIG. 2, disc 14 may be fixedly mounted or integrated, disc 12 may be rotatable.

In the adjustment range I, the flow opening 18 moves via the flow opening 16 in order to set the flow cross section 78 (FIGS. 13, 14) through the inlet A. At the same time, flow port 20 moves across flow port 24 to adjust the flow through port B.

In the adjustment range II, the flow opening 20 moves via the flow opening 16 in order to set the flow cross-section 78 through the inlet A. At the same time, flow opening 22 via flow opening 24 to adjust the flow through input B.

Adjustment range I! is traversed opposite to the adjustment range I in the opposite direction. The characteristics can be adapted to the particular problem by modifying the openings 16-24.

In Fig. 5, the opposing characteristics K _{18 + 16} and K _{20 + 24} in the control range I and K _{20 + 16} and K _{22 + 24} Jm control range Il are shown.

FIG. 6 a shows a schematic variant of a throttle body 10. This cylindrical throttle body 10 is rotatable about a rotation axis A, which is indicated by a double arrow 26. Further, this cylindrical throttle body 10 is displaceable in the axial direction A, which is indicated by a further double arrow 28. This cylindrical throttle body 10 has three actuating regions in the axial direction A, which are designated by I, II and III. These three control areas have flow openings of different geometry, in the present school example, the flow opening 32 in the control range I has an elliptical cross-section, the flow opening 34 in the control range Il a rectangular and the flow opening 36 in the control range III a triangular. In industrial practice, the adjustment ranges are of similar geometric shape. The flowing through an inlet 43 and an outlet 45 of a pipe 42 medium 38 is characterized by an arrow.

The drive motor, not shown, initially selects the setting range I, II or III and then rotates the throttle body 30 until the operating point is reached. The two movements can be performed by the same or by two different drive motors. The shape of the characteristic curves in the setting areas I, II and III is determined by the geometric shape of the flow openings 32, 34, 36 and the flow cross section 78 (FIGS. 13, 14) in the valve.

Fig. 6b substantially corresponds to Fig. 6a, but it is a fine channel 30 is formed, which extends in the axial direction A and the control areas I, II and III connects. The function of the valve remains unchanged, but it only has one flow opening. In Fig. 7 and 8, the throttle body 10 is spherical, which is freely rotatable about the rotational axis A and positionable by the drive motor, not shown.

A flow tube 42 according to FIG. 7 with an inlet 43 and an outlet 45 for the flowing medium 38 at the same time forms the valve housing 44, which is sealed against a drive shaft 46. The semi-open spherical throttle body 10 has a column-shaped large flow opening 47 and a likewise columnar small

Flow opening 49 with a plane of symmetry E. The large flow opening 47 forms the control range I, the small flow opening 49 the control range II. The sealing part 48 of the spherical throttle body 10 against the valve housing 44 is annular and shown with a dashed line. The ball is rotated in both directions by 90 °.

Fig. 8 shows a section along the plane E in Fig. 7, wherein in the spherical throttle body 10, the large flow opening 47 and the small flow opening 49 are formed substantially prismatic. The ball is only rotated by 60 ° in one direction or the other. It is a recess 50 for the drive port 46 (Fig. 7) recognizable.

FIG. 9 shows one of the numerous uses of the valve 66 according to the invention. The flow temperature in a district heating line 56 is much higher in winter than in summer. This results in completely different operating points for the direct temperature control of domestic hot water in a building 64 with a tap 68. In this case, cold water from the drinking water supply is brought directly to a desired temperature via a heat exchanger 62 via a line 54. Due to the strongly fluctuating hot water demand, the regulation is made even more difficult. If the control vibration is too strong, the user may contract burn injuries in a shower, for example. To improve the control quality, in particular at high flow temperature and low hot water requirement, a valve 66 according to the invention is installed, in the present case a two-way valve in throttle circuit.

Fig. 10 and Fig. 1 1 describe switching conditions of a control range I with a large flow opening on a control range Il with small flow opening and back. Shown is the time course of the position setpoint S for a valve, which may result from a room temperature control.

In FIG. 10, the valve initially operates in setting range I. If the position setpoint S falls below the threshold value S _k and remains below it for an adjustable time period Δt, the throttle body is guided into the setting range II. The control can be set so that not only the time period .DELTA.t is relevant, but the drive motor also has to execute a minimum number N of movements, for example N = 10. The valve now operates in adjustment range II to at most the conditions according to FIG be fulfilled.

In Fig. 1 1, the opposite case is shown, the control operates initially in the small control range II. As soon as the position setpoint S exceeds the threshold S _g , the throttle body changes immediately in the large control range I, otherwise the consumer to be controlled would be under-supplied. The valve now works in setting range I until the conditions according to FIG. 10 are at most met again.

12 to 14 show a further variant of a throttle body 10 which comprises a fixed first plate 70 with a rectangular flow opening 74 and a longitudinally and transversely, in the x and y direction, displaceable second plate 72 with a presently congruent flow opening 76. However, the flow openings do not have to be the same size or the same geometric shape. The two sealingly superimposed plates 70, 72 form depending on the position of the displaceable plate 72 an adjustable flow cross-section 78. In a control range I according to FIG. 13, the displaceable plate 72 is located on the fixed plate 70, that in the position 0 no flow occurs , When the plate 72 is displaced in the x direction, the maximum flow cross section 78 is reached at 100%, where the two flow openings 74, 76 are congruent to one another. In the position shown in Fig. 13, the flow area 78 is about 30% of the maximum possible value.

In the position according to FIG. 14, the drive motor has switched over into the setting range II. The maximum flow cross section 78 is only about 35% of the maximum value at 100% as shown in FIG. 13. The control in the x-direction can be performed much more accurately in the adjustment range II if the flow cross-section 78 drops below a predetermined value.

Fig. 15 shows a circuit arrangement according to the invention. A valve module 80 regulates the flow through the conduit 82. At a desired location of the conduit system, a sensor 84, e.g. the temperature measured. The signal from the sensor is sent to the central control circuit 86, which generates the so-called system control signal V (t) in a manner not of further interest here. This is the input signal for the control circuit 88 according to the invention of the valve module 80. The control circuit contains a calculation algorithm which determines the suitable characteristic of the valve 92 and the position x of the throttle body. With these two parameters, the drive motor 90 is controlled, which drives the throttle body in the position which achieves the desired hydraulic cross section.

The module can be marketed as a self-contained product. But it is also possible to implement the valve, the motor and the control circuit as separate units.

FIGS. 16a to 16e show a further preferred embodiment. The throttle body is formed by a centered with a channel 102 ball 100, which sits in a ball valve housing, as it is z. B. is shown schematically in Fig. 7. The channel 102 forms on each of two opposite surface areas of the ball 100 each a mouth opening 104 and 106, respectively. Each of these mouth openings 104, 106 has an edge region 105, 107 with a contour which (in conjunction with the circular inlet or outlet of the valve housing) Characteristic curve for the rotational position-dependent free (or hydraulic) cross-section forms. As such, the free cross section of the channel 102 is sufficiently large so that the maximum flow rate (u = 100%) is possible with a suitable rotational position.

Between the two mouth openings 104, 106 there is a surface closing area 108 (preferably arranged symmetrically with respect to the equatorial plane EE) (compare, in particular, the equatorial section according to Figure 16d), which is sufficiently large so that it can close the inlet and outlet of the valve housing , This means that the supervisor Area closing region 108 includes a circle in geometric terms corresponding to the diameter of the inlet and outlet. (If the inlet or outlet is not circular but otherwise limited, the surface closure area must accordingly contain a different geometric shape so that it can close at least the cross-sectional area of the inlet or outlet.) The arrangement of the surface closure area 108 thus defining the closed position of the valve.

The contour of the edge region 105 provided for the small adjustment range (control range 0 - u%, u <100%) encloses a first surface area which is first strip-shaped and then widens wedge-shaped thereafter. Said area is symmetrical in the present example with respect to the equatorial plane E-E of the ball.

The contour of the edge region 107 provided for the large adjustment range (control range 0-100%) encloses a circle-like second surface region. Also, this surface area is symmetrical in the present example with respect to the equatorial plane of the sphere.

The ball 100 has at the "north pole" on a recess 1 10, in which a (not dargesteller) coupling part of a valve axis can engage against rotation.

The described embodiments can be varied in many ways without the basic idea of the invention having to be abandoned. Thus, the adjustment ranges can be realized by differently sized rotation angle ranges of the throttle body. They can be separated or connected directly to each other. The zero position can be provided between the two control ranges, that is the position in which the valve blocks.

It can z. B. two ball bodies (Fig. 7, 8) are connected via a shaft, so that a "dumbbell" throttle body is formed. The embodiments shown in FIGS. 7, 8 and 16 can also be circular-cylindrical instead of spherical.

Claims

claims

A valve (66) for liquid and / or gaseous, flowing media (38), comprising a valve housing (44) which forms a valve chamber provided with at least one respective inlet (43) and outlet (45), and one therein moving and positionable throttle body (10) for controlling the hydraulic cross section (78), wherein at least one flow path is formed, characterized in that the throttle body (10) alternately forms at least two different characteristics during movement in the valve chamber per flow path.

2. Valve (66) according to claim 1, characterized in that in the throttle body (10 at least two flow openings are provided, wherein at least a part of

Flow openings (18, 20, 22, 32, 34, 36, 47, 49) with a channel (30) are interconnected.

3. Valve (66) according to claim 1 or 2, characterized in that the throttle body (10) of a valve housing (44) fixed or integrated therein first disc (12) arranged with at least one arranged in a circular sector

Flow opening (16, 24) and a sealingly resting, freely rotatable second disc (14) having at least two different flow openings (18, 20, 22) for forming control areas (I, II, III), said flow openings in the same peripheral area as the flow openings (16, 24) of the first disc (12) and arranged to form different flow cross-sections

(78) are movable over one another and positionable.

4. Valve (66) according to claim 3, characterized in that in a two-way valve in the first fixed disc (12) has a flow opening (16), in a three-way valve (15) has two such flow openings (16, 24), preferably by 120 ° - 150 ° offset from each other, are arranged.

5. Valve (66) according to claim 3, characterized in that the flow openings (18, 20, 22) in the positionable by a drive motor second disc (14) are formed in the tangential direction changing.

6. Valve (66) according to claim 1, characterized in that the throttle body (10) of a valve housing (44) fixed to the first plate (70) with at least one

Through-flow opening (16, 24) and a sealingly resting, in the x- and y-direction longitudinally and / or transversely displaceable second plate (72) having at least two different sized flow openings (18, 20, 22) for forming parking areas (I, II , III), said flow openings in the region of the flow openings (16, 24) of the attached first plate and under

Training of different flow cross-sections (78) can be moved over one another and positioned.

7. Valve (66) according to claim 6, characterized in that the flow openings (18, 20, 22) of the displaceable second plate (72) are formed in the / the direction of movement / s changing.

8. Valve (66) according to one of claims 2 to 7, characterized in that the second disc (14) or the second plate (72) attached to the valve housing (44) or integrated therein and the first disc (12) rotatable or The first plate is designed to be movable.

9. Valve (66) according to claim 1, characterized in that the throttle body (10) is formed as positionable in the axial direction, freely rotatable cylinder, which in the axial and / or tangential direction to form the control ranges (I, II, III) gradually having different flow openings (32, 34, 36).

10. Valve (66) according to claim 1, characterized in that the throttle body (10) as a freely rotatable ball with at least two, substantially wedge-shaped, different lain throttle gaps (47, 49) or two angled, prismatic punctures through the ball center is formed.

1 1. Valve (66) according to claim 10, characterized in that the throttle gaps (47, 49) have a common plane of symmetry (E), or the prismatic punctures are angled approximately 60 °.

12. Valve (66) in particular according to one of claims 1 to 1 1, characterized in that the throttle body (10) has a single flow opening (16, 18, 74, 76) with at least two, preferably by means of at least one drive motor selectable control ranges (I , II, III).

13. Valve (66) according to claim 12, characterized in that the throttle body (10) consists of a valve housing (44) fixed or integrated therein first disc (12) and a sealingly resting, motor-freely rotatable second disc (14), wherein the second disc (14) is also displaceable in the radial direction.

14. Valve (66) according to claim 12, characterized in that the throttle body (10) of a valve housing (44) fixed or integrated therein first plate (70) and a sealingly resting, motor freely displaceable in the x and y direction second plate (72) consists.

15. Valve (66) according to one of claims 1 to 14, characterized in that the throttle body (10) in two control ranges on a first control range (I) a flow cross section (78) from 0 to 100% of the largest flow opening (18, 34 .

47) and a flow area (78) can be set from 0 to u% of the largest flow opening on a second setting range, wherein preferably u = 1 to 50.

16. Valve (66) according to one of claims 1 to 14, characterized in that the throttle body (10) in three control ranges on a first control range a Flow cross-section (78) from 0 to 100% of the largest flow opening (18, 34, 47), on a second adjustment range, a flow area (78) from 0 to v% of the largest flow opening and on a third adjustment range, a flow area (78) from 0 to w% of the largest flow opening is adjustable, wherein preferably v = 30 to 60 and w = 1 to 20.

17. Valve according to one of claims 1 to 16, characterized in that it comprises a drive motor (90) and a control circuit (88) which can be acted upon by a system control signal.

18. Valve according to claim 17, characterized in that the control circuit is designed so that for a selection of an operating point of the throttle body (10) by the drive motor autonomously in a different adjustment range (I, II, III) is performed to the appropriate characteristic (K).

19. Valve according to claim 17 or 18, characterized in that the control circuit is designed such that the throttle body (10) is guided by the drive motor autonomously in a lower control range, when the control circuit, preferably by a frequency analysis such as wavelet, Fourier or Min / Max analysis, detects an oscillation.

20. Valve according to claim 17 or 18, characterized in that the control circuit is formed so that the throttle body (10) is guided by the drive motor autonomously in a lower control range (I, II, III) when a position setpoint (S) of the

Valve (66) during a predetermined period of time (.DELTA.t) and preferably a minimum number of (N) movements of the drive motor does not exceed a predetermined first threshold value (S _k ).

21. Valve according to claim 17 or 18, characterized in that the control circuit is formed so that the throttle body (10) by the drive motor autonomously in a higher control range (I, II) is performed when a position setpoint (S) of the valve (60) exceeds a predetermined second setpoint (S _g ).

22. A method for eliminating vibrations (S) in a control loop using a valve (66) according to any one of claims 1 to 21, characterized in that the throttle body (10) for selecting the appropriate operating point by the process-controlled drive motor autonomous in another range (I, II, III) out and the appropriate characteristic (K) is adjusted by motor.

23. The method according to claim 22, characterized in that the selection of the appropriate characteristic curve (K) by an external controller or a control takes place.

24. The method according to claim 22 or 23, characterized in that the selection of the appropriate characteristic curve (K) is program-controlled, preferably by an ASIC or microprocessor.

25. The method according to any one of claims 22 to 24, characterized in that the speed of the drive remains the same.

26. The method according to any one of claims 22 to 25, characterized in that the throttle body (10) is guided by the drive motor autonomously in a lower control range (II, III) when the position setpoint (S) of the valve (66) during a predetermined period of time (.DELTA.t) and preferably a minimum number (N) movements of the drive motor does not exceed a likewise predetermined first threshold value (S _k ).

27. The method according to any one of claims 22 to 26, characterized in that the throttle body (10) from the drive motor autonomously in a higher control range (I, II) is performed when the position setpoint (S) of the valve (60) has a predetermined second setpoint (S _g ) exceeds.