FLOW REGULATOR

Abstract: A flow regulator for gaseous substances, particularly a flow regulator intended for air in air-conditioning and ventilation installations, for maintaining the volumetric flow of the gaseous substance at desired magnitude with sufficient accuracy when the differential pressure acting across the flow regulator (10) varies within given limits. The flow regulator (10) comprises an envelope (11) and a regulating member (12) turnably disposed in the flow passage confined by the envelope (11). The torque produced by the flow of gaseous substance on the regulating member (12) and on the other hand a countertorque dependent on the position of the regulating member (12) cause the regulating member (12) turning in the flow passage to assume a position of equilibrium such that the requisite pressure drop is obtained for maintaining the volumetric flow rate at predetermined magnitude. The regulating member (12) is substantially slightly curved at least in the flow surface facing the incoming flow of the gaseous substance. The turning angle between the initial and ultimate positions of the regulating member (12) is substantially the same at volumetric flows of different magnitudes when the differential pressure range is the same. The initial and ultimate positions of the regulating member (12) are dependent on the magnitude of the volumetric flow when the differential pressure is the same.

Description: Flow regulator The present invention concerns a flow regulator for gaseous substances, in particular for air in air-conditioning and ventilation installations, serving to maintain the volumetric flow of a gaseous substance at desired magnitude with sufficient accuracy when the differential pressure across the flow regulator varies within given limits, said flow regulator comprising an envelope and a regulating member turnably disposed in a flow passage confined by the envelope, and which when the differential pressure increases turn progressively towards a position at right angles to the direction of flow, the torque exerted by the flow of the gaseous substance on the regulating member and on the other hand a countertorque dependent on the position of the regulating member causing the regulating member turning in the flow passage to assume a position of equilibrium in which the required pressure drop is obtained for keeping the volumetric flow at predetermined magnitude. In low pressure regulators of prior art, which allow fairly wide regulation of the volumetric flow set-point, the lowest pressure at which the means starts to operate increases with increasing volumetric flow rate. Even at small volumetric flows, the lowest pressure is usually relatively high. The high end pressure also icreases with increasing volumetric flow rate set-point. Because the lowest pressure is high and/or because it depends on the volumetric flow set-point value, the regulators of prior art, in order to function, require extra blower energy and possibly a bigger blower; owing to the increase of pressure they tend to cause noise problems; they impede the designing work, and they cause difficulties in the implementation phase of the installation. In general, the setting of the volumetric flow in flow regulators at the site of installation with accuracy and steplessly is OMPI exceedingly difficult and often impossible in practice, particu¬ larly if the regulator has been installed already, and. it is also a fact that the flow rate setting cannot be directly read. Regulators of prior art also do not allow the throttling pressure to be read with which the regulator impedes the flow. It is true that in certain regulator designs of prior art one may observe from the outside whether the regulator is within its operating range, but they allow no regulation of the volumetric flow rate. A prerequisite of serial manufacturing, storing, distribution and convenient use of regulators is that they can with ease and accuracy be regulated at the site of installation, also after installation. It is important with a view to the balancing and inspection of an air-conditioning installation that it is possible to observe from outside the regulator which set-point value of volumetric flow has been selected, whether the regulator is within its operating range, and how strongly the regulator throttles the flow. In addition, the basic construction and the manufacturing technology of the regulator shall be such that the required calibration measures are as simple and as few as possible and independent of the setting of volumetric flow. In regulators known at present, the movement of the regulating member cannot be steplessly limited. Therefore, regulators of prior art cannot be used at all for mere balancing based on so-called single pass regulation, which would eliminate the risk of binding of the means. Secondly, regulators of prior art cannot be used for restricted and controlled correction. Thirdly, regulators of prior art cannot be used in the best possible way in air-conditioning installations where the air quantities are varied, e.g. different air quantities in the daytime and during the night. In regulators of prior art, the force that is used to counteract the regulating member is a mass or a spring, or a spring and bellows in combination. Each design has its advantages and dis¬ advantages. Disadvantages connected with the use of springs are OM e.g. their relaxing, inaccuracies of manufacture, liability to suffer damage, etc. Disadvantages encountered when a mass is used as counterforce are the facts that the regulator can only be installed in a horizontal duct or passage, that the axis has to be horizontal with reference to the direction of flow at all times and that the mass must always be on one and the same side of the passage. Advantages of a mass in the role of counterforce are, for instance, reliability in use, manufacturing accuracy and permanence. Disadvantages of the use of springs combined with bellows are that the design is more liable to disturbances and more expensive than a mere spring and has a shorter life span. In regulators of prior art a particular damping means is required to allay the oscillations, or hunting, of the regulating member. In some designs of prior art, damping of the dashpot type is used. In another regulator of prior art, bellows type damping is used. Disadvantages of the damping designs described above are, for instance, that the damping designs may in the course of time either bind or be blocked or break, that they require maintenance, and that they may impair the accuracy. The object of the invention is to provide an improvement of regulator designs known in the art. A more detailed aim of the invention is to provide a flow regulator in which the drawbacks present in regulators of prior art are overcome. The aims of the invention are achieved by a flow regulator the characteristic features of which are presented in the claims following below. The regulator of the invention is primarily characterized in that at least one of the halves of the regulating member, with reference to the turning angle, is substantially slightly curved at least in the flow surface facing the flow of the gaseous substance. In an advantageous embodiment of the invention, the flow regulator is characterized in that when the regulating member turns in the OMPI range of operation of the flow regulator, a part of the flow surface of the regulating member is left in the shadow of the flow surface as viewed in the flow direction of the gaseous substance. In an advantageous embodiment, when the regulating member turns in the range of operation of the flow regulator, at least part of one of the halves of the flow surface of the regulating member, with reference to the turning shaft, is left in the shadow of the flow surface of the opposite half of the regulating member, as viewed in the flow direction ' of the gaseous substance. In an advantageous embodiment, when the regulating member is turning in the range of operation of the flow regulator, a part of the flow surface of the regulating member is left in the shadow of the regulating member, when viewed in the rectangular direction against the flow direction of the gaseous substance and the turning shaft. In an advantageous embodiment, when the regulating member is turning in the range of operation, at least part of one of the halves of the flow surface of the regulating member, with reference to the flow regulator, is left in the shadow of the flow surface of the opposite half of. the regulating member, as at right angles against the flow direction of the gaseous substance and the turning shaft. Several advantageous embodiments of the invention are characterized in that in the flow passage, particularly at the highest volumetric flow rate set-point value, there is no other element causing substantial throttling than the turning regulating member. This enables the lower pressure to be made low enough. Several advantageous embodiments of the invention are characterized in that the regulating member is a slightly curved plate. The turning angle between the initial and ultimate positions of the regulating member is substantially of the same order at different volumetric flow rates, the differential pressure being the same. The initial and ultimate positions of the regulating member are dependent on the magnitude of the volumetric flow rate, the differential pressure being the same. The flow regulator is advantageously provided with adjustable and/or self-adjusting OMP limiting members to limit the differential pressure range of the flow regulator, the limiting members being disposed to limit the angular movement of the regulating member. The operating range of the flow regulator is also advantageously changeable by changing the effective flow aperture between the regulating member and the flow passage. Similarly, the operating range of the flow regulator is advantageously changeable by the aid of a shiftable mass causing a countertorque dependent on the position of the regulating member. By the flow regulator of the invention several remarkable advantages are gained. Firstly, the set-point value of the flow regulator can be regulated in a relatively wide volumetric flow range e.g. duct velocity 2-8 m/s, without any change of the pressure range in which the flow regulator operates. In addition, the flow regulator operates with lower differential pressure, e.g. about 20 Pa, than any regulator known in prior art, where the operating range is 20-200 Pa throughout. In the regulator of the invention, it has been understood to make use of a turning angle of the regulating member about 90 , thus affording, with additional adjustment of the effective flow aperture, a large movement of the regulating member relative to the change of differential pressure, and a relatively wide operating range. Secondly, In the regulator of the invention the volumetric flow rate can be regulated steplessly and simply at the site of installation, even if the regulator has already been installed, simply by turning a control knob on the flow regulator. The volumetric flow rate may be directly read on a scale, as well as the degree in which the regulator throttles the flow, and whether the regulator is within its operating range, i.e., whether the regulator admits the correct air quantity, or too little or too much. Thirdly, in the flow regulator of the invention the movement of the regulating member may be limited, or the movement of the regulating member may, if needed, be entirely arrested. Thanks to this charac¬ teristic feature, the flow regulator of the invention may also be Or'.P! used in applications such as balancing based merely on so-called single pass regulation. Secondly, the flow regulator may be used for minor controlled correction, and thirdly the flow regulator may successfully be used in air-conditioning installations where centralized altering of the air flows is desirable. In the flow regulator of the invention, a mass is used advan¬ tageously for counterforce. However, in the regulator of the invention the disadvantages of a mass have been eliminated in practice. The flow regulator of the invention may be installed in a passage with any direction, and the mass used for counterforce can be disposed on either side of the passage or duct. This is based on the fact that the turning axis of the regulating member is mounted horizontally by the aid of a levelling means provided in the flow regulator, and the mass is moreover so positioned that the mass is turned through the same angle but in opposite direction as is the deviation of the particular instance of the installation from a separately determined basic installation. The flow regulator of the invention also requires no separate oscillation inhibiting means, certainly no oscillation inhibitor which would be likely to bind or accumulate dirt or be blocked: as a rule the counterpressure in the duct system is alone enough to keep the regulating member stable. Factors contributing to this favourable feature are in the first place that the regulating member is slightly curved and that the regulating does not nearly completely close the passage in any position. As a result, the air is enabled to flow past on all sides of the regulating member even when the regulating member is in the "closed" position. Further factors contributing to the favourable feature just described are for instance the size and shape of the regulating member, the location of the turning axis of the regulating member with reference to the regulating member, the size and location of the counterweight, and the limiters of the regulating member. Thanks to the slightly curved regulating member, the flow regulator can be made accurate, silent, and a slightly curved regulating member like this moves smoothly from one end position to the other. The invention is described in detail, referring to an advantageous embodiment of the invention presented in the figures of the drawing attached, but to which the invention is not meant to be exclusively confined. Fig. 1 presents an advantagous embodiment of the invention in partly sectioned elevational view. Fig. 2 shows the section along the line II-II in Fig. 1. Fig. 3A presents in schematic elevational view an advantageous embodiment of the regulating member utilized in the flow regulator of the invention. Fig. 3B presents in schematic elevational view a second advantageous embodiment of the regulating member utilized in the flow regulator of the invention. Fig. 3C presents in schematic elevational view a third advantageous embodiment of the regulating member utilized in the flow regulator of the invention. Fig. 3D presents in schematic elevational view a fourth advantageous embodiment of the regulating member utilized in the flow regulator of the invention. Fig. 3E presents in schematic elevational view a fifth advantageous embodiment of the regulating member utilized in the flow regulator of the invention. Fig. 3F presents in schematic elevational view a sixth advantageous embodiment of the regulating member utilized in the flow regulator of the invention. Fig. 4A presents in elevational view the initial and ultimate positions of the regulating member of the flow regulator at high volumetric flow rate. Fig. 4B presents in elevational view the initial and ultimate positions of the regulating member of the flow regulator at low volumetric flow rate. Fig. 5A presents the effective flow aperture of the flow regulator of the invention at its smallest, with the regulating member so regulated that the effective flow aperture is large, viewed in the direction of flow. Fig. 5B presents the effective flow aperture of the flow regulator of the invention at Its smallest, with the regulating member so regulated that the effective flow aperture is small, viewed in the direction of flow. Fig. 5C illustrates in elevational view the changing of the. effective flow aperture of the flow regulator in a flow passage with variable cross section. Fig. 5D illustrates in elevational view the changing of the effective flow aperture of the flow regulator by means of a separate regulating member. Fig. 6 presents the principle of limiting the differential pressure range of the flow regulator, in a schematic elevational view. Fig. 7 shows a detail of Fig. 6 viewed in the direction 6A. Fig. 8 shows a way of changing the operating range of the flow regulator of the invention, in a schematic elevational view. In the embodiment of Figs 1 and 2, the constant flow regulator of the invention has been generally indicated by reference numeral 10. The regulator 10 comprises an envelope 11 and a regulating member 12 disposed within the envelope 11. In this embodiment, the regulating member 12 is a curved flap-like regulating member composed of two curved flaps 12a and 12b overlapped with each other. The regulating member 12 is attached to a turnable shaft 13 by the aid of a regulating and fixing nut 14 and a combined sleeve, regulating and fixing nut 16. The shaft 13 is rotatably carried by bearings 15 and 18 in the envelope 11. The regulating member 12 turns by effect of the air flowing in the flow passage confined by the envelope 11, and the countertorque generated by the weight 23 is disposed to set the regulating member 12 in a position producing the requisite throttling. The weight 23 is integrally connected with the regulating member 12 by means of the sleeve, control and fixing nut 16 and by a member 19 and cover 20 rotatably attached thereto, and it rotates along with the turning of the regulating member 12. The axis 13 is installed horizontally by the aid of a balance and a levelling ball 31 in the protecting case 32. The operating range of the constant flow regulator 10, as regards volumetric flow rate, can be changed by turning the regulating knob 24, whereby in this embodiment the size of the flap-resembling regulating member 12 and simultaneously the effective flow aperture, the location of the weight 23 and the initial and ultimate pos¬ itions of the regulating member 12 are changed. The halves 12a and 12b of the flap-like regulating member 12 move in different directions with reference to each other on the shaft 13, by effect of the different-handed threads on the shaft 13 and in the regu¬ lating nuts 14,16. One end of the shaft 13 is laterally fixed in the bearing 15, whereby the effect of the adjustment also causes the member 19, which has by mediation of the sleeve 16 been mounted on the flap-like closing member 12 on one half 12b thereof rotatably, and the cover, attached to said member 19, to move in the direction of the shaft 13. The gear 22 attached to the cover 20 is in contact with the shaft 13, and the gear 22 is due to the pinion rack formed by grooves on the shaft 13 and to the sidewise movement of the rotatably disposed member 19 set in rotation, whereby the gear 22 at the same time by means of the pinion rack ^ 34 shifts the weight 23. In Figs 3A-3F are presented some advantageous embodiments of the regulating member 12 employed in the regulator 10 of the invention. In Figs 3A-3D, the halves of the regulating member 112a,112b,112c and 112d, with reference to the turning shaft 13, are slightly curved, whereas in Figs 3E and 3F only one of the halves of the regulating member I12e and 112f is slightly curved. In Figs 4A and 4B is observed that at high volumetric flow rate, at the smallest differential pressure of the operating range, the regulating member 12 is in a more horizontal position than at a small volumetric flow rate at the corresponding differential pressure. Similarly, it is observed that at a small columetric flow rate at the highest differential pressure of the operating range, the regulating member 12 is in a more vertical position than at a large volumetric flow at the corresponding differential pressure. The position of the regulating member 12 at the highest volumetric flow rate and at the smallest differential pressure of the operating range advantageously deviates about 90 from the position of the regulating member 12 at the smallest volumetric flow rate and the highest differential pressure of the operating range. In contrast, the turning angle φ- is substantially of the same order as the respective turning angle φ. for high volumetric flow rate when the differential pressure is the same. Thus, in the regulator 10 of the invention the rotation angle φ.,φ 9 of the regulating member 12 for the minimum and maximum differential pressures is substantially of the same order at the different volumetric flow rates. At the same minimum and maximum values of the differential pressure Δp, the angle of rotation t »Φ 2 is advantageously about 60°. In the embodiment of Figs 5A and 5B, in the flow regulator 10 of the invention the effective flow aperture 37 is changed by regulating the size of the regulating member 12. In this embodiment, the size of the effective flow aperture 37 is changed by moving the halves 12a and 12b of the flap-resembling regulating member 12 in the manner indicated by the arrow A in Fig. 5A. In the embodiment of Fig. 5C, the effective flow aperture 37 is changed by moving the regulating member 12 in the flow passage 11,11a with variable cross-section as indicated by the arrow B, in other words, by shifting the regulating member 12 in the direction of flow. In the embodiment of Fig. 5D, the effective flow aperture 37 is changed by regulating the flow aperture by the aid of a separate regulating member 36, consisting of one or several parts, placed in the flow passage. The shafts of the regulating members 36 are denoted by the reference numeral 35. The regulating members 36 may be rotated around the axes 35 as indicated by arrows C. In the flow regulator 10 of the invention, the differential pressure range is limited by limiting members 25 and 26a,26b. When the limiters 26a and 26b are moved as indicated by arrows D in Fig. 6, the movement of the regulating member 12 is limited. The limiters 26a and 26b are advantageously self-regulating limiting members in accordance with the volumetric flow rate that has been selected, as shown in Fig. 7. The limiters 26a and 26b have bevelled faces in that case. The limiters 26a and 26b regulate themselves when a limiter pin 25 moves as the volumetric flow rate is regulated, In the manner indicated by the arrow E in Fig. 7. The movement of the flap-like regulating member 12 of the constant flow regulator 10 may also be arrested totally or partially with the aid of the adjustable limiters 26a and 26b. The limiter pin 25 and the adjusting scale 39 on the protective case 32 indicate the differential pressure Δp acting across the constant flow regulator 10. When the limiter pin 25 touches the limiter 26a, the differential pressure Δp is at the lowest, and at the limiter 26b it is at the highest (Fig. 7). When the limiter pin 25 is intermediate between the limiters 26a and 26b, OM ^ WIP the means is in the operating range; if not, either too much or too little air Is admitted. As shown in Fig. 8, the operating range of the flow regulator 10 can be changed by the aid of a movable mass or weight 23 by shifting the weight 23 as indicated by the arrow F. The weight 23 and the limiting members 25 and 26a,26b automatically assign different initial and ultimate positions to the flap-like regulating member 12 at different volumetric flow rates. In the constant flow regulator 10 of the invention, the effect of gravity can be made the same independent of the installation mode by the aid of the fixable cover 20 which is adjustable with reference to the turning axle 13 of the regulating member 12, of the ball case 29 on the protecting case 32 and of the ball 30 moving in the case 29• The constant flow regulator 10 is balanced by a balancing weight 38 in connection with manufacturing, first without the countertorque produced by the weight 23. The ball 30 and the scale 40 on the case 29 show in which position the means Is. The cover 20 is turned to a position corresponding to the position indicated by the ball 30 by the aid of a scale 41 on the cover 20 and Is locked by a set screw 21. In the foregoing only a few advantageous embodiments of the invention have been presented, and it Is obvious to a person skilled in the art that numerous modifications thereof are feasible within the scope of the inventive idea presented in the claims following below. For instance, it is not meant to restrict the invention exclusively to ducts with circular cross section.

Claims: Claims 1. A flow regulator for gaseous substances, particularly for air in air-conditioning and ventilation installations, for maintaining the volumetric flow rate of the gaseous substance at desired magnitude with sufficient accuracy when the differential pressure (ΛP) acting across the flow regulator (10) varies within given limits, said flow regulator (10) comprising an envelope (11) and a regulating member (12) turnably disposed in a flow passage confined by the envelope (11), said member turning with increasing differential pressure progressively crosswise with reference to the direction of flow, whereby the torque produced by the gaseous substance on the flow regulating member (12) and on the other hand a countertorque dependent on the position of the regulating member (12) cause the regulating member (12) turning in the flow passage to assume an equilibrium position such that the requisite pressure drop for maintaining the volumetric flow at pre-selected magnitude is achieved, characterized in that at least one of the two halves with reference to the turning shaft (13) of the regulating member (12,112a,112b,112c,112d,112e,112f) is substantially slightly curved at least in the flow surface facing the flow of the incoming gaseous substance. • 2. A flow regulator for gaseous substance, particularly for air in ' air-conditioning and ventilation installations, for maintaining the volumetric flow rate of the gaseous substance at desired magnitude with sufficient accuracy when the differential pressure <2 p) acting across the flow regulator (10) varies within given limits, said flow regulator (10) comprising an envelope (11) and a regulating member (12) turnably disposed in a flow passage confined by the envelope (11), said member turning with increasing differential pressure progressively crosswise with reference to the direction of flow, whereby the torque produced by the gaseous substance on the flow regulating member (12) and on the other hand a countertorque dependent on the position of the regulating member (12) cause the regulating member (12) turning in the flow passage to assume an equilibrium position such that the requisite pressure drop for maintaining the volumetric flow at pre-selected magnitude is achieved, characterized in that as the regulating member (12, 112a,112b,112c,112d,112e,112f) is turning in the operating range of the flow regulator, at least a part of the flow surface of the regulating member is left in the shadow of the flow surface as viewed in the direction of flow of the gaseous substance. 3. A flow regulator for gaseous substances, particularly for air in air-conditioning and ventilation installations, for maintaining the volumetric flow rate of the gaseous substance at desired magnitude with sufficient accuracy when the differential pressure (Δp) acting across the flow regulator (10) varies within given limits, said flow regulator (10) comprising an envelope (11) and a regulating member (12) turnably disposed in a flow passage confined by the envelope (11), said member turning with increasing differential pressure progressively crosswise with reference to the direction of flow, whereby the torque produced by the gaseous substance on the flow regulating member (12) and on the other hand a countertorque dependent on the position of the regulating member (12) cause the regulating member (12) turning in the flow passage to assume an equilibrium position such that the requisite pressure drop for maintaining the volumetric flow at pre-selected magnitude is achieved, characterized in that as the regulating member (12,112a,112b,112c,112d,112e,112f) is turning in the operating range of the flow regulator, at least a part of the flow surface of the regulating member is left in the shadow of the flow surface of the opposite half with reference to the turning axis (13) of the regulating member as viewed in the direction of flow of the gaseous substance. 4. A flow regulator for gaseous substances, particularly for air in air-conditioning and ventilation installations, for maintaining the volumetric flow rate of the gaseous substance at desired magnitude with sufficient accuracy when the differentail pressure ) acting across the flow regulator (10) varies within given limits, said flow regulator (10) comprising an envelope (11) and a regulating member (12) turnably disposed in a flow passage -$TT£ ' EX OMPI confined by the envelope (11), said member turning with increasing differential pressure progressively crosswise with reference to the direction of flow, whereby the torque produced by the gaseous substance on the flow regulating member (12) and on the other hand a countertorque dependent on the position of the regulating member (12) cause the regulating member (12) turning in the flow passage to assume an equilibrium position such that the requisite pressure drop for maintaining the volumetric flow at pre-selected magnitude is achieved, characterized in that as the regulating member (12, 112a,112b,112c,112d,112e,112f) is turning in the operating range of the flow regulator, at least a part of the flow surface of the regulating member is left in the shadow of the flow surface of the regulating member as viewed at right angles to the direction of flow of the gaseous substance and the turning shaft (13) . 5. A flow regulator for gaseous substances, particularly for air in air-conditioning and ventilation installations, for maintaining the volumetric flow rate of the gaseous substance at desired magnitude with sufficient accuracy when the differential pressure (ΔP) acting across the flow regulator (10) varies within given limits, said flow regulator (10) comprising an envelope (11) and a regulating member (12) turnably disposed in a flow passage confined by the envelope (11), said member turning with increasing differential pressure progressively crosswise with reference to the direction of flow, whereby the torque produced by the gaseous substance on the flow regulating member (12) and on the other hand a countertorque dependent on ' the position of the regulating member (12) cause the regulating member (12) turning in the flow passage to assume an equilibrium position such that the requisite pressure drop for maintaining the volumetric flow at pre-selected magnitude is achieved, characterized in that as the regulating member (12, 112a,112b,112c,112d,112e,112f) is turning in the operating range of the flow regulator, at least a part of one of the two halves of the flow surface of the regulating member with reference to the turning shaft (13) is left in the shadow of the flow surface of the opposite half of the regulating member, as viewed at right angles against the direction of flow of the gaseous substance and the turning shaft (13). 6. A flow regulator according to any one of claims 1-5, character¬ ized in that the flow passage is free from any fixed elements causing substantial throttling. 7. A flow regulator according to any one of claims 1-6, character¬ ized in that the regulating member (12,112a,112b,112c,112d,112e, 112f) is a slightly curved plate. 8. A flow regulator according to any one of claims 1-7, character¬ ized in that the turning angle (.φ , ,φ 2 between the initial and ultimate positions of the regulating member (12) is substantially of the same magnitude at volumetric flows of different magnitudes as the differential pressure range is the same. 9. A flow regulator according to any one of claims 1-8, character¬ ized in that the initial and ultimate positions of the regulating member (12) are dependent on the magnitude of the volumetric flow when the differential pressure range is the same. 10. A flow regulator according to any one of claims 1-9, character¬ ized in that the flow regulator (10) is provided with adjustable and/or self-adjusting limiters (26a,26b) for limiting the differential pressure range of the flow regulator, said limiting members (26a,26b) being disposed to limit the turning movement of the regulating member (12). 11. A flow regulator according to any one of claims 1-10, charac- terized in that the range of operation of the flow regulator (10) is changeable by changing the effective flow aperture (37) between the regulating member (12) and the flow passage. 12. A flow regulator according to any one of claims 1-11, charac- terized in that the operating range of the flow regulator (10) is changeable by the aid of a shiftable mass (13) producing a counter¬ torque dependent on the position of the regulating member (12) . < SRE OMPI ^V„ TPO

Inventors: AALTO ERKKI, YLAE-HEMMILAE VEIKKO, AALTO, ERKKI, YLAE-HEMMILAE, VEIKKO
Applicants: HALTON OY
Application year: 1984
Main classification: F24F11
IPC codes: F16K1, F24F11, F24F13, G05D7