ADJUSTABLE VOLUME FLOW REGULATOR

Abstract

 Adjusting elements (4) of the regulator with multiple valves (1) are mutually coupled, preferably they are coupled by the mechanical draw rod (12) with a lock (14). The axes of the valves (1) are placed in a single plane which is perpendicular to the direction of the fluid's flow. The regulation spaces of individual valves (1) are separated by the partition (8) which is placed between the neighboring valves (1). In the preferable arrangement the valves (1) and the adjusting mechanisms (16) of all valves (1) are the same. The valve (1) of the regulator has the adjusting mechanism (16) which includes a valve's (1) lever (2), a spring (3), a damper (5) and the adjusting element (4) for the change of the spring's (3) prestress. The spring (3) connected with the adjusting element (4) acts upon the valve's (1) lever (2). The arm (7) of the damper (5) has a curved groove (9). The groove's (9) shape is comprised of two continuous sections, where the first section of the groove (9) is led by straight line, while the second section is curved.

Description

Field of technology

[0001] The invention concerns a regulator of flow of fluids with multiple regulation valves, mainly for regulation of a flow of air in the ventilation elements, systems and distributions. The regulation valves regulate the flow together with the setting mechanism; the regulator keeps the set flow of the liquid in the broad adjustable scope and with high precision. The invention allows for modular construction suitable for large flow cross-sections, too.

Prior state of the art

[0002] In air distributions various flow regulators with one or many closable or regulation valves are used. Use of multiple valves bring and advantage of smalle dimensions and smaller weight of a single valve and also smaller rotational moment of inertia of individual valves as well as rotational moment of inertia of all valves together. The use of multiple closable valves in case of ending outlets has aesthetic reasons, too, where multiple similar closable valves appears more pleasurable to the eye; it has a look of blinds and therefore it is used with smaller cross-sections of ventilation pipes, too. In case of larger rectangular pipes two are more regulation valves of square or rectangular shape can be used, which together in synergy regulate the flow of the air in the distribution, whereby it is not neccesary to use large and difficult to control regulation valve with large inertia.

[0003] Various mechanical connections of mulitple closable and/or regulation valves are known in the prior state of the art, whose axes of rotation are placed in a single plane, whereby the rotation of the valves is synchronized by means of the gearing or by means of levers, common draw rod and so on. The angles of rotation of individual valves in a given group are basically the same; or they are the same if we disregard the gap in the control mechanism of the valves.

[0004] In order to set the correct angle of the regulation valve with regulators of the constant flow, the electronic control systems can be used, where the assessment of the pressure gathers the actual flow and subsequently control the rotation of the regulation valve (publication EP1980798A2, SK UV 8137). More often, the mechanically regulated regulation valves are used, which are simple, cheap and do not require a source of energy.

[0005] The flat blade of the valve of the mechanical regulator is shaped in such a way that the first side of the valve creates different force moment as the other side of the valve. The resulting difference in moments during the flow of fluid is in balance with the strength of the spring which has adjustable prestress (publications DE10222673C1, DE20214414U1, FR1313310A, SK U3174). The prestress sets the desired flow. In order to achieve a reliable function of the regulator, a damper is part of the mechanism, which prevents the vibration of the valve with the spring.

[0006] Solutions pursuant to EP 1318359 A2, GB1269277A use pneumatic linear damper which, however, proved to be unsuitable in multiple regimes, the system is prone to vibrations and hysteresis, where the actual flow is dependent on whether the entry pressure decreases or rises, to which the valve reacts by opening or closing. The publication DE102010038150A1 discloses a rotational damper which through the gearing acts upon the valve. The damping is similar with various angles of rotation of the valve, which causes regulation problems. The mechanism pursuant to publication EP 2940396 A1 has many components and it lacks the damping of the movement of the valve.

[0007] The published patent file EP 3244134 uses a varying level of damping, where the changeable gearing between the valve's lever and the rotationl damper is used by means of the placement of the damper on the holder, which moves pursuant to the desired flow. The solution according to publication SK U7733 discloses nonlinear acting of the spring and the damper in the adjusting mechanism of the valve. With increased flow cross-section the dimension of the valve rises, too, and this causes the problems with a regulation stability and accuracy.

[0008] Such solution of the regulator is desired, which will keep the set flow of the fluid, mainly air with various pressure conditions at the entry, which will prevent the valve or valves, respectively, from vibrating - which is the common cause of the instability of the flow in the distribution. New solution should bring about the increased precision of the regulation and increased scope mainly for the larger flow cross-section of the distribution.

Essence of the invention

[0009] The invention is defined in claims 1 to 15. The deficiencies in the state of art are significantly remedied by the adjusting regulator of the flow of the fluids, mainly flow of the air in the ventilation elements at larger flow cross-sections, where the regulator has a channel for the flow of the fluid, whereby the regulation is achieved by means of the valve tiltably placed in the body of the channel; the valve is connected with the adjusting mechanism placed outside the inside of the channel; and where the adjusting mechanism includes a spring and a damper which act upon the valve according to this invention which essence lies in the fact that the regulator has in the channel's body tiltably placed at least two regulation valves; each valve has its own adjusting mechanism placed outside the inside of the channel; each adjusting mechanism includes a lever of the valve, a spring, a damper and an adjusting element for the adjustement of the prestress of the spring, where the spring connected with the adjusting element acts upon the valve's lever, and where the damper is connected with the valve's lever, whereby the adjusting elements of all adjusting mechanisms of the valves are mutually mechanically coupled in order to achieve a similar position of adjustment.

[0010] An important feature of the proposed invention with multiple valves is the indirect regulation coupling of the regulation valves, the angular position of the valves is not directly connected, but each valve has its own adjusting mechanism and only the controls of the adjusting mechanisms are connected. The change in deviation of one valve is not transferred to the deviation of the other valve, but such deviation is regulated within the respective adjusting mechanism. The adjusting elements will usually be coupled in such a way that they alive have identical value of the adjustment, that is, identical value of the prestress of the spring for the valve. Such arrangement will in preferable arrangement involve identical regulation valves and identical adjusting mechanisms of each valve. The channel in such adjustment will be separated to parts with similar cross-sections and similar valves.

[0011] The term "identical/similar" in this file denotes the elements with a similar characteristic or functionality; tiny deviations, mainly due to the production or installation allowances, are not important and are not to mean the deviation from the essence of this invention.

[0012] The advantage of the proposed invention is the easy construction of the regulator with the larger flow cross-section, mainly with rectangular cross-section, into which two or more regulation valves are placed, preferably with the parallel axes of rotation in the plane which is perpendicular to the direction of the flow of the fluid. An own adjusting mechanism is attached ot each valve. If the valves are similar, which will be the most common arrangement, each valve will have similar adjusting mechanism with similar spring and similar damper.

[0013] Use of multiple valves in a single regulator separates the respective flow cross-section to multiple zones with independently regulated valves, thanks to which the valves react independently to the irregularly running and dissimilar states within the flow cross-section. The flows are regulated independently for the zones of individual valves, which achieves the stable summary flow of the whole regulator.

[0014] In case of regulators with a single regulation valve the adjusting element has a lock of the position which sets the desired flow of the fluid, or it has a motorized position control which can remotely alter the desired flow. The adjusting element forms a support for one end of the spring; the other end of the spring is connected with the valve's lever. After the manual or motorized setting of the position the adjusting element fors a firm support for the spring. A lock of the adjusting element or the self-lock of the motorized control element in the non-active position serves this point. In the proposed invention the individual adjusting elements lack their own lock but it is preferrable if that element which achieves the common coupling of the adjusting elements has a lock. A solution is also possible where the own lock is left with a single adjusting element and other adjusting elements lack the lock, or are carried or blocked by the adjusting element which has the lock.

[0015] If the adjusting elements are produced as rotational, the coupling can be created by a draw rod which connects the rotation of all adjusting elements. In another case it can be a coupling by means of a chain drive, wires, gear wheels, toothed belt, and so on. The position of a draw rod can be simply lockped by the screw connection which rauns through the longitudional groove. The screw connection connects the draw rod with the firm support which is connected, for example, with the body of the channel or with the basic plate of a single adjusting mechanism.

[0016] The lock of the desired position of the draw rod or a single adjusting element can be solved by means of a screw which forms a friction joint of the draw rod, or by adjusting element with a base plate or a casing which is connected with the base plate. The casing can also create a support for the rotational or tiltable placement of some element or multiple elements of the setting mechanism. The outer surface of the casing can have connecting elements or at least connecting guiding for mounting of the motorized action mamber by which one can change the position of the adjusting element pursuant to the instructions from the superior system. The regulation of the constant flow itself is in the regulator ensured by the mechanical arrangement according to this invention, but the change of the desired flow can be controlled remotely.

[0017] From the point of view of accuracy of regulation a solution proved preferable where the functional spaces of individual regulation valves are separated by a partition, where the partition is parallel with the axis of the rotation of the valves and it is parallel with the direction of the flow of the fluid. The partition is placed between the neighboring valves. With two valves a single partition is used; with three valves two partitions are used. The partition forms in the body of the channel two independent regulation zones for each regulation valve. The partition's dimension in the direction of flow is identical as or larger than the height of the valve, that is, the dimension of the valve led perpendicularly to the axis of its rotation.

[0018] With the presumed laminar flow before the entry to the channel of the regulator, the conditions of flow should theoretically be identical in each regulation zone. In reality, uneven distribution of the flowing fluid to the regulation zones separated by the partitions takes place. In the solution according to this invention the flow is even out in individual regulation zones, since the valves in these zones are regulated independently and they are not mechanically directly coupled. Thanks to this such total flow in the channel is achieved, which is the multiple of individual flows in the individual regulation zones pursuant to the number of valves. The denotation of the adjusted flow, for example in case of draw rod, can directly express the summary flow of the whole channel of the regulator.

[0019] Multiple use of a single adjusting mechanism within a single regulator allows to modularly produced variously large regulators. Pursuant to the desired flow or dimension of the pipe a respective number of the valves is chosen and the body of the channel is partitioned by the partitions so that the regulation zones for the individual valves are produced.

[0020] A flat board place just behind the axis of the valve in the direction of the fluid's flow has positive effect on the increase the repeated accuracy of the resultion flow. The board prevents the turbulences behind the regulation valve's blade. The board is oriented in the direction of the flow in the channel of the regulator and has a length which is at least half the height of the regulation valve, preferably the leght corresponds to the height of the regulation valve. The board can have a lock for the maximally open valve. In case the board is produced from the sheet metal, the lock can be produced as an overpress (embossment) with the sufficient height. The lock of the opposite position for the maximally closed valve can be on the inner sheath of the body of the channel, for example simply in form of the protruding shank of the blind rivet.

[0021] The board behind the valve separates the flows of the fluid which arise behind the valve from its dissimilarly sloped sides of the blade; it prevents the mixing of these flows just behind the valve. It is preferable if the board is placed in such a way that its front edge is placed just behind the axis of the rotation of the valve with the gap necessary for the smooth rotation of the valve, whereby the board is parallel with the direction of flow and it separates the place behind the valve to the identically large spaces. The rear edge of the board can have straight or rounded course in the groundplan. Preferably, the board will be produced from the sheet metal, the rounded edges will be riveted to the inner surface of the channel's sheath. In case of larger cross-sections of the channel of the regulator the board can have a fold formed in the vicinity of the valve's placement. The strenghtening fold can be part of the height shoulder of the board, which simplifies the approachement of the front edge of the board to the shaft of the valve during the placement of the board in the middle of the regulator's pipeline.

[0022] In order to limit the effects of various mounting position of the regulator on the accuracy of the regulation of the constant flow, it is preferable if the valve together with the lever is balanced or at least statically balanced against the axis of the rotation. Since the blade of the valve with the regulator according to this invention is bent or offset, the valve has a tendency to descend, rotate into one position, in order to achieve a different force moment on both sides of the valve. This affects the regulation moment acting upon the valve. If, however, the valve together with the connected lever is balanced in such a way that with varying positions and orientation there is no additional moment operating in a single direction of the rotation of the valve, the regulator can be used in any position. In order to balance the valve a matter of some of the valve's components can be preferably used; preferably, for example, the enlarged parts of the connecting element - connecting the valve's shaft with the valve's blade - will be used. For example, the increased head of the screw or blind closed matrix have a weight acting on the side opposite to the bending of the valve's blade. The static balancing of the valve together with the nonlinearly acting damping increase the accuracy of the desired constant flow.

[0023] Aerodynamically proved preferable and, at the same time, constructionally simpler a solution where the valve's blade lacks shaped embossing for the insertion of the shaft, axis, but it is simply flatly screwed to the shaft by means of at least two flat head screws. The screws have transition openings through which the valve's shaft runs. The matrices can be used as a balancing matter, preferably the closed matrices with the blind opening will be used. The flat heads of the screws are oriented to the side to which the valve's blade is bent; on the opposite side runs the shaft and the matrices.

[0024] In order to decrease the vibration of the valve which lowers the accuracy of the flow's regulation, an adjusting mechanism has a rotational damper which has a rotational arm connected with the valve's lever, whereby the damper is placed on the tiltably placed holder. The holder rotates around the axis in order to achieve varying position of the damper against the axis of the valve's lever, which achieves different transmission ratio between the rotation of the valve's lever and rotation of the damper. During such arrangement the rotational damper of the vibration with the arm is used; the damper is in the adjusting mechanism active only in certain angular scope; its ability of unlimited rotation is not used wholly. Thanks to the arm and the adjustable position of the holderer with the damper a varying transmission ratio between the valve and the rotational damper can be achieved.

[0025] The adjustable (changeable) transmission ration between the rotation of the valve and the rotation of the damper allows to suitable choose the size of damping at varying adjustment of the spring's prestress; that means that varying damping effect is achieved with variously set flows of the regulator.

[0026] In order to achieve a change of the position of the damper and in order to ensure the kinematic connection of the valve and the damper, the valve's lever or the arm of the damper have a radially oriented groove into which a pin - firmly attached on the second member of the gear - falls. The pin moves in the groove during the change of the position of the damper, which changes the ratio of the semi-diameters of the valve's lever and damper's arm. From the point of view of simple construction it is preferable if the pin is firmly fixed in the valve's lever and the groove is produced on the damper's arm. The pin falls into the groove in the damper's arm; the pin during the rotation in the direction of the tangent acts upon the arm, and in this direction the pin has only the necessary gap; in this way the angular change of the valve's position is transferred to the change of the angle of the rotational damper. The applicant has already described such an arrangement in his published application EP3244134 A1.

[0027] The adjusting mechanism has a valve's lever and a spring with the adjustable prestress, where the spring acts against the direction of the moment induced on the valve by the fluid during its flow through the channel. The adjusting mechanism has an adjusting element for the change of the spring's prestress. The adjusting mechanism has a damper and damper's holder. The damper has an arm which is connected with the valve's lever for the transfer of the angular changes of the valve to the damper. The damper is placed on the holder which is movably, preferably rotationally placed in the adjusting mechanism in such a way that the varying position of the damper against the position of the valve's axis is achieved for varying setting of the flow, which achieves various transmission ration between the valve's rotation and the rotation of the rotational damper. Such adjustable transmission ration between the valve's rotation and the rotation of the damper can be achieved in such a way that the arm of the damper has a gate (coulisse) with a radially oriented groove into which the pin protruding from the valve's lever falls.

[0028] The possibilities of the choices of damping of the regulation valve (throttle) can be imporved in such a way that the damper's arm does not have a radially oriented straight groove, but curved groove. The choice of the shape of the groove allows to more precisely refine the transmission ratio between the rotation of the valve and the rotation of the rotational damper in the actual position of the adjusting element. The shape of the groove can be designed in such a way that the gradual measurement of during variously set flows a necessary correction of the damping effect is found out and subsequently this correction is counted in terms of moving of the position of the pin on the valve's lever against the position of the damper's arm. The position of the pin on the valve's lever is stable, the necessary correction is done through the change of the groove in the damper's arm. The gathering of the data during multiple measurements provides us with an inde of the necessary curvature, deviation or angular rotation of the groove in the damper's arm. The curved groove in the arm creates a closed coulisse or open curved fork.

[0029] It appeared that the use of the damper's arm with a curved groove synergistically acts with the coupling of the adjusting mechanisms with multiple valves. The regulation of a single valve and changes in its deviation in a single regulation zone have a feedback effect on the actual pressure and flow before the valve in the neighboring regulation zones. The closing of a single valve within the function of a respective adjusting mechanism causes an increase of a pressure in the other regulation zones, to which the adjusting mechanisms of the respective valves must react. It is the use of independent adjusting mechanisms with their own nonlinear damping which leads to high stability of the flow even with changing flows at the entry of the regulator.

[0030] A shape of the groove proved preferable, which consists of two continuous sections. The first section of the groove is during the rotation of the arm led by straight line which is sloped against the radial line at least by 15°, preferably 22° to 23°. The straight line starts at point A which is the initial middle point of the groove on the side by the axis of the rotation of the arm, and which is present on the radial line, and continuous to the point B which is outside the radial line and it is a middle point of the groove at the end of the straight line. The radial line runs through the axis of the rotation of the arm and the point A. The second section of the groove is led by the curvature which continues from the point B to the point C which lies away from the radial line, whereby the point C is against the radial line in the opposite semiplane as is the poin B, and whereby it forms a middle point of the ending of the groove on the side opposite to the axis of the arm's rotation. The curvature can be part of the circle, ellipsis, hyperbole or it can have another basically continuous character.

[0031] In order to achieve a smooth movement of the pin in the groove, a cylindrical ring or a bearing can be mounted on the pin, thanks to which the friction between the groove and the pin decreases. The cylindrical ring or bearing rotates on the pin and rolls on the edge of the groove.

[0032] The holder of the damper can be arranged in such a way that at some of its positions, for example in a position with the maximum flow, the transmission ration between rotation of the valve and the rotation of the rotational damper close to 1:1. The holder can in such arrangement be place in such a way that in the said extreme position the axis of the damper is close to the axis of the placement of the valve or in the axis of the placement of the valve. The valve's lever acst on the damper's arm by means of a pin.

[0033] The geometry of the kinematic relationship between the damper with the arm with the curved groove and between the valve's lever also causes that the transmission ration, that is, the angular transmission between the rotation of the valve and the rotation of the damper is changed even if the position of the holder with the damper stays the same. This change of the transmission ratio is smaller than the change of the transmission ratio caused by eventual change of the position of the damper against the axis of the valve's rotation and this follows from the use of the lever gear and from the use of the curved groove. If the holder with the damper is placed in such a way that its axis of rotation gets closer to the axis of rotation (tilting) of the valve, the lever gear from the valve to the will create a transmission ratio 1:1; the lever and the arm will form a coupled crank. During the deviation from the coaxial position what changes is not only the transmission ratio changed by the change of the damper's position, but during the change of the valve's rotation an effective ration of the lever and the arm changes, too. This arrangement ensures a nonlinear course of the damping with use of a simple rotational damper and with basically constant course of the damping.

[0034] Desired nonlinearity of the damping or damping's hysteresis, respectively, can be eventually achieved or affected by the choice of the pin's gap in the arm's groove. The pin can have a small gap sufficient for the smooth operation of the gear, but intentional increase of the gap by setting of larger breadth of the groove in a given place of the groove can ensure desired course of the damping in a given coposition of the valve and the holder of the damper.

[0035] Various dimensional and spatial arrangements and placements of the holder with the damper against the valve's lever or against the axis of the lever, respectively, and various courses of the groove allow one to achieve varying course of the damping depending on the angular position of the valve and on the setting of the holder of the damper. A holder of the damper has been invented as reliable and simple for construction, which is rotationally or tiltably, respectively, placed in such a way that the circle or its part, respectively, which discloses possible points in the axis of rotation of the damper at various positions of the damper, runs through the axis of the valve or in the vicinity of its axis, respectively. It can be an extreme position corresponding to the maximally set flow of the regulator. When the desired flow diminishes, the holder with the damper is rotated in such a way that the axis of the damper distances itself alongside the circle from the axis of the valve's rotation.

[0036] It is preferable if the adjusting element for the change of the prestress of the spring is connected by the gear with the damper's holder. In a preferable arrangement of the regultor a linearly acting draw spring is used, which is on one end connected to the valve's lever and on the other end it is connected to the adjusting element. The adjusting element alters the spring's prestress, it has a lock of the set position and preferably it has a display, too, or the scale of adjustment, respectively. In order to produce kinematic bind between the adjusting element and the holder of the damper a toothing can be used or - which proved to be preferable during inventing - a simple lever gear. For example, on the circumference of the rotationally adjusting element is a stud (stub, journal) which acts in the opening or in the groove on the holder of the damper. The holder of the damper is placed tiltably and during the adjusting of the desired position of the adjusting element the angular rotation of the damper's holder changes, too, and this changes also the position of the damper against the axis of the rotation of the valve. The change of the setting of the spring's prestress is by this coupled with the necessary change in the damper's position.

[0037] A base plate attached from the outer side of the channel's body is preferably used for the placement of the holder with the damper and the adjusting element with the spring. Between the body of the channel and the plate an insulation is inserted in order to reduce the transfer of the heat and noise.

[0038] The proposed invention by its simple, operationally reliable construction allows modularly design and produce regulators which supress the undesired vibrations, lower the hysteresis when the entry conditions change, mainly during the decrease or increase of the entry air pressure. The described invention ensures reliable regulation of the constant flow of the fluid even in cases of larger cross-sections. The adjusted flow is maintained with desired accuracy when the pressure decreases or increases on the entry side of the regulator, too, and the reaction of the valve to the changing entry pressure is quick and without vibration tail. The advantage is also its simple and reliable construction when the adjusting mechanisms tested for the smaller cross-sections are used. Nonlinear acting of the spring and the damper ensures repeatedly accurate maintaining of the set flow without problems with the hysteresis of the system and it prevents vibrations. Adjusting mechanism is adaptable for a broad scope of the cross-sections of the regulator; the independent valves can adapt to the changes of the entry pressure conditions independently for the conditions in their environment.

Description of drawings

[0039] The invention is further disclosed by means of drawings 1 to 14. The depicted construction details are an example only; they cannot be interpreted as features limiting the scope of protection.

Figure 1 is a view of the channel with two valves and two adjusting mechanisms on the outer side of the channel. The valves and the partition inside the channel are depicted by the dashed line.

Figure 2 is a simplified view of the channel with two valves and one partition between them from inside. The boards are placed beyond the valves. The arrows depict the direction of air flow in the regulation zones of the regulator.
On the figures 3 and 4 the kinematic scheme of the coupling of two adjusting mechanisms of the regulator in various positions is depicted. For the purposes of clarity, the holder of the damper is moved on these figures in such a way that in the groundplan it does not cover the valve's lever. Both valves and the partition are inside the channel and they are depicted by dashed lines.

Figure 3 depicts a position with the adjusting elements close to the minimal position of the flow, for example in position "1" from the ten degree scale, whereby both valves have approximately similar angular position. Subsequently, figure 4 depicts identical setting, but both valves have a different angular position, which documents the operation of the adjusting mechanisms themselves, which are coupled by the adjusting elements but which regulate the position of the valves autonomously.

Figure 5 is a view of the coupling of the adjusting elements by means of the draw rod with the lock; both adjusting mechanisms are the same and they are in position "4".

Figures 6 and 7 depicts the kinematic scheme of the adjusting mechanism at the same position of the adjusting element, whereby the actual angular position of the valve differs and thereby the place of the acting of the lever on the arm in the curved groove differs, too. For the purposes of clarity, the holder of the damper is moved on these figures in such a way that in the groundplan it does not cover the valve's lever. The valve is inside the channel and it is depicted by dashed line.

Figures 8 and 9 depicts the adjusting mechanism after the casing is removed, whereby on both figures the holder of the damper is disclosed as transparent by the dashed line. On figure 8 the holder of the damper is in the position of low flow.

Figure 9 is a view of the detail of cooperation of the lever with the pin and the arm with the curved groove.

Figures 10 and 11 depict the results of the measurements of accuracy of a give flow and they depict the deviation from the set desired flow at varying air pressure at the entry of the regulator. The figure 10 holds for the state of the art with the straight groove in the arm; the figure 11 holds for the curved groove according to this invention.

Figure 12 depicts the placement of the board in the vicinity of the valve's shaft.

Figure 13 depicts a detail of the connection of the valve to the rotationally placed shaft, where the robust matrix produces a balancing matter.

Figure 14 is a detail of the arm with the curved groove where points A, B, C are depicted in a line on which the pin can move. The angle α presents a deviation of the first section of the groove from the radial line which is denoted by letter "r". The point A is a starting point of the straight line, the point B is a connecting point of the straight line to the curvature which ends in point C.

Examples of realization

Example 1

[0040] In this example according to figures 1 to 9, 11 to 14 the body of the regulator's channel is formed by the metal sheet pipe with the rectangular cross-section with dimensions 400 mm x 500 mm. The channel is produced from the galvanized sheet and on the ends it has connecting flanges designed fro the connection of the pipe of the air distribution.

[0041] On the opposite side walls of the channel are two identical valves 1 from the aluminimu sheet mounted on the plastic casings. The blade of each valve 1 has rectangular groundplant. A partition 8 is riveted between the valves 1; the partition 8 separates the channel to two similar regulation zones. The valve's 1 blade is produced as a smooth, without embossment for the insertion of the shaft. The shaft is connected with the valve's 1 blade with two screws 15; the matrices of these screws 15 create a balancing matter. The screws 15 have a flat head and the transversal opening for the shaft. The tightening of the matrix pushes the shaft into the valve's 1 blade, which leans onto the flat head of the screw 15 and the blade is reliably led even without the production of embossment. The valve's 1 blade is bent in such a way that the lower and upper part of the blade in this example are bent approximately for 14°.

[0042] Behind the valves 1, and in the direction of air flow, the boards 13 from the galvanized sheet are riveted, which separate the space behind the valves 1 and thereby separate the air flows flowing alongside the valves 1. The boards 13 are oriented in parallel with the direction of the air flow and they can carry stops of the valve 1 in its most open position.

[0043] The valve's 1 shaft ruhs, on the side with the adjusting mechanism 16, out from the side wall, where it runs through the opening in the base plate of the adjusting mechanism 16. On the end of the shaft of the valve 1 a double-arm lever 2 is mounted. A spring 3 is attached to one of the lever's 2 arm. A pin 10 is pressed on the other arm of the lever 2. On the base plate a holder 6 of a damper 5 is tiltably placed. The holder 6 is produced by bending of the metal sheet cut-out and it has a function of the double-arm lever. On one side the damper 5 is mounted in the holder 6, on the other side the holder 6 has a fork. The rotational damper 5 is inserted in the opening of the holder 6 and kept there by rivets. On the axis of the damper 5 a plastic arm 7 is mounted. The arm 7 has a groove 9 into which the pin 10 from the lever 2 falls. In this example a cylindrical ring if mounted on the pin 10; this ring diminishes the friction between the groove's 9 coulisse; during the movement of the pin 10 in the groove 9 the ring rotates on the pin 10 and rolls on the groove's 9 edge.

[0044] The adjusting element 4 for the adjustment of the prestress of the spring 3 is a plastic pressing with a scale on the circular arc. The adjusting element 4 has a foursquare opening in its axis of rotation, whereby a short foursquare rod on which the levelr with the stud is mounted is inserted into this opening. The studs on the levers connected to both adjusting element 4 are connected with the draw rod 12 which achieves the coupling of the adjusting mechanisms to the same regulation position. In the draw rod 12 a longitudinal groove is produced, through which a screw of the lock 14 runs. This screw ensures the set position of both adjusting elements 4.

[0045] Inside the adjusting mechanism 16 the axis of the adjusting element 4 is rotationally mounted, in the opening of the base plate and in the opposite opening in the casing. The adjusting element 4 has first, longer arm on whose end there are two openings for the connection of the spring 3. In the casing there is a window to determine the adjusted position from the scale on the adjusting element 4. The second, short arm on the pressing of the adjusting element 4 is ented by the stud 11 which falls into the fork in the damper's 5 holder 6. During the rotation of the adjusting element 4 the prestress of the spring 3 changes and, at the same time, the stud 11 rotates the holder 6 through the fork.

[0046] The air led to the regulator's entry rotates the valve 1 pursuant to the size of the entry pressure. The changes in pressure lead to the change of the valve's 1 position. The increasing air pressure at the entry gradually closes the valve 1.

[0047] Even in case that the air led to the regulator's entry is distributed unevenly between the regulation zones separated by the partition 8, the correct operation of the regulator occurs since each of the valves 1 is controlled by its own adjusting mechanism.

Example 2

[0048] In this example according to figures 6 to 9, 11 to 14 the regulator's body is formed by the piece of the circular steel galvanized pipe with the sealings on the ends, which are designed for connection to the air distribution pipe. In the pipe a valve 1 from the aluminium sheet is mounted on the plastic casings. The valve's 1 blade has circular groundplan. The shaft is connected with the valve's 1 blade by two screws 15; the matrices of these screws 15 produce a balancing matter.

[0049] Behind the valve 1 and in the direction of air flow a board 13 from the galvanized sheet is riveted, which separates the space behind the valve 1 and thereby separates the air flows flowing alongside the valve's 1 walls. The board 13 is oriented in parallel with the direction of the air flow; on the board 13 there are two rubber stops for the maximally open valve 1.

[0050] The valve's 1 shaft on the side with the adjusting mechanism 16 runs outside the pipe, where it runs through the opening in the base plate. The base plate carries the adjusting mechanism 16 and the casing. The base plate in this example is screwed to the pipe by the self-drilling screws; a foam isolation is placed between the base plate and the outer surface of the pipe.

[0051] At the end of the valve's 1 shaft a double-arm lever 2 is mounted. On the one arm of the lever 2 there is a system of openings for the connection of the spring 3. On the other arm of the lever 2 a steel pin 10 is pressed in. On the base plate a damper's 5 holder 6 is freely placed. The holder 6 is produced by bending of the metal sheet cut-out and it has a function of the double-arm lever. The rotational damper 5 is placed inside the opening in the holder 6 a kept by the rivet. On the axis of the damper 5 a plastic arm 7 is mounted, which has a groove 9 into which the pin 10 from the lever 2 falls.

[0052] The shape of the groove 9 consists of two continuous sections. The first section of the groove 9 at the axis of the arm's 7 rotation is led by straight line which is sloped away from radiali line r; in this example it is sloped from the radial line r by angle α = 22,7°. The straight line begins in point A which is the beginning middle point of the groove 9 on the side by the axis of arm's 7 rotation, and which is present on the radial line r and continues to the point B which is outside the radial line r and which is a middle point of the groove 9 on the end of the straight line. The radial line r runs through the axis of rotation of the arm 7 and through the point A. The second section of the groove 9 is led by curvature which from the point B continuous to the point C which lies outside the radial line r, whereby the point C is against the radial line r in the opposite half-plane as a point B, and it forms the middle point of the end of the groove 9 on the side opposite to the axis of the arm's 7 rotation. The curvature can be part of circle, ellipsis or hyperbole, or it can have other but basically continuous character. The combination of straight line and curvature is a line of the middle of the groove 9. therefore the pin 10 from the lever 2 will move on this line. The groove's 9 shape is thus an envelope of the circle with the diameter of the pin 10 during the movement on the line, which is composed of the straight line and the curvature.

[0053] Thanks to the abovementioned curvature of the groove 9 the repeated accuracy of the actual flow with the set flow has increased.

[0054] The assessment of the deviation pursuant to EN 12589:2001 (E):

	groove in the prior state of the art			curved groove 9 from the example
Δp scope (Pa)	qv scope (m3/h)	qv (m3/h)	±Δpv (%)	qv scope (m3/h)	qv (m3/h)	±Δpv (%)
60 ÷ 1000	321 ÷ 426	373,8	14,1	323 ÷ 390	356,3	9,3
100 ÷ 1000	336 ÷ 426	381,0	11,9	323 ÷ 390	356,5	9,3
150 ÷ 1000	341 ÷ 426	383,6	11,1	323 ÷ 390	356,5	9,3
200 ÷ 1000	341 ÷ 426	383,6	11,1	321 ÷ 390	355,1	9,7
250 ÷ 1000	345 ÷ 426	385,6	10,5	326 ÷ 390	357,7	8,9
50 ÷ 1000	314 ÷ 426	370,2	15,1	319 ÷ 385	352,1	9,3

[0055] The comparison of the basic characteristics shows smaller standard. In the first column there are values for arm with the straight groove pursuant to the state of art; in the second column are values for the arm 7 with the curved groove 9 according to this example.

min qv (≈ 1000 Pa)	321,2 m3/h	323,1 m3/h
min qv (≈ 60 Pa)	426,3 m3/h	389,6 m3/h
mean value	378,8 m3/h	358,0 m3/h
mean value from the range	378,8 m3/h	356,3 m3/h
standard deviation	± 32,0 m3/h	± 21,0 m3/h

[0056] The adjsuting element 4 for the adjusting of the prestress of the spring 3 is a plastic pressing with the scale on the circular arc. The axis of the adjusting element 4 has a foursquare opening for the insertion of the control tool or for the connection with the output of the controlling servomotor or for the coupling with the other adjusting mechanisms 16.

[0057] The axis of the adjusting elment 4 is rotationally mounted in the opening of the base plate and in the opposite opening in the casing. The adjusting element 4 has first, longer arm on whose end it has two openings for the attachment of the spring 3. On the first arm the matrix is pressed into which the lock's screw enters. The lock's screw connects the adjusting element 4 with the casing by means of a friction joint, whereby in the casing a groove 9 is led arc-like and there is also an opening for the determination of the set popsition on the basis of scale in the adjusting element 4. The casing in this example of realization transfers the force from the adjusting element and from the spring and it is thus produced as a sufficiently strong pressing with a guiding for the accurate locking into the bent edges of the base plate.

[0058] The second, shorter arm on the pressing of the adjusting element 4 is ended by the stud 11 which falls into the fork in the holder 6 of the damper 5. During the rotation of the adjusting element 4 the prestress of the spring 3 changes and at the same time the stud 11 rotates the holder 6 through the fork. During the rotation of the adjusting element 4 towards the smaller values of flow the damper 5 distances itself from the valve's 1 axis, which changes the transmission ration between the valve 1 and the damper 5, too; the damper 5 now acts against the changes in valve's 1 position with a smaller damping effect.

Example 3

[0059] In this example the regulator has three regulation zones with three valves 1 and two partitions 8 in the channel's body.

[0060] A servomotor is attached to the casing of one adjusting mechanism 16; the servomotor's output shaft with the foursquare cross-section falls into the opening in the adjusting element 4. For the simple connection of the servomotor there is a connecting element pressed on the casing. The servomotor changes the gear of the adjusting element 4 pursuant to the instructions from the central system of control in a building. Thanks to tw draw rod 12 the first, second and third adjusting mechanisms 16 are coupled in order to achieve the same position of the adjusting element 4. The regulation of the rotation of the three valves 1 itself is further controlled by the mechanism, without electronic circuits as in example 1.

Industrial applicability

[0061] The industrial applicability is obvious. According to this invention it is possible to industrially and repeatedly produce and use a regulator of the flow of fluids with multiple valves, mainly for the regulation of the flow of air in the air distribution elements, for example in climatization, ventilation or heating systems or in the distributions, whereby it is posssible to produce various sizes of the regulator modularly.

List of symbols

[0062] 

1

- valve

2

- valve's lever

3

- spring

4

- adjusting element

5

- damper

6

- damper's holder

7

- arm

8

- partition

9

- groove

10

- pin

11

- stud

12

- draw rod

13

- board

14

- lock

15

- screw

16

- adjusting mechanism

r

- radial line

α

- angle

A

- starting point of the straight line

B

- point of connection of the straight line and curvature

C

- end point of curvature

Claims

1. An adjustable regulator of a flow of fluids, mainly for the air flow into air distribution systems, where the regulator has a channel for the fluid's flow, whereby a regulation is achieved by throttling by means of a valve (1) tiltably placed inside the channel; the valve (1) is connected with an adjusting mechanism (16) placed outside the channel's inside; and where the adjusting mechanism (16) includes a lever (2) of the valve (1), a spring (3), a damper (5), and an adjusting element (4) for a change of a prestress of the spring (3), whereby the spring (3) and the damper (5) are connected by a lever (2),
is characterized by the fact, that
in the channel's body there are tiltably placed at least two regulation valves (1), each valve (1) has its own adjusting mechanism (16) placed outside the channel's inside;
each adjusting mechanism (16) includes the valve's (1) lever (2), the spring (3), the damper (5) and the adjsuting element (4) for the change of the prestress of the spring (3),
whereby the adjusting elements (4) of all the adjusting mechanisms (16) of the valves (1) are mutually coupled.

2. The adjustable regulator of the flow of the fluids, mainly for the regulation of the air flow, according to the claim 1, is characterized by the fact, that axes of the valves (1) are placed in a single plane which is perpendicular to a direction of the fluid's flow.

3. The adjustable regulator of the flow of the fluids, mainly for the regulation of the air flow, according to the claim 1 or 2, is characterized by the fact, that regulation spaces of the individual valves (1) are separated by a partition (8) which is placed between the neighboring valves (1); the partition (8) is in parallel with the direction of the fluid's flow and its length in the direction of the fluid's flow is larger than a height of the valve (1).

4. The adjustable regulator of the flow of the fluids, mainly for the regulation of the air flow, according to any of the claims 1 to 3, is characterized by the fact, that all the valves (1) are identical; the adjusting mechanisms (16) of all the valves (1) are identical and the adjusting elements (4) are coupled for the identical own value of a setting of the flow.

5. The adjustable regulator of the flow of the fluids, mainly for the regulation of the air flow, according to any of the claims 1 to 4, is characterized by the fact, that a coupling element has a lock (14) of a position.

6. The adjustable regulator of the flow of the fluids, mainly for the regulation of the air flow, according to any of the claims 1 to 5, is characterized by the fact, that the coupling element is a draw rod (12) and/or a chain drive and/or a wire transmission and/or a gear transmission and/or a toothed belt transmission.

7. The adjustable regulator of the flow of the fluids, mainly for the regulation of the air flow, according to any of the claims 1 to 6, is characterized by the fact, that it has flat boards (13) placed behind a shaft of the valves (1) in the direction of the fluid's flow, whereby the board (13) is in parallel with the direction of the fluid's flow.

8. The adjustable regulator of the flow of the fluids, mainly for the regulation of the air flow, according to any of the claims 1 to 7, is characterized by the fact, that a servomotor is connected to the adjusting mechanism (16), whereby an output of the servomotor is designed for a control of the adjusting element (4).

9. The adjustable regulator of the flow of the fluids, mainly for the regulation of the air flow, according to any of the claims 1 to 8, is characterized by the fact, that the damper (5) is rotational and it is placed on a tiltably placed holder (6); a stud (11) placed on the adjusting element falls into a fork in the holder (6); the damper (5) has an arm (7) with a curved groove (9); the arm is connected with the lever (2) by means of a pin (10) on the lever (2); where the pin (10) falls into the groove (9) and the pin's (10) connection with the groove (9) is designed for a movement of the pin (10) in the groove (9).

10. adjustable regulator of the flow of the fluids, mainly for the regulation of the air flow, according to the claim 9, is characterized by the fact, that a shape of the groove (9) comprises of two continuous sections, where a first section of the groove (9) is led by a straight line sloped away from a radial line (r); the straight line starts in a point A which is the initial middle point of the groove (9) on a side by the rotation of the arm's (7) axis and this point is on the radial line (r); the straight line continues to a point B which is outside the radial line (r) and it is the middle point of the groove (9) at an end of the straight line; where a second section of the groove (9) follows, this section being led by a curvature which continues from the point B to a point C, whereby the point C lies outside the radial line (r) and against the radial line (r) it is in an opposite half-plane as compared to the point B.

11. The adjustable regulator of the flow of the fluids, mainly for the regulation of the air flow, according to the claim 9 or 10, is characterized by the fact, that the first section of the groove (9) is led by the straight line which is sloped away from the radial line (r) by 15°, preferably by 22° to 23°.

12. The adjustable regulator of the flow of the fluids, mainly for the regulation of the air flow, according to any of the claims 9 to 11, is characterized by the fact, that on the pin (10) a cylindrical ring or a bearing, which is in a contact with an edge of the groove, is mounted.

13. The adjustable regulator of the flow of the fluids, mainly for the regulation of the air flow, according to any of the claims 9 to 12, is characterized by the fact, that the valve (1) together with the lever (2) is balanced towards the axis of the rotation.

14. The adjustable regulator of the flow of the fluids, mainly for the regulation of the air flow, according to the claim 13, is characterized by the fact, that connecting elements for the connection of the valve (1) with the shaft include a balancing matter.

15. The adjustable regulator of the flow of the fluids, mainly for the regulation of the air flow, according to any of the claims 9 to 14, is characterized by the fact, that the valve's (1) blade is flatly attached to the shaft by means of at least two screws (15), where the screws (15) have a flat hand and in their waists they have transversal openings in which the valve's (1) shaft is placed, whereby a matrice pushes the shaft to the valve's (1) blade which leans on an opposite side to the screw's (15) head; preferably the transversal opening of the screw (15) has a gape for the placement of the shaft at least in a direction of an axis of the screw (15), whereby the gap is delimited by the screwed, fixed matrix.

Drawing