Damper for controlling an air flow and ventilation facility comprising such a damper

Abstract

Said control damper (100) comprises a body (102) defining a duct (V100) with a blowing axis (A100), and an adjustment device (104), and comprising: - a flap (108) for closing the duct, the flap being rotatably movable relative to the body (102) around a pivot axis (A108) orthogonal to the blowing axis, - adjustment means (110) for adjusting a nominal position of the flap (108), - a return device (140) for returning the flap (108) to its nominal position when the air flow (F100) causes the flap (108) to be moved away from the nominal position. For improved control, the adjustment device (104) further comprises: - a shaft (150) pivotally mounted relative to the body (102) around an adjustment axis (A150) parallel to the pivot axis, an angular position of the shaft (150) around the adjustment axis (A150) being adjustable, and - at least one adjustment cam (160) provided so as to radially protrude from the shaft (150) and engage with a respective first stop (130) of the shutter (108) so as to limit the movements of the shutter (108) between its nominal position and an open position of the shutter, the return device comprising a tension spring with a first end connected to an attachment point (164) provided on the shaft (150), and a second end connected to an attachment point (128) provided on the flap (108), such that the spring is tensioned when the flap is in the nominal position.

Description

[0001] The present invention relates to a register for regulating an air flow and a ventilation installation comprising such a register.

[0002] A ventilation system generally comprises a driving member, such as a fan, which draws air from at least one suction outlet, blows this air into one or more ventilation ducts and expels this air from each duct through at least one blower outlet.

[0003] For each duct, the air flow depends in particular on the air pressure and the cross-section of this duct. To regulate the flow of an air flow circulating in a duct, it is known to install a control damper with a pivoting flap in this duct. A nominal angular position of the flap is defined by a user to more or less close the duct, and thus regulate the flow of the air flow to a nominal flow value.

[0004] On the other hand, the air pressure in said duct may vary, for example under the effect of clogging of filters when the ventilation installation includes them, under the effect of variation in the electrical voltage supplying the motor unit, etc. To maintain a substantially constant air flow over a wide range of pressures, it is known to use a so-called "self-regulating" regulating register, the flap of which automatically closes the duct when the air pressure increases, the flap returning to its nominal position when the pressure decreases.

[0005] DE-202004003811-U1 describes, for example, such a self-regulating damper. This self-regulating damper comprises a pivoting flap, abutted against an adjustable support, the nominal angular position of which is set by the user. This damper also comprises a bellows, which tends to move the flap away from the support when the pressure increases, and a spring blade, which tends to bring the flap back into abutment against the support. The bellows is relatively fragile and causes a delay in regulating the flow rate when the pressure varies. The bellows is not suitable for sudden pressure variations, and the spring blade has no restoring force when the flap is in the nominal position.

[0006] It is these problems that the invention specifically seeks to address by proposing an improved regulation register, the regulated flow rate of which remains more stable over wide flow and pressure intervals.

[0007] To this end, the invention relates to a register for regulating an air flow for a ventilation duct, comprising: a cylindrical body extending along a blowing axis, delimiting an air duct, an adjustment device, comprising: ∘ a shutter for closing the duct, the shutter being received in the duct and movable in rotation relative to the body around a pivot axis orthogonal to the blowing axis, between an open position, in which the closing of the duct is minimal, and a closed position, in which the closing of the duct is maximum, ∘ adjustment means, configured to adjust a nominal position of the shutter, the nominal position being intermediate between the open position and the closed position, the shutter in the nominal position defining with a median plane of the register a nominal angle, the median plane being parallel to the blowing axis and to the pivot axis, a return device, configured to return the shutter to its nominal position when, under the effect of the air flow, the shutter is moved away from the nominal position.

[0008] According to the invention, the adjustment device further comprises: a shaft, which extends along an adjustment axis and which is pivotally mounted relative to the body around the adjustment axis, the adjustment axis being parallel to the pivot axis, an angular position of the shaft around the adjustment axis being adjustable, and at least one adjustment cam, each adjustment cam being arranged radially projecting from the shaft and cooperating with a respective first stop of the shutter, so as to limit the movements of the shutter between its nominal position and its open position when the user defines the angular position of the shaft, whereas the return device comprises a tension spring with a first end and an opposite second end, the first end being connected to an attachment point provided on the shaft, and the second end being connected to an attachment point provided on the shutter, such that the spring is tensioned when the shutter is in the nominal position.

[0009] Thanks to the invention, regardless of the nominal position of the damper, defined by the user, the damper is returned to its nominal position by the return spring. The spring is robust and easy to adjust. The damper of the invention is thus particularly durable and efficient, the flow being more stable over the entire pressure place. The spring being tensioned when the damper is in nominal position, the regulation is more stable even when an air flow pressure in the duct is minimal. The spring tension is also independent of the air flow pressure, which improves the stability of the damper regulation.

[0010] According to advantageous but not mandatory aspects of the invention, such a register may incorporate one or more of the following features taken in isolation or in any technically admissible combination: the attachment point is offset relative to the adjustment axis, so that as the nominal angle increases, a length of the spring, and therefore the return moment of the flap towards its nominal position relative to the pivot axis, decreases. The attachment point and the hooking point are carried by a longitudinal plane of the body, the longitudinal plane being orthogonal to the pivot axis and carrying the blowing axis. The adjustment device comprises at least two adjustment cams, arranged symmetrically on either side of the longitudinal plane. The adjustment device comprises a slide, while the flap and the shaft are each assembled to the slide and rotatable relative to the slide, the slide being received in the duct and fixed to the body, the angular position of the shaft being controlled from outside the duct by means of a control member, for example a thumbwheel.The regulating damper further comprises a damping member, configured to dampen the movements of the flap when the flap moves between its nominal position and its regulating position under the effect of variations in the air flow and the return device. The damping member has two opposite ends, which are respectively connected to a flange of the flap and to an anchoring point of the slide and which are aligned along a damping axis, the damping member being configured to generate a damping force along the damping axis, while the anchoring point is arranged in a hollow of the slide, such that the damping axis does not intersect the pivot axis of the flap, regardless of the position of the flap. The damping member is a gas damper.The shaft also comprises at least one regulating cam, each regulating cam being arranged radially projecting from the shaft, while the shutter comprises at least one second stop, each second stop cooperating with a respective regulating cam so as to prevent movements of the shutter between the closed position and a regulating position, intermediate between the nominal position and the closed position of the shutter.

[0011] According to another aspect, the invention also relates to a ventilation installation, comprising a ventilation duct and a motor member, the duct being configured to guide the flow of air moved under the action of the motor member, the ventilation installation comprising a regulating damper installed in the duct to regulate the flow rate of the air flow, this damper being as described previously.

[0012] The invention will be better understood, and other advantages thereof will appear more clearly in the light of the following description of an embodiment of a regulating register and of a ventilation installation, in accordance with its principle, given solely by way of example and made with reference to the appended drawings, in which: [ Fig 1 ] there figure 1 is a schematic view of a ventilation installation according to the invention, comprising a regulation register according to the invention; [ Fig 2 ] there figure 2 is a perspective view of the control register of the installation of the figure 1 , represented in a first configuration; [ Fig 3 ] there figure 3 is a perspective view of the regulation register of the figure 1 , represented in a second configuration, with certain elements omitted; [ Fig 4 ] there figure 4 is a perspective and sectional view, along a longitudinal plane IV-IV at the figure 2 , from the regulatory register of the figure 2 , the perspective being taken from a different angle than that of the figure 2 ; [ Fig 5 ] there figure 5 is a perspective view of a shutter of the regulation register of the figure 2 ; [ Fig 6 ] there figure 6 is a perspective view of a regulating register tree of the figure 2 ; [ Fig 7 ] there figure 7 represents in section along the longitudinal plane IV-IV, on two inserts A) and B), the regulation register of the figure 2 , respectively in a first nominal configuration and a first regulation configuration; [ Fig 8 ] there figure 8 is a view analogous to the figure 7 , partially representing and on a larger scale, on two inserts A) and B), the regulation register of the figure 2 , respectively in a second nominal configuration and a second regulation configuration, and [ Fig 9 ] there figure 9 is a view analogous to the figure 7 , representing, on two inserts A) and B), the regulation register of the figure 2 , respectively in a third nominal configuration and a third regulation configuration.

[0013] A ventilation installation 2 is shown schematically on the figure 1 . The ventilation installation 2 is here located inside a building 20 and is therefore an indoor installation. Alternatively, the ventilation installation 2 is located outside the building 20, for example on the roof of the building 20, or even includes indoor and outdoor portions.

[0014] The ventilation installation 2 comprises a ventilation duct 22 and a motor member 24. The duct 22 connects an inlet vent 26 to two outlet vents 28, while the motor member 24, which is here a fan received in the duct 22, is located on an intermediate portion of the duct 22 between the inlet vent 26 and the outlet vents 26. The number of inlet vents 26 and outlet vents 28 is not limiting, each ventilation installation 2 comprising at least one inlet vent 26 and at least one outlet 28. The duct 22 is configured to guide an air flow F100 displaced under the action of the motor member 24. The motor member 24 is configured to suck in an air flow F26 from the inlet vent 26, and discharge an outlet air flow F28 through the outlet vents 28. The ventilation installation 2 is therefore here an insufflation installation, which blows into the interior of the building 20 the air taken from outside.Alternatively, the ventilation installation 2 is an extraction installation, which discharges the air taken from inside the building 20 outside.

[0015] The ventilation installation 2 also comprises a regulating damper 100, installed in the duct 22. In the example illustrated, the damper 100 is located downstream of the motor member 24 following the direction of the air flow F100 in the duct 22, however other configurations are possible. For example, in the case of an extraction ventilation installation 2, the damper 100 is generally located upstream of the motor member 24.

[0016] Under the action of a user, the damper 100 is configured to more or less close the duct 22, so as to regulate the flow rate of the air flow F100 passing through the duct 22 to a level called the “nominal flow rate”. The nominal flow rate therefore corresponds to the flow rate level desired by the user, this nominal flow rate being variable depending on the user's choices. The user is for example an installer of the ventilation installation 2, who sets the nominal flow rate in each duct 22 when the ventilation installation 2 is put into service. In a variant not illustrated, a damper 100 is installed between the duct 22 and each of the outlet vents 28. The user can thus adjust the flow rate of the air flow passing through each of the outlet vents 28.

[0017] The damper 100 is a self-adjusting damper, that is to say that once the user selects a nominal flow rate, the damper 100 is configured to adapt to variations in air pressure within the duct 22, so as to maintain the air flow rate substantially at the level of the nominal flow rate. Schematically, when the air pressure increases, the damper 100 no longer closes the duct 22, while when the air pressure decreases, the damper 100 returns to a nominal configuration.

[0018] We now detail the structure of register 100 using the figures 2 à 6 .

[0019] The register 100 comprises a body 102 and an adjustment device 104. The body 102 has a cylindrical shape, here of generally circular section, which extends along a blowing axis A100 and which delimits a duct V100. For the sake of simplification, the turbulence phenomena are neglected here and it is assumed that, schematically, in the duct V100, the air flow F100 is laminar and parallel to the blowing axis A100.

[0020] The sheath 22 is preferably modular, that is to say that the sheath 22 comprises several elements assembled together, for example rectilinear tubes, elbows, etc. The body 102 is configured to be assembled to these modular elements in a sealed manner, for example by means of specific connectors and / or sealing members. The modular elements and the connectors or sealing members are not shown. In the example, the body 102 is configured to be fitted, in a sealed manner, into the sheath elements 22 of 125 mm in diameter. The section of the body 102 is adapted accordingly.

[0021] The register 100 has a preferred mounting direction, that is to say that the air flow F100 is preferably always oriented in the same direction relative to the register 100. The body 102 thus has a downstream side 102A and an upstream side 102B. The register 100 is assembled to the duct 22 so that, preferably, the blowing axis A100 is horizontal, as shown in the figures. A longitudinal plane P100 of the register 100 is defined as being a vertical plane parallel to the blowing axis A100.

[0022] The adjustment device 104, shown isolated on the figure 3 , comprises a support 106, a flap 108 and means 110 for adjusting the orientation of the flap 108 relative to the support 106. In the assembled configuration of the register 100, the adjustment device 104 is essentially received in the duct V100, only a control member 152 of the adjustment means 110 is located outside the duct V100.

[0023] The support 106 comprises a main portion 112, which extends along a median plane P112, and two lateral portions 114 and 116, which are located opposite each other and each extend in a plane orthogonal to the median plane P112.

[0024] When the support 106 is assembled to the body 102, the median plane P112 is horizontal, the blowing axis A100 is carried by the median plane P112, which is also a median plane of the register 100, while the lateral portions 114 and 116 are parallel to the longitudinal plane P100.

[0025] The lateral portions 114 and 116 are configured to cooperate with slides, arranged in the body 102. The lateral portion 114 cooperates with a slide 118, visible in the figure 2 , while the lateral portion 116 cooperates with a slide 120, visible on the figure 4 Advantageously, the lateral portion 114 comprises a shoulder 122, which cooperates with a complementary stop not shown and arranged in the slide 118, so that the mounting of the support 106 is only possible in one direction, here the direction opposite to the air flow F100. In other words, the support 106 thus constitutes a drawer for mounting the register 100.

[0026] Advantageously, the body 102 comprises two flats 122, arranged projecting into the duct V100 on either side of the longitudinal plane P100 and in which the slides 118 and 120 are arranged, so that the lateral portions 114 and 116 are flush with an internal surface of the duct V100, thus limiting the generation of turbulence, and therefore of noise, when the register 100 mounted in a ventilation installation 2 is operating.

[0027] The main portion 112 has a slot 113, which divides the main portion into a downstream plate 112A and an upstream plate 112B. When the damper 100 is assembled, the downstream plate 112A is located on the downstream side 102A of the body 102 relative to the slot 113. The slot 113 here has a rectangular shape extending in its length orthogonally to the lateral portions 114 and 116. The slot 113 allows the passage of the flap 108, as explained later.

[0028] The flap 108 and the upstream plate 112B delimit between them a pressure chamber C100, which is open facing the air flow F100, that is to say towards the upstream side 102B. The air flow F100 thus generates a force which tends to separate the flap 108 from the upstream plate 112B.

[0029] Shutter 108, shown isolated on the figure 5 , here comprises a downstream panel 124A and an upstream panel 124B, which are substantially planar and parallel to each other and which are connected to each other by an intermediate portion 126. The intermediate portion 126 here has a rectangular shape, which extends in its length along a pivot axis A108. At its ends, the intermediate portion 126 comprises bearings 127, here produced by pins, which are configured to cooperate with the lateral portions 114 and 116, so that the flap 108 is movable in rotation relative to the support 106 around the pivot axis A108.

[0030] The pivot axis A108 is therefore orthogonal to the lateral portions 114 and 116. In the example, the pivot axis A108 is aligned with the slot 113, the downstream 124A and upstream 124B panels being located on either side of the median plane P112. When the register 100 is in the assembled configuration, the flap 108 is received in the duct V100 and is rotatable relative to the body 102 around the pivot axis A108, which is therefore orthogonal to the blowing axis A100.

[0031] A shutter plane P108 is defined as a plane passing through the pivot axis A108 and parallel to the downstream panel 124A.

[0032] When the flap plane P108 is not parallel to the median plane P112, the flap plane P108 and the median plane P112 are intersecting and define between them a closing angle α. In other words, the closing angle α is the angle between the downstream panel 124A and the downstream plate 112A. The closing angle α is therefore zero when the flap plane P108 is parallel to the median plane P112. Depending on the closing angle α, the duct V100 is more or less closed by the flap 108. A closing of the duct V100 is therefore determined by a position of the flap 108, which is determined by the closing angle α.

[0033] When the obstruction of the duct V100 is minimal, the flap 108 is in a so-called open position, in which the closing angle α is equal to a minimum angle α MIN . The air flow F100 then has a maximum flow rate, taking into account the air pressure prevailing in the duct V100. In the example illustrated, the minimum angle α MIN is equal to 0°, in other words in the open position, the flap plane P108 is parallel to the median plane P112.

[0034] When the obstruction of the duct V100 is maximum, the flap 108 is in a so-called closed position, in which the closing angle α is equal to a maximum angle α MAX. The air flow F100 then has a minimum flow rate, which is a function of the air pressure prevailing in the duct V100. In the example illustrated, the maximum angle α MAX is equal to 90°, in other words in the closed position the flap plane P108 is orthogonal to the median plane P112.

[0035] The flap 108 also includes a hooking point 128 and a flange 129, which are provided on the flap 108 at a distance from the pivot axis A108. The hooking point 128, visible on the figure 4 , is here produced by a mushroom-shaped projection, arranged on the downstream panel 124A on the side facing the support 106. The attachment point 128 is used for fixing a spring 140 of the adjustment device 110, as explained later. The flange 129, which is here arranged on the upstream panel 124B on the side facing the support 106, is used for fixing a shock absorber 142 of the adjustment device, as explained later.

[0036] The flap 108 finally comprises first stops 130 and second stops 132. The first stops 130, which are here arranged on the downstream panel 124A, are configured to be pushed back by adjustment cams described later, so as to prevent movements of the flap 108 between the open position and the nominal position. In other words, the nominal position of the flap 108 is defined by the cooperation of the first stops 130 and the adjustment cams.

[0037] The intermediate portion 126 comprises a bulge 134, which has the shape of a portion of a cylinder with a circular section and is centered on the flap axis A108. The bulge 134 extends along the intermediate portion 126, between the two bearings 127. When the register 100 is assembled, the bulge 134 is arranged opposite an edge B112 of the upstream plate 112B, so as to close, apart from the assembly clearances, the pressure chamber C100 at the junction between the flap 108 and the upstream plate 112B regardless of the closing angle α. Air leaks from the pressure chamber C100 are reduced, contributing to the proper functioning of the register 100. In other words, the bulge 134 cooperates with the edge B112 of the upstream plate 112B, so as to limit air leaks between the flap 108 and the upstream plate 112B.

[0038] The second stops 132, which are here arranged on the upstream panel 124B, are configured to be pushed back by regulation cams described later, so as to prevent the movements of the flap 108 between the closed position and a regulation position, intermediate between the nominal position and the closed position of the flap 108. In other words, the regulation position of the flap 108 is defined by the cooperation of the second stops 132 and the regulation cams, and corresponds to a regulation angle α REG .

[0039] Under the combined effect of the first stops 130 cooperating with the adjustment cams and the second stops 132 cooperating with the regulation cams, the movements of the flap 108 are limited between the nominal position and the regulation position.

[0040] The adjustment means 110 are configured to adjust a nominal position of the shutter 108, the nominal position being intermediate between the open position and the closed position. In other words, the nominal position of the shutter 108 corresponds to a nominal angle α NOM , which is between the minimum angle α MIN and the maximum angle α MAX .

[0041] We define angular travel Δα, which is equal to the difference between the regulation angle α REG and the nominal angle α NOM , in other words Δα = α REG - α NOM . For a given nominal position of the flap 108, the angular travel Δα therefore represents the amplitude of the movement of the flap 108 between this nominal position and the corresponding regulation position.

[0042] It is understood that if the air pressure in the duct V100 is too low, the air flow F100 will have too low a flow rate, even if the flap 108 is in the open position. To function properly, the register 100 requires that a minimum air pressure P MIN prevails in the duct V100. The nominal position of the flap 108 is therefore defined by the user according to the desired air flow rate when the air pressure in the duct V100 is equal to the minimum pressure P MIN . Conversely, the self-regulating nature of the regulator 100 is effective for pressures lower than a maximum pressure P MAX , strictly greater than the minimum pressure P MIN .

[0043] Thus, as long as the air pressure in the duct 22 is between the minimum pressure P MIN and the maximum pressure P MAX , the flow rate of the air flow F100 is substantially equal to the nominal flow rate, which is determined by the nominal position of the flap 108, in other words by the nominal angle α NOM .

[0044] In the example illustrated, the duct 22 has a diameter of 125 mm, the minimum pressure P MIN is equal to 50 Pa - Pascal -, the maximum pressure P MAX is equal to 300 Pa, while the register 100 is configured to regulate a nominal flow rate between the minimum flow rate equal to 15 m 3 < / h - cubic meter per hour - and the maximum flow rate equal to 240 m 3 < / h.

[0045] The adjustment means 110 comprise a shaft 150 and a control member, here a graduated wheel 152.

[0046] Tree 150, represented alone in the figure 6 , has an elongated shape and extends along an adjustment axis A150. The shaft 150 is preferably made of synthetic polymer material, for example polyamine - noted PA -. The shaft 150 is for example manufactured by hot injection, or even by an additive manufacturing process, also called 3D printing.

[0047] The shaft 150 comprises a first end 154A and a second end 154B, opposite the first end 154A. The first end 154A is connected to the wheel 152 through the body 102, such that the shaft 150 is rotated about the adjustment axis A150 by the wheel 152.

[0048] In the illustrated example, the first end 154A has a bulge, which forms a housing 155 of cylindrical shape extending along the adjustment axis A150. The housing 155 advantageously has a non-circular profile, configured to receive a rod of complementary shape connected to the wheel 152. The shaft 150 is thus configured to be driven in rotation around the adjustment axis A150 by the wheel 152. An angular position of the shaft 150 around the adjustment axis 150 is fixed by the user by means of the control member formed by the wheel 152. Other methods of assembling the shaft 150 and the wheel 152 are possible, in particular by screwing or by gluing.

[0049] The first end 154A and the second end 154B each cooperate with a respective lateral portion 114 and 116, so that the shaft 150 is pivotally mounted relative to the support 106 around the adjustment axis A150, which is orthogonal to the lateral portions 114 and 116. For this purpose, a bearing 156 is provided on each of the first and second ends 154A and 154B, each bearing 156 being received in a complementary orifice provided in the corresponding lateral portion 114 or 116. The complementary orifices are not shown.

[0050] In the assembled configuration of the adjustment device 110, the adjustment axis A150 is parallel to the pivot axis A108 of the flap 108. The adjustment axis A150 is distinct from the pivot axis A108, in particular for reasons of cam kinematics.

[0051] Thus, when the register 100 is fully assembled, the shaft 150 is rotatable relative to the body 102 around the adjustment axis A150. The angular position of the shaft 150 around the adjustment axis A150 is set by the user by means of the control member 152. A locking member 158, here a screw, is advantageously provided to prevent any untimely change in the angular position of the shaft 150, once it has been adjusted using the thumbwheel 152. The locking member 158 immobilizes the thumbwheel 152 in rotation around the axis A150 relative to the body 102, and therefore the shaft 150 relative to this body 102, since the components 150 and 152 are integral in rotation around the axis A150. The locking member 158 also allows the support 106 to be held in the body 102.

[0052] The shaft 150 also comprises two adjustment cams 160. The adjustment cams 160 have the same profile and are arranged to project from the shaft 150, radially to the adjustment axis A150. Each adjustment cam 160 has a cylindrical shape with an axis A160, which is parallel to and distinct from the adjustment axis A150. The axes A160 of the two adjustment cams 160 are aligned with each other.

[0053] In a non-limiting manner, the adjustment cams 160 here have a circular profile, which is not centered on the adjustment axis A150. In a variant not shown, the adjustment cams 160 have an elliptical profile, or even an ovoid profile.

[0054] Each adjustment cam 160 is configured to cooperate with one of the respective first stops 130 of the flap 108, so as to prevent movements of the flap 108 between its open position and its nominal position.

[0055] When the shaft 150 rotates around the adjustment axis A150, under the action of a user who adjusts the nominal flow rate, the adjustment cams 160 push back the first stops 130. When the first stops 130 are in contact with the adjustment cams 160, the flap 108 is in its nominal position, the nominal angle α NOM depending on the angular position of the shaft 150 around the adjustment axis A150.

[0056] The two adjustment cams 160 are advantageously arranged symmetrically on either side of a transverse plane P150 of the shaft 150, the transverse plane 150 being orthogonal to the adjustment axis A150 and located midway between the ends 154A. When the register 100 is fully assembled, the transverse plane P150 coincides with the longitudinal plane P100 of the register 100. Thus the forces of the adjustment cams 160 on the flap 108 result in a moment, relative to the pivot axis A108, carried by the longitudinal plane P100, which reduces the risks of deformation of the flap 108, and therefore reduces the risks of malfunction.

[0057] Traditionally, in state-of-the-art regulators, when the air pressure increases, the movement of the flap 108 is only returned to its nominal position by a return device. However, if the flap 108 gets too close to the closed position, the air flow rate risks falling significantly below the nominal flow rate expected by the user. In other words, the regulator 100 "suffocates" and no longer fulfills its function.

[0058] Advantageously, the shaft 150 also comprises two regulating cams 162. The two regulating cams 162 have the same profile and are arranged radially projecting from the shaft 150. Each regulating cam has a cylindrical shape with axis A162, which is parallel and distinct from the adjustment axis A150. The axes A162 of the two adjustment cams 162 are aligned with each other. In a non-limiting manner, the regulating cams 162 here have a circular profile, which is not centered on the adjustment axis A150. In a variant not shown, the regulating cams 162 have an elliptical profile, or even an ovoid profile.

[0059] Each regulating cam 162 is configured to cooperate respectively with one of the second stops 132 provided on the flap 108, so as to prevent the movements of the flap 108 between its closed position and its regulating position. The shape and arrangement of the regulating cams 162 and the stops 132 are chosen by the manufacturer of the register 100, so as to avoid the choking effect of the register 100.

[0060] The regulating cams 162 are radially offset, with reference to the adjustment axis A150, relative to the adjusting cams 160. In other words, the axis A160 of the adjusting cams 160 and the axis A162 of the regulating cams 162 are not located in the same plane radial to the adjustment axis A150, so that the angular movement Δα is non-zero.

[0061] The shaft 150 also comprises an attachment point 164, produced here by means of a pin having a groove 165. The attachment point 164, which is here arranged between the two adjustment cams 160, is configured to cooperate with a first end of the spring 140. When the register 100 is fully assembled, a second end of the spring 140 is fixed to the attachment point 128 arranged on the flap 108, so that the spring 140 is tensioned whatever the position of the flap 108, that is to say including when the flap 108 is in the nominal position. The spring 140, which is here a helical traction spring made of metal, preferably stainless steel, is an exemplary embodiment of a return device, configured to return the flap 108 to the nominal position when, under the effect of the air flow F100, the flap 108 is moved away from its nominal position.

[0062] Advantageously, the attachment point 164 is offset relative to the adjustment axis A150, so that a distance between the attachment point 164 and the attachment point 128 is variable when the angular position of the shaft 150 changes, under the action of a user who adjusts the nominal position of the flap 108, in other words who adjusts the nominal angle α NOM . The spring 140 is here a tension spring. A length L140 of the spring 140 is equal to the distance between the attachment point 164 and the attachment point 128.

[0063] As the nominal angle α NOM increases, the length L140 decreases, so that the restoring force of the spring 140 decreases. This effect is illustrated in the figures 7 à 9 , described further.

[0064] As a result, the restoring force of the spring 140 is all the weaker as the flow rate chosen by the user is reduced, which makes the damper 100 more sensitive to low flow rates, the flow rate of the air flow F100 being more stable over a wide pressure range. A stiffness of the spring 140 is determined experimentally as a function of the dimensioning of the damper 100.

[0065] When the register 100 is assembled, the attachment point 164 and the attachment point 128 are advantageously carried by the longitudinal plane P100 of the register, so as to avoid deformations of the flap 108 under the effect of the return force of the spring 140. When the flap 108 is in the nominal position, each first stop 130 bears on a respective adjustment cam 160, and the spring 140 exerts its return force between the contact points of each first stop 130 with the respective adjustment cam 160.

[0066] Since aeraulic phenomena are not linear, the higher the nominal flow rate set by the user, the greater the amplitude of movement of the flap 108 must be for the flow rate regulation to be effective over the entire pressure range. In other words, when the nominal angle α NOM is close to α MIN , that is to say when the user wants a high air flow rate, the angular movement Δα necessary to regulate the air flow F100 to the requested level between the minimum pressure P MIN and the maximum pressure P MAX is greater than the angular movement Δα necessary when the nominal angle α NOM is close to α MAX , that is to say when the user wants a reduced air flow rate.

[0067] Advantageously, the radial offset between the axes A160 and A162 of the adjustment cams 160 and regulation cams 162, as well as the respective profiles of the adjustment cams 160 and regulation cams 162, are chosen so that as the nominal angle α NOM increases, the angular displacement Δα decreases. This effect is illustrated in the figures 7 à 9 , described further.

[0068] The flap 108 tends, on the one hand, to move away from its nominal position under the effect of the pressure of the air flow F100 and, on the other hand, to be returned to its nominal position under the effect of the spring 140. Since the air pressure in the duct V100 is never perfectly stable, the flap 108 risks exhibiting an oscillating movement, which could generate noise and harm the stability of the flow rate of the air flow F100. Advantageously, the register 100 therefore comprises a damping member 142, configured to dampen the movements of the flap 108 when the flap 108 moves, under the effect of the variations in the air flow F100 and the return device, between its nominal position and its regulation position.

[0069] In the example illustrated, the damping member 142 has an elongated cylindrical shape along a damping axis A142 and comprises two opposite ends, aligned along the damping axis A142 and connected respectively to the flange 129 of the flap 108 and to an anchoring point 123 provided on the support 106. In the example, the flange 129 is provided on the upstream panel 124B of the flap 108, while the anchoring point 123 is provided on the upstream plate 112B of the support 106.

[0070] When a distance between the flange 129 and the anchor point 123 changes, the damping member 142 generates a damping force which opposes this change and which is aligned with the damping axis A142.

[0071] The damping member 142 is preferably a gas damper, which has a sufficiently low inertia to dampen the oscillating movements of the flap 108.

[0072] Advantageously, the flange 129 and the anchoring point 123 are arranged so that the moment of the damping force relative to the pivot axis A108 is not zero, whatever the position of the flap 108. Thus the damping member 142 is effective even when the flap 108 is in the open position and the flow rate of the air flow is maximum.

[0073] In the example, the flange 129 is carried by the flap plane P108, while the anchoring point 123 is arranged in a hollow 112B1 of the upstream plate 112B, so that the damping axis A142 does not intersect the pivot axis A108 of the flap 108, whatever the position of the flap 108.

[0074] On each of the figures 7 , 8 And 9 , the register 100 is respectively represented in three different configurations, each corresponding to an angular position of the shaft 150, set by the user. In other words, at each of the figures 7 à 9 corresponds to a different nominal angle α NOM.

[0075] On insert A) of each of the figures 7 , 8 And 9 , the flap 108 is in its nominal position. The first stops 130 of the flap 108 are in contact with the adjustment cams 160, in other words the closing angle α is equal to the nominal angle α NOM .

[0076] On insert B) of each of the figures 7 à 9 , the flap 108 is in its regulation position. The second stops 132 of the flap 108 are in contact with the regulation cams 162, in other words the closing angle α is equal to the regulation angle α REG .

[0077] On the figure 7 , the nominal angle α NOM is equal to the minimum angle α MIN , i.e. here 0°. On insert A), the flap plane P108 is parallel to the median plane P112. The flap 108 is in the open position, and the air flow F100 has a maximum flow rate.

[0078] From its nominal position, if the air pressure in the duct V100 increases, the flap 108 is moved away from its nominal position, until it reaches its regulation position, shown in insert B).

[0079] In the example illustrated, the regulation angle α REG is equal to approximately 40°. The angular amplitude Δα is here equal to approximately 40°. In other words, for a nominal angle α NOM equal to 0°, the angular displacement Δα is substantially equal to 40°.

[0080] On the figure 8 , the angular position of the shaft 150 corresponds to a nominal angle α NOM of the flap 108 of approximately 25°. On the insert B), the flap 108 is in its regulation position, and the regulation angle α REG is substantially equal to 50°. In other words, for a nominal angle α NOM of approximately 25°, the angular movement Δα is substantially equal to 25°.

[0081] On the figure 9 , the angular position of the shaft 150 corresponds to a nominal angle α NOM of approximately 80°. On the insert B), the flap 108 is in its regulation position, and the regulation angle α REG is substantially equal to 85°. In other words, for a nominal angle α NOM substantially equal to 80°, the angular displacement Δα is substantially equal to 5°.

[0082] The three figures 7 , 8 And 9 thus illustrate one of the advantages of the invention, according to which the angular displacement Δα decreases as the nominal angle α NOM increases.

[0083] Between insert A) of the figure 7 and insert A) of the figure 9 , the shaft 150 rotates by approximately 180° around the adjustment axis A150, while the nominal angle α NOM changes from 0° to approximately 85°. During this movement, the attachment point 164 moves closer to the attachment point 128, in other words the length L140 decreases.

[0084] Inserts A) of the three figures 7 ,8 And 9 thus illustrate another of the advantages of the invention, according to which the return force of the return device 140 decreases as the nominal angle α NOM increases.

[0085] In addition, on each of the figures 7 , 8 And 9 , when the flap 108 moves from its nominal position, illustrated in insert A), to its regulation position, illustrated in insert B), on the one hand, the length L140 of the spring 140 increases, in other words the return force of the spring 140 increases, and on the other hand, the flap plane P108 moves away from the attachment point 164, in other words the moment of said return force relative to the pivot axis A108 increases. The two effects add up, which contributes to improving the regulation capacity of the damper 100 when the air pressure increases in the duct 22.

[0086] When assembling the register 100, the flap 108 and the shaft 150 are each assembled to the support 106 which is received in the duct V100 and fixed to the body 102. The angular position of the shaft 150 is controlled from outside the body 102 by means of the control member formed by the wheel 152. The assembly of the register 100 is particularly simple to carry out.

[0087] The closing angle α and the nominal flow rate of the flow F100 are not linked to each other by a linear relationship, just as the angular position of the shaft 150 around the adjustment axis A150 and the nominal flow rate of the flow F100 are also not linked to each other by a linear relationship. The thumbwheel 152 advantageously comprises graduations 152A, so that the user knows, from outside the body 102, the closing angle α and / or the corresponding flow rate.

[0088] In the illustrated example, the angular position of the shaft 150 is manually defined by the user, who adjusts the angular position of the shaft 150 by means of the wheel 152, immobilized by the screw 158.

[0089] In a variant not shown, the wheel 152 and the screw 158 are replaced by a motorized device, for example connected to a programmer or to a home automation system.

[0090] In the illustrated example, the shaft 150 comprises two adjustment cams 160, each of which cooperates with a respective first stop 130. In a variant not shown, the shaft comprises only one adjustment cam 160 or more than two adjustment cams.

[0091] In the illustrated example, the shaft 150 comprises two regulating cams 162, each of which cooperates with a respective second stop 132. In a variant not shown, the shaft comprises only one regulating cam 162 or more than two regulating cams.

[0092] In the illustrated example, the adjustment cam 160 and regulation cam 162 are separate cams, each of which has a circular profile. In a variant not shown, each regulation cam 162 is associated with a respective adjustment cam 160, each regulation cam 162 and the associated adjustment cam 160 are respective portions of the same radial projection provided on the shaft 150.

[0093] In the example illustrated, the return device 140 is located on the downstream side 102A, and the damping device 162 is located on the upstream side 102B, which allows for easy assembly using simple and inexpensive components - spring and damper. In a variant not shown, the respective positions of the return devices 140 and damping devices 142 are swapped, or the return and damping devices are located on the same side, downstream or upstream, or even are integrated into the same return and damping device.

[0094] The embodiments and variations mentioned above can be combined with each other to generate new embodiments of the invention.

Claims

1. A control damper (100) for regulating an air flow (F100) for a ventilation duct, comprising: - a cylindrical body (102) extending along an axis of blowing (A100), defining an air duct (V100), - an adjustment device (104) comprising: • a flap (108) for blocking the duct (V100), the flap (108) being received in the duct (V100) and being movable in rotation with respect to the body (102) about a pivot axis (A108) orthogonal to the axis of blowing (A100), between an open position, wherein the duct (V100) is minimally closed, and a closed position, wherein the blockage of the duct (V100) is maximum, • means of adjustment (110), configured for adjusting a nominal position of the flap (108), the nominal position being intermediate between the open position and the closed position, the flap (108) in the nominal position defining, along with a median plane (P112) of the damper (100), a nominal angle (αNOM), the median plane (P112) being parallel with the axis of blowing (A100) and with the pivot axis (A108), - a return device (140), configured for returning the flap (108) to the nominal position thereof when the flap (108) is moved away from the nominal position by the air flow (F100), characterized in that: - the adjustment device (104) further comprises: • a shaft (150), which extends along an axis of adjustment (A150) and which is pivotally mounted with respect to the body (102) about the axis of adjustment (A150), the axis of adjustment (A150) being parallel to the pivot axis (A108), an angular position of the shaft (150) about the axis of adjustment (A150) being adjustable, and • at least one adjustment cam (160), each adjustment cam (160) protruding radially from the shaft (150) and cooperating with a respective first stop (130) of the flap (108), so as to limit the movements of the flap (108) between the nominal position thereof and the open position thereof when the user defines the angular position of the shaft (150), - the return device (140) comprises a tension spring with a first end and an opposite second end, wherein the first end is connected to a hard point (164) provided on the shaft (150), whereas the second end is connected to an attachment point (128) provided on the flap (108), so that the spring is tensioned when the flap is in the nominal position.

2. The control damper (100) according to claim 1, wherein the hard point (164) is offset from the axis of adjustment (A150) such that as the nominal angle (αNOM) increases, the length of the spring (L140), and hence the moment of return of the flap (108) towards its nominal position with respect to the pivot axis (A108), decrease.

3. The control damper (100) according to any one of claims 1 or 2, wherein the hard point (164) and the attachment point (128) are carried by a longitudinal plane (P100) of the body (102), the longitudinal plane (P100) being orthogonal to the pivot axis (A108) and carrying the axis of blowing (A100).

4. The control damper (100) according to claim 3, wherein the adjustment device (104) comprises at least two adjustment cams (160) provided symmetrically on both sides of the longitudinal plane (P100).

5. The control damper (100) according to any one of claims 1 to 4, wherein the adjustment device (104) comprises a slide (106), wherein the flap (108) and the shaft (150) are each connected to the slide (106) and are movable in rotation with respect to the slide (106), the slide being received in the duct (V100) and attached to the body (102), the angular position of the shaft (150) being controlled from outside the duct (V100) by means of a control member (152), e.g. a handwheel.

6. The control damper (100) according to claim 5, further comprising a damping member (142), configured for damping the movements of the flap (108) as the flap (108) moves between the nominal position thereof and the control position thereof under the effect of the variations of the air flow (F100) and of the return device (140).

7. The control damper (100) according to claim 6, wherein: - the damping member (142) has two opposite ends which are connected to a flange (129) of the flap (108) and to an anchoring point (123), respectively, of the slide (106) and which are aligned along an axis of damping (A142), the damping member (142) being configured for generating a damping force along the axis of damping (A142), - the anchoring point (123) being provided in a recess (112B1) of the slide (106), so that the axis of damping (A142) does not intersect the pivot axis (A108) of the flap (108), irrespective of the position of the flap.

8. The control damper (100) according to any one of claims 6 to 7, wherein the damper member (142) is a gas spring.

9. The control damper (100) according to any one of claims 1 to 8, wherein the shaft (150) further comprises at least one control cam (162), each control cam (162) radially protruding from the shaft (150), and wherein the flap (108) comprises at least one second stop (132), each second stop (132) cooperating with a respective control cam (162) so as to prevent movements of the flap (108) between the closed position and a control position, intermediate between the nominal position and the closed position of the flap (108).

10. A ventilation installation (2), comprising a ventilation duct (22) and a driving element (24), the duct (22) being configured for guiding the air flow (F100) displaced by the driving element (24), the ventilation installation comprising a control damper (100) installed in the duct (22) for regulating the flow-rate of the air flow (F100), characterized in that the control damper (100) is according to any one of claims 1 to 9.

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