Fire damper

Abstract

The invention relates to a fire damper with a housing having a housing wall, preferably having a round or a square flow cross-section, and with a damper blade, preferably made of calcium silicate and having a thickness D, pivotably mounted therein, preferably centrally on the flow cross-section, between an open position and a closed position about an axis of rotation, wherein the damper blade has two opposing damper blade surfaces connected by a circumferential end face, and wherein the fire damper has two centrally opposing bearing points, forming the axis of rotation and relating to the flow cross-section, for mounting the damper blade, and wherein at least one bearing point is formed on the one hand by a receptacle provided in the housing, preferably designed as a recess, and on the other hand by a bearing pin.wherein the bearing pin is connected to the damper blade at one end, and projects into the corresponding receptacle at the other end, which projects away from the end face of the damper blade, and wherein the fire damper further comprises at least one thermal seal made of a material that expands when exposed to heat, wherein the at least one thermal seal is provided on the circumferential end face of the damper blade, wherein, in the closed state of the damper blade, a circumferential movement gap is provided between the inside of the housing and the thermal seal, which has not yet expanded due to heat, and / or, at least in the part extending along the circumference of the damper blade in the closed state, a movement gap is provided on the inside of the housing, wherein, in the closed state of the damper blade, between the end face of the damper blade and the thermal seal,which has not yet expanded due to heat exposure, a circumferential movement gap is provided. In order to specify a fire damper that is well-balanced in terms of weight, that has good structural integrity of the damper blade in the area of ​​the two bearing points, and that also has a good seal in the event of a fire, the bearing pins are to be arranged offset from each other with respect to the central plane M of the damper blade, which extends parallel to the two damper blade surfaces, wherein one bearing pin is arranged offset by a distance A1 in the direction of one damper blade surface to the central plane M, and the other bearing pin is arranged offset by a distance A2 in the direction of the other damper blade surface to the central plane M.where distance A1 is understood to be the distance between the median plane M and the center point of one bearing pin, and distance A2 is understood to be the distance between the median plane M and the center point of the other bearing pin, and where the centers of the two supports are arranged at a distance A in the direction of flow, which results from the sum of the distances A1 + A2.

Description

[0001] The invention relates to a fire damper with a housing having a housing wall, preferably having a round or a square flow cross-section, and with a damper blade, preferably made of calcium silicate and having a thickness D, pivotably mounted therein, preferably centrally on the flow cross-section, between an open position and a closed position about an axis of rotation, wherein the damper blade has two opposing damper blade surfaces connected by a circumferential end face, and wherein the fire damper has two centrally opposing bearing points, forming the axis of rotation and relating to the flow cross-section, for mounting the damper blade, and wherein at least one bearing point is formed on the one hand by a receptacle provided in the housing, preferably designed as a recess, and on the other hand by a bearing pin.wherein the bearing pin is connected with one end to the damper blade, and with its other end, projecting towards the end face of the damper blade, extends into the corresponding receptacle and wherein the fire damper further comprises at least one thermal seal made of a material which expands when exposed to heat, wherein the at least one thermal seal , a circumferential end face of the flap blade is provided, wherein, in the closed state of the flap blade, a circumferential movement gap is provided between the inside of the housing and the heat seal, which has not yet expanded due to heat exposure. and / or on the inside of the housing, at least in the part that extends along the circumference of the flap leaf in the closed state, a circumferential movement gap is provided between the end face of the flap leaf and the heat seal, which has not yet expanded due to heat exposure, in the closed state of the flap leaf.

[0002] Known fire dampers have a damper blade pivotally mounted about an axis of rotation, which has two opposing damper blade surfaces connected by a circumferential end face. For mounting the damper blade, a known fire damper includes a continuous shaft or two stub shafts. The two stub shafts are aligned. If two stub shafts are provided, a recess designed as a receptacle is provided in the end face of the damper blade in each of the two opposing areas, into which one stub shaft engages. When a continuous shaft is used instead of two stub shafts, the recess extends through the entire damper blade. In both cases, the damper blade is weakened in the area of ​​each receptacle. In another embodiment, each stub shaft has an angled mounting element.The angled section extends around the edge between the end face and a flap blade surface. The mounting element rests on the flap blade surface and is fixed to it by screws. Both mounting elements are located on a common flap blade surface. Therefore, the flap blade is not optimally balanced in terms of weight.

[0003] A disadvantage of the known designs described above is that, if the bearing extends over a substantial portion of the thickness D of the flap blade, the thermal seal is interrupted in the area of ​​each of the two bearing points. While it is possible to wrap the thermal seal around each of the two bearing points on both sides if the bearing point is narrower, the two remaining strips of the thermal seal that wrap laterally around the bearing point are then very narrow, leaving little material available for expansion. Furthermore, in the two areas wrapped around each bearing point, the thermal seal is located close to the adjacent circumferential edge of the flap blade's end face. A damper arrangement for a ventilation system is known from EP 2 823 862 B1.GB 2499818 A concerns a flap blade for a fire damper and US-PS 3,384,340 a butterfly damper for high vacuum operation.

[0004] The object of the invention is to avoid the aforementioned disadvantages and to provide a fire damper that is well balanced in terms of weight, has good structural integrity of the damper blade in the area of ​​the two bearing points and also has good sealing in case of fire.

[0005] This problem is solved in a fire damper according to the invention by arranging the bearing pins offset from each other relative to the median plane M of the damper blade which extends parallel to the two damper blade surfaces, wherein one bearing pin is arranged offset at a distance A 1 in the direction of one damper blade surface to the median plane M and the other bearing pin is arranged offset at a distance A 2 in the direction of the other damper blade surface to the median plane M, wherein distance A 1 is understood to be the distance between the median plane M and the center point of one bearing pin and distance A 2 is understood to be the distance between the median plane M and the center point of the other bearing pin, and wherein the centers of the two receptacles are arranged in the direction of flow at a distance A which results from the sum of the distances A 1 + A 2.

[0006] The fire damper according to the invention is characterized by the fact that the damper blade has no recesses in its end face. This prevents the damper blade from being weakened in the area of ​​the two bearing points. Since the bearing pins are arranged offset from each other in the direction of flow, a continuous, uninterrupted, strip-shaped section is formed on the end face, which is located centrally with respect to the thickness D of the damper blade. One bearing pin is located on one side and the other bearing pin on the other side of this section. This allows, for example, a continuous, uninterrupted thermal seal to be applied to the continuous section of the damper blade's end face, which runs between the two bearing pins.

[0007] Unlike conventional fire dampers, the thermal seal of this design is uninterrupted and has no reduced width at any point. In the event of a fire, the thermal seal expands due to the heat and fills the circumferential gap between the front face and the housing wall, ensuring a tight seal across the entire front face to prevent fire spread. The gap between the front face and the housing wall is dimensioned to allow the damper blade to move easily between its two positions.

[0008] The two valve leaf surfaces are preferably aligned parallel to each other. The median plane M is understood to be the imaginary plane that extends parallel to the two valve leaf surfaces through the valve leaf and is located centrally with respect to the end face of the valve leaf. If the valve leaf has a thickness D of 2 cm, the distance of the median plane M to each of the two valve leaf surfaces is 1 cm.

[0009] A bearing pin can be fixed to the valve leaf at one end. In this configuration, the bearing pin rotates with the valve leaf when it is twisted. Alternatively, one end of a bearing pin can engage with a bearing that is, for example, screwed onto a valve leaf surface. In this case, the bearing pin is not fixed to the valve leaf.

[0010] If a receptacle is designed as a recess in the housing, the end of the relevant bearing pin protrudes through the recess and extends outwards from the housing.

[0011] The damper blade of a fire damper is typically pivotable from its closed position to its open position against a restoring force of a spring element, wherein a retaining element is provided to fix the damper blade in its open position, which in the open position of the damper blade interacts with a holding area of ​​a thermally releasable release device, wherein the holding area can be released from its holding position by heat or the like and automatically moved into its release position, wherein the damper blade is held in its open position by the interaction of the retaining element and the holding area in the holding position, and wherein after release of the release device and thus after movement of the holding area from its holding position to its release position, the damper blade is moved into its closed position by the restoring force of the spring element.

[0012] At least one mounting point of the fire damper can have a bearing cup. The bearing cup can be formed integrally with the housing wall. In such a design, the bearing cup is, for example, deep-drawn into the housing wall. The bearing cup can also be designed as a separate component. In this case, the bearing cup can be inserted into a recess in the housing wall and seals the interior of the fire damper from the environment. The end of the bearing pin that interacts with this bearing cup projects into it. The bearing cup is preferably closed, so that the interior of the fire damper is sealed from the environment in the area of ​​this bearing point.

[0013] It is advantageous if the bearing cup has an outwardly projecting, preferably circumferential, collar and if the bearing cup is positioned in its corresponding receptacle such that the collar rests against the inside of the housing and the end of the bearing cup protrudes from the housing through the receptacle. The bearing cup simply needs to be inserted into the receptacle from the inside. Then the end of the bearing pin that interacts with this bearing cup can be inserted. This eliminates the need for additional components to secure the bearing cup to the receptacle. The bearing cup can be made of metal, for example. However, other designs, materials, or material combinations are conceivable.

[0014] In at least one receptacle, a bushing, preferably rotatably mounted in the bearing cup, can be provided. The bushing has both a receiving opening and a clearance behind the receiving opening (viewed in the insertion direction) for receiving the free end of the bearing pin associated with this bushing. The receiving opening is dimensioned such that the bearing pin is adequately held within it. If the receptacle is round and the bearing cup also has a round outer contour, the bearing cup can rotate in the receptacle when the flap blade is pivoted. If, for example, the receptacle is rectangular and the bearing cup also has a rectangular outer contour, the bearing cup does not rotate in the receptacle when the flap blade is pivoted. In such a configuration, the bearing pin rotates in the bushing and / or the bushing rotates in the bearing cup.

[0015] The bushing is preferably designed as a separate component. During assembly, the bushing is inserted into the bearing cup. After insertion, the free end of the bearing pin is located in the recess. Since the recess is larger than the receiving opening, pivoting the flap blade allows the end of the bearing pin to pivot and / or tilt within the recess.

[0016] In at least one bushing, the free space can be limited, at least in a partial area, preferably circumferentially, by a bushing wall, viewed orthogonally to the insertion direction, i.e., laterally, and the free space expands, preferably continuously, in the insertion direction. If the bushing wall is continuous, the free space is formed as a cavity. With a uniform and continuous expansion, the free space has the shape of a truncated cone.

[0017] The socket wall can consist of four wall sections forming the rectangular receiving opening. Two of the four wall sections are trapezoidal and parallel to each other, while the other two are rectangular and angled with respect to the insertion direction, thus increasing the distance between the wall sections in the insertion direction. The two trapezoidal wall sections are opposite each other, as are the rectangular wall sections. In this configuration, the clearance is wedge-shaped.

[0018] It is advantageous for the bushing wall to widen linearly, with the slope S of the bushing wall corresponding, at least in the area along which the end of the bearing pin travels during the movement of the flap leaf between the closed and open positions and vice versa, to the tilt angle of the end of the bearing pin located in this bushing when the flap leaf is in its open position. In the case of a free space, the bushing wall is designed as a conical segment, while in the case of a cavity, the bushing wall is continuous and forms a truncated cone. The area along which the end of the bearing pin travels during the movement of the flap leaf between the closed and open positions and vice versa is designed as a quarter segment when the flap leaf pivots at a 90° angle.

[0019] To accommodate the free end of a bearing pin, the receiving opening of at least one bushing can be round.

[0020] To accommodate the free end of a bearing pin, the receiving opening of at least one bushing can be rectangular, preferably square. Other embodiments are of course also conceivable.

[0021] For the purpose of weight-saving construction, a bushing can, for example, be made of a plastic, preferably of polytetrafluoroethylene.

[0022] In at least one mounting, the bearing cup and the bushing can be formed as a single unit. In such a design, the bearing cup simultaneously encompasses the bushing. When inserted, the collar rests against the inside of the housing, and the bearing cup, including the bushing, protrudes from the housing through the mounting. The bearing cup is preferably closed, thus sealing the interior of the fire damper from the environment in the area of ​​this mounting point.

[0023] The end of at least one bearing pin that engages in the receiving opening can have a round cross-section. A round cross-section ensures the rotational properties of the bearing pin regardless of the design of the receiving opening.

[0024] It is also possible that the end engaging in the receiving opening of at least one bearing pin has a square, preferably rectangular, cross-section.

[0025] At least one bearing point, the contour of the end of the bearing pin engaging in the receiving opening can be matched to the contour of the receiving opening that interacts with this bearing pin. For example, if the end of a bearing pin engaging in the receiving opening is round, the receiving opening that interacts with this bearing pin will also have a round contour.

[0026] Alternatively, at least at one bearing point, the end of the bearing pin engaging in the receiving opening can have a square contour, and the receiving opening interacting with this bearing pin can also have a square contour, with the respective bushing being rotatably mounted relative to the receiving opening. In such a configuration, the flap leaf is thus fixedly mounted relative to the bushing. If the bushing and the bearing cup are formed as a single piece, the bearing cup rotates in the receiving opening. When the flap leaf pivots, the bearing cup rotates in the receiving opening. In a two-part configuration of bearing cup and bushing, the bushing can, for example, be rotatably mounted in the bearing cup. Then, advantageously, the bushing rotates in the bearing cup when the flap leaf is rotated. Preferably, the bushing has a round outer contour and the bearing cup a round inner contour for this purpose.Instead of a square design for the end of the bearing pin and the receiving opening, other non-round designs, such as an oval design, are also possible.

[0027] In at least one bearing pin, the end engaging the receptacle and the end interacting with the valve leaf can be aligned. A bearing pin can have an unchanged contour along its length. However, it is also possible that the end interacting with the valve leaf of at least one bearing pin is, for example, a flat surface. In a flat design, the end has the form of a mounting plate, which can be screwed to the valve leaf surface. However, other designs and configurations of the interaction are also conceivable.

[0028] In at least one bearing pin, the end engaging the receptacle and the end interacting with the valve leaf can be offset from each other. This offset is orthogonal to the valve leaf surface. In such a configuration, the sum of the distances A1 + A2 can be greater than the thickness D of the valve leaf.

[0029] Furthermore, the distance A1 and the distance A2 can be identical. This means that the centers of the two bearing pins are equidistant from the imaginary center plane M.

[0030] At least at one bearing point, the outer region of at least the free end of the respective bearing pin, as seen from the central plane M, can lie flush with the plane of the flap blade surface. In such an embodiment, both the distance A1 and the distance A2 are each half the thickness D of the flap blade minus half the thickness C of the end of the bearing pin engaging in the receptacle. In such a configuration, at least the free end of the respective bearing pin is flush with the flap blade surface.

[0031] Preferably, at at least one bearing point, the outer region of the respective bearing pin, as seen from the central plane M, lies completely flush with the plane of the flap blade surface. In such a design, the region in contact with the flap blade is recessed into the flap blade, resulting in improved flow characteristics of the flap blade, particularly in the open position.

[0032] Alternatively, at at least one bearing point, the distances A1 and A2 can each be greater than half the thickness D of the flap blade minus half the thickness C of the end of the bearing pin engaging in the receptacle.

[0033] In this case, at least one bearing point can have distances A1 and A2 greater than half the thickness D of the flap blade.

[0034] Furthermore, it is possible that, in at least one bearing pin, the end engaging in the receptacle is aligned orthogonally to the area of ​​the front face opposite which the bearing pin protrudes. Thus, the flap blade, in its closed position, is orthogonal to the general flow direction.

[0035] In order to improve the sealing of the fire damper in the direction of flow when the damper blade is closed, even without the expansion of at least one hot seal, the damper blade can have at least one, preferably circumferential, cold seal on its circumferential end face.

[0036] The following section explains exemplary embodiments of the invention illustrated in the drawings. The drawings show: Fig. 1 is an oblique side view of a first embodiment of a fire damper according to the invention, Fig. 2 is a view in the direction of flow towards the object. Fig. 1 , Fig. 3 the detail "X" from Fig. 2 Fig. 4 shows an oblique view of a fire damper cut through the axis of rotation in the direction of flow; Fig. 5 shows a first embodiment of a bearing point of the object according to Fig. 1 , Fig. 6 a second embodiment of a bearing point of the object according to Fig. 1, Fig. 7 a third embodiment of a bearing point of the object according to Fig. 1 Fig. 8 shows a cross-sectional view of the object as seen in the direction of flow. Fig. 7 Fig. 9 shows an oblique side view of a second embodiment of a fire damper according to the invention, and Fig. 10 shows an oblique view of a fire damper cut parallel to the axis of rotation (at a small distance above the axis of rotation) as seen in the direction of flow. Fig. 9 with the flap blade in the open position, Fig. 11 a view seen in the direction of flow towards the object. Fig. 9 , Fig. 12 the detail "X" from Fig. 11 , Fig. 13 an oblique view of a fire damper seen in the direction of flow through the axis of rotation according to Fig. 9 with the flap leaf in the closed position, Fig. 14 shows a first embodiment of a bearing point of the second embodiment according to Fig. 9, Fig. 15 a second embodiment of a bearing point of the second embodiment according to Fig. 9 , Fig. 16 a third embodiment of a bearing point of the second embodiment according to Fig. 9 , Fig. 17 the right bearing point in an enlarged view of the object according to Fig. 16 , when the damper blade is in its closed position, Fig. 18 an oblique side view of a third embodiment of a fire damper according to the invention, Fig. 19 an oblique view of a fire damper cut parallel to the axis of rotation (at a small distance above the axis of rotation) in the direction of flow Fig. 18 with the flap blade in the open position, Fig. 20 a view seen in the direction of flow towards the object. Fig. 18 , Fig. 21 the detail "X" from Fig. 20 , Fig. 22 a bearing point in enlarged view of, for example, the object according to Fig. 15with a flap leaf in its closed position and Fig. 23 the bushing made of Fig. 22 in enlarged view.

[0037] In all figures, identical reference symbols are used for identical or similar components.

[0038] The Figs. 1 to 8 show a fire damper 1 with a round flow cross-section, while the Figs. 9 to 17 and 18 to 21 two different fire dampers 1 each with a rectangular flow cross-section.

[0039] As can be seen in the figures, each fire damper 1 has a housing 3 with a housing wall 2 and a round or square flow cross-section. In the case of a round housing 3, the housing wall 2 is a single piece, while in the case of a square housing 3, the housing wall 2 consists of four housing parts arranged at right angles to each other. The four housing parts can be produced, for example, by bending a sheet metal blank along three bend lines, with the triple-bent sheet metal blank being welded together along its two free edges to form a circumferential housing wall 2. Alternatively, for example, four separately formed housing parts can also be welded together to form a circumferential housing wall 2.

[0040] Inside the housing 3, a damper blade 4 is provided, pivotably mounted about a rotational axis. The damper blade 4 has two opposing damper surfaces 6 connected by a circumferential end face 5 and has a thickness D. For mounting the damper blade 4, the fire damper 1 further has two bearing points 7 forming the rotational axis and arranged centrally and oppositely with respect to the flow cross-section.

[0041] The fire damper 1 is connected at both ends to a ventilation duct (not shown) of an air conditioning system. Air flows in the housing 3 of the fire damper 1 in the direction of flow 8.

[0042] The flap blade 4 is moved between its open position, which is located, for example, in the following positions, via a mechanism not shown. Fig. 2 , 11 or 20 is depicted, and its closing position, which is shown, for example, in the Fig. 4 or 13as shown, movable. In the open position, the flap blade 4 is essentially aligned parallel to the general flow direction 8. In the closed position, as shown, for example, in the Fig. 4 and 13 As shown, the flap blade 4 is orthogonal to the general flow direction 8.

[0043] A cold seal 9 is provided on the end face 5 of the damper blade 4 to seal the fire damper 1. In addition, the fire damper 1 has a hot seal 10 on the inside of the housing 3. The hot seal 10 is located in the section of the housing 3 that extends along the circumference of the damper blade 4 when it is in its closed position.

[0044] In the event of a fire, the temperature rises. As a result, the thermal seal 10 expands. This expansion closes the circumferential gap between the end face 5 of the damper blade 4 and the housing wall 2 with the thermal seal 10 mounted on it. The expansion of the thermal seal 10, perpendicular to the flow direction 8, is only stopped when the thermal seal 10 comes into contact with the end face 5 of the damper blade 4. Then, the thermal seal 10 can only expand in or against the flow direction 8.

[0045] Fig. 2 Figure 3 shows the two bearing points 7 provided in the housing 3. Each bearing point 7 has a receptacle 11 on one side and a bearing pin 12 engaging in the corresponding receptacle 11 on the other. The receptacles 11 are arranged centrally on opposite sides with respect to the flow cross-section. Thus, the bearing in the Fig. 2 , 11 or20 The distance x 1 shown between the outermost point of the flow cross-section in the lower half of the housing 3 and the left-hand image 11 in the relevant figure is equal to the distance x 1 between the outermost point of the flow cross-section in the lower half of the housing 3 and the right-hand image 11 in the relevant figure. The identical distance x 1 is also found both between the outermost point of the flow cross-section in the upper half of the housing 3 and the left-hand image 11 in the relevant figure, and between the outermost point of the flow cross-section in the upper half of the housing 3 and the right-hand image 11 in the relevant figure.

[0046] For example, the Fig. 2 , 11 and 20As can be seen, the two bearing pins 12 are arranged offset from each other relative to the central plane M of the flap blade 4, which extends parallel to the two flap blade surfaces 6. The circumferential cold seal 9 is located in the central plane M. One bearing pin 12 is offset by a distance A1 in the direction of one flap blade surface 6 relative to the central plane M. Distance A1 is defined as the distance between the central plane M and the center point of the respective bearing pin 12. The other bearing pin 12 is offset by a distance A2 in the direction of the other flap blade surface 6 relative to the central plane M. Distance A2 is defined as the distance between the central plane M and the center point of the other bearing pin 12.

[0047] The distance A1 and the distance A2 are identical. Therefore, the centers of the two bearing pins 12 are equidistant from the imaginary center plane M. The centers of the two receptacles 11 in the housing 3 are thus – as in the Fig. 4 , 13 and 19 As can be seen - viewed in the direction of flow 8 - they are arranged at a distance A, which results from the sum of the distances A 1 + A 2.

[0048] As can be seen from the figures, the end of each bearing pin 12 that engages in the receptacle 11 is oriented orthogonally to the area of ​​the end face 5 opposite which the bearing pin 12 projects. Each bearing pin 12 thus has a free end that projects opposite the end face 5 of the flap leaf 4, and an end that serves to fasten the bearing pin 12 to the flap leaf 4.

[0049] According to the Fig. 3 , 12 and 21The bearing pin 12 engages with one end in the receptacle 11. The other end of each bearing pin 12 is designed as a flat mounting plate 14, by means of which the respective bearing pin 12 is fastened in a recess on the flap blade surface 6.

[0050] The Figs. 5 to 7 Figures 14 to 16 show different embodiments of bearing pins 12 and thus of the designs of the receptacles 11 in the housing 3.

[0051] In the Figs. 5 and 6 as in the Figs. 14 and 15 The bearing pins 12 have an offset between the end engaging in the receptacle 11 and the end interacting with the flap blade surface 6. This means that the receptacles 11 are located outside the heat seal 10 in the housing 3. This is due to the offset between the two ends of each bearing pin 12. In this configuration, the distances A1 and A2 are each greater than half the thickness D of the flap blade 4.

[0052] In the exemplary embodiments according to the Fig. 7 and 16 The two ends of each bearing pin 12 are aligned with each other. The outer region of the respective bearing pin 12, as seen from the central plane M, lies completely flush and aligned with the plane of the respective flap surface 6. In such an embodiment, both the distance A1 and the distance A2 are each half the thickness D of the flap surface 4 minus half the thickness C of the end of the bearing pin 12 engaging in the receptacle 11. A recess is provided in each of the two flap surfaces 6 for the complete reception of the end of each bearing pin 12, which is designed as a mounting plate 14.

[0053] In the illustrated embodiments, each receptacle 11 contains a bearing cup 13 with an outwardly projecting, circumferential collar 15. The collar 15 rests against the inside of the housing 3. Thus, the bearing cup 13, with its closed end, protrudes through the receptacle 11 and out of the housing 3. Since the bearing cup 13 is closed at the end protruding from the housing 3, the housing 3 is also sealed to the outside in the area of ​​each bearing point 7.

[0054] The end of the bearing pin 12, inserted into a receiving opening 16, supports the flap blade 4 in the receiving opening 11. Viewed in the insertion direction 17, a clearance 18 exists behind the receiving opening 16. After insertion, the free end of the bearing pin 12 is located in this clearance 18. The clearance 18 has a larger cross-section than the receiving opening 16. Therefore, when the flap blade 4 pivots, a pivoting and / or tilting movement of the end of the bearing pin 12 within the clearance 18 is possible.

[0055] In the Fig. 6, 7 , 15 , 16 and 17The end of the bearing pin 12 projecting from the end face 5 is square. In this embodiment, a separately formed bushing 19 is provided in the bearing cup 13, which has a square receiving opening 16 into which the end of the bearing pin 12 is inserted. Since the bearing cup 13 is round and the bushing 19 also has a round outer contour, the bushing 19 can rotate in the bearing cup 13 when the flap blade 4 is pivoted. The bushing 19 is thus rotatably mounted in the bearing cup 13. In this embodiment, the flap blade 4 is fixed against rotation relative to the bushing 19. Instead, when the flap blade 4 is pivoted, the bushing 19 rotates in the bearing cup 13.

[0056] As far as the Fig. 3 , 5 , 12 , 14 and 21As regards, these show a design in which the bearing cup 13 and the bushing 19 are formed in one piece at each bearing point. A previously described two-part design of bearing cup 13 and bushing 19 is shown, for example, in the Fig. 6, 7 , 15 or 16 depicted.

[0057] How especially the Fig. 6, 7 , 15 , 16 and 17As can be seen, each bushing 19 comprises both a receiving opening 16 and a clearance 18 located behind the receiving opening 16 (viewed in the insertion direction 17) for receiving the free end of the bearing pin 12 associated with that bushing 19. The receiving opening 16 is dimensioned such that the bearing pin 12 is adequately held within it. In the illustrated embodiments, the bushing 19 is designed as a separate component. It is inserted from the inside into the respective bearing cup 13. After insertion, the free end of the bearing pin 12 is located in the clearance 18. Since the clearance 18 is larger than the receiving opening 16, pivoting of the flap 4 allows for both pivoting and tilting movements of the end of the bearing pin 12 within the clearance 18. Furthermore, in each bushing 19, the clearance 18 is bounded laterally (i.e., perpendicular to the insertion direction 17) by a circumferential bushing wall 20.In the illustrated embodiment, the free space 18, as in particular in the . Figs. 22 and 23 The shape of a wedge, pointing against the insertion direction 17, can be seen. The bushing wall 20 consists of four wall sections 20', 20", which form the rectangular receiving opening 16. The two parallel to the drawing plane of Fig. 22 The two aligned wall sections 20' have a trapezoidal shape and are aligned parallel to each other. The two other wall sections 20" have a rectangular shape and are oriented obliquely with respect to the insertion direction 17, so that the distance between the wall sections 20" increases when viewed in the insertion direction 17.

[0058] The inclined orientation, i.e., the slope S, of the wall sections 20" corresponds to the tilt angle α of the end of the bearing pin 12 located in this bushing 19 when the flap leaf 4 is in its open position. Since, in the illustrated embodiment, both wall sections 20" are inclined with respect to the insertion direction 17, the end of the bearing pin 12 can be inserted into the bushing 19 in two orientations offset by 180°. Of course, an arrangement is also conceivable in which only one of the two wall sections 20" is inclined with respect to the insertion direction 17. Then the end of the bearing pin 12 can only be inserted into the bushing 19 in a single orientation. The two trapezoidal wall sections 20', which are aligned parallel to each other, provide lateral support to the end of the bearing pin 12 when the flap leaf 4 is displaced.

[0059] Since the bushing wall 20 is formed circumferentially in the illustrated embodiment, the free space 18 is designed as a cavity. Of course, other configurations of the free space 18 are also possible. For example, the free space 18 can widen uniformly and continuously over the entire circumference of the receiving opening 16. In this case, due to the uniform and continuous widening, the free space 18 has the shape of a truncated cone.

[0060] As the Fig. 6, 7 , 15 , 16 and 17 As shown, the bushing wall 20 expands linearly in the insertion direction 17, at least in a partial area of ​​the circumference of the receiving opening 16, wherein the slope S of the bushing wall 20 corresponds to the tilt angle α of the end of the bearing pin 12 located in this bushing 19 when the flap leaf 4 is in its open position.

[0061] In the design, for example according to the Fig. 6or 15 The receiving opening 16 and the free end of the bearing pin 12 associated with this bushing 19 are rectangular. The clearance 18 of the bushing 19 is designed such that the end of the bearing pin 12 can tilt within the clearance 18. Pivoting of the flap 4 is made possible by the fact that the bushing 19 is rotatably mounted in the bearing cup 13.

[0062] For example, in the Fig. 5 and 14An alternative embodiment is shown. Here, the bearing cup 13 and the bushing 19 are formed as a single unit. The collar 15 of the bearing cup 13 rests against the inside of the housing 3. The bushing 19 thus protrudes from the housing 3 through the receptacle 11. The bearing cup 13 can be rotatably or rotationally fixedly mounted in the receptacle 11. The clearance 18 of the bushing 19 is bounded laterally, orthogonally to the insertion direction 17, by a circumferential bushing wall 20. The clearance 18 widens continuously and uniformly around the entire circumference of the receiving opening 16 in the insertion direction 17. Since the bushing wall 20 is circumferential, the clearance 18 is formed as a cavity. Due to the uniform and continuous widening, the clearance 18 has the shape of a truncated cone.Due to the design of the free space 18, both a pivoting and a tilting movement of the end of the bearing pin 12 within the free space 18 is possible when the flap blade 4 is pivoted. Therefore, with this design, the bushing 19 can also be mounted in the receptacle 11 in a rotationally fixed manner.

[0063] It is possible that the slope S of the bushing wall 20 corresponds to the tilt angle α of the end of the bearing pin 12 located in this bushing 19 only in the area along which the end of the bearing pin 12 travels when the flap leaf 4 is moved between the closed and open positions and vice versa, when the flap leaf 4 is in its open position. In this case, the bushing wall 20 has a corresponding design only in the area of ​​the circumference of the receiving opening 16 along which the end of the bearing pin 12 travels when the flap leaf 4 is moved between the closed and open positions and vice versa. The area along which the end of the bearing pin 12 travels when the flap leaf 4 is moved between the closed and open positions and vice versa is designed as a quarter segment when the flap leaf is pivoting at a 90° angle.

[0064] For example, in the Fig. 3 , 12 and 21 The illustrations show embodiments in which the bearing cup 13, the collar 15, and the bushing 19 are formed as a single unit. The collar 15 rests against the inside of the housing 3. The bushing 19 thus protrudes from the housing 3 through the receptacle 11. The bushing 19 can be rotatably or non-rotatably mounted in the receptacle 11.

[0065] How the Fig. 3 , 12 and 21As can be seen, each bushing 19 comprises both a receiving opening 16 and a clearance 18 located behind the receiving opening 16, viewed in the insertion direction 17, for receiving the free end of the bearing pin 12 associated with that bushing 19. The receiving opening 16 is dimensioned such that the bearing pin 12 is adequately held within it. After insertion, the free end of the bearing pin 12 is located in the clearance 18. Since the clearance 18 is larger than the receiving opening 16, pivoting the flap 4 allows at least a pivoting movement, or alternatively a pivoting and tilting movement, of the end of the bearing pin 12 within the clearance 18. Furthermore, in each bushing 19, the clearance 18 is bounded laterally, orthogonally to the insertion direction 17, by a circumferential bushing wall 20, with the clearance 18 widening continuously and uniformly in the insertion direction 17.Since the bushing wall 20 is formed all around, the free space 18 is designed as a cavity. Due to the uniform and continuous expansion, the free space 18 has the shape of a truncated cone. Of course, the free space 18 can also have a different shape, for example, as shown in the [reference]. Figs. 22 and 23 The design shown is present.

[0066] Even in the designs according to the Fig. 3 , 12 and 21 The bushing wall 20 widens linearly in the insertion direction 17, with the slope S of the bushing wall 20 corresponding to the tilt angle α of the end of the bearing pin 12 located in this bushing 19 when the flap leaf 4 is in its open position.

[0067] In the illustrated embodiments, each bearing pot 13 is designed to be closed.

[0068] In the Fig. 5 and 14In the illustrated embodiments, the receiving opening 16 of the bushing 19, which is formed integrally with the bearing cup 13, has a round cross-section for receiving the end of the bearing pin 12, which also has a round cross-section. This allows the end of the bearing pin 12, and thus also the flap blade 4, to rotate in the bushing 19.

[0069] The arrangement of the two bearing pins 12 on the opposite flap leaf surfaces 6 is described, among other things, in the Fig. 2 and 4 depicted. In Fig. 2 The image shows flap 4 in its open position. Fig. 4 and 13 The closed position is shown. Due to the offset of the receptacles 11 in the direction of flow 8, the circumferential heat seal 10, located on the inside of the housing 3, is not interrupted.

[0070] Since the thermal seal 10 is circumferential and has the same width at every point, there are no weak points between the end face 5 and the housing 3 in the area of ​​the two bearing points 7 when the flap leaf 4 is closed. For example, the Fig. 4 and 13 As shown, the flap blade 4 is orthogonal to the flow direction 8 in the closed position. In In the closed position, a movement gap is located around the entire circumference of the flap blade 4 between the end face 5 and the housing wall 2 with the thermal seal 10 applied thereto. The movement gap is dimensioned such that the flap blade 4 can be easily moved between its open and closed positions.

[0071] As explained above, the Figs. 10 to 17 a fire damper 1 with a rectangular flow cross-section. The ones in the Figs. 10 to 17The fire damper shown has a rectangular flow cross-section. The difference to the previously described fire damper with a round flow cross-section ( Figs. 1 to 9 ) consists primarily in the fact that the in the Figs. 10 to 17 The fire damper 1 shown has a housing 3 consisting of three housing parts arranged one behind the other in the direction of flow 8, namely a wall frame 21 and two connection frames 22. The wall frame 21 is arranged between the two connection frames 22. Each of the three housing parts has a circumferential flange 23 in the area of ​​each of its two ends, so that the wall frame 21 is connected to the two connection frames 22 and the free end of each connection frame 22 can be connected to a duct (not shown) on site.

[0072] The two connection frames 22 have identical flow cross-sections because their internal dimensions are identical. In contrast, the flow cross-section of the wall frame 21 is smaller. This is because the distance Y between the pair on opposite sides, extending orthogonally to the axis of rotation, is smaller than the corresponding distance in the area of ​​each of the two connection frames 22. Therefore, the flow cross-section in the area of ​​the wall frame 21 is somewhat constricted.

[0073] The wall frame 21 has a width B smaller than the height H of the flap blade 4. The height H of the flap blade 4 is defined as the distance between the two edges of the flap blade 4 extending parallel to the axis of rotation. The width B is the extent of the wall frame 21 as seen in the direction of flow 8. Since the width B of the wall frame 21 is smaller than the height H of the flap blade 4, the flap blade 4, in its open position, projects into the respective connecting frame 22 in the area of ​​its edges extending parallel to the axis of rotation.

[0074] Since in the area of ​​each connection frame 22 the distance Y of the pair on opposite sides of the housing 3, which extend orthogonally to the axis of rotation, is greater than in the area of ​​the wall frame 21, there is sufficient clearance between the area of ​​the end face 5 of the flap leaf 4 extending orthogonally to the axis of rotation and the adjacent inner side of the housing 3, which also extends orthogonally to the axis of rotation.

[0075] In the Figs. 18 to 21 A fire damper 1 with a rectangular flow cross-section is shown, but the housing 3 - as in the round design - is formed in one piece in the direction of flow 8.

[0076] Fig. 20 The diagram shows the 4th leaf in its open position. The oblique orientation of the 4th leaf in the open position is clearly visible. While - as in Fig. 20It can be seen that on the left side of the flap 4, the distance between the inside of the housing wall 2 and the rear corner of the flap 4 is significantly smaller than the distance between the inside of the housing wall 2 and the front corner; on the right side of the flap 4, this is exactly the opposite. Here, the distance between the inside of the housing wall 2 and the front corner of the flap 4 is significantly smaller than the distance between the inside of the housing wall 2 and the rear corner.

[0077] In the various embodiments shown in the figures, the thermal seal 10 is arranged in a groove 24 with a rectangular cross-section. The groove 24 extends along the circumference of the flap blade 4 when closed. Thus, the thermal seal 10 also extends along the circumference of the flap blade 4 when closed. Due to the arrangement of the thermal seal 10 in the groove 24, the thermal seal 10 is flush with the adjacent inner surface of the respective housing wall 2. The flap blade 4 is dimensioned such that, in the closed position of the flap blade 4, there is a circumferential gap between the end face 5 of the flap blade 4 and the thermal seal 10, which has not yet expanded due to heat.

Claims

1. Fire damper (1) with a housing (3) having a housing wall (2), preferably with a round or square flow cross-section, and with a flap leaf (4) preferably mounted in the middle in relation to the flow cross-section such as to be pivotable about a rotation axis between an open position and a closed position, preferably consisting of calcium silicate and having a thickness D, wherein the flap leaf (4) has two opposed flap leaf surfaces (6) connected by a circumferential face surface (5), and wherein, in order to mount the flap leaf (4), the fire damper (1) has two mounting points (7) forming the rotation axis and centrally opposed in relation to the flow cross-section, and wherein at least one mounting point (7) is formed by a receptacle (11) provided in the housing (3), preferably in the form of a recess, on the one hand and by a bearing pin (12) on the other hand, wherein one end of the bearing pin (12) is connected to the flap leaf (4) and its other end, which projects from the face surface (5) of the flap leaf (4), projects into the corresponding receptacle (11), and wherein the fire damper (1) further comprises at least one hot seal (10) consisting of a material which expands when exposed to heat, wherein the at least one hot seal (10) is provided on the circumferential face surface (5) of the flap leaf (4), wherein, when the flap leaf (4) is in the closed state, a circumferential movement gap is provided between the inside of the housing (1) and the hot seal (10) which has not yet expanded due to the effect of heat and / or is provided on the inside of the housing (3) at least in the part region which extends along the circumference of the flap leaf (4) in the closed state, wherein when the flap leaf (4) is in the closed state a circumferential movement gap is provided between the face surface (5) of the flap leaf (4) and the hot seal (10) which has not yet expanded due to the effect of heat, characterised in that the bearing pins (12) are arranged offset relative to one another with respect to the centre plane M of the flap leaf (4) extending parallel to the two flap leaf surfaces (4), wherein one bearing pin (12) is arranged offset at a distance A1 in the direction of one flap leaf surface (6) relative to the centre plane M and the other bearing pin (12) is arranged offset at a distance A2 in the direction of the other flap leaf surface (6) relative to the centre plane M, wherein the distance A1 is understood to be the distance between the centre plane M and the centre point of the one bearing pin (12) and the distance A2 is understood to be the distance between the centre plane M and the centre point M of the other bearing pin (12), and wherein the centre points of the two receptacles (11) are arranged in the direction of flow (8) at a distance A which results from the sum of the distances A1 +A2.

2. Fire damper (1) according to claim 1, characterised in that at least one receptacle (11) has a bearing cup (13).

3. Fire damper (1) according to the preceding claim, characterised in that at least one bearing cup (13) has an outwardly facing, preferably circumferential, collar (15) and that the at least one bearing cup (13) is arranged in the receptacle (11) assigned to it such that the collar (15) lies against the inside of the housing (3) and the bearing cup (13) projects with its end region through the receptacle (11) out of the housing (3).

4. Fire damper (1) according to one of claims 2 or 3, characterised in that, in the case of at least one receptacle (11), a bush (19) is provided in the bearing cup (13), preferably rotatably mounted in the bearing cup (13), the bush (19) having both a receiving opening (16) and a free space (18) located behind the receiving opening (16), as viewed in the insertion direction (17), for receiving the free end of the bearing pin (12) assigned to this bush (19).

5. Fire damper (1) according to the preceding claim, characterised in that, in the case of at least one bush (19), the free space (18), viewed orthogonally to the insertion direction (17), is bounded, preferably circumferentially, by a bush wall (20), at least in a part region, the free space (18) widening, preferably continuously, as viewed in the insertion direction (17).

6. Fire damper (1) according to the preceding claim, characterised in that the bush wall (20) consists of four wall regions (20', 20") forming the rectangular receiving opening (16), wherein two of the four wall regions (20') have a trapezoidal shape and are aligned parallel to one another and wherein the other two of the four wall regions (20") have a rectangular shape and are aligned obliquely with respect to the insertion direction (17), so that the distance between the wall regions (20") increases when viewed in the insertion direction (17).

7. Fire damper (1) according to one of claims 4 or 5, characterised in that the bush wall (20) widens linearly, the slope S of the bush wall (20), at least in the region along which the end of the bearing pin (12) travels during the displacement of the flap leaf (4) between the closed position and the open position and vice versa, corresponding to the tilt angle α of the end of the bearing pin (12) located in this bush (19) when the flap leaf (4) is in its open position.

8. Fire damper (1) according to any of claims 4 to 7, characterised in that the receiving opening (16) of at least one bush (19) is round in shape.

9. Fire damper (1) according to any of claims 4 to 8, characterised in that the receiving opening (16) of at least one bush (19) is angular, preferably rectangular, in shape.

10. Fire damper (1) according to any of claims 4 to 9, characterised in that at least one bush (19) is made from a plastic, preferably polytetrafluorethylene.

11. Fire damper (1) according to any of claims 4 to 10, characterised in that, in the case of at least one receptacle (11), the bearing cup (13) and the bush (19) are formed in one piece.

12. Fire damper (1) according to any of claims 4 to 11, characterised in that the end of at least one bearing pin (12) engaging in the receiving opening (16) has a round cross-section.

13. Fire damper (1) according to any of claims 4 to 12, characterised in that the end of at least one bearing pin (12) engaging in the receiving opening (16) has an angular, preferably rectangular, cross-section.

14. Fire damper (1) according to any of claims 4 to 13, characterised in that, in the case of at least one mounting point (7), the contour of the end of the bearing pin (12) engaging in the receiving opening (16) is matched to the contour of the receiving opening (16) interacting with this bearing pin (12), the receiving opening (16) of at least this bush (19) being round in shape.

15. Fire damper (1) according to any of claims 4 to 14, characterised in that, in the case of at least one mounting point (7), the contour of the end of the bearing pin (12) engaging in the receiving opening (16) is matched to the contour of the receiving opening (16) interacting with this bearing pin (12), wherein, in the case of at least the receptacle (11) of this mounting point (7), a bush (19) is provided in the bearing cup (13), being rotatably mounted in the bearing cup (13), the bush (19) having both a receiving opening (16) and a free space (18) located behind the receiving opening (16), as viewed in the insertion direction (17), for receiving the free end of the bearing pin (12) assigned to this bush (19).

16. Fire damper (1) according to one of claims 14 or 15, characterised in that, in the case of at least one mounting point (7), the end of the bearing pin (12) engaging in the receiving opening (16) has an angular contour and that the receiving opening (16) interacting with this bearing pin (12) also has an angular contour, the relevant bush (19) being mounted rotatably in relation to the receptacle (11).

17. Fire damper (1) according to any of the preceding claims, characterised in that, in the case of at least one bearing pin (12), the end engaging in the receptacle (11) and the end interacting with the flap leaf (4) are aligned.

18. Fire damper (1) according to any of the preceding claims, characterised in that, in the case of at least one bearing pin (12), the end engaging in the receptacle (11) and the end interacting with the flap leaf (4) are arranged offset relative to one another.

19. Fire damper (1) according to any of the preceding claims, characterised in that the distance A1 and the distance A2 are identical.

20. Fire damper (1) according to any of the preceding claims, characterised in that, in the case of at least one mounting point (7), the outer region of at least the free end of the relevant bearing pin (12), as seen from the centre plane M, lies flush and aligned in the plane of the flap leaf surface (6).

21. Fire damper (1) according to any of the preceding claims, characterised in that, in the case of at least one mounting point (7), the distances A1 and A2 are each greater than half the thickness D of the flap leaf (4) minus half the thickness C of the end of the bearing pin (12) engaging in the receptacle (11).

22. Fire damper (1) according to any of the preceding claims, characterised in that, in the case of at least one bearing pin (12), the end engaging in the receptacle (11) is aligned orthogonally to the region of the face surface (5) from which the bearing pin (12) protrudes.

23. Fire damper (1) according to any of the preceding claims, characterised in that the flap leaf (4) has at least one, preferably circumferential, cold seal (9) on its circumferential face surface (5).

Images