Apparatus for stabilizing blade for relief damper

Abstract

Provided is a blade stabilization apparatus for a relief damper, and more specifically, to a blade stabilization apparatus for a relief damper which can stably maintain an opening angle of a damper blade at any angle when the damper opens or closes after the center of gravity is always aligned with a centerline of a rotating shaft in a perpendicular direction to the damper blade.

Claims

1. A blade stabilization apparatus for a relief damper, comprising: a rotating shaft installed on a relief damper side; a damper blade which is always balanced on the rotating shaft when no pressure is acting thereon while being horizontally positioned on the rotating shaft; and a counterweight installed perpendicular to a centerline of the rotating shaft, wherein a center of gravity of the entire damper blade is necessarily aligned with the centerline of the rotating shaft perpendicular to the damper blade, and wherein the damper blade opens or closes by itself while rotating about the rotating shaft according to a pressure difference acting on the damper blade when pressure acts on the damper blade.

2. The apparatus of claim 1, wherein the damper blade is formed by integrating a first blade which has a long length and is formed on one side with a second blade which has a short length and is formed on the other side centered on the rotating shaft, and a weight is added to an upper end of the second blade to match a center of gravity of the second blade with that of the first blade which has the long length.

3. The apparatus of claim 1, wherein the counterweight is installed on a lower end of the rotating shaft.

Description

DESCRIPTION OF DRAWINGS

(1) FIG. 1 is a configuration view of a blade stabilization apparatus for a relief damper according to the present invention.

(2) FIG. 2 is a configuration view for describing the blade stabilization apparatus for a relief damper according to the present invention.

(3) FIG. 3 is a configuration view that illustrates an operating state of the blade stabilization apparatus for a relief damper according to the present invention.

(4) FIG. 4 is a configuration view that illustrates a rotational force relationship of the blade stabilization apparatus for a relief damper according to the present invention.

(5) FIG. 5 is another example of a blade stabilization apparatus for a relief damper according to the present invention.

(6) FIG. 6 is another example of a rotational force relationship of the blade stabilization apparatus for a relief damper in FIG. 5.

MODES OF THE INVENTION

(7) Exemplary embodiments of the present invention will be illustrated in the accompanying drawings and described in detail in the detailed description, but the embodiments may be changed and have many alternative forms. However, the present invention is not limited to specific embodiments, and it should be understood that the present invention includes all changes, equivalents, and substitutes included in the spirit and technical scope of the present invention. In the description of the present invention, when it is determined that a detailed description of related known technologies may unnecessarily obscure the gist of the present invention, the detailed description will be omitted.

(8) First, the present invention is similar to the related art, in the present invention, the apparatus is also installed and used in a pressure differential smoke control system to appropriately discharge excessively supplied air to special evacuation stairways, vestibules, emergency platforms, and so on of high-rise buildings, thereby maintaining an appropriate pressure differential, preventing harmful gases and smoke from entering evacuation routes, and facilitating the opening of evacuation doors to promote human safety. Also, the apparatus may be also used to stably adjust and maintain pressure in all gas systems, similar to a relief valve that stably adjusts and maintains pressure in liquid systems. For example, the apparatus may be used as a pressure relief device in a gas-based fire extinguishing device protection area.

(9) Therefore, the processes and methods for installation in the system will be omitted below.

(10) FIG. 1 is a configuration view of a blade stabilization apparatus for a relief damper according to the present invention.

(11) Referring to FIG. 1, the blade stabilization apparatus for a relief damper includes a rotating shaft 300 installed on a relief damper side and a damper blade 100 which is always balanced on the rotating shaft 300 when no pressure is acting thereon while being horizontally positioned on the rotating shaft 300, wherein the damper blade 100 opens or closes while rotating about the rotating shaft 300 according to a pressure difference acting on the damper blade 100 when pressure acts on the damper blade 100. Opening force: M1 (opening force) Restoring force: M2 (closing force)

(12) The damper blade 100 is made of a flat plate. In this case, the damper blade 100 is formed as a single piece, and when subdivided, a long first blade 110 formed on one side and a short second blade 120 formed on the other side are integrally formed.

(13) A weight is added to the second blade 120 to adjust the center of gravity with the long first blade 110. A pressure-acting part 130 is formed on an end portion of the first blade 110 to extend therefrom so that the entire damper blade 100 moves and opens when pressure acts thereon.

(14) The center of gravity of the damper blade having the structure of the damper blade 100 is aligned with the centerline of the rotating shaft 300 perpendicular to the damper blade 100, and the damper blade 100 horizontally installed on the rotating shaft 300 is in a state of being horizontally maintained by itself when an external force such as pressure is not acting on it.

(15) FIG. 2 is a configuration view for describing the blade stabilization apparatus for a relief damper according to the present invention.

(16) Referring to FIG. 2, the apparatus will be described in more detail in relation to the length and the mark of the damper blade. L1: Total length of first blade L2: Length of second blade L3: Length of pressure-acting part

(17) As described above, the damper blade 100 has an unbent flat plane shape and includes a first blade 110, a second blade 120, a pressure-acting part 130, and an additional weight 140 which are integrally formed. In this case, the length L1 of the first blade 110 and the pressure-acting part 130 is longer than the length L2 of the second blade 120, and the length L2 of the second blade 120 is the same as the length L2 of the first blade 110.

(18) In this case, because the length L2 of the second blade 120 is smaller than the length L1, the additional weight 140 is used to add weight to the second blade 120, and thus the center of gravity of the entire damper blade is aligned with the centerline of the rotating shaft 300.

(19) The pressure-acting part 130 formed to extend from an end portion of the first blade 110 corresponds to the length L3 and plays an important role in fully opening the damper blade 100 when pressure acts thereon.

(20) FIG. 3 is a configuration view that illustrates an operating state of the blade stabilization apparatus for a relief damper according to the present invention. ?P: Pressure difference *W: Center of gravity

(21) Referring to FIG. 3, pressure in a primary side space is higher than pressure in a secondary side space, and a pressure difference ?P is a state in which pressure is evenly acts evenly on the entire surface of the damper blade 100 in the primary side space. Therefore, the pressure acting on the length L2 of the first blade 110 and the pressure acting on the length L1 of the second blade 120 are in equilibrium, but the pressure acting on the pressure-acting part 130 that corresponds to the L3 portion becomes an opening force that moves and rotates the damper blade 100 clockwise.

(22) Meanwhile, the center of gravity W of the damper blade 100 serves as a restoring force that rotates the damper blade 100 in a direction opposite to the action of the pressure and acts counterclockwise. Therefore, when the opening force is greater than the restoring force, the damper blade rotates and opens.

(23) FIG. 4 is a configuration view that illustrates a rotational force relationship of the blade stabilization apparatus for a relief damper according to the present invention. ?: Rotation angle of damper blade

(24) Referring to FIG. 4, the pressure ?P acting on the pressure-acting part 130 corresponding to the length L3 of the damper blade 100 obliquely acts on a surface of the damper blade 100 as the damper blade 100 rotates. Therefore, a force acting perpendicular to the damper blade 100 is proportional to a cosine value of the rotation angle, i.e., ?P.Math.cos ?. However, the distance between the center where pressure acts and the rotating shaft is not changed.

(25) When the distance refers to L, the force (opening force) that rotates the damper blade 100 is as follows.
M1=?P.Math.cos ?.Math.L

(26) The weight W that causes the center of gravity of the damper blade 100 to reversely rotate the damper blade is not changed, but the distance from the rotating shaft 300 that exerts the rotational force (restoring force) changes from R to R1. In this case, R1 is equal to R.Math.cos ?. Therefore, the restoring force that causes the center of gravity to reversely rotate the damper blade 100 is as follows.
M2=W.Math.R cos ?

(27) When the rotational force M1 (opening force) is equal to the rotational force M2 (restoring force), the damper blade 100 stops rotating.

(28) When the primary side pressure ?P becomes small and M2 is greater than or equal to M1, the damper blade 100 is closed and does not move. As the primary side pressure ?P increases, at the point where M1 is greater than or equal to M2, the damper blade 100 begins to rotate and open. When the damper blade 100 is opened to discharge pressure so that the pressure ?P is lowered, the damper blade 100 stops rotating at the angle where M1 and M2 are balanced.

(29) The formula for determining at what pressure the damper blade 100 will be balanced is as follows.
M1=M2.fwdarw.?P.Math.cos ?.Math.L=W.Math.R cos ?
?P.Math.L=W.Math.R.fwdarw.?P=W.Math.R/L

(30) In the above formula, because L is a constant determined by the size of damper blade 100, ?P may be determined by adjusting the weight W of the counterweight 200 or the distance R from the rotating shaft 300.

(31) That is, as described above, the main point of the present invention is that the center of gravity of the entire damper blade 100 should be always aligned with the centerline of the rotating shaft 300 perpendicular to the damper blade 100, rather than adjusting the counterweight 200.

(32) Because the phenomenon where the position of the equilibrium point between the opening force and the restoring force varies according to the opening angle of the damper blade and the pressure energy acting on the damper blade changes according to the opening angle of the damper blade is not analyzed, in all conventional gravity-type dampers, the relationship between the opening force and the restoring force cannot be explained mathematically. However, in the structure of the present invention, both the opening force M1 and the restoring force M2 of the damper blade 100 are precisely proportional to cos ?, and thus mathematical interpretation of damper movement is clear, and an opening angle of the damper blade 100 is stably maintained at any angle.

(33) In the result of tests using the damper blade 100 as described above, with an opening angle of 80? and an effective opening of 80% or greater, a much larger degree of opening is achieved compared to the conventional gravity-type dampers, and the variation range of primary side pressure is stable within +6% in all opening angle ranges of 0 to 80? compared to the pressure at which opening starts.

(34) While the center of gravity should be necessarily aligned with the blade in the same direction when viewed from the rotating shaft, the position of the counterweight may be in the opposite direction depending on the damper installation conditions. Therefore, as described above, under the premise that the center of gravity of the entire damper blade 100 should be always aligned with the centerline of the rotating shaft 300 perpendicular to the damper blade 100 and the center of gravity should be in the same direction as the blade when viewed from the rotating shaft, the present invention may be modified to the following structure.

(35) FIG. 5 is another example of a blade stabilization apparatus for a relief damper according to the present invention, and FIG. 6 is another example of a rotational force relationship of the blade stabilization apparatus for a relief damper in FIG. 5.

(36) When the damper blade 100 is horizontally positioned on the rotating shaft 300 and pressure is not acting thereon, the damper blade 100 is always balanced on the rotating shaft 300. Also, the damper blade 100 opens or closes by itself while rotating about the rotating shaft 300 according to the pressure difference acting on the damper blade 100 when pressure acts on the damper blade 100. Therefore, if the aforementioned conditions are satisfied, a counterweight 200 may be installed and used under the rotating shaft 300, as illustrated in FIGS. 5 and 6.

(37) While the present invention has been particularly described with reference to exemplary embodiments, it should be understood by those of skilled in the art that various changes, modifications, and replacements in form and details may be made without departing from the spirit and scope of the present invention. Therefore, the exemplary embodiments and claims disclosed in the present invention should be considered in a descriptive sense only and not for purposes of limitation. Accordingly, the scope of the present invention is not limited by the embodiments and the accompanying drawings. The scope of the present invention should be defined by the appended claims and encompasses all modifications and equivalents that fall within the scope of the appended claims.