JP2010060220A - Damper for pressure control - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a damper for pressure control capable of stably controlling a chamber pressure irrespective of an amount of operation of a damper blade even in a room under execution of chamber pressure control such as a bioclean room, a regenerative medicine facility, or an animal experiment and breeding facility. <P>SOLUTION: The damper for pressure control comprises a casing 12 and the movable damper blade 14, and it is formed such that a passage cross-sectional area A<SB>t</SB>m<SP>2</SP>of a throttle part comprising a gap between the casing and the damper blade satisfies a formula of A<SB>t</SB>=A<SB>0</SB>√äf/(C<SB>β</SB>+C<SB>0</SB>)} where a cross-sectional area of a casing inlet is represented by A<SB>0</SB>m<SP>2</SP>, and the amount of operation of the damper blade is represented by θ% such that a resistant coefficient with respect to the amount of operation of the damper blade 14 is changed in a substantially linear manner. Here, f represents a resistant coefficient based upon a wind velocity Vt m/s in the throttle part, and C<SB>1</SB>, C<SB>0</SB>represent constants. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a pressure control damper used in a room where room pressure control is performed, such as a bio clean room, a regenerative medical facility, and an animal experiment breeding facility.

  In bio-clean rooms, regenerative medical equipment, animal experimental breeding equipment, etc., a pressure difference is created between adjacent rooms to prevent the entry of microorganisms from adjacent rooms and to prevent pathogens in the room from flowing out into adjacent rooms. ing. Here, the pressure difference between adjacent rooms is usually about 15 to 30 Pa.

  And, as in Patent Document 1 and Patent Document 2, the pressure in each room is provided with a damper in the air supply / exhaust duct that ventilates the room, and the operation loss of the damper blade is changed to reduce the pressure loss in the damper. It is adjusted by changing. For example, when there are a room A, a room B, and a room C, and the room pressure of the room A> the room pressure of the room B> the room pressure of the room C, as shown in FIG. Reduce the pressure loss and increase the pressure loss at the exhaust damper. In the room C, the pressure loss at the supply side damper is increased, and the pressure loss at the exhaust side damper is decreased. Further, in the room B, the pressure loss at the supply side damper and the pressure loss at the exhaust side damper are set to be intermediate between the room A and the room C.

In addition, as a damper used for pressure control in air conditioning, there are a so-called butterfly damper and a multi-blade damper.
JP 2002-39580 A JP 2006-223207 A

  By the way, as shown in FIG. 10, the conventional dampers such as the butterfly damper and the multi-blade damper are non-linear in which the resistance coefficient increases rapidly when the operation amount of the damper blade is brought close to 100% (the damper is closed). It has special characteristics. That is, when the air volume is constant, the pressure loss at the damper is proportional to the resistance coefficient, so the relationship between the operation amount of the damper blade and the pressure loss at the damper is also nonlinear.

  Therefore, such nonlinear characteristics make it difficult to control the pressure by operating the damper blade. For example, when the damper is controlled by PID control or the like, an appropriate control parameter varies depending on the operation amount of the damper blade. Therefore, even if the parameter adjustment is performed in the vicinity of 50% of the operation amount of the damper blade, the operation amount is 20% or 80%. %, There is a problem that satisfactory control performance cannot be obtained or the control becomes unstable.

  The present invention has been made in view of such circumstances, and even in a room in which heavy pressure control is performed such as a bioclean room, a regenerative medical facility, and an animal experiment and breeding facility, the room pressure is reduced regardless of the operation amount of the damper blade. An object of the present invention is to provide a pressure control damper that can be stably controlled.

In order to achieve the above object, the present invention comprises a casing and a movable damper blade, and the sectional area of the casing inlet is set to A ₀ so that the resistance coefficient changes in a substantially straight line with respect to the operation amount of the damper blade. (m ^2), when representing the operation amount of the damper blade in theta (%), molded casing and the throttle section composed of a gap between the damper blade flow path cross-sectional area a _{t (m} ²⁾ is to satisfy the following formula A pressure control damper is provided.

(Where f is a resistance coefficient based on the wind speed Vt (m / s) at the throttle portion, and C ₁ and C ₀ are constants.)
Then, in the present invention, the flow path cross-sectional area A _{t (m} ²⁾ is preferably within the scope of the error from the value obtained in 10% from the formula.

  By forming the pressure control damper in this way, it is possible to realize a pressure control damper whose resistance coefficient changes linearly with respect to the operation amount of the damper blade, so that the chamber does not depend on the operation amount of the damper blade. The damper for pressure control which can control a pressure stably can be provided.

  As a pressure control damper that can stably control the chamber pressure regardless of the operation amount of the damper blade, for example, the casing has an elbow shape bent by approximately 90 °, and the casing inlet is formed wider than the casing outlet. The damper blade is achieved by being provided in the casing so as to rotate around the elbow-shaped corner. In the pressure control damper, the outer periphery of the casing is preferably formed in an arc shape and a linear shape, and the tip end side of the damper blade is preferably in an R shape toward the casing outlet side.

  The room pressure control system using the pressure control damper according to the present invention can easily and accurately control the room pressure (room pressure) of the room, so that a safer bioclean room, regenerative medical equipment, animal experiment breeding A room pressure control system such as equipment can be provided.

  According to the present invention, even in a room that performs room pressure control such as a bioclean room, regenerative medical equipment, and animal experiment and breeding equipment, pressure control that can stably control the room pressure regardless of the operation amount of the damper blades A damper can be provided.

  Hereinafter, preferred embodiments of a pressure control damper according to the present invention used in a room where heavy pressure control is performed, such as a bio clean room, a regenerative medical facility, and an animal experiment and breeding facility, will be described in detail with reference to the accompanying drawings.

FIG. 1 shows the damper inlet and the damper outlet, where the damper sectional area (damper inlet) of the damper is A ₀ (m ² ) and the sectional area of the throttle part (damper outlet) is A _t (m ² ). It is a conceptual diagram of a damper.

Based on the conceptual diagram of the damper shown in FIG. 1, the present inventor uses a damper for pressure control including a casing and movable damper blades to set the sectional area of the casing inlet (damper inlet) to A ₀ (m ² ), the damper. when the operation amount of the blade in terms of theta (%), the throttle portion comprising a gap between the casing and the damper blade flow path cross-sectional area a _t of the (damper outlet) _(m ²⁾ is shaped so as to satisfy the following equation Thus, it was found that the resistance coefficient can be changed substantially linearly with respect to the operation amount of the damper blade, and the chamber pressure can be controlled stably.

(Where f is a resistance coefficient based on the wind speed Vt (m / s) at the throttle portion, and C ₁ and C ₀ are constants.)
The pressure loss ΔP (Pa) in the damper shown in FIG. 1 can be expressed by the following equation (1) using the wind speed Vt (m / s) at the damper outlet (the gap between the casing and the damper blade). .

Here, f is a resistance coefficient with respect to the wind speed at the damper outlet based on Vt, and ρ is the density (kg / m ³ ) of the fluid (air).

  Here, when the flow at the damper outlet is gradually expanded from the gradually contracted flow, f becomes a substantially constant value (f = 1.0 to 1.3) regardless of the amount of restriction and the wind speed.

Further, the pressure loss ΔP of the damper can be expressed by the following equation (2) using a typical wind speed of the duct, that is, a resistance coefficient F based on the wind speed V ₀ at the casing inlet.

  Also, from the continuous formula,

It becomes.

  Further, when Vt in the formula (1) is deleted using the formula (3), the following formula (4) is obtained.

Therefore, the typical wind speed of the duct, that is, F based on the wind speed V ₀ at the casing inlet, is obtained from the equations (1) and (4).

It becomes.

  By the way, when the resistance coefficient F changes linearly with respect to the operation amount θ (%) of the damper,

It can be expressed as. C ₁ and C ₀ are constants.

  From the equations (5) and (6), the relationship between the operation amount θ and the damper outlet area At is

It becomes.

  As described above, the present inventor creates a pressure control damper in which the pressure loss changes substantially linearly with respect to the operation amount of the damper blade if the sectional area of the throttle portion (damper outlet) is determined according to the equation (7). I got the knowledge that I can do it.

  From this knowledge, as a damper capable of stably controlling the chamber pressure regardless of the operation amount of the damper blade, for example, as shown in FIG. 2, a casing 12 having an elbow shape bent by approximately 90 °, and the casing 12 A damper blade 14 that rotates around the corner portion of the elbow shape, and the outer periphery of the casing 12 is formed in an arc shape and a linear shape, and the tip shape of the damper blade is directed to the casing outlet side. A pressure control damper 10 has been proposed. In addition, by forming the outer periphery of the casing 12 in an arc shape and a linear shape, it is possible to easily manufacture the pressure control damper 10 that satisfies the above expression (7). However, so as to satisfy the above expression (7). If it can be manufactured, the outer periphery of the casing 12 is not limited to the arc shape and the linear shape. Further, if the front end side of the damper blade has an R shape toward the casing outlet side, it is preferable but not required in that it suppresses the turbulence of the airflow when flowing through the gap between the casing and the damper blade and keeps the resistance coefficient f at a substantially constant value. .

  3A is a view of the pressure control damper 10 of FIG. 2 as viewed from the casing inlet 12a side, and FIG. 3B is a view of the pressure control damper 10 as viewed from the casing outlet side. FIG. 3C is a view of the pressure control damper 10 as viewed from the side of the casing 12.

  As can be seen from FIG. 2 and FIG. 3 (b), the R-shaped damper blade 14 whose tip is directed to the casing outlet side has an elbow-shaped corner 16 vicinity of the casing 12 as an axis 14a, and the shaded portion in the figure. Rotate the range (90 ° range). The damper blade 14 is rotated by a motor (not shown).

And as shown in FIG.3 (b), the outer periphery of the casing 12 consists of the circular arc part 13a and the linear part 13b. The center of the arc of the arc portion 13a is slightly shifted from the corner portion 16 toward the casing inlet 12a. Further, as shown in (b) of FIG. 3, the damper blade 14 is set such that there is an offset angle theta _W.

  In this way, by using the damper as shown in FIGS. 2 and 3, the cross-sectional area of the flow path formed by the gap between the casing and the damper blade can substantially satisfy the above expression (7).

  FIG. 4 is a diagram for pressure control in which the pressure loss changes substantially linearly with respect to the operation amount of the damper blade by forming the flow path cross-sectional area formed by the gap between the damper blade and the casing so as to satisfy the expression (7). It is another embodiment of a damper. FIG. 4A shows a cross-sectional view as seen from the side of the casing 12 ', and the casing 12' is cylindrical. The damper blade 14 'includes a dynamic closing member 20 and a static closing member 22. The dynamic closing member 20 is rotated by a motor M, and the static closing member 22 is fixed to the casing 12'.

  FIG. 4B is a view of the dynamic closing member 20 and the static closing member 22 as viewed from the front. The dynamic closing member 20 closes the opening 24 of the static closing member 22 to adjust the air volume. In addition, as shown in FIG. 4B, a part of the dynamic closing member 20 is a member having an aperture ratio of 40%. Further, the motor M that rotates the dynamic closing member 20 is provided at a location that does not affect the air flow that does not block the opening 24.

  FIG. 5 is a front view of the state of the damper blade 14 ′ when the dynamic closing member 20 of the pressure control damper 10 ′ is rotated by 0 °, 15 °, 30 °,... 90 °. The opening (channel cross-sectional area) is the largest at 0 ° (damper operation amount 0%), and the opening is the smallest at 90 ° (damper operation amount 100%).

  FIG. 6 is a graph plotting resistance coefficients in damper operation amounts of the pressure control damper 10 of FIG. 2 (and FIG. 3) and the pressure control damper 10 'of FIG. 4 (and FIG. 5).

  In the pressure control damper 10 of FIG. 2, the damper operation amount is 0% when the damper blade 14 is closest to the casing inlet 12a side, and the damper operation is when the damper blade 14 is closest to the casing outlet 12b side. The amount is 100%. The dimensions of the pressure control damper 10 are as follows. In FIG. 3, H2 is 100 (mm), W ′ is 97 (mm), H1 is 129.95 (mm), Lw is 84.4 (mm), x Is 7.34 (mm), a is 6.83 (mm), b is 2.85 (mm), and θw is 1.8 (°). The R shape of the damper blade 14 is an arc having a radius of 17.6 (mm). The pressure control damper 10 'shown in FIG. 4 has dimensions as shown in FIG. However, the said dimension is an example and is not restricted to this.

  As can be seen from FIG. 6, in the pressure control damper of the present invention, the resistance coefficient of the pressure control damper changes in a substantially straight line with respect to the operation amount of the damper blade, as compared with the conventional damper of FIG. I understand that. In the pressure control damper formed so that the flow path cross-sectional area formed by the gap between the damper blade and the casing satisfies the above equation (7), the resistance coefficient of the pressure control damper is substantially linear with respect to the operation amount of the damper blade. You can see that it can change.

  Therefore, since the pressure loss at the damper is proportional to the resistance coefficient, the relationship between the operation amount of the damper blade and the pressure loss at the damper is also substantially a straight line.

Note that the pressure control damper of the present invention is preferably formed so that the flow path cross-sectional area A _t (m ² ) falls within an error range of 10% from the numerical value obtained from the equation (7).

  FIG. 7 shows a room pressure control system 30 using the pressure control damper 10 (or 10 ') of the present invention.

  FIG. 7A shows the pressure control damper 10 of the present invention installed in the air supply duct 34 or the exhaust duct 36 in combination with a constant air volume device 32 such as CAV, and adjusts the damper opening according to the room pressure. This is a method of keeping the chamber pressure constant. In addition, although it has shown about the case where there are three rooms here, it is not limited to it and various aspects can be taken. Further, which of the constant air volume device 32 and the pressure control damper 10 is installed on the supply side or the exhaust side depends on the case.

  In FIG. 7B, the pressure control damper of the present invention is installed in both the air supply duct 34 and the exhaust duct 36, the pressure control damper on the air supply side is adjusted according to the chamber pressure, and The pressure control damper is operated in the same direction as the pressure control damper on the supply side in the opposite direction.

  In the pressure control damper according to the present invention, the resistance coefficient changes linearly with respect to the amount of operation of the damper blade. Therefore, pressure control dampers are provided on both the supply side and the exhaust side, and the supply side and the exhaust side are provided. If the side is moved by the same amount in the opposite direction (see FIG. 7C), the sum of the resistances of the two pressure control dampers is kept substantially constant. Therefore, in the room pressure control system 30 shown in FIG. 7B, the change in the ventilation volume of the room due to the pressure control can be minimized, so that the room speed is higher than the pressure control with a single pressure control damper. The pressure can be adjusted.

  As mentioned above, although embodiment of this invention was described, this invention is not limited to the said embodiment, Various aspects can be taken. For example, a pressure control damper 10 ″ as shown in FIG. 8 is also conceivable. FIG. 8A is a view of the pressure control damper 10 ″ as viewed from the front, and FIG. 8B is a view of the pressure control damper 10 ″ as viewed from the side. That is, the casing 12 '' has a rectangular cross section, the damper blade 14 '' is an elliptical cylinder formed with the major and minor axes as shown in the figure, and the central axis is rotated by a motor (not shown). is there. Even in the pressure control damper 10 ″ formed in this way, the resistance coefficient of the pressure control damper can change to a substantially straight line with respect to the operation amount of the damper blade 14 ″.

Conceptual diagram of damper The perspective view which shows the damper for pressure control of this invention The figure which shows the damper for pressure control of this invention The figure which shows the damper for pressure control which is the 2nd embodiment of this invention The figure which shows the opening of the damper for pressure control which is the 2nd embodiment of this invention Graph plotting resistance coefficient at damper operation amount The figure which shows the room pressure control system using the damper for pressure control of this invention The figure which shows the damper for pressure control which is the 3rd embodiment of this invention Diagram showing pressure control by damper Graph showing the relationship between damper operation amount and resistance coefficient in conventional dampers

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 ... Pressure control damper, 12 ... Casing, 12a ... Casing inlet (damper inlet), 12b ... Damper outlet, 13a ... Arc part, 13b ... Straight part, 14 ... Damper blade, 14a ... Shaft, 16 ... Corner part, 20 DESCRIPTION OF SYMBOLS ... Dynamic closing member, 22 ... Static closing member, 24 ... Opening part, 30 ... Room pressure control system, 32 ... Constant air volume apparatus, 34 ... Supply air duct, 36 ... Exhaust duct

Claims (6)

It consists of a casing and movable damper blades,
When the cross-sectional area of the casing inlet is represented by A ₀ (m ² ) and the operation amount of the damper blade is represented by θ (%) so that the resistance coefficient changes in a substantially straight line with respect to the operation amount of the damper blade, A pressure control damper, wherein a flow passage cross-sectional area A _t (m ² ) of a constricted portion formed by a gap with a damper blade satisfies the following formula.

(Where f is a resistance coefficient based on the wind speed Vt (m / s) at the throttle portion, and C ₁ and C ₀ are constants.) ^2. The pressure control damper according to claim 1, wherein the flow path cross-sectional area A _t (m ² ) falls within an error range of 10% from a numerical value obtained from the equation. The casing has an elbow shape bent by approximately 90 °, and the casing inlet is formed wider than the casing outlet,
The damper for pressure control according to claim 1 or 2, wherein the damper blade is provided in the casing so as to rotate around an elbow-shaped corner portion as an axis.   The pressure control damper according to claim 3, wherein the outer periphery of the casing is formed in an arc shape and a linear shape.   The damper for pressure control according to claim 3 or 4, wherein a tip end side of the damper blade has an R shape toward the casing outlet side.   A room pressure control system using the pressure control damper according to any one of claims 1 to 5.

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