JPS6318864Y2 - - Google Patents

Description

[Detailed description of the invention] The present invention relates to a damper for opening and closing a required duct path, and in particular, a highly airtight damper that is equipped with a new boost mechanism and improves the reliability of the opening/closing function and high airtightness. It is related to.

A typical example of a damper installed in a duct conventionally installed in a building or other structure for ventilation is the device shown in FIGS. 4 and 5. Figure 4 is a plan view of the damper, Figure 5
The figures each show a front view of the damper, where 1 shows the damper body, 1A shows the duct part, and 2 shows the flange. A gate plate 10 having substantially the same shape as the inner periphery of the damper body 1 is rotatably attached to the inside of the damper body 1 by a rotary operating shaft 12. By rotating the rotary operating shaft 12, the gate plate 10 is rotated. The rotating damper body 1 opens and closes ventilation. In addition, 21,
Reference numerals 22, 23, and 24 are rotational auxiliary mechanisms including electrical piping and the like, which may be implemented as desired. The seal 11, the gate plate receiver 9', the latch mechanism 20, the latch actuating part 20A, and the locking part 25 each represent an auxiliary mechanism for closing the gate plate 10. 45, a guide hole 46, and a pin 47 each constitute an auxiliary mechanism when opening the gate plate 10, and 62 indicates a return handle portion.

By the way, this type of damper has a structure in which the rotary operating shaft 12 of the gate plate 10 is driven to open and close while supplementing the elasticity of a spring body such as the spring body 12S, thereby obtaining a predetermined ventilation blocking state. In order to obtain a high degree of flow blocking effect, a spring body with higher elasticity must be used, and on the other hand, a larger driving force is required when the gate plate 10 is fully opened.

Furthermore, the assistance of the opening and closing action of the gate plate 10 by the spring body 12S results in the rotational movement of the gate plate 10 becoming excessively rapid, which causes the damper itself to receive more so-called air hammer action from the flow body to be blocked. The damage effect is accordingly increased, and this has caused a serious disadvantage in that the damper structure has to be made overweight and expensive. Furthermore, a return handle portion 62 is connected to the end of the rotation operating shaft 12, and this handle portion 62
The gate plate 10 is reset to its original position by the rotation operation, but in this case, it is necessary to apply a force to the handle portion 62 to compress the spring body 12S. Further, when the temperature fuse 30 is activated and the full-open stopper 45 is released, the elastic force of the spring body 12S causes the gate plate 10 to come into violent contact with its receiving portion 9', causing the seal of the gate plate 10 to 11 and the receiving portion 9' are severely worn out, and the so-called air hammer phenomenon acts on the gate plate 10, which completely closes the flow path suddenly. Therefore,
In order to withstand the action of the spring body 12S, the main part of the damper is constructed to be strong, so the weight of the damper becomes excessive, which forces the use of thick material, which has the disadvantage of increasing cost. be.

The present invention is intended to eliminate the above-mentioned drawbacks, and aims to provide a damper that can reliably maintain high airtightness with a relatively small driving force. That is, in the highly airtight damper of the present invention, one connecting end 9 is connected to the rotary operating shaft 12 of the gate plate 10.
0 and a first link 81 with a slide groove 83 extending from the connecting end 90 toward the other connecting end 91, and one sliding end 85 can be freely slid into the sliding groove 83 of the first link 81. It consists of a second link 82 which is connected to the cylinder and has a fixed end 84 pivotally pivoted to the other position, and a cylinder 86 which is connected to the sliding end 85 of the second link 82 via a stroke shaft 88. One embodiment will be described below with reference to the drawings.

This example is configured to be applied to a duct that is in a horizontal state and has a rectangular flow passage cross section.
Furthermore, it is a disaster prevention damper with smoke exhaust (duct opening) and fire prevention (duct closing) functions. Of course, this disaster prevention function is configured to operate automatically.

1 and 2 show the overall appearance of the damper according to the present invention, and FIG. 1 is a front view showing the same part as FIGS. 4 and 5, and FIG. 2 is a side view of the same part. It is. At both ends of the damper body 1, which is formed into a rectangular shape with the required flow cross-sectional area, flanges 2 are attached which are provided with a number of bolt holes 5 for arbitrarily connecting to the omitted predetermined duct path, and furthermore, a hanging fitting 3 is attached to the upper part.
is provided. 4 is an opening/closing operation part of the damper, 7 is a flow path of the damper, and 6 is an inspection port provided with a suitable cover plate at all times so that the inside of the damper can be looked into as needed.

Next, such an external configuration is equipped with a boosting mechanism according to the present invention.

FIG. 3 shows an enlarged view of the boosting mechanism, which is a major feature of the damper of the present invention. It is something. That is, there is almost no leakage of the fluid when the damper is in the closed state. Furthermore, the gate plate can be opened and closed with a small amount of driving force.

Note that the connecting end 90 provided on the first link 81 in the enlarged configuration diagram shown in FIG. 3 can be connected to the rotary operating shaft 12 shown in FIG. It is something that can be implemented.

The booster mechanism 80 comprises a toggle mechanism including a first link 81, a second link 82, and an operating shaft such as a stroke shaft 88 of a damper opening/closing source connected to a sliding end 85 of the second link.

As shown in FIG. 3, the first link 81 is provided at one end with a connecting end 90 connected to the rotary operating shaft 12 of the gate plate 10, and at the other end facing toward the other end from the connecting end 90. The second link 82 is formed by providing a slide groove 83 of a constant length.
a sliding end 85 slidably connected therein;
Moreover, a predetermined damper opening/closing action source is added to this sliding end 85.

That is, the one shown in the third figure uses the air control cylinder 86 as the damper opening/closing source, but
If this is done manually, the stroke shaft 88 can be replaced with an actuation shaft (not shown), such as a manual lever or wire.

In the figure, the sliding end 85 of the second link 82 mentioned above is shown.
A stroke shaft 88 of the cylinder 86 is rotatably connected to the cylinder 86, and the cylinder 86 is rotatably connected to the end portion 87.
is rotatably fixed to an appropriate location on the damper body. As shown in FIG. 3c, the rotating end portion 84 of the second link 82 is located on a horizontal line passing through the same plane as the plate surface of the gate plate 10 when the gate plate 10 is fully open.
Parallel line L ₂ with L ₁ , that is, the first link 81
The connecting end 90 of the slide groove 83 and the connecting end 91 of the slide groove 83
are on the parallel line _L2 which is separated from the horizontal line _L1 by an distance equal to the distance _l1 between the rotational supports 100 and 101, respectively, and this parallel line _L2 and the axis of the rotation operating shaft 12 of the gate plate 10. axis perpendicular to
The pivot point _84a of the sliding end portion 85 and the fixed end portion 84 is positioned at a distance equal to the distance l ₂ between the respective pivot points 84a and 85a of the sliding end portion 85 and the fixed end portion 84 from the intersection with L3, and the sliding end portion 85 and the fixed end portion 84 are pivotably connected. It is composed of:

Now, FIG. 3a shows a case where the gate plate 10 is in a fully closed state, and the air brake cylinder 86 is actuated to move the stroke shaft 88 to the rearward end and the second link 8
2 via the rotation fulcrum 84a of the fixed end 84, and while sliding the sliding end 85 in the slide groove 83 of the first link 81, the rotation fulcrum 85a of the sliding end 85 The rotation axis 12 of the gate plate 10 passes through the rotation fulcrum 90a of the connecting end 90 of the link 81
The gate plate 10 is held in a fully closed state by bringing the gate plate 10 to the intersection point between an axis perpendicular to the axis of the second link 82 and a turning line of the sliding end 85 with the fixed end 84 of the second link 82 as a turning fulcrum. is possible, and the third
As shown in FIG. b, the cylinder 86 is actuated to move the stroke shaft 88 forward to rotate the second link 82 about the rotation fulcrum 84a, and the sliding end 85
The rotation fulcrum 90 of the connecting end 90 of the first link 81
a and the rotation fulcrum 8 of the fixed end 84 of the second link 82
4a, the gate plate 10 is held in the half-open position, and the third
As shown in FIG. 91 and to the intersection of the parallel line L ₂ and the axis L ₃ described above, the gate plate 10 can be held in a fully open state.

In addition, each of the figures in FIGS. 3a, b, and c shows the cylinder 8.
6 shows the transition between half-cycle operations of the stroke shaft 88 in FIG. From Figure 4b,
It operates to the state shown in FIG. 4a.

Further, even if the stroke speed of the cylinder 86 is constant, the gate plate rotation speed can be changed appropriately. For example, the rotational speed of the gate plate 10 toward the fully closing operation can be reduced to a fraction of the previous speed.
Since the speed can be reduced to a minimum, it is possible to prevent the air hammer from decreasing, and it is possible to suppress unnecessary damage and wear to the gate plate and its receiving portion to an extremely low level. This inventor has also confirmed this through experiments.

be.

Next, Figures 6 to 8 relate to the characteristic experiments of the damper of the present invention conducted by the present inventor, and are shown in Fig. 7.
The figure is a cross-sectional view showing the outline of the leakage test equipment (microflow measuring device), in which B is a continuously variable pressure blower and TD is the test specimen, that is, the device equipped with the boosting mechanism of the present invention. The damper, mp-1 and mp-2 are manometers (micro-pressure measuring meters), and mQ is a micro-flow measuring instrument, respectively. The value P supported by the manometer mp-1 represents the design differential pressure value, and the value V supported by the microflow measuring device mQ represents the leakage amount of the fluid.

7 and 8 are diagrams showing the data of the experimental results, in which FIG. 7 shows the data on the amount of leaves, and FIG. 8 shows the data on the operating characteristics of the gate plate.

First, let's talk about the experiments and their results shown in Figures 6 and 7. With the required design condition differential pressure applied before and after the closed gate plate 10 of the damper TD under test, The amount of leakage was as shown in Figure 7.

However, the damper TD to be tested had a round cross-section with a diameter of 1000 mm, and the fluid passing through it was air at 20°C.

The data in FIG. 8 is obtained by measuring the relationship between the rotational torque T applied to the gate plate 10 and the rotational speed of the gate plate 10. The rotational torque T applied to the gate plate 10 increases rapidly just before closing, causing the seal to close. Otherwise, the gasket is tightened, while the rotational speed of the gate plate 10 is rapidly reduced just before closing to prevent the air hammer phenomenon. In addition, T is the rotational torque applied to the gate plate, θ is the rotational speed of the gate plate 10, and O
is the fully open point of the gate plate 10, and S is the fully closed point of the gate plate.

As explained above, the highly airtight damper of the present invention has the advantage that as a result of being equipped with a new and useful boosting mechanism, the damper is almost completely closed, and in addition, the gate plate can be opened and closed. The opening/closing driving force associated with the operation can be further reduced, and since the air hammer phenomenon can be prevented, the durability of the damper itself can be greatly increased, and has various advantages.

It should be noted that the configuration of the illustrated damper is an example of this type of damper, and it goes without saying that the main parts of these dampers are not limited in the slightest.

[Brief explanation of the drawing]

Figures 1 and 2 are front and left side views showing the overall appearance of the highly airtight damper according to the present invention, and Figures 3a, 3b, and 3c are main parts of the damper according to the present invention. FIGS. 4 and 5 are an enlarged plan view with a part of the conventional damper broken down, a front view,
Fig. 6 is a cross-sectional view showing the configuration of an experimental device for testing the leakage amount of the damper of the present invention, Fig. 7 is a diagram showing the experimental data, and Fig. 8 is a diagram showing the rotational torque of the gate plate of the highly airtight damper of the present invention. FIG. 3 is a diagram showing experimental data of operating characteristics in relation to rotational speed.

Claims (1)

[Scope of utility model registration request] A first link 81 whose one connecting end 90 is connected to the rotation operating shaft 12 of the gate plate 10 and a slide groove 83 is provided from this connecting end 90 toward the other connecting end 91; A second link 82 has one sliding end 85 slidably connected to the sliding groove 83 of the second link 82 and a fixed end 84 pivotably connected to the other position, and the sliding end 85 of the second link 82 has a stroke. A highly airtight damper consisting of a cylinder 86 connected via a shaft 88.