JPS58140541A - Intake and exhaust ventilator - Google Patents

Abstract

PURPOSE:To reduce the size of a casing and make uniform the distribution of airflows through intake ports for blowers, by a method wherein ducts formed by intake-side faces of blowers and faces of a total heat exchanger are made to be uniform, and the center line of intake ports for blowers is located in proximity to the center of a heat-exchanging element. CONSTITUTION:A total heat exchanger 5 is so placed that the side faces of the heat-exchanging element are parallel to end plates 18 for blowers 3, 4. The center line Y-Y' of the intake ports 12, 13 for the blowers 3, 4 is located at a position in proximity to a straight line X-X' which passes through the center of the heat-exchanging element of the heat exchanger 5 and intersects orthogonally with a partition plate 2. In this case, each of the ducts extending from intake ports 6, 7 of the casing 1 to the intake ports 12, 13 for the blowers 3, 4 through the heat-exchanging element has a uniform airflow resistance, so that air flows orderly through the ducts without any turbulence, the distribution of velocities of airflows through the intake ports 12, 13 for the blowers 3, 4 becomes uniform, and a high performance is maintained.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an intake/exhaust ventilation system that is constructed of a rectangular parallelepiped casing, two centrifugal blowers, a total heat exchanger, and a t-n17Lt.

Figures vl, It is partitioned into two ventilation passages by the plate 2, and a centrifugal i-blower 3.4 is housed in each ventilation passage, and a partition 412
A rotating cylindrical total heat exchanger 5 is housed passing through it. 6. lt is the suction port of the casing 1, 8.9 is the discharge port of the casing 1, and 1/'0.11 is the electric motor of the centrifugal blower 3.4.

In such a structure, since the electric motor 10.11 and the impeller casing of the centrifugal blower 3.4 are generally arranged as shown in the figure, the length dimension of the centrifugal blower 3.4 is 1. ．． 1. Therefore, the length dimension of the rectangular parallelepiped casing 1 is restricted, making it difficult to downsize.

Therefore, it may be possible to configure the structure as shown in FIGS. 2 and 3, but in this case, the suction port 12.13 of the centrifugal blower 3.4
If the shape of the ventilation passages in the vicinity is different, the center of the heat exchange element of the total heat exchanger 5 (x-x') and the center of the suction port (Y-Y') may be separated from each other. Since there are 9 gates that are only partially wide, centrifugal blowers 3 and 4 are used.
and the heat exchange element of the total heat exchanger 5 “@ e ”
1k, the ventilation resistance of the flow from the suction port 6.7 of the rectangular parallelepiped casing 1 to the suction ports 12.13 of the centrifugal blowers 3 and 4 will differ depending on the flow path.
The air inflow distribution at the suction port 12.13 of the centrifugal blower 3.4 is no longer uniform. In other words, the characteristics of the centrifugal blower have non-uniform inflow characteristics that are different from normal integral inflow characteristics.
The disadvantage is that the characteristics when considering a full centrifugal blower 3.4 from the suction port 6.7 to the discharge port St of the rectangular parallelepiped casing 1 are significantly lower than those of the centrifugal blower 3.4 without the rectangular parallelepiped casing 1. have a meeting

In addition, in practice, it is often necessary to change the air volume t"f, and it is always necessary to change the rotation speed of the blower and replace it with a motor with a corresponding output, but in this case, the shape and size of the motor may be different. However, since the condition of the space 14 also changes, the suction of the centrifugal blower 3゜4 due to the influence of the space 14 -012,13
The inflow distribution will also change.

Therefore, since the characteristics of the blower are affected not only by changes in rotation speed but also by this inflow distribution, there is a drawback that it is difficult to determine the characteristics unless the characteristics are experimentally confirmed each time.

The present invention relates to an intake/exhaust ventilation system comprising a centrifugal blower disposed in each of two ventilation passages formed in a rectangular parallelepiped casing fabric, and a total heat converter disposed in the middle of these ventilation passages. In addition, even if the rotation speed of the centrifugal blower is changed, the characteristics of the blower are not influenced by the rotation speed. The purpose is to configure the system so that it will not be affected.

The ventilation system fIItFi of the present invention is a centrifugal blower housed in a rectangular parallelepiped casing, and the end plate t of the centrifugal blower is formed into a rectangular shape, and the electric motor and transmission mechanism are housed in the rectangular space. As a result, the ventilation path formed by the suction port side of the blower and the total heat exchanger surface is formed to be uniform, and the airflow path formed by the suction port side of the blower is formed at t1. ．． By moving the heat exchange element closer to the center of the total heat exchanger to eliminate wasted space t, etc., air uniformly reaches the air blower's inlet from the inlet of the rectangular parallelepiped casing. The centrifugal blower is configured to have a uniform inflow distribution at its suction port. Furthermore, even if the rotational speed of the blower is changed, the output of the motor is changed, and the shape and dimensions of the blower are changed, the non-uniform inflow characteristics of the blower are not affected.

An embodiment of the ventilation system according to the present invention will be described below with reference to FIGS. 4 to 7.

The inside of the rectangular parallelepiped casing 1 is divided into two ventilation passages by a partition plate 2, and a centrifugal blower 3.4 is installed in each ventilation passage.
9f'z is accommodated and penetrates through the partition plate 2.

Centrifugal blower 3F1 impeller (not shown) and this impeller (
It consists of an electric motor 10 that drives a motor (not shown), a transmission mechanism part 15, a circumferential plate 16 surrounding the impeller, and mirror plates 17 and 18 surrounding both sides of the circumferential plate 16.

In this case, the mirror plate 17.181 is rectangular. Moreover, the electric motor 10 and the transmission unit 15 are housed within the hexahedral space formed by the rectangular parallelepiped of the mirror plates 17 and 18.

The total heat exchanger 5 has a cylindrical heat exchange element, which is rotatably provided through a partition plate 27 in the center of the rectangular parallelepiped casing 1 and into two ventilation passages. In each of the six ventilation passages in the casing 1, centrifugal blowers 3.4 having the above-mentioned characteristics are provided so as to be located on both sides of the above-mentioned total heat exchanger 50, and suction ports 6.4 are provided in each of the six ventilation paths. 7 and a discharge port 8.And,
The total heat exchanger 5 is arranged so that the side surface of the heat exchange element and the end plate 18 of the centrifugal blower 3.4 facing the side surface are parallel to each other. Also, centrifugal air blower 4i1!3.
The center position Y-Y' of the suction ports 12 and 13 of No. 4 is brought close to ax-x' which passes through the center position of the heat exchange element of the total heat exchanger 5 and is perpendicular to the partition plate 2.

In such a structure, the air sucked in from the suction ports 6.7 on both sides of the casing 10 passes through the areas of the heat exchange elements of the total heat exchanger 5 located in the two ventilation paths, respectively, and is then sent to the centrifugal blowers 3, 4. and is discharged from the discharge ports on both sides of the casing 1. In this case, the air sucked in from the suction port is aerodynamically cut off. Furthermore, the outlet 12 of the centrifugal blower 3 and the outlet 8 of the casing 1 are aerodynamically connected by a connecting body 19.

In the case of the present invention, the total heat exchanger 5 is
The ventilation resistance of each ventilation path leading to the centrifugal blower suction port via the heat exchange element of , the air velocity distribution at the suction port of the centrifugal blower is uniform.

According to the present invention, the resistance value of each ventilation path from the suction port of the casing to the suction port of the centrifugal blower via the total heat exchanger is almost the same, and the flow is not overflowed by the centrifugal blower. It's neat and tidy, and there's no wasted space in the ventilation channels inside the casing, and no flow.

Because of this, the inflow distribution at the suction port of the centrifugal blower has been improved to be uniform, and the non-uniform inflow characteristics of the blower can be improved. It is possible to aim for

9. When changing the motor output by changing the rotational speed of a centrifugal blower, even if the external shape and dimensions of the motor change, the shape and dimensions of the air passage leading to the blower's suction port will not change, and the flow will be affected. This allows the non-uniform inflow characteristics of the blower to be kept in an optimal state.

[Brief explanation of drawings]

Figure 1 is a front cross-sectional view showing an example of a conventional one-stroke device;
The figure is a front sectional view showing another example of the conventional ventilation system, FIG. 3 is a side sectional view of FIG. 2, and FIGS. Figure 4 is a front sectional view, Figure 5 is a side sectional view, Figure 6 is an enlarged view of the far Iq submerged part, and Figure 7 is a top view of Figure 6. l... Rectangular parallelepiped casing, 3, 4... Centrifugal blower, 5... Total heat exchanger, 6, 7... Casing suction port, 8.9... Casing discharge port, 10 .11・
...Electric motor, 12.13...Centrifugal blower suction port,
16...Fig.

Claims (1)

[Claims] 1. A rotary total heat exchanger disposed in the middle of two ventilation passages formed in a rectangular casing, and a total heat exchanger disposed in each of the tail air passages. A centrifugal blower consisting of a facing impeller, an electric motor that drives the impeller, a circumferential plate surrounding the impeller, and an end plate surrounding both sides of the circumferential plate, and ventilation for each of the rectangular parallelepiped casings. In an intake/exhaust ventilation system equipped with a suction port and a discharge port provided in a road, the end plate of the centrifugal blower is made into a rectangular parallelepiped shape, and the motor and transmission mechanism portion t is a rectangular parallelepiped formed by the rectangular end plate. The heat exchange element surface of the total heat exchanger is arranged in parallel with the end plate of the centrifugal blower facing the element surface, and the suction port of the centrifugal blower is placed opposite to the heat exchange element. The characteristic intake and exhaust ventilation system. 2. Claim 1 characterized in that the center position of the suction port of the cancerous core blower is brought close to the center position of the heat exchange element of the total heat converter to a line perpendicular to the partition plate. The intake and exhaust chivalry device described.