JPS61268988A - Heat exchanger - Google Patents

Abstract

PURPOSE:To reduce the pressure loss of primary fluid, flowing between pipes, by a method wherein the flow pipe of secondary fluid, which is provided with the same surface area as the surface area of the pipe under a condition that the section thereof is true round, is deformed specially so as to be thinner with respect to the flow direction of primary fluid. CONSTITUTION:Both of the flow pipes 6a, located at the upstream side of primary fluid A, and the flow pipes 6b, located at the downstream side of the same, are deformed into elliptical or flattened round pipes for example, so as to be thinner with respect to the flow direction of the primary fluid and keep the same surface area as the surface area of them under a condition that the section thereof is round. According to this constitution, flow paths between the flow pipes 6a and between each of the flow pipes 6b located in the rear are widened, therefore, the pressure loss may be reduced and, further, turbulent flow effect in the back sides of respective flow pipes 6a, 6b, which are located in fore-and-back relation of secondary fluid, with respect to the flow direction of the primary fluid A may be prevented.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] This invention relates to improving the heat transfer characteristics of heat exchangers used in air conditioners and the like.

[Conventional technology]

Figures 2 and 3 are patent applications filed in 1983, which form the basis of this invention.
-264087 is a longitudinal sectional view showing the main parts of the heat exchanger and a side view showing the secondary fluid distribution pipe in cross section.
In the figure, (1aX1bX1c) are heat exchanger plates each having a large number of through holes (2), and as shown in the figure, a plurality of these are arranged side by side in a stacked state at a predetermined interval, and between them, as shown in Figure 2, They constitute branch channels (A1) (A2) for the generated primary fluid for cooling outside air, etc. (3) is a bent wall portion repeatedly formed at the same pitch on each of the heat exchanger plates (1a), (1b), and (1c), which allows the above-mentioned Enlarged channels (4) and narrow channels (5) whose cross-sectional areas differ periodically with respect to the fluid flow direction are alternately formed back to back.

(6aX6b) tri Each heat exchanger plate (1
a) (1b) (1r:) with a series of flow vibrators that penetrate in the stacking direction and pass a secondary fluid (B) Th such as a refrigerant that exchanges heat with the primary light body (A).

Distribution pipe (6a) located upstream of the primary light body (4)
The nine adjacent distribution pipes (6b) located on the downstream side are staggered so that they do not overlap in the flow direction of the primary fluid (4).

Since the conventional heat exchanger is configured as described above, when the primary fluid (5) is passed between the parallel heat transfer plates (1aX1bX1c), the enlarged flow channel (4) and the narrow flow channel are formed back to back. (5) A pressure difference occurs between them, and the flow direction of the fluid passing through the one-minute flow path (AI) (A2) does not change, but a portion of the fluid flows through the above-mentioned numerous through holes (2) at back-to-back locations. As a result, the so-called temperature boundary layer that develops and forms along the surface of each heat transfer plate (1a), (1b), and (1c) can be made thinner, and the heat transfer coefficient can be improved.
Since the distribution pipes (6aX6b) through which the secondary fluid (inside the secondary fluid) passes are perfectly circular, there is a drawback that the flow path between them becomes narrow.

[Problem that the invention seeks to solve]

In this invention, the surface area of the secondary fluid circulation vibrator is kept the same as in the case of a perfectly circular state, and the heat exchange effect with the primary light body is maintained, but the shape is changed to allow the primary fluid to pass between the two. The purpose is to widen the distance between

[Failure to solve the problem]

In the case of this invention, the secondary fluid circulation pipe has the same surface area as the surface area in a perfect circle state, but it is specially deformed so that it becomes thinner in the flow direction of the primary light body, so that the primary fluid can flow. reducing resistance.

[Effect]

In the case of this invention, without impairing the heat exchange effect with the primary fluid,
The pressure loss of the primary fluid through the secondary fluid flow pipe will be reduced.

〔Example〕

FIG. 1 shows an embodiment of the heat exchanger of this invention.
The same parts as in the conventional example shown in FIGS. 2 and 3 are indicated by the same reference numerals, but in the case of the present invention, the shape of the secondary fluid (B) distribution pipe is different. That is, also the distribution pipe (6a) located upstream of the primary fluid reservoir and the distribution pipe (6b) located downstream.

Both are characterized in that they are thinner with respect to the flow direction of the primary light body and are deformed into, for example, an elliptical or flattened shape so as to maintain the same surface area as that in a perfectly circular state.

With this configuration, the flow path between the front circulation vibrator (6a) and the rear circulation pipe (6b) located on the upstream and downstream sides of the primary fluid prisoner is widened, and pressure loss can be reduced. Furthermore, it is also possible to prevent turbulence at the rear with respect to the flow direction of the primary fluid trapped in each of the flow pipes (6a) (6b) located in front and behind the secondary fluid (B).

〔Effect of the invention〕

Since the heat exchanger of this invention is configured as described above,
This has the effect of reducing the pressure loss of the primary fluid flowing between the flow pipes while maintaining the heat exchange area of each flow pipe in its perfectly circular state.

[Brief explanation of drawings]

FIG. 1 is a side view of a heat exchanger of the present invention showing a cross section of a secondary fluid distribution pipe, and FIGS. 2 and 3 are longitudinal sectional views showing a conventional heat exchanger and a secondary fluid distribution pipe. FIG. 2 is a side view showing a section. In the figure, (4) is the primary light body, and (AIXA2) is the branch channel. (1aX1bX1c) is a heat exchanger plate, (2) is a through hole, (4
) is an expanded channel, (5) is a narrow channel, (6a) (6b
) indicates a flow pipe, ■) indicates a secondary fluid. In other figures, the same reference numerals indicate the same parts.

Claims (1)

[Claims] The branch channels are installed opposite each other such that the cross-sectional area of the branch channels differ periodically along the flow direction of the primary fluid flowing between them, and each branch channel has a large number of through holes, A plurality of heat exchanger plates are arranged back to back to form an enlarged flow path and a narrow flow path, and the enlarged flow path and the narrow flow path for the primary fluid in the back-to-back state are penetrated in the stacking direction of each heat exchanger plate, and the primary fluid The distribution pipes for the secondary fluid that exchanges heat with the secondary fluid are arranged alternately so that the front and rear distribution pipes that are adjacent to each other in the flow direction of the primary fluid do not overlap in the flow direction of the primary fluid, and each of the above A heat exchanger characterized in that a secondary fluid distribution pipe is thinner in the flow direction of the primary fluid and is deformed into, for example, an elliptical or flat shape that maintains the same surface area as a perfect circle. .