JP2002318095A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger which has a small pressure loss of a fluid and which is reduced in size of a fan and in an electric bill. SOLUTION: The heat exchanger comprises a chamber A3 and a chamber B16 formed via a corrugation 10, in which a fluid A and a fluid B respectively flow to heat exchange between the fluid A and the fluid B. The exchanger further comprises straightening plates 6 provided at positions where the flowing direction of the fluid A near an inlet 2 or an exist 4 of the fluid A3 of the chamber A changes. Thus, the size of a turbulent flow near the inlet 2 or the exist 4 of the fluid A is reduced or its number is reduced by the plates 6, and the pressure loss of the fluid A is decreased. This exchanger can be manufactured by providing the straightening plates 6 by cutting to rise the inlet 2 part or the exist 4 part of the fluid A of a base plate without impairing productivity.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger capable of reducing the pressure loss of a fluid, reducing the size of a fan and reducing the cost of electricity.

[0002]

2. Description of the Related Art As shown in FIG.
The base plate 1 is joined to the front surface of the corrugate 10 to form a plurality of chambers A3, and the base portion 15 of the cover 14 is joined to the rear surface of the corrugate 10 to form a plurality of chambers B16. Of the base plate 1
An inlet 2 and an outlet 4 for the fluid A are provided at an upper portion and a lower portion, respectively. A cylindrical body (not shown) is attached to the inlet 2 and the outlet 4 at a substantially right angle to the longitudinal direction of the chamber A3. A
The upper end and lower end of 3 are sealed with a sealing material 5. The outlet 4 may not be provided with a cylinder. In this conventional heat exchanger, the fluid A flows into the chamber A3 through the cylinder and the fluid A inlet 2, and passes through the chamber A3 and out through the outlet 4 and the cylinder. The fluid B flows in from the lower end of the chamber B16, passes through the chamber B16, and flows out of the upper end. During this time, heat exchange is performed between the fluid A and the fluid B via the corrugate 10.

[0003] In addition, the heat exchanger is provided with an inlet 2 for a fluid A at an upper portion of a base plate 1 as shown in FIG.
In some cases, the outlet of the chamber A3 is the lower end (corrugate lower end), the inlet 18 for the fluid B is provided below the cover base 15, and the outlet is the upper end of the chamber B (corrugate upper end).

[0004]

However, the conventional heat exchanger has a problem that the pressure loss is large, the fan becomes large, and the electricity cost increases. Therefore, the present inventors assembled the heat exchanger shown in FIG. 5 using a transparent vinyl chloride resin plate, and mixed the smoke with the heat exchanger in order to investigate the cause of the large pressure loss in the conventional heat exchanger. The fluid (air) A flowed, and the flow pattern of the fluid A at the fluid A inlet 2 and the fluid A outlet 4 was observed. As a result, as shown in FIG. 7, the flow of the fluid A passing through the cylindrical body and flowing from the fluid A inlet 2 has a turbulent flow area at the end of the inlet in the chamber A3, immediately below the inlet, directly above the outlet, and deep inside the outlet. It was found that these turbulent regions 8, 9 increased the pressure loss. In particular, a large turbulence region was generated at the end of the inlet and at the back of the outlet.

Incidentally, the total pressure loss Δp which the fluid A receives in the heat exchanger shown in FIG. 5 is a pressure loss Δp _in1 due to a change in the flow direction at the inlet of the fluid A, a Δp _in2 due to a reduction in the flow channel area, and the fluid A Pressure loss Δp when flowing in a room
_The value obtained by subtracting the pressure rise Δp _out2 due to the expansion of the flow path area at the fluid A outlet from the sum of the pressure loss Δp _out1 due to the change in the flow direction when the _core and the fluid A flow _out from the outlet (Δ
_{p = Δp in1 + Δp in 2} + Δp core + Δp out1 -Δp
_out2 ), of which Δp _in2 , Δp _core and Δp _in2
Since p _out2 is determined by the design specification, the reduction of the pressure loss Δp depends on how to reduce Δp _in1 and Δp _out1 .

SUMMARY OF THE INVENTION An object of the present invention is to provide a heat exchanger in which the pressure loss of a fluid is small, the size of a fan can be reduced, and the cost of electricity can be reduced.

[0007]

According to the first aspect of the present invention,
In a heat exchanger in which a fluid A and a fluid B flow through a chamber A and a chamber B formed through a corrugate to perform heat exchange between the fluid A and the fluid B, respectively, A heat exchanger characterized in that a flow straightening plate is provided at a position where a flow direction of a fluid changes near a fluid inlet or a fluid outlet.

According to a second aspect of the present invention, there is provided the heat exchanger according to the first aspect, wherein the current plate is provided by cutting and raising the fluid inlet portion or the fluid outlet portion.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a heat exchanger according to the present invention will be specifically described with reference to the drawings. In all the drawings showing the embodiments of the present invention, components having the same function are denoted by the same reference numerals, and their repeated description will be omitted. FIG. 1A is a plan view and a front view showing a first embodiment of the heat exchanger of the present invention. Fluid A flows from a fluid A inlet 2 provided in a base plate 1 of the heat exchanger. It passes through the chamber A3 and flows out of the fluid A outlet 4. The upper and lower ends of the chamber A3 are shown in FIG.
As shown in (b), it is hermetically sealed by the sealing material 5, and straightening plates 6 are provided in contact with the sealing material 5 at the fluid A inlet 2 portion and the fluid A outlet 4 portion, respectively.

[0010] The heat exchanger is assembled using a transparent vinyl chloride resin plate, and a fluid (air) A in which smoke is mixed with this.
And the flow pattern of the fluid A at the fluid A inlet 2 and the fluid A outlet 4 was observed. In the vicinity of the fluid A inlet 2, the flow direction of the fluid A changes along the surface 7 of the current plate 6 from the horizontal direction to the downward direction while maintaining substantially laminar flow, as shown in FIG. However, small turbulence regions 8, 9 were found at the end of the entrance A2 and immediately below the entrance A2. The flow pattern near the fluid A outlet 4 was similar.

FIG. 2A is a perspective view of a base plate 1 as viewed from the inside of a chamber A showing a second embodiment of the heat exchanger of the present invention. 10
A portion that contacts the front surface is cut off, and a portion that does not contact the front surface of the corrugate 10 (opens to the chamber A3) is left in a lattice shape. The comb 12 has a structure in which the base 12 is bent (cut and raised) to push the comb-like body 11 into the chamber A3. The comb-like body 11 pushed into the chamber A3 is fitted at a predetermined angle to a side surface of the corrugate 10 constituting the chamber A3, and functions as a rectifying plate. The surface 7 of the comb-like body (hereinafter referred to as a cut-and-rectified plate) 11 to which the fluid A is applied is a flat surface. The fluid A outlet 4 is also cut and raised as described above, and the current plate 11 is formed.

When the flow pattern of the fluid A near the fluid inlet 2 of the heat exchanger was observed in the same manner as described above, the flow pattern was generally laminar as shown in FIG. Small turbulence zones 8, 9 were found at the end of the fluid inlet 2 and immediately below. The flow pattern near the fluid A outlet 4 was the same. Note that, in FIG.
1 and the current plate 11 are provided in front of the corrugate (FIG. 5).
See) side.

FIG. 3 (a) is a perspective view of a base plate viewed from the inside of a chamber A showing a third embodiment of the heat exchanger of the present invention. This heat exchanger is the same as the heat exchanger shown in FIG. 2A except that the cut-and-raised flow straightening plate 13 is concavely curved toward the center in the chamber A3.

The fluid A near the fluid A inlet 1 of the heat exchanger
When the flow pattern was observed in the same manner as described above, the flow pattern was generally laminar as shown in FIG.
A small turbulence zone 9 was observed immediately below the fluid A inlet 2, but not at the end of the fluid A inlet 2. The flow pattern near the fluid A outlet 4 was similar.

In the present invention, an arrangement position of the current plate,
The inclination angle, shape, and the like of the surface of the current plate to which the fluid is applied are appropriately determined depending on the properties of the fluid, the flow velocity, and the like.

The straightening plate 1 shown in FIGS.
1 and 13 can be easily processed in the process of manufacturing the base plate 1. Therefore, as compared with a case where the current plate is manufactured separately, the productivity is excellent and the processing cost can be reduced.

[0017]

The present invention will be described below in detail with reference to examples. (Example 1) JIS4 on one side of JIS3003 alloy core material
The base plate 1 is brazed to the front surface of a corrugate 10 composed of a clad plate having a thickness of 0.5 mm and composited with a 045 alloy brazing material, the base portion 15 of the cover 14 is bonded to the rear surface with an adhesive, and the upper end of the chamber A3 The lower end is sealed with a sealing material 4, and a rubber flow straightening plate 6 is provided on the fluid inlet 2 portion and the fluid outlet 4 portion of the fluid A by bonding to the sealing material 4 with an adhesive to manufacture a heat exchanger. (See FIG. 1).

(Embodiment 2) Inlet 2 of fluid A and outlet 4
A heat exchanger was manufactured in the same manner as in Example 1 except that a straightening plate 11 was cut and raised in a portion (see FIG. 2).

Example 3 A heat exchanger was manufactured in the same manner as in Example 2 except that the surface of the straightening and straightening plate 13 was curved concavely toward the center of the room (see FIG. 3).

(Comparative Example 1) Except that the current plate was not provided,
A heat exchanger was manufactured in the same manner as in Example 1 (see FIG. 5).

The pressure loss of each of the heat exchangers manufactured in Examples 1 to 3 and Comparative Example 1 was examined by the method shown in FIG. That is, the wind tunnels 20 and 21 are attached to the inlet 2 and the outlet 4 of the fluid A, respectively. The air A flows in from the wind tunnel 20 attached to the fluid A inlet 2 by a fan, and the air A flows out from the wind tunnel 21. The wind pressure difference between the wind tunnels 20 and 21 was examined by the fine differential pressure gauge 22. A wind pressure difference of less than 50 Pa was evaluated as good (○), and a wind pressure difference of 50 Pa or more was evaluated as poor (x).
Table 1 shows the results. Table 1 also shows productivity.

[0022]

[Table 1]

As is clear from Table 1, the sample of the present invention (N
o. Each of the samples 1 to 3) had a small pressure loss as compared with the comparative example (No. 4, conventional product). This is because, in the example product of the present invention, the rectifying plate was provided, so that the turbulent flow area was reduced or the number thereof was reduced. In particular, No. 1 in which the surface of the current plate was concavely curved toward the center of the room. In No. 3, only a small turbulent flow area was present immediately below the fluid inlet and just above the fluid outlet, and the pressure loss was minimized. No.
In Nos. 2 and 3, the straightening plates were provided by cutting and raising the fluid inlet portion and the fluid outlet portion. The productivity of the heat exchanger was superior to that of No. 1. Examples 1-3
In the example of the present invention and the comparative example 1 (conventional product), air B having a temperature different from that of the air A was flown into the chamber B, and the heat exchange characteristics between the air A and the air B were examined. Compared to the conventional product, it showed the same or better heat exchange characteristics.

Although the case where the heat exchange between the air is performed by using the heat exchanger of the type shown in FIG. 5 has been described above, the present invention is applied to the case where the heat exchanger of the type shown in FIG. The effect is exhibited when applied to any heat exchanger that performs heat exchange by applying heat, not only between gas but also between liquids (such as water) and between liquid and gas. Is done.

[0025]

As described above, according to the heat exchanger of the present invention, the fluid A and the fluid B flow into the chamber A and the chamber B formed through the corrugate, respectively, so that the fluid A and the fluid B In a heat exchanger that performs heat exchange in the fluid flow direction of the fluid in the vicinity of the fluid inlet or the fluid outlet of the chamber A or the chamber B is provided at a place where the flow direction of the fluid changes, so that the vicinity of the fluid inlet or The size of the turbulence region near the outlet or the number of turbulence regions is reduced, and the pressure loss of the fluid is reduced. This heat exchanger can be manufactured without impairing productivity by providing the straightening plate by cutting and raising a fluid inlet portion or a fluid outlet portion. Therefore, an industrially remarkable effect is achieved.

[Brief description of the drawings]

FIG. 1 shows a first embodiment of the heat exchanger of the present invention;
(A) is a plan view and a front view, (B) is a view taken in the direction of arrow aa in the front view (longitudinal sectional view of the chamber A), and (C) is a flow pattern diagram of the fluid near the fluid inlet of the chamber A. is there.

FIG. 2 shows a second embodiment of the heat exchanger of the present invention;
(A) is a perspective view of the base plate viewed from the inside of the chamber A, (B)
Is a flow pattern diagram of the fluid near the fluid inlet of the chamber A.

FIG. 3 shows a third embodiment of the heat exchanger of the present invention;
(A) is a perspective view of the base plate viewed from the inside of the chamber A, (B)
Is a flow pattern diagram of the fluid near the fluid inlet of the chamber A.

FIG. 4 is an explanatory diagram of a method for checking a pressure loss of a heat exchanger.

FIG. 5 is an explanatory diagram of a conventional heat exchanger.

FIG. 6 is an explanatory diagram of another conventional heat exchanger.

FIG. 7 is a flow pattern diagram of a fluid A in a chamber A of a conventional heat exchanger.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 base plate 2 fluid A inlet 3 heat exchanger chamber A 4 fluid A outlet 5 sealing material 6 rectifier plate 7 rectifier plate surface 8 turbulent region at the end of inlet 9 turbulent region immediately below the inlet 10 corrugated 11 comb-shaped body (surface Is a flat cut-and-rectified plate) 12 A base of a comb-shaped body 13 A comb-shaped body (a cut-and-rectified plate with a curved surface) 14 A cover 15 A base body of a cover 16 A heat exchanger chamber B 17 A sleeve of a cover 18 Fluid B inlet provided on cover base 20, 21 Wind tunnel 22 Micro differential pressure gauge

Claims (2)

[Claims] 1. A heat exchanger in which a fluid A and a fluid B flow through a chamber A and a chamber B formed through a corrugate to exchange heat between the fluid A and the fluid B, respectively. A heat exchanger characterized in that a flow straightening plate is provided at a position in the chamber B where the flow direction of the fluid changes near the fluid inlet or the fluid outlet, respectively. 2. The heat exchanger according to claim 1, wherein the current plate is provided by cutting and raising the fluid inlet portion or the fluid outlet portion.