JPH0749262Y2 - Heat exchanger - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION <Industrial Application Field> The present invention relates to a parallel flow heat exchanger.

<Prior Art> A parallel-flow heat exchanger is one type of heat exchanger used in an air conditioner such as a room air conditioner or a package air conditioner. A conventional parallel flow heat exchanger will be described with reference to the drawings. FIGS. 4 to 6 are drawings relating to the prior art, and FIG. 4 is an external perspective view showing the structure of the heat exchanger,
FIG. 5 is a front view illustrating the flow of the refrigerant, and FIG. 6 is an explanatory view of the refrigerant inflow state in the cooling pipe.

The heat exchanger 50 includes header pipes 51 and 52 and side members 5
3, includes a cooling pipe 40, an insert 41, and a fin 42.

The pair of parallel lower header pipes 51 and upper parallel header pipes 52 are connected to each other by a pair of side members 53 on both sides.

One end of the lower header pipe 51 is open and the other end is closed.

Contrary to the lower header pipe 51, the upper header pipe 52 has one end closed and the other end open.

In the portion sandwiched between the side members 53 between the header pipes 51, 52, a large number of cooling pipes 40 orthogonal to the header pipes 51, 52 are arranged at predetermined intervals in the axial direction of the header pipes 51, 52. There is. Each cooling pipe 40 is flattened in its arrangement direction and has a corrugated insert 41 inside. The lower end of the cooling pipe 40 communicates with the header pipe 51, and the upper end communicates with the header pipe 52. Corrugated fins 42 are arranged between the cooling pipes 40 and between the side members 53 and the cooling pipes 40 at both ends.

When the refrigerant is supplied to the header pipe 51 from its one end side,
The refrigerant rises up the many cooling pipes 40 and flows to the header pipe 52 side. The refrigerant exchanges heat with the outside air while flowing through the cooling pipe 40. The refrigerant passing through the cooling pipe 40 is led out to the outside from the header pipe 52.

In the above-mentioned configuration, when a sufficient amount of refrigerant circulation is not obtained, the flow velocity of the refrigerant in the cooling pipe 40 decreases, so the heat exchange capacity decreases. Therefore, the partition plate 51 is provided between the open ends and the closed ends of the header pipes 51 and 52, respectively.
1 and 521 are provided, the refrigerant has an optimum flow velocity, and the cooling pipe 40
The internal resistance of the pipe is determined to be an allowable number of cooling pipes 40. As shown by the arrow in FIG. 5, the refrigerant flowing in from the lower header pipe 51 flows into the lower header pipe 51.
The cooling pipe 40 rises between the open end side and the partition plate 511 and flows into the upper header pipe 52. The refrigerant flowing into the upper header pipe 52 is
Is turned horizontally and guided by the partition plate 521 to descend the cooling pipe 40 and flow into the lower header pipe 51. Further, the refrigerant flowing into the lower header pipe 51 is guided by the closed end portion of the lower header pipe 51, moves up the cooling pipe 40, and flows into the upper header pipe 52. And
This refrigerant flows out from the open end of the upper header pipe 52. That is, the refrigerant meanders inside the heat exchanger 50.

<Problems to be solved by the invention> However, in the conventional heat exchanger, when the refrigerant flows from the header pipes 51 and 52 into the cooling pipe 40, the refrigerant flows due to inertia and negative pressure due to the flow velocity of the refrigerant. Becomes uneven. This will be described below with reference to FIG. In the figure, the solid line R indicates the flow of the refrigerant during cooling, and the broken line H indicates the flow of the refrigerant during heating. In addition, in the figure, a large number of cooling tubes
In order to explain the refrigerant distribution of 40, for convenience, three cooling pipes 40
The heat exchanger 50 as a whole is indicated by a, 40b, and 40c.

During cooling, the refrigerant flowing into the lower header pipe 51 rises inside the cooling pipe 40a. However, in the vicinity of the inflow side, that is, rather than flowing into the cooling pipe 40a and rising at the open end of the lower header pipe 51, the header pipe 51 on the lower side goes straight horizontally and the cooling pipe near the partition plate 511. More will flow into the interior of 40a. Therefore, a shortage of the refrigerant occurs in the portion A shown by the diagonal lines above the cooling pipe 40a near the inflow side.

Further, the refrigerant flowing into the upper header pipe 52 goes straight through the upper header pipe 52, rather than flowing into the cooling pipe 40b near the inflow side, that is, near the cooling pipe 40a and descending,
More of the gas flows into the cooling pipe 40b near the partition plate 521. Therefore, a shortage of the refrigerant occurs in the portion B shown by the diagonal lines below the cooling pipe 40b near the inflow side.

For the same reason, in the cooling pipe 40c, the shortage of the refrigerant occurs in the upper portion near the inflow side in the portion C shown by the diagonal lines.

On the other hand, at the time of heating, the shortage of the refrigerant occurs in the multipoint illustration portions D, E and F for the same reason as described above. The portion in which the refrigerant is insufficient is not heat-exchanged and only bypass air passes through. Therefore, in addition to the insufficient capacity of the heat exchanger, there are problems that the bypass air causes dew condensation on the blower and the blowing grille. In addition, a long-time simulation may be required to eliminate the non-uniformity of the refrigerant inflow.

The present invention has been made in view of the above circumstances, and an object thereof is to provide a heat exchanger that does not generate dew on a blower, a blowout grill, or the like.

<Means for Solving the Problems> A heat exchanger according to the present invention is composed of first and second heat exchangers which are arranged side by side in a direction orthogonal to a ventilation direction, and each heat exchanger is parallel. Two header pipes, a plurality of cooling pipes whose both ends are connected to the header pipe and are arranged in parallel at a predetermined interval in the axial direction of the header pipe, and a header so that the refrigerant flowing through the cooling pipe meanders between the header pipes. A plurality of partition plates for closing the pipes on the way are provided, the header pipes of the heat exchangers communicate in series, and each partition plate is a cooling member constituting the first and second heat exchangers. The shortage of the refrigerant generated in the pipe is provided at a position where they do not overlap with each other when viewed from the ventilation direction.

<Operation> The refrigerant flows through the cooling pipe while meandering between the header pipes by the partition plate, and flows in and out between the first heat exchanger and the second heat exchanger. Since the positions of the partition plates provided in the header pipes are arranged so as not to overlap with each other in the ventilation direction, the refrigerant inflow into the heat exchanger of either the first or the second becomes uneven. However, due to the cooling power and dehumidifying power of the other heat exchanger, the bypass air generated by the refrigerant shortage portion in one of the heat exchangers is absorbed by the refrigerant flow.

<Embodiment> An embodiment according to the present invention will be described below with reference to the drawings. FIG. 1 is an external perspective view of a heat exchanger, FIG. 2 is a side view of the same, and FIG. 3 is a plan development view showing a refrigerant passage. The same parts as those in the prior art are designated by the same reference numerals.

The heat exchanger 1 according to the present invention comprises a first heat exchanger 10 and a second heat exchanger 20, which are arranged side by side at right angles to the ventilation direction indicated by the white arrow in FIG. ing.

The first heat exchanger 10 is a pair of parallel lower header pipes.
11, the upper header pipe 12, the side member 53,
Includes a cooling tube 40.

The lower header pipe 11 is provided with a partition plate 111, and the upper header pipe 12 is provided with a partition plate 121.

The header pipes 11, 12 and 111, 121 are all constructed according to those described in the prior art.

On the other hand, the second heat exchanger 20 includes a lower header pipe 21, an upper header pipe 22, a side member 53, and a cooling pipe 40 in the same manner as the first heat exchanger 10. The lower header pipe 21 is provided with partition plates 211 and 212 at two locations, and the upper header pipe 22 is provided with partition plates 221 and 222 at two locations. The lower header pipe 11 and the upper header pipe 22 of the first heat exchanger 11 are connected by a connecting pipe 30 so that the first heat exchanger 10 and the second heat exchanger 20 are connected. There is.

The distance between both ends of the header pipe and the partition plate closest to the header pipe and the space between the adjacent partition plates are called paths. Generally, the number of cooling pipes 40 arranged in each of the paths is sequentially changed by changing the volumes of the refrigerant gas and liquid. That is, each path is adjusted so that the flow velocity of the refrigerant passing through the cooling pipe 40 is the same.

Further, the mounting positions of the partition plates 111, 121 and 211, 212, 221, 222 are determined so as to have an optimal volume change with respect to the change of the gas and the liquid of the refrigerant, and the position of each of the partition plates is the ventilation direction. Are arranged so that they do not overlap each other. That is, each partition plate 111, 121, 211, 212, 22
1, 222 are provided at positions where the refrigerant-deficient portions generated in the cooling pipes 40 constituting the first and second heat exchangers 10, 20 do not overlap with each other when viewed from the ventilation direction. .

At the time of cooling, as shown by the solid line R in FIG.
Inflow from the lower header pipe 21 of the heat exchanger 20, flows through the cooling pipe 40, the connection pipe 30, and the cooling pipe 40, and flows out from the upper header pipe 12 of the first heat exchanger 10. Further, during heating, the refrigerant flows into the first heat exchanger as indicated by a broken line H.
It flows in from the upper header pipe 12 of 10, flows through the cooling pipe 40, the connection pipe 30, and the cooling pipe 40, and flows out from the lower header pipe 21 of the second heat exchanger 20. Each partition plate 111, 1
21 and 211, 212, 221, 222 do not overlap with each other in the ventilation direction, so the refrigerant inflow into the first or second heat exchanger becomes uneven, and even if a refrigerant shortage occurs, either heat exchange will occur. The bypass air generated by the cooling power and dehumidifying power of the device is absorbed by the refrigerant flow in other heat exchangers. The number of partition plates in the above embodiment is not limited to this.

<Effects of the Invention> As described above, two heat exchangers are arranged side by side at right angles to the ventilation direction, and the positions of the plurality of partition plates that generate the meandering flow of the refrigerant are compared with the ventilation direction. Are placed so that they do not overlap.

In particular, each partition plate is provided at a position such that the refrigerant-deficient portions generated in the cooling pipes forming the first and second heat exchangers do not overlap with each other when viewed from the ventilation direction.

Therefore, even if the refrigerant flow becomes non-uniform in one of the heat exchangers and a refrigerant shortage portion occurs, the bypass air does not flow due to the action of the other heat exchangers. Therefore, since the air is not exposed to the blower and the blowout grill portion by the bypass air, insulation failure is not caused, and cleaning and maintenance are not required, which is convenient. Furthermore, the long-time simulation required for determining the safe distribution of the refrigerant can be simplified.

[Brief description of drawings]

1 to 3 are drawings according to the present invention, wherein FIG. 1 is an external perspective view of a heat exchanger, FIG. 2 is a side view of the same, and FIG. 3 is a plan development view showing a refrigerant flow path. Is. FIGS. 4 to 6 are drawings relating to the prior art, FIG. 4 is an external perspective view showing the structure of the heat exchanger, FIG. 5 is a front view for explaining the flow of the refrigerant, and FIG. It is explanatory drawing of the refrigerant | coolant inflow state in a cooling pipe. 1 ... Heat exchanger 10 ... First heat exchanger 11, 12 ... Header pipe 111, 121 ... Partition plate 20 ... Second heat exchanger 21, 22 ... Header pipe 211, 212, 221 , 222 …… Partition plate 30 …… Connection pipe 40 …… Cooling pipe

Claims (1)

[Scope of utility model registration request] 1. A first heat exchanger and a second heat exchanger which are arranged side by side in the front and rear direction orthogonal to the ventilation direction. Each heat exchanger has two parallel header pipes and both ends of the header pipe. A large number of cooling pipes connected in parallel in the axial direction of the header pipe at a predetermined interval, and a plurality of partition plates that close the header pipe halfway so that the refrigerant flowing through the cooling pipe meanders between the header pipes. It comprises, the header pipe of each heat exchanger communicates in series, each partition plate,
A heat exchanger, characterized in that the refrigerant-deficient portions generated in the cooling pipes constituting the first and second heat exchangers are provided at positions where they do not overlap with each other when viewed from the ventilation direction.