JPH0612228B2 - Heat exchanger - Google Patents

Description

Description: FIELD OF THE INVENTION This invention relates to heat exchangers, especially aluminum heat exchangers such as those used as condensers for car coolers.

2. Description of the Related Art A heat exchanger used as a condenser for a car cooler is required to have excellent pressure resistance in terms of safety because a relatively high pressure gas is used as a refrigerant.

Therefore, conventionally, a serpentine tube type heat exchanger is generally used. That is, a generally extruded flat tube called a harmonica tube is bent in a meandering shape, and fins are arranged between parallel portions to form a core.

DISCLOSURE OF THE INVENTION Problems to be Solved by the Invention However, in the heat exchanger as described above, since the refrigerant circuit is formed in a meandering manner in one tube from one end to the other end, the refrigerant flow There was a drawback that the resistance was relatively large. In order to reduce this flow resistance, it is natural to consider increasing the cross-sectional area of the tube, but since the size of the core of the heat exchanger is restricted by its installation space, such a countermeasure is It was difficult to apply. In addition, in the above-mentioned serpentine tube heat exchanger, since the refrigerant circuit is formed in a meandering shape from one end of the tube to the other end as described above, a detailed analysis reveals that the refrigerant is near the inlet side of the refrigerant. There is a large difference in heat exchange efficiency between the portion near the outlet side and the difference in heat exchange efficiency between the width direction of the tube, that is, the front portion located on the inflow side of the air flow and the rear portion located on the outflow side. However, it cannot be said that it is possible to use the entire area of the core as effectively as possible to perform efficient heat exchange. Furthermore, in terms of manufacturing, the meandering bending process of the tube is a little troublesome, and the tube-fin assembly also tends to expand the meandering bending state of the tube due to the insertion of the fin. It is difficult to assemble by automatic mechanical assembly, resulting in low productivity, resulting in high cost.

In view of the above-mentioned conventional technology, the present invention has a pressure resistance suitable for practical use as a condenser, while reducing flow resistance and improving heat exchange efficiency, and heat exchange that enables automation of assembly and production. The purpose is to provide a container.

Means for Solving the Problems The present invention is a header type in which a large number of tubes are arranged in parallel between a pair of headers, and the refrigerant passages in the tube groups are arranged in a direction in which the outside air flows. The front side passage and the rear side passage are divided so that the refrigerant flows in the opposite direction in the front and rear of each tube in the thickness direction of the core.

More specifically, the heat exchanger according to the present invention comprises one hollow extruded material header (1) (2) arranged in parallel.
And a large number of tubes (3) arranged in parallel between both headers and having both ends inserted into the headers and connected to the refrigerant passages (18) (10) therein, and between adjacent tubes and both ends. One of the headers (1) and (2) on the refrigerant inlet / outlet side, which includes a fin (5) arranged in an air flow gap between the tube (3) and the side plate (4). A central partition wall (9) which divides the internal refrigerant passage (10) into a front passage (10a) and a rear passage (10b) along the length direction is integrally provided therein, and the tube (9) Also in 3), a central partition (1) that divides the internal refrigerant passage (13) into a front passage (13a) and a rear passage (13b).
2) is provided, and the partition walls (9) (12) of the header (2) and the tube (3) are brought into contact with each other in the connected state, so that the front passages (10a) (13a) of the two are provided.
The dorsal passage and the rear passage (10b) (13b) are communicated with each other in an independent state, while the other header (1) extends from its inner surface toward the center. The disturbing plate (17) is provided so as to project along the length direction, and the central partition (1) of the tube (3) is positioned on the positioning and disturbing plate.
By contacting 2), a detour-shaped refrigerant reversal passage portion (18a) that exceeds the top end of the positioning and disturbing plate (17) is formed in the header (1), and the reversal passage portion (18a) is formed. Through the passageway (13) of the tube (3).
The gist is a heat exchanger characterized in that a) and the rear passageway (13b) are communicated with each other.

Embodiment Hereinafter, the configuration of the present invention will be described in more detail with reference to the illustrated embodiment.

1 to 5 show a concrete example of the structure of the most basic heat exchanger according to the application of the present invention.

The heat exchanger of this embodiment is made of an aluminum alloy, and its main constituent members are a pair of upper and lower headers (1) and (2) arranged in parallel as shown in FIG.
And a plurality of tubes (3) which are arranged in parallel across them and both ends of which are respectively connected and communicated with the headers (1) and (2), and between the adjacent tubes and the outermost tube. (3) and the side plates (4) and (4) have corrugated fins (5) arranged in the air flow space.

Each of the headers (1) and (2) is made of a circular pipe-shaped hollow extruded material made of an aluminum material, and the header (1) on the upper stage side is located in the center upper part of the inner surface as shown in FIG. A positioning and disturbing plate (17) that extends toward the center of (1) and whose lower end reaches near the approximate center point of the header is projected downwardly, and both ends are lid pieces (6).
(6) is closed to form a single refrigerant passage (18) as a closed space inside. On the other hand, both ends of the lower header (2) are formed at the inlet (7) and the outlet (8) of the refrigerant, and a vertically oriented partition (9) is integrally provided vertically at the center of the inside. The internal refrigerant passage (10) is divided into two along the length direction, and the front passage (10
It is divided into a) and the rear passage (10b). Then, one end of the rear passage (10b) on the side of the refrigerant inlet (7) is closed by an insertion blocking plate (11) extended from the side plate (4) as shown in FIG. The refrigerant flowing in from is introduced only to the front passage (10a) side. On the contrary, the front passage (10a) is blocked by the insertion blocking plate (11) of the side plate (4) at the one end on the refrigerant outlet (8) side in the same manner as described above, and the refrigerant outlet (8). Is opened only in the rear passage (10b).

The tube (3) is made of a flat hollow extruded material made of an aluminum material, and also has a central partition wall (12) in the central portion in the widthwise direction so as to correspond to the lower header (2). Inside refrigerant passage (13) is front passage (13a)
And the rear passage (13b) is divided into two. The tube (3) may be of a porous type such as a so-called harmonica tube. In this case, the front passage and the rear passage are each formed with a plurality of independent passage portions.

The connection between the header (1) (2) and the tube (3) is
As shown in Fig. 3, make a notch (14) corresponding to the tube width in the tube mounting part of the header (1) (2),
While tightly fitting the end of the tube (3) to this,
This is carried out by firmly joining the two using a joining material such as a zinc layer coated in advance on the tube material or a brazing material that is separately attached. At the time of this joining,
The tube (3) fits by fitting a pre-formed recess (15) at the center of its end with the positioning and disturbing plate (17) and the partition wall (9) of each header (1) (2). The depth and relative position are regulated. In the connected state, the central partition wall (12) of the tube (3) is
In particular, its lower end is in close contact with the partition wall (9) of the lower header (2), whereby each lower passage (10a) of the lower header (2) and the tube (3).
(13a) and the rear passages (10b) and (13b) are connected to each other in an independent state. Also,
The upper end of the central partition wall (12) is brought into contact with the top end of the positioning and disturbing plate (17) of the upper header (1), whereby the refrigerant passage (1) in the upper header (1) is contacted.
A detour-shaped refrigerant reversal passage portion (18a) is formed in 8) above the top end of the positioning / disturbing plate (17) (see FIG. 2), and the tube (3) is inserted through the reversal passage portion (18a). The front passage (13a) and the rear passage (13b) are communicated with each other. Therefore, the refrigerant circuit (C1) in this heat exchanger has a lower header (2) as shown in FIG.
From the front side passageway (10a) of the tube (3) to the inside of the refrigerant passageway (18) of the upper header (1) by the reversal passage portion (18a), and then after the tube (3). From the side passage (13b) to the refrigerant outlet (8) via the rear passage (10b) of the lower header (2).

The fin (5) has a corrugated shape having a height corresponding to the distance between the adjacent tubes (3) and (3), and is joined to the tube (3) and the side plate (4) by a general brazing means. ing.

The side plate (4) has a substantially U-shaped cross section as shown in FIG. 3, and is arranged between both ends of the headers (1) and (2) with its opening surface side facing outward. The side plate (4) is attached by inserting the insertion portions (4a) (4b) protruding in an extended shape at both ends thereof into the header (1).
Insert it into the slit (16) made in the corresponding part of (2),
And it is done by brazing as appropriate.

In the above, the refrigerant enters the front passage (10a) in the header from the refrigerant inlet (7) at one end of the lower header (2). Since the inlet side of the rear passage (10b) is blocked by the insertion blocking plate (11) of the side plate (4) as described above, the gaseous refrigerant from the inlet (7) does not directly enter. The gaseous refrigerant that has entered the front passage (10a) of the lower header (2) continues to the front passage (13) of the tube (3).
It is distributed to a) and rises in it. In this process, first, by the external air flow flowing between the adjacent tubes (3) (3),
Since the gaseous refrigerant has a large relative temperature difference with the air flow, efficient heat exchange is performed throughout the core. Subsequently, the refrigerant enters the refrigerant passage (18) in the upper header (1). And here the positioning and disturbing plate (17)
Due to the existence of the above, the refrigerant reversal passage portion (18a) therebelow is detoured as shown by the arrow in FIG. At this time, a part of the refrigerant flowing into the header (1) from the front passage (13a) of the tube (3) has already been liquefied, but the positioning and disturbing plate (17) functions as a kind of baffle plate. As a result, the flow of the refrigerant is reversed in a detour shape over the top end of the disturbing plate (17) as described above, so that the refrigerant undergoes a vigorous mixing action. Therefore, after the refrigerant portions having a temperature gradient between them are mixed and subjected to the gas-liquid mixing action to make the temperature of the refrigerant uniform, the tube (3) is then provided with a rear passage (13b). Enter and descend this.
At this time, most of the refrigerant is already in a gas-liquid mixed state, and during this descending heat, heat exchange with the outside air is taken away, and the amount of heat retained is deprived, eventually becoming a required low temperature state, that is, a supercooled state. Collected in the rear passage (10b) of the lower header (2), and then delivered from the outlet (8).

In the above embodiment, a vertical type heat exchanger having a pair of headers arranged above and below is shown, but the present invention may be configured as a horizontal type having headers arranged on the left and right. Further, the refrigerant circuit may be configured to have four paths by providing a partition at a proper position in the length direction in the header (2) having at least the doorway. That is, after passing through the front passage (13a) and the rear passage (13b) for a plurality of tubes (3) group, further inside the adjacent tube groups, this time from the rear passage (13b) to the front passage (13a). And finally sent out from the outlet (8) of the header (2). Furthermore, by providing a partition at the proper position also on the other header (1) on the reverse side,
A refrigerant circuit having more than one pass may be configured.

EFFECTS OF THE INVENTION In the heat exchanger according to the present invention, the pair of headers forming the refrigerant circuit are each made of a hollow extruded material made of aluminum material, and they insert the end portion of the tube into the peripheral surface of the header. It is said that they are connected in a communicating state. Therefore, it has a pressure resistance comparable to that of conventional serpentine tube type heat exchangers, and is convenient for use as a condenser for car coolers that handle relatively high-pressure gaseous refrigerant. It can be used.

Further, a large number of tubes are provided in parallel between both headers, and for all or a predetermined number of tube groups, the refrigerant is circulated through the front passage and the rear passage thereof, It is easy to arbitrarily expand / contract the passage cross-sectional area of the refrigerant circuit in accordance with design requirements.
Therefore, the flow resistance of the refrigerant can be made sufficiently small, and the pressure loss can be reduced as compared with the conventional serpentine tube type condenser.

Further, in the heat exchanger of the present invention, the refrigerant passage in the tube is divided into the front passage and the rear passage, and the refrigerant is inverted from the front passage to the rear passage in at least a part of the core so that each single passage The inside of the tube is passed twice in opposite directions. Therefore, for example, after highly efficient heat exchange is performed in the windward side of the air flowing between the adjacent tubes, that is, in the front portion of the tube, heat exchange is further repeated separately in the rear portion thereof. Therefore, in the comprehensive evaluation using all tubes, the heat exchange efficiency can be averaged over the entire core, and the heat exchange efficiency of each tube can be increased, greatly increasing the heat exchange efficiency as a whole. it can.

In addition, in the header on which the refrigerant makes a U-turn, that is, in the header without the refrigerant inlet / outlet, a positioning / disturbing plate extending along the length direction thereof and toward the center of the header is provided in a protruding manner. By contacting the central partition wall of the tube with this, a detour-shaped refrigerant inversion passage portion is formed in the header so as to extend beyond the top end of the positioning / disturbing plate. Therefore, the refrigerant having condensed to some extent through the front passage of the tube group is vigorously mixed in the inversion passage portion in the header. That is,
The temperature is homogenized by the action of mixing gas and liquid. Then, subsequently, it is distributed and introduced into, for example, the rear passage on the opposite side of the tube group, and further heat exchange is performed.
Therefore, even in the rear passage, efficient heat exchange is performed over the entire tube group, and a so-called liquid sealing phenomenon or the like occurs in which condensed refrigerant remains in some passages and hinders heat exchange. To improve the heat exchange efficiency. As a result, both of the above items work together to make it possible to reduce the size of the heat exchanger due to its excellent heat exchange efficiency, and to significantly reduce the amount of refrigerant CFC used, which has recently caused pollution problems. To do.

Furthermore, since the heat exchanger of the present invention is assembled by arranging the side plate, the tube and the fin between the pair of extruded material headers, the header, the side plate and the tube make a strong joint during the assembly. Can form a framework. Therefore, even if the fins are forcibly fitted into the frame, the shape of the fins is not significantly changed, and the temporarily assembled state of the constituent members can be stably maintained by itself.
As a result, it is possible to mechanically perform the assembly process, and it is possible to reduce the cost by automating the manufacturing process of the heat exchanger.

[Brief description of drawings]

1 to 5 show an embodiment of the present invention,
Fig. 1 is a front view of the entire heat exchanger, and Fig. 2 is Fig. 1 II-
A sectional view taken along line II, FIG. 3 is a perspective view of an essential part showing constituent members in a separated state, FIG. 4 is a sectional view taken along line IV-IV in FIG. 1, and FIG. 5 is a refrigerant circuit configuration diagram. . (1) ... upper header, (2) ... lower header, (3) ... tube, (4) ... side plate,
(5) ... fins, (7) ... refrigerant inlet, (8) ... refrigerant outlet, (9) ... partition, (10) ... refrigerant passage, (10
a) …… Front passage, (10b) …… Rear passage, (12) ……
Central bulkhead, (13) ... Refrigerant passage, (13a) ... Front passage, (13b) ... Rear passage, (17) ... Positioning / disturbing plate, (18) ... Refrigerant passage, (18a) ... ... Refrigerant inversion passage part.

Claims (1)

[Claims] 1. A pair of hollow extruded material headers (1) (2) arranged in parallel with each other, and both ends of the headers (1) and (2) arranged in parallel between the headers and inserted into the header so that a refrigerant passage (1) inside thereof is formed.
8) A large number of tubes (3) connected in communication with (10)
And fins (5) arranged in the air flow gap between the adjacent tubes and between the tubes (3) at both ends and the side plate (4), the refrigerant of the both headers (1) and (2) A central partition wall (9) that divides the internal refrigerant passage (10) into a front passage (10a) and a rear passage (10b) along the length direction is provided in one of the headers (2) on the inlet and outlet sides. A central partition wall (12) which is integrally provided and divides the refrigerant passage (13) inside the tube (3) into a front passage (13a) and a rear passage (13b) is also provided. (2) and tube (3)
When the partition walls (9) (12) are brought into contact with each other in a connected state with the front passages (10a) (13).
a) The dorsal passage and the rear passages (10b) (13b) are communicated with each other in their respective independent states, while in the other header (1), from the inner surface toward the central part. The extended positioning / disturbing plate (17) is provided so as to project along the length direction, and the central partition (12) of the tube (3) is brought into contact with the positioning / disturbing plate, whereby the header (1) is concerned. A detour-shaped refrigerant reversal passage portion (18a) that extends over the top end of the positioning and disturbing plate (17) is formed therein, and is connected to the front passage (13a) of the tube (3) through the reversal passage portion (18a). A heat exchanger characterized by being communicated with a rear passage (13b).