JP2011226674A - Capacitor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a capacitor which can reduce an installation space and setting the quantity of a cooling medium to be sealed to a proper sealing quantity in an early stage.SOLUTION: At one terminal side of a capacitor 1, there are provided a first header tank 3 for connecting first heat exchange tubes 2A of third and fourth heat exchange paths P3 and P4 and a second header tank 4 for connecting second heat exchange tubes 2B of first and second heat exchange paths P1 and P2, and an upper end of the former is positioned higher than a lower end of the latter. The first header tank 3 has a function for collecting liquid while separating the gas and the liquid. The first to third heat exchange paths P1 to P3 are cooling medium condensation paths, and the fourth heat exchange path P4 is a cooling medium overcooling path. When the number of all the first heat exchange tubes 2A of the third and fourth heat exchange paths P3 and P4 is denoted as n, and the total number of all the first heat exchange tubes 2A of the third and fourth heat exchange paths P3 and P4 and all the second heat exchange tubes 2B of the first and second heat exchange paths P1 and P2 is denoted as N, the relationship of 0.15≤n/N≤0.25 is satisfied.

Description

  The present invention relates to a capacitor suitably used for, for example, a car air conditioner that is a refrigeration cycle mounted on an automobile.

  In this specification and claims, the upper, lower, left, and right refer to the upper, lower, left, and right of FIGS.

  For example, as a condenser of a car air conditioner, a plurality of flat heat exchange pipes extending in the left-right direction and arranged in parallel with a gap in the up-down direction and the left and right end portions of the heat exchange pipe are directed in the ventilation direction in the width direction. The header tank that extends in the up and down direction, and is provided with three heat exchange paths each consisting of a plurality of heat exchange tubes that are continuously arranged in the vertical direction, all the heat constituting each heat exchange path A condenser in which the refrigerant flow direction of the exchange pipe is the same, and the refrigerant flow direction of the heat exchange pipes of two adjacent heat exchange paths is different. A first header tank to which the heat exchange pipe constituting the path is connected, and a second header tank to which the heat exchange pipe constituting the heat exchange path excluding the heat exchange path at the lower end is connected separately, 2 header data Is disposed on the first header tank, the thickness of the first header tank is much larger than the thickness of the second header tank, and the desiccant is disposed in the first header tank, whereby the first The header tank has a function as a liquid receiver that separates gas and liquid using gravity and accumulates the liquid, and is connected to the first heat exchange pipe connected to the first header tank and the second header tank. The lengths of the second heat exchange tubes are equal, and the end of the first heat exchange tube on the first header tank side and the end of the second heat exchange tube on the second header tank side are on the same vertical line. There is a known capacitor in which all heat exchange paths are refrigerant condensation paths for condensing refrigerant (see Patent Document 1).

  In the capacitor described in Patent Document 1, in order to effectively perform gas-liquid separation in the first header tank, the inner volume of the first header tank needs to be considerably larger than that of the second header tank. The thickness of one header tank is considerably larger than the thickness of the second header tank, and there is a problem that a large space is required to arrange the capacitor.

  Usually, other devices are arranged near the capacitor. However, according to the capacitor described in Patent Document 1, the first header tank interferes with other devices. For example, a radiator is generally disposed on the downstream side in the ventilation direction of a condenser for a car air conditioner. However, according to the condenser described in Patent Document 1, the first header tank interferes with the installation of the radiator, and the engine Unnecessary space is generated in the room, and space cannot be saved. Moreover, since the heat exchange pipe is connected over almost the entire length of the first header tank, there is a problem that the gas-liquid separation performance is not sufficient.

Japanese Utility Model Publication 3-31266

  An object of the present invention is to solve the above-mentioned problems, reduce the installation space as compared with the capacitor described in Patent Document 1, and allow the amount of refrigerant to be filled in the refrigeration cycle to an appropriate amount at an early stage. Is to provide.

  In order to achieve the above object, the present invention comprises the following aspects.

1) Vertical direction in which the width direction is directed in the ventilation direction and a plurality of flat heat exchange tubes extending in the left-right direction are arranged in parallel in the vertical direction and the left and right ends of the heat exchange tube are connected And three or more heat exchange paths, each having a plurality of heat exchange pipes arranged in a row in the vertical direction, and the refrigerant flow in all the heat exchange pipes constituting each heat exchange path A capacitor having the same direction and different refrigerant flow directions in the heat exchange pipes of two adjacent heat exchange paths,
A first header tank to which a first heat exchange pipe constituting at least two heat exchange paths including a heat exchange path at the lower end and continuously arranged is connected to either one of the left and right ends; and a first header tank And a second header tank to which a second heat exchange pipe constituting a heat exchange path provided above the heat exchange path formed by the first heat exchange pipe connected to the first heat exchange pipe is connected. However, the upper end of the first header tank is located higher than the lower end of the second header tank, and the first header tank uses gravity. A heat exchange path at the upper end of a heat exchange path comprising a first heat exchange pipe connected to the first header tank and a second header tank connected to the second header tank. A heat exchange path consisting of two heat exchange tubes and A refrigerant condensing path for condensing the refrigerant, wherein the heat exchanging path excluding the upper end heat exchanging path among the heat exchanging paths composed of the first heat exchanging pipes connected to the first header tank supercools the refrigerant. 0.15 ≦ n / N ≦ 0.25, where n is the number of all first heat exchange tubes and N is the total number of all first heat exchange tubes and all second heat exchange tubes. Capacitors that satisfy this relationship.

  2) The first heat exchange pipe constituting the two heat exchange paths is connected to the first header tank, and the second heat exchange pipe constituting the two heat exchange paths is connected to the second header tank 1) The capacitor described.

  3) The vertical thickness of the first and second heat exchange tubes is 1.0 to 2.0 mm, the width of the first and second heat exchange tubes in the ventilation direction is 12 to 20 mm, and the second heat The capacitor according to 1) or 2) above, wherein the exchange pipe has a length of 400 to 700 mm, and the first header tank has a cylindrical shape with a vertical length of 350 to 450 mm and an inner diameter of 24 to 30 mm.

  According to the above capacitors 1) to 3), the first heat exchange pipe constituting at least two heat exchange paths including the heat exchange path at the lower end and continuously arranged is connected to either one of the left and right ends. A first header tank that is connected to a second heat exchange pipe that constitutes a heat exchange path provided above a heat exchange path that is composed of a first heat exchange pipe connected to the first header tank. 2 header tanks are provided, the first header tank is disposed on the outer side in the left-right direction than the second header tank, and the upper end of the first header tank is located above the lower end of the second header tank. Since the first header tank has a function of separating gas and liquid using gravity and storing the liquid, the upper end of the first header tank is extended upward, for example, to the vicinity of the upper end of the second header tank. Of Patent Document 1 Compared with the capacitor, the inner volume of the first header tank can be made large enough to effectively perform gas-liquid separation without making the thickness of the first header tank larger than the thickness of the second header tank. it can. Therefore, the space for disposing the capacitor can be reduced as compared with the capacitor described in Patent Document 1. As a result, it is possible to save space. In addition, since a relatively large space exists above the portion of the first header tank to which the heat exchange pipe is connected, the gas-liquid separation effect by gravity is excellent.

  Moreover, the heat exchange path | pass of the upper end of the heat exchange path | pass which consists of a 1st heat exchange pipe | tube connected to the 1st header tank, and the heat exchange path | pass which consists of a 2nd heat exchange pipe | tube connected to the 2nd header tank A refrigerant condensing path for condensing the refrigerant, wherein the heat exchanging path excluding the upper end heat exchanging path among the heat exchanging paths composed of the first heat exchanging pipes connected to the first header tank supercools the refrigerant. Since it is a supercooling path, the refrigerant flows into the first header tank from the plurality of first heat exchange pipes constituting the refrigerant condensing path located at the lower end, and gas and liquid are separated in the first header tank. It is possible to prevent the liquid phase refrigerant from being re-vaporized by suppressing the occurrence of the drop. Moreover, since the refrigerant flows into the first header tank from the plurality of first heat exchange pipes constituting the refrigerant condensing path located at the lower end, gas and liquid are separated in the first header tank. Gas-liquid separation can be performed efficiently. That is, a gas-liquid mixed phase refrigerant with a large amount of gas phase component flows in the upper heat exchange tube among the plurality of heat exchange tubes constituting the refrigerant condensation path, and a gas with a large amount of liquid phase component in the lower heat exchange tube. Although the liquid-phase refrigerant flows, these gas-liquid refrigerants flow into the first header tank without being mixed, so that gas-liquid separation can be performed efficiently.

  Furthermore, when the number of all first heat exchange tubes is n and the total number of all first heat exchange tubes and all second heat exchange tubes is N, the relationship 0.15 ≦ n / N ≦ 0.25 is satisfied. Therefore, it is possible to set the refrigerant charging amount in the refrigeration cycle using the capacitors 1) to 3) above to an appropriate charging amount with a constant degree of supercooling at an early stage. Moreover, since the width of the refrigerant filling amount in the stabilization region where the degree of supercooling is constant becomes wider, more stable supercooling characteristics can be obtained against load fluctuations and refrigerant leakage.

  According to the condenser of 3), the gas-liquid separation effect due to gravity in the first header tank is further improved, and the amount of refrigerant filled in the refrigeration cycle using the condenser of 3) is reduced at an early stage. While it becomes possible to make the proper amount of filling that makes the degree of supercooling constant, the range of the amount of refrigerant filled that makes the degree of supercooling constant becomes wider.

It is a front view which shows the whole structure of the capacitor | condenser by this invention. FIG. 2 is a front view schematically showing the capacitor of FIG. 1. It is a graph which shows the relationship between the refrigerant | coolant enclosure amount of each sample, and a supercooling degree. Ratio of the number of all first heat exchange tubes to the total number of all first heat exchange tubes and all second heat exchange tubes of each sample: n / N, the width of the refrigerant filling amount in the stabilization region, and the heat radiation performance It is a graph which shows a relationship.

  Embodiments of the present invention will be described below with reference to the drawings.

  In the following description, the downstream side in the ventilation direction (the back side in FIG. 1) is referred to as the front, and the opposite side is referred to as the rear.

  In the following description, the term “aluminum” includes aluminum alloys in addition to pure aluminum.

  FIG. 1 specifically shows the overall configuration of a capacitor according to the present invention, and FIG. 2 schematically shows a capacitor according to the present invention. In the capacitor of FIG. 1, the number of heat exchange tubes is different from the actual one in order to facilitate the illustration. In FIG. 2, illustration of individual heat exchange tubes is omitted, and illustration of corrugated fins, side plates, a refrigerant inlet member, and a refrigerant outlet member is also omitted.

  In FIG. 1, a capacitor (1) has a plurality of flat aluminum heat exchange tubes (2A) spaced apart in the vertical direction with the width direction directed in the front-rear direction and the length direction directed in the left-right direction. ) (2B) and three aluminum header tanks (3), (4) and (5) extending in the vertical direction where the left and right ends of the heat exchange tubes (2A) and (2B) are connected by brazing. Aluminum corrugated fins (6A) (6B) placed between the exchange tubes (2A) (2B) and outside the upper and lower ends and brazed to the heat exchange tubes (2A) (2B), and corrugations on the upper and lower ends It is equipped with aluminum side plates (7) that are placed outside the fins (6A) (6B) and brazed to the corrugated fins (6A) (6B). Three or more heat exchange paths (P1), (P2), (P3), and (P4) made up of pipes (2A) and (2B) are arranged in the vertical direction. The four heat exchange paths are referred to as first to fourth heat exchange paths (P1) (P2) (P3) (P4) in order from the top. The refrigerant flow directions of all the heat exchange tubes (2A) (2B) constituting each heat exchange path (P1) (P2) (P3) (P4) are the same, and two adjacent heat exchange paths The refrigerant flow directions in the heat exchange tubes (2A) and (2B) are different.

  As shown in FIGS. 1 and 2, at the left end side of the condenser (1), there are at least two heat exchange paths, including the lower end heat exchange path and arranged in series, here, the third and fourth heat exchange paths. (P3) The first header tank (3) to which the heat exchange pipe (2A) constituting (P4) is connected by brazing and the heat exchange constituting the first and second heat exchange paths (P1) (P2) A second header tank (4) to which the pipe (2B) is connected by brazing is provided separately. Here, the heat exchange pipe (2A) connected to the first header tank (3) is the first heat exchange pipe, and the heat exchange pipe (2B) connected to the second header tank (4) is the second heat. It is an exchange tube. Further, corrugated fins (6A) arranged between the adjacent first heat exchange tubes (2A) and between the first heat exchange tube (2A) at the lower end and the lower side plate (7) are provided as the first. It is called a corrugated fin, between adjacent second heat exchange tubes (2B), between the first heat exchange tube (2A) at the upper end and the second heat exchange tube (2B) at the lower end, and at the second heat at the upper end. The corrugated fin (6B) disposed between the exchange pipe (2B) and the upper side plate (7) is referred to as a second corrugated fin.

  Here, the thickness of the first and second heat exchange tubes (2A) (2B) in the vertical direction is preferably 1.0 to 2.0 mm. Moreover, it is preferable that the width | variety of the ventilation direction of a 1st and 2nd heat exchange pipe | tube (2A) (2B) is 12-20 mm. Furthermore, the length in the left-right direction of the second heat exchange tube (2B) is preferably 400 to 700 mm.

  The front and rear dimensions of the first header tank (3) and the second header tank (4) are substantially the same, but the horizontal header is larger in the first header tank (3) than in the second header tank (4). Is bigger than. The first header tank (3) is arranged on the left side (outside in the left-right direction) of the second header tank (4), and the center in the left-right direction of the first header tank (3) is the second header tank (4). It is located on the outer side in the left-right direction than the center in the left-right direction. Therefore, the first header tank (3) and the second header tank (4) are displaced without overlapping when seen from the plane. Also, the upper end of the first header tank (3) is above the lower end of the second header tank (4), here, at the same height as the upper end of the second header tank (4). 3) has a function as a liquid receiving part that separates gas and liquid using gravity and stores the liquid. That is, the internal volume of the first header tank (3) is such that the liquid-phase mixed refrigerant flows into the lower part of the first header tank (3) due to gravity. At the same time, the gas phase component of the gas-liquid mixed-phase refrigerant is accumulated in the upper part of the first header tank (3) due to gravity, and thereby enters the first heat exchange pipe (2A) of the fourth heat exchange path (P4). The internal volume is such that only the liquid-phase main mixed refrigerant flows.

  Here, the first header tank (3) preferably has a cylindrical shape having a vertical length of 350 to 450 mm and an inner diameter of 24 to 30 mm.

  A third header tank (5) to which all the heat exchange pipes (2A) (2B) constituting the first to fourth heat exchange paths (P1) to (P4) are connected to the right end side of the condenser (1). ) Is arranged. The cross-sectional shape of the third header tank (5) is the same as that of the second header tank (4). The third header tank (5) has a height position between the first heat exchange path (P1) and the second heat exchange path (P2), and the third heat exchange path (P3) and the fourth heat exchange path. Aluminum partition plates (8) and (9) respectively provided at a height position between (P4) and the upper header portion (11), the intermediate header portion (12), and the lower header portion (13) It is divided into. The left end of the second heat exchange pipe (2B) of the first heat exchange path (P1) is the second header tank (4), and the right end is the upper header (11) of the third header tank (5). The left end of the second heat exchange pipe (2B) of the second heat exchange path (P2) is connected to the second header tank (4), and the right end is the intermediate header (12) of the third header tank (5). ), The left end of the first heat exchange pipe (2A) of the third heat exchange path (P3) is the first header tank (3), and the right end is the intermediate header of the third header tank (5). The left end of the first heat exchange pipe (2A) of the fourth heat exchange path (P4) is connected to the first header tank (3) and the right end is connected to the third header tank (5). Are connected to the lower header section (13).

  The second header tank (4), the portion of the first header tank (3) where the first heat exchange pipe (2A) of the third heat exchange path (P3) is connected, the upper side of the third header tank (5) The header section (11), the intermediate header section (12), and the first to third heat exchange paths (P1) to (P3) form a condensing section (1A) for condensing the refrigerant, and the first header tank (3) In the fourth heat exchange path (P4) in which the first heat exchange pipe (2A) is connected, the lower header portion (13) of the third header tank (5) and the fourth heat exchange path (P4). A supercooling section (1B) for supercooling is formed, and the first to third heat exchange paths (P1) to (P3) serve as a refrigerant condensation path for condensing the refrigerant, and a fourth heat exchange path (P4 ) Is a refrigerant supercooling path for supercooling the refrigerant.

  A refrigerant inlet (14) is formed in the upper header part (11) of the third header tank (5) constituting the condensing part (1A), and is located under the third header tank (5) constituting the supercooling part (1B). A refrigerant outlet (15) is formed in the side header portion (13). A refrigerant inlet member (16) communicating with the refrigerant inlet (14) and a refrigerant outlet member (17) communicating with the refrigerant outlet (15) are joined to the third header tank (5).

  Here, the number of all first heat exchange pipes (2A), that is, all of the third heat exchange path (P3) that is the final refrigerant condensation path and the fourth heat exchange path (P4) that is the refrigerant subcooling path. When the number of first heat exchange tubes (2A) is n and the total number of all first heat exchange tubes (2A) and all second heat exchange tubes (2B) is N, 0.15 ≦ n / N ≦ 0 .25 is satisfied. That is, the total number of all first heat exchange tubes (2A) and all second heat exchange tubes (2B): the number of all first heat exchange tubes (2A) to N: the ratio of n: n / N is 0. The relationship of 15 ≦ n / N ≦ 0.25 is satisfied. This is obtained from the following experimental results.

First, samples A to F of six types of capacitors shown in Table 1 were prepared. In all samples A to F, the first heat exchange pipe (2A), the second heat exchange pipe (2B) and the first to third header tanks (3), (4) and (5) have the same configuration. Was used.

  Next, the condenser samples A to F, the compressor, the expansion valve, and the evaporator are used to assemble a refrigeration cycle. First, a predetermined amount of refrigerant is put into these refrigeration cycles, and the operation of the refrigeration cycle is started. A charge graph was created by examining the degree of supercooling at various refrigerant charging amounts while adding. The result is shown in FIG. The width: W of the refrigerant filling amount in the stabilization region where the degree of supercooling in the charge graph shown in FIG. 3 is constant was determined. The results are shown in Table 2. In Table 2, the width of the refrigerant filling amount in the stabilization region: W is expressed as a ratio relative to the sample C being 100%.

Further, the heat radiation performance Q of Samples A to F at the wind speeds of 1.0 m / sec, 2.5 m / sec, and 4.0 m / sec introduced into the capacitor was examined. Sample C showed the best heat dissipation performance when the wind speed was 1.0 m / sec (V1), and the wind speed was 2.5 m / sec (V2) and the wind speed was 4.0 m / sec (V3). Sample B showed the best heat dissipation performance in this case. The results are also shown in Table 2. In Table 2, heat dissipation performance: Q is expressed as a ratio of 100% for sample C when wind speed: V1, and 100% for sample B when wind speed: V2 and wind speed: V3. Expressed as a ratio to.

  Then, the relationship between the above-mentioned n / N, the width W of the refrigerant filling amount at which the degree of supercooling becomes constant, and the heat radiation performance Q were obtained. The result is shown in FIG. In FIG. 4, ◇ is sample A, □ is sample B, ◯ is sample C, Δ is sample D, x is sample E, and ● is sample F.

  3 and 4, the width W of the refrigerant filling amount at which the degree of supercooling is constant becomes wider as n / N is smaller. On the other hand, the heat dissipation performance Q improves as n / N increases, but decreases rapidly when n / N exceeds a certain value. As for the performance of the condenser, it is desirable that the width W of the refrigerant filling amount in which the degree of supercooling is constant is wide and that the heat radiation performance Q is excellent, but based on FIG. 4, a practical range in which both are balanced , The total number of all first heat exchange tubes (2A) and all second heat exchange tubes (2B): the number of all first heat exchange tubes (2A) to N: the ratio of n: n / N is It should be 0.15 ≦ n / N ≦ 0.25.

  The capacitor (1) is manufactured by brazing all parts together.

  The condenser (1) constitutes a refrigeration cycle together with a compressor, an expansion valve (decompressor) and an evaporator, and is mounted on a vehicle as a car air conditioner.

  In the condenser (1) having the above-described configuration, the high-temperature and high-pressure gas-phase refrigerant compressed by the compressor passes through the refrigerant inlet member (16) and the refrigerant inlet (14), and the upper header portion of the third header tank (5). (11) flows into the second heat exchange pipe (2B) of the first heat exchange path (P1) and is condensed while flowing leftward and flows into the second header tank (4). The refrigerant flowing into the second header tank (4) is condensed while flowing to the right in the second heat exchange pipe (2B) of the second heat exchange path (P2), and the third header tank (5). Into the intermediate header portion (12). The refrigerant flowing into the intermediate header portion (12) of the third header tank (5) is condensed while flowing leftward in the first heat exchange pipe (2A) of the third heat exchange path (P3). 1 Flows into the header tank (3).

  The refrigerant flowing into the first header tank (3) is a gas-liquid mixed phase refrigerant. Among the gas-liquid mixed phase refrigerant, the liquid-phase main mixed phase refrigerant is accumulated in the lower part of the first header tank (3) due to gravity. Enter the first heat exchange pipe (2A) of the heat exchange path (P4).

  The liquid phase main mixed refrigerant entering the first heat exchange pipe (2A) of the fourth heat exchange path (P4) is supercooled while flowing rightward in the first heat exchange pipe (2A), It enters the lower header portion (13) of the three header tank (5), flows out through the refrigerant outlet (15) and the refrigerant outlet member (17), and is sent to the evaporator through the expansion valve.

  On the other hand, the gas phase component of the gas-liquid mixed phase refrigerant that has flowed into the first header tank (3) accumulates in the upper part of the first header tank (3).

  In the capacitor (1) described above, at least one of a desiccant, a gas-liquid separation member, and a filter may be disposed in the first header tank (3).

  The capacitor | condenser by this invention is used suitably for the car air conditioner mounted in a motor vehicle.

(1): Capacitor
(1A): Condensing part
(1B): Supercooling section
(2A): 1st heat exchange tube
(2B): Second heat exchange tube
(3): First header tank
(4): Second header tank
(5): Third header tank
(P1): First heat exchange path
(P2): Second heat exchange path
(P3): Third heat exchange path
(P4): Fourth heat exchange path

Claims (3)

A plurality of flat heat exchange pipes extending in the left-right direction and arranged in parallel at intervals in the vertical direction, and the vertical direction where the left and right ends of the heat exchange pipe are connected, with the width direction facing the ventilation direction There are three or more heat exchange paths, each having a header tank, and each of which is composed of a plurality of heat exchange pipes arranged continuously in the vertical direction, and the refrigerant flow directions of all the heat exchange pipes constituting each heat exchange path are It is the capacitor | condenser which is the same, and the refrigerant | coolant flow directions of the heat exchange pipe | tube of two adjacent heat exchange paths differ,
A first header tank to which a first heat exchange pipe constituting at least two heat exchange paths including a heat exchange path at the lower end and continuously arranged is connected to either one of the left and right ends; and a first header tank And a second header tank to which a second heat exchange pipe constituting a heat exchange path provided above the heat exchange path formed by the first heat exchange pipe connected to the first heat exchange pipe is connected. However, the upper end of the first header tank is located higher than the lower end of the second header tank, and the first header tank uses gravity. A heat exchange path at the upper end of a heat exchange path comprising a first heat exchange pipe connected to the first header tank and a second header tank connected to the second header tank. A heat exchange path consisting of two heat exchange tubes and A refrigerant condensing path for condensing the refrigerant, wherein the heat exchanging path excluding the upper end heat exchanging path among the heat exchanging paths composed of the first heat exchanging pipes connected to the first header tank supercools the refrigerant. 0.15 ≦ n / N ≦ 0.25, where n is the number of all first heat exchange tubes and N is the total number of all first heat exchange tubes and all second heat exchange tubes. Capacitors that satisfy this relationship. The first heat exchange pipe constituting two heat exchange paths is connected to the first header tank, and the second heat exchange pipe constituting two heat exchange paths is connected to the second header tank. Capacitor. The first and second heat exchange tubes have a vertical thickness of 1.0 to 2.0 mm, and the first and second heat exchange tubes have a ventilation direction width of 12 to 20 mm. The capacitor according to claim 1, wherein the first header tank has a cylindrical shape with a vertical length of 350 to 450 mm and an inner diameter of 24 to 30 mm.

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