JP2006242458A - Heat exchanger, heat exchanger core and method of manufacturing heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger having a constitution for improving drainability of moisture condensed on a tube surface while holding an interval between tubes in a heat exchanger having no fin shape between the tubes; and a manufacturing method of the heat exchanger. <P>SOLUTION: This heat exchanger has a plurality of adjacent tubes 4 for making a refrigerant flow inside, a refrigerant inflow header tank 10 and a refrigerant outflow header tank 14 respectively arranged in a refrigerant inflow part 7 and a refrigerant outflow part 8 of the tubes 4. The plurality of tubes 4 are arranged so that one side is positioned lower than the other side in the flowing direction of a refrigerant, and are constituted by arranging a holding member 19 for holding an interval of the adjacent tubes 4 between the one side and the other side of the tubes 4, to thereby improve drainability of the moisture sticking to the tubes by eliminating the fin shape between the tubes. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a heat exchanger used in a low-temperature environment in order to maintain the inside temperature of a refrigerator or a freezer car at a low temperature, a heat exchanger core, and a method for manufacturing the heat exchanger.

  In this type of conventional heat exchanger, a liquid refrigerant is fed into the inside, and the temperature of the air flowing through the heat exchanger is lowered by evaporating the liquid refrigerant in a tube of the heat exchanger. And the water vapor | steam contained in the air condenses on the surface of the tube of a heat exchanger, and adheres as a water | moisture content.

Therefore, as a conventional heat exchanger of this type, in order to drain water adhering to the surface of the flat tube, a plurality of flat tubes that are elongated in the horizontal direction are stacked in the vertical direction, and the corrugated fins are sandwiched between the flat tubes. And a header tank provided at both ends in the longitudinal direction of the core portion, each flat section of the plurality of flat tubes being downstream with respect to the horizontal direction in which an external fluid flows The thing inclined so that the side may fall is known (for example, refer patent document 1).
Japanese Unexamined Patent Publication No. 2004-69228 (FIG. 4)

  However, in the above conventional heat exchanger, each flat cross section of the flat tube is inclined so that the downstream side is lowered with respect to the horizontal direction in which the external fluid flows. Drainage is improved by collecting and dripping smoothly at the lower end on the downstream side using the force of the fluid flow, but moisture attached to corrugated fins arranged between flat tubes is difficult to flow down. There was a problem that it was difficult to drain.

  The present invention has been made in view of the above-described problem, and maintains a gap between tubes in a heat exchanger that does not have a fin shape between the tubes and improves the drainage of moisture condensed on the tube surface. An object of the present invention is to provide a heat exchanger provided with a heat exchanger core, and a method for manufacturing the heat exchanger.

  In order to achieve the above object, the present invention employs the following technical means.

The invention of the heat exchanger according to claim 1, wherein the refrigerant flows inside, a plurality of adjacent tubes (4, 4A),
A refrigerant inflow header tank (9, 9A) and a refrigerant outflow header tank (14, 30) respectively disposed in the refrigerant inflow portion (7) and the refrigerant outflow portion (8) of the tube (4, 4A). ,
With respect to the direction in which the refrigerant flows, one side of the plurality of tubes (4, 4A) is disposed at a position lower than the other side, and the one side and the other side of the plurality of tubes (4, 4A) A holding member (19) for holding a gap between the adjacent tubes (4, 4A) is provided therebetween.

  According to the first aspect of the present invention, by holding the interval between the adjacent tubes (4, 4A) by the holding member (19), a certain heat exchange performance can be secured, and the tubes (4, 4A) can be secured. ) Since moisture condensed on the surface easily flows down through the holding member (19), drainage is improved, and performance deterioration of the heat exchanger due to freezing of condensed water can be reduced.

  In the invention of the heat exchanger according to claim 2, the shape of the plurality of tubes (4A) on both sides of the holding member (24, 25, 26, 27) in the direction in which the refrigerant flows is a mountain shape or a valley shape. It is formed in this.

  According to the second aspect of the present invention, it is possible to further promote the tendency that the moisture adhering to the tube (4A) flows down through the holding member (24, 25, 26, 27) or the tube (4A). it can.

  The invention of the heat exchanger according to claim 3 is characterized in that the holding member (24, 25, 26, 27) has a valley bottom (31, 33) of a predetermined number of tubes (4A) formed in the mountain shape and the valley shape. ), The tube (4A) is held.

  According to the third aspect of the present invention, the moisture adhering to the surface of the tube (4A) flows along the inclined tube (4A) toward the holding member and then flows down along the holding member. As a result, drainage can be improved.

  According to a fourth aspect of the present invention, the tube (4, 4A) is formed in a flat shape.

  According to the fourth aspect of the present invention, since the flat tube that is easily bent is stably held, the shape of the heat exchanger is stabilized, the handling property is improved, and the flat tube is accumulated on the upper surface of the flat tube. Easily flow of moisture, so drainage can be improved.

The invention of the heat exchanger according to claim 5 is characterized in that the refrigerant flows inside and a plurality of adjacent flat tubes (4B);
A refrigerant inflow header tank (9A) and a refrigerant outflow header tank (14A) arranged in each of the refrigerant inflow portion (7A) and the refrigerant outflow portion (8A) of the flat tube (4B),
The flat tube (4B) is provided with a holding member (19A) that inclines the longitudinal direction in the flat cross section of the flat tube (4B) with respect to the horizontal direction and holds the interval between the adjacent flat tubes (4B).

  According to the invention described in claim 5, since the flexible flat tube (4B) is stably held, the shape of the heat exchanger is stabilized and the handleability is improved, and the outer side of the flat tube (4B) is improved. Water that tends to accumulate on the upper surface of the flat tube (4B) can be drained by utilizing the flow of the external fluid flowing through the flat tube (4B).

The invention of the method for manufacturing a heat exchanger core according to claim 6 includes a step of continuously forming a plurality of tubes (4A) through which a refrigerant flows into a desired mountain shape and valley shape in the refrigerant flow direction. When,
The predetermined number of tubes so that the refrigerant inlet (35) of the predetermined number of tubes (4A) continuously formed in a mountain shape and a valley shape communicate with the inlet (10) of the refrigerant inflow header tank (9). (4A) and the refrigerant inflow header tank (9) are connected so that the refrigerant outlet (36) of the predetermined number of tubes (4A) and the outlet (28) of the refrigerant outflow header tank (30) communicate with each other. Connecting the predetermined number of tubes (4A) and the refrigerant outflow header tank (30);
Forming a heat exchanger core (20) having a temporary stable form as a whole by holding each interval of the tubes (4A) by holding members (24, 26);
Placing the heat exchanger core (20) in the temporary stable form into a furnace and brazing in the furnace as a whole;
It is characterized by comprising.

  According to the sixth aspect of the present invention, there is provided a method of manufacturing a heat exchanger that can improve the drainage of water adhering to the tube (4A) and has a stable form and good handleability during manufacture. Can do.

  According to a seventh aspect of the present invention, in the step of forming the temporary stable heat exchanger core (20), the holding members (24, 26) The said tube (4A) is hold | maintained in the valley bottom part (31, 33) of the some tube (4A) formed in the shape.

  According to the seventh aspect of the present invention, by holding the bent portion of the tube (4A), which is a portion that is easily subjected to stress due to thermal contraction and is also a portion that is easily deformed by an external force, by the holding member, Strength can be improved.

  According to an eighth aspect of the present invention, there is provided the heat exchanger manufacturing method according to the sixth aspect, wherein the heat exchanger core manufactured by the heat exchanger core manufacturing method according to the sixth aspect is arranged in a state where a plurality of heat exchanger cores are arranged. The arranged heat exchanger cores are integrated by joining members together.

  According to the eighth aspect of the invention, by increasing or decreasing the number of heat exchanger cores, it is possible to easily supply a heat exchanger suitable for the required heat exchange capacity.

  In addition, the code | symbol in the bracket | parenthesis of each said means shows a corresponding relationship with the specific means of embodiment mentioned later.

(First embodiment)
The heat exchanger according to the present invention is an evaporator used in a refrigerator car or a refrigerator used in a low temperature environment in order to maintain the inside temperature at a low temperature, for example, an evaporator, and plays an important role in a refrigeration cycle apparatus. It is a component made. This heat exchanger is firmly fixed to parts on the vehicle side via a side plate that supports a plurality of tubes through which the refrigerant flows so as not to be affected by vibrations of the vehicle. Below, the heat exchanger which concerns on this invention is demonstrated.

  FIG. 1 is a schematic perspective view showing a configuration when the heat exchanger of the present invention is mounted on a refrigeration vehicle. FIG. 2 is a front view showing the configuration of the tube of the heat exchanger in the present embodiment. FIG. 3 is a graph showing experimental data in which the drainage of the heat exchanger according to this embodiment is examined. FIG. 4 is a front view showing the configuration of the heat exchanger in the present embodiment.

  As shown in FIG. 1, the freezer 1 is provided with a freezer 2 at the rear of the driver's seat, and the freezer 2 is further opened with a door 3 at the rear for loading frozen products such as frozen foods.

  The refrigeration vehicle 1 has a refrigeration cycle device 5 mounted on the front side of the vehicle. The refrigeration cycle apparatus 5 includes a compressor 6 that compresses and discharges a refrigerant at a high temperature and a high pressure, and the compressor 6 is driven by a vehicle travel engine via an electromagnetic clutch.

  The gas refrigerant compressed to high temperature and high pressure by the compressor 6 flows into the condenser 9. The condenser 9 is installed at a position under the floor of the vehicle, and cools and condenses the gas refrigerant in the vehicle with the driving wind of the vehicle and the cooling air blown by the electric compressor fan.

  A receiver 11 is provided on the refrigerant outlet side of the condenser 9, and the refrigerant condensed by the receiver 11 is separated into a gas phase refrigerant and a liquid phase refrigerant, and the liquid phase refrigerant is once stored. A decompression device 12 that decompresses the liquid-phase refrigerant sent from the receiver 11 is provided on the outlet side of the receiver 11, and the low-pressure gas-liquid two-phase refrigerant decompressed by the decompression device 12 is evaporated by the evaporator 13. Let An accumulator 14 is provided between the outlet side of the evaporator 13 and the suction side of the compressor 6.

  The accumulator 14 performs gas-liquid separation of the refrigerant that has passed through the evaporator 13, stores the liquid-phase refrigerant, and sends the gas-phase refrigerant to the compressor 6 side. Further, a hot gas bypass passage 15 that directly communicates between the discharge side of the compressor 6 and a portion that is downstream of the decompression device 12 and upstream of the evaporator 13 is provided. Is provided for defrosting the evaporator 13, and an electromagnetic valve 16 is provided in the middle of the flow path.

  The evaporator 13 cools the air in the freezer 2 by the latent heat of vaporization of the refrigerant, and is disposed in the upper part of the freezer 2 on the front side of the vehicle. In the freezer 2, an electric freezing fan 17 that blows air toward the evaporator 13 is provided adjacent to the evaporator 13. The refrigeration fan 17 and the evaporator 13 constitute a cooling unit 130. The refrigeration fan 17 sucks in-chamber air in the freezer 2, passes through the evaporator 13 and cools, and then blows cooling air into the refrigerator again.

  Next, the structure of the heat exchanger core 40 in the heat exchanger of this embodiment applied to this evaporator 13 is demonstrated. As shown in FIG. 4, the heat exchanger core 40 includes a plurality of tubes 4 arranged vertically (10 in this embodiment), a refrigerant inflow header tank 9 and a refrigerant outflow header provided at both ends of these tubes 4. The tank 14 and the holding member 19 that holds the interval between the tubes 4 for all of the plurality of tubes 4 are configured.

  The tube 4 is inclined so as to be disposed at a position lower than the other side with respect to the longitudinal direction (the direction in which the refrigerant flows), and is connected to both header tanks 9 and 14. In the present embodiment, as an example, a configuration is shown in which the refrigerant inflow header tank 9 side is arranged higher and the refrigerant outflow header tank 14 side is arranged lower than that. Moreover, it is good also as a structure which arrange | positions the refrigerant | coolant outflow header tank 14 side high, and arrange | positions the refrigerant | coolant inflow header tank 9 side lower than it.

  The refrigerant inflow header tank 9 is provided with an inlet 10 through which refrigerant flowing in the refrigeration cycle apparatus 5 flows, and all the tubes 4 are connected so that the refrigerant inflow portions 7 of the plurality of tubes 4 are located inside. An opening is provided. All the tubes 4 inserted into the openings are fixed by being brazed to the refrigerant inflow header tank 9.

  On the other hand, the refrigerant outflow header tank 14 is provided with an outlet 18 through which the refrigerant flowing into the tube 4 flows out, and all of the tubes 4 are disposed so that the refrigerant outflow portions 8 of the plurality of tubes 4 are located inside. An opening to be connected is provided. All the tubes 4 inserted into the openings are fixed by being brazed to the refrigerant outflow header tank 14.

  The refrigerant flowing through the refrigeration cycle device 5 and flowing into the refrigerant inflow header tank 9 from the inlet 10 enters the tube 4 from the refrigerant inflow portion 7 of the tube 4 and enters the refrigerant outflow header tank 14 from the refrigerant outflow portion 8. Flows out. And it is sent from the outflow port 18 to other components (for example, accumulator 14) of the refrigeration cycle apparatus.

  The holding member 19 is composed of a plate-like aluminum plate, supports the upper and lower surfaces of the tube 4, and has groove-shaped slits opened on the sides so as to sandwich the tube 4 from above and below the number of tubes 4 (this embodiment) 10). The vertical opening width of each slit is equal to the vertical height of the tube 4, and the vertical spacing of each slit matches the desired vertical spacing of the plurality of tubes 4 arranged in the vertical direction. Is formed.

  When all the tubes 4 supported at both ends by the header tanks 9 and 14 are held by the holding member 19, all the tubes 4 are simultaneously applied to the openings of the slits, and all the tubes 4 are accommodated in the slits as they are. Thus, the holding member 19 is pushed in from the front side of the heat exchanger core 40 toward the back side (in the depth direction shown in FIG. 4). The tube 4 is restricted from moving sideways when the side surface of the tube 4 reaches the deep part of the groove-shaped slit. Since the upper and lower surfaces of the tube 4 are held by the inner upper and lower surfaces of the groove-shaped slit, the vertical movement of the tube 4 is restricted.

  The holding member 19 may hold any position of the tube 4 between the header tanks 9 and 14, may hold the refrigerant inflow header tank 9 side, or the refrigerant outflow header tank 14 side. May be held. Further, an intermediate position between the header tanks 9 and 14 may be maintained.

  By the way, when the liquid refrigerant is sent into the tube 4 of the heat exchanger constituting the refrigeration cycle apparatus 5 and this liquid refrigerant is evaporated in the tube of the heat exchanger, it flows through the heat exchanger due to the latent heat of vaporization of the refrigerant. Cool the air. And the water vapor | steam contained in this air condenses on the surface of the tube 4 of a heat exchanger, and it adheres as a water | moisture content, and this water | moisture content becomes frost and forms frost on the tube 4 at the time of freezing operation. In addition, this frost is melted by a defrosting operation by flowing a refrigerant through the hot gas bypass passage 15, but the melted water that is not drained but is retained on the surface of the tube 4 is frozen. It will be frozen again.

  Thus, the moisture that has condensed and adhered to the surface of the tube 4 needs to be drained from the surface of the tube 4. Therefore, the holding member 19 that holds the tube 4 is condensed on the surface of the tube 4 as shown in FIG. 4 in addition to the function of holding the space between the tubes 4 to ensure a certain heat exchanger performance. In order to prevent moisture from staying, it flows on the inclined surface of the tube 4, flows down the side wall of the holding member 19, and drops from the lower end of the holding member 19 to drain the condensed water on the surface of the tube 4. It has a function. The water dropped and drained from the lower end of the holding member 19 is received by a drain pan (not shown) provided below the holding member 19 or directly dropped outside the vehicle. Further, the water condensed on the surface of the tube 4 between the holding member 19 and the refrigerant outflow header tank 14 is drained by flowing down the side wall of the refrigerant outflow header tank 14.

  By improving drainage in this way, icing on the tube 4 can be prevented, and an increase in air resistance due to icing can be prevented, so that a reduction in the capacity of the heat exchanger can be prevented.

  Next, the experimental result which showed the effect in the drainage of the heat exchanger core 40 of this embodiment is demonstrated. In this experiment, as shown in FIG. 2, the holding member 19 is removed from the heat exchanger core 40 described above. The tube 4 is arranged with an inclination of an angle θ with respect to the flow direction of the refrigerant, that is, the horizontal direction.

  Under each condition of the inclination θ, the heat exchanger core 40 is once completely submerged in the water tank, and 5 minutes after the heat exchanger core 40 is pulled up, the water remaining in the heat exchanger core 40 is collected. Measure the amount. The water in the water tank is 5 ° C. in consideration of the actual use state, and the ambient temperature is 10 ° C. The heat exchanger core 40 has a width of 1000 mm and a height of 1000 mm, the tube has a flat shape, and the longitudinal dimension of the flat cross section is 23.65 mm.

  FIG. 3 shows a relationship between the case where the inclination θ is changed in the range of 0 to 30 ° and the amount of water retained on the surface of the tube 4.

  As shown in FIG. 3, the experimental results show that the water retention amount when the inclination angle θ = 0 ° is 5.6 g, the water retention amount when the inclination angle θ = 3 ° is 4.5 g, and the inclination angle θ = 6 °. The water retention amount is 3.6 g, the water retention amount is 3.5 g when the inclination angle θ = 10 °, the water retention amount is 3.2 g when the inclination angle θ = 20 °, and the inclination angle θ = 30 °. The water retention amount was 2.7 g.

  The mechanism by which the condensed water flows on the surface of the tube 4 is considered to flow down when the balance between the surface tension of the water adhering to the surface of the tube 4 and the gravity acting on the water becomes larger. Since the gravity increases as the angle of the surface of the tube 4 approaches the vertical direction, naturally, the water retention amount is smaller at the inclination angle θ = 30 ° than at the inclination angle θ = 3 °. However, inclining the tube 4 greatly increases the height and lateral dimensions in which the entire heat exchanger core 40 can be accommodated, increasing the space for mounting the heat exchanger core 40 on the vehicle and is not suitable as a product. . Therefore, a heat exchanger that balances the space required for the product and the drainage performance is desired.

  From such a viewpoint, it can be judged that the inclination angle θ of the tube 4 is preferably in the range of 3 ° to 6 °. The experiment result with the inclination angle θ = 10 ° or more shows that the rate of decrease in the water retention amount is small compared to the size of the angle, the drainage performance is not excellent, and the heat exchanger core becomes large as a whole. Is not desirable. Further, even when the heat exchanger core 40 is lifted from the water tank and visually observed 5 minutes later, the moisture remaining on the surface of the tube 4 when the inclination angle θ is 3 ° or more is the refrigerant outflow header tank 14 and the tube 4. It was felt that there was not much difference at an inclination angle θ = 3 ° or more.

  In addition, at present, public roads have a slope of 6 ° or less with respect to the width direction of the road. Even in view of this situation, setting the inclination angle θ of the tube 4 in the range of 3 ° to 6 ° with respect to the horizontal direction in advance is when traveling on a road having an inclination of 0 ° to 6 °. As a result, the inclination of the tube 4 with respect to the horizontal direction falls within the range of 0 ° to 9 °, and as described above, desirable drainage can be obtained from the experimental results.

  Thus, according to the heat exchanger of this embodiment, the refrigerant | coolant inflow header tank 9 and refrigerant | coolant outflow header which are distribute | arranged to each of the adjacent tube 4 and the refrigerant | coolant inflow part 7 and the refrigerant | coolant outflow part 8 of this tube 4 respectively. A tank 14, and arranged so that one side of the plurality of tubes 4 is lower than the other side in the refrigerant flow direction, and adjacent tubes between the one side and the other side of the tubes 4. Since the holding member 19 that holds the gap between the four tubes is provided, by holding the gap between the adjacent tubes 4 by the holding member 19, a certain heat exchange performance can be secured and the surface of the tube 4 can be secured. Since the condensed water flows on the surface of the tube 4 and flows down through the holding member 19 existing in the middle of the tube 4, the drainage is also improved.

  Moreover, when the inclination angle θ of the tube 4 is configured in a range of 3 ° to 6 ° with respect to the horizontal direction, the space for housing the heat exchanger in the vehicle and the inclination of the public road with respect to the road width direction are taken into consideration. A heat exchanger capable of obtaining excellent drainage can be provided.

(Second Embodiment)
The second embodiment will be described below. FIG. 5 is a conceptual diagram schematically showing the configuration of the tube of the heat exchanger of this embodiment, and shows a state before the tube is held by the holding member.
FIG. 6 is a perspective view showing the configuration of the heat exchanger in the present embodiment. FIG. 7 is a schematic diagram showing the relationship between the tube and the holding member of the heat exchanger in the present embodiment.

  As shown in FIG. 5, the heat exchanger core 20 includes a plurality of tubes 4 </ b> A through which refrigerant flows, and a refrigerant arranged in communication with a refrigerant inlet 35 provided at one end of the tubes 4 </ b> A in the longitudinal direction. The inflow header tank 9 and the refrigerant outflow header tank 30 arranged in communication with the refrigerant outflow port 36 provided at the other end in the longitudinal direction of the plurality of tubes 4A are configured.

  The tube 4A is arranged in a zigzag shape so as to continuously form the peak 29, valley bottom 31, peak 32, valley bottom 33, peak 34 in the refrigerant flow direction. Are arranged in a state where a plurality of are arranged at a predetermined interval.

  The plurality of tubes 4A have a refrigerant inlet 35 at one end arranged in the refrigerant inflow header tank 9, and a refrigerant outlet 36 at the other end arranged in the refrigerant outflow header tank 30, Between the inflow header tank 9 and the refrigerant outflow header tank 30, three peak portions 29, 32 and 34 and two valley bottom portions 31 and 33 are formed as a whole to constitute the heat exchanger core 20. Yes. The heat exchanger core 20 has a horizontally long flat rectangular parallelepiped shape as a whole, and a plurality of groups of tubes 4A have a horizontally long zigzag shape.

  As shown in FIG. 6, the group of tubes 4 </ b> A (14 tubes in this embodiment) formed in this way are formed at two locations between the refrigerant inflow header tank 9 and the refrigerant outflow header tank 30. 31 and 33 are integrally held by holding members 24 and 26 while maintaining a desired interval between the tubes.

  The tube 4A has a flat shape, and the main surface of the flat shape is arranged up and down, and the main surface is arranged substantially in parallel with the direction in which air cooled by the latent heat of vapor passing through the tube 4A passes. Has been.

  In addition, although the cross-sectional shape of the tube in this embodiment has demonstrated the flat tube 4A as an example, it is not necessarily limited to this. For example, the cross-sectional shape may be circular or rectangular.

  Between the plurality of tubes 4A through which the refrigerant as the heat exchange medium flows, a predetermined gap is provided over almost the entire length thereof. The clearance gap between the tubes 4A is ensured in the extension part extended along the longitudinal direction of the heat exchanger core 20 among the tubes 4A. That is, a predetermined gap is secured between the plurality of tubes 4 </ b> A in the short direction as the heat exchanger core 20. These gaps are for the passage of air as the heat exchange medium.

  The inlet 10 through which the refrigerant flows into the heat exchanger and the outlet 28 through which the refrigerant flows out are provided so as to open substantially at the center of the refrigerant inlet header tank 9 and the refrigerant outlet header tank 30. . The low-pressure gas-liquid two-phase refrigerant decompressed by the decompression device 12 flows into the inflow port 10, and this refrigerant evaporates in the tube 4 </ b> A to cool the air and from the outflow port 28 toward the accumulator 14. Will be leaked.

  The group of tubes 4A is configured such that both ends thereof are inserted into the refrigerant inflow header tank 9 and the refrigerant outflow header tank 30, respectively, and are fixed by brazing or the like.

  The refrigerant inflow header tank 9 has a height dimension that allows communication with the inside of all 14 tubes 4A. Similarly, the refrigerant outflow header tank 30 includes all 14 tubes 4A. The height is such that it can communicate with the interior of the.

  As shown in FIG. 6, the heat exchanger cores 21, 22, and 23 having the same configuration as the heat exchanger core 20 configured as described above are arranged in four stages along with the heat exchanger core 20 in the air flow direction. They are arranged and fixed together by holding members 24, 25, 26 and 27 to constitute a heat exchanger.

  As shown in FIG. 7, the heat exchanger cores 20 and 21 are held by the holding member 24 at the valley bottom 31 near the refrigerant inflow header tank 9, and similarly the holding member at the valley bottom 33 near the refrigerant outflow header tank 30. 26 is integrally held. On the other hand, the heat exchanger cores 22 and 23 are held by the holding member 25 at the valley bottom 31 near the refrigerant inflow header tank 9, and are also integrally formed by the holding member 27 at the valley bottom 33 near the refrigerant outflow header tank 30. It is a configuration to be held.

  The integrated heat exchanger cores 20 and 21 and the heat exchanger cores 22 and 23 braze the coupling portion 37 in a state where the holding member 24 and the holding member 25 are abutted or overlapped. When applied, it is integrated as a heat exchanger. Similarly, the heat exchanger cores 20 and 21, and the heat exchanger cores 22 and 23, which are respectively integrated, are connected to the joint portion when the holding member 26 and the holding member 27 are abutted or overlapped. It is integrated as a heat exchanger by brazing. Thus, the heat exchanger which combined the several heat exchanger core shown in FIG. 6 is assembled. For the brazing material applied to the joint portion, an appropriate metal material having a melting point lower than that of the material is used in consideration of the material of the holding members 24, 25, 26, and 27.

  The holding member 24 has a thin plate shape and a comb shape, and is configured by a rectangular aluminum plate as a whole. Further, the holding member 24 supports the upper and lower surfaces of the tube 4A, and has groove-shaped slits opened on the sides so as to sandwich the tube 4A from above and below the number of the tubes 4A of this embodiment (14 in this embodiment). Book). The adjacent slits are partitioned by a connecting portion.

  In addition, the vertical opening width of each slit is equal to or slightly larger than the vertical height of the tube 4A, and the vertical interval at which each slit is disposed is a plurality of slits constituting the heat exchanger core. It corresponds to a desired interval in the vertical direction of the tube 4A. The holding member 24 is provided with the above-mentioned slits opened on both sides so that the tubes constituting the two heat exchanger cores can be held, and the two rows of slits opened on both sides are arranged in the vertical direction. They are offset from each other.

  The holding member 24 is formed with a plurality of slits penetrating in the thickness direction. Each slit is formed so as to extend substantially horizontally along the width direction of the holding member 24 from both sides of the holding member 24 in the longitudinal direction (the stacking direction of the tubes 4A). Each slit is formed from one side to the center of the holding member 24 in the width direction. The plurality of slits are arranged so as to be shifted from each other by a half pitch with respect to the longitudinal direction of the holding member 24. With this configuration, the tubes of the adjacent heat exchanger cores are held in a state shifted from each other by a half pitch.

  The holding member 24 has a connecting portion extending in the longitudinal direction at the center portion, and is formed in a comb-like shape in which comb teeth alternately extend from the connecting portion toward both sides thereof. The connecting portion at the center of the holding member 24 provides a wall surface that is continuous in the vertical direction.

  The holding members 25, 26, and 27 have the same configuration as the holding member 24.

  The tube 4A is a flat shape including a curved surface portion having a curved shape at both ends in the major axis direction of the cross section and a side wall surface having mutually parallel line segments connecting the both ends in the major axis direction of the cross section. Heat exchanged between the air and the tube 4 </ b> A is performed by the air that is forcibly sent by, for example, not shown) being ventilated along the side wall surface.

  The tube 4A has a very long cross-sectional shape with a flat shape having a minor axis direction dimension of about 2 mm and a major axis dimension of about 24 mm, and the group of tubes 4A has a dimension of a pitch of about 6 mm in the flat minor axis direction. Fourteen air lines are formed between adjacent tubes.

  As described above, the heat exchanger cores 21, 22, and 23 having the same configuration as the heat exchanger core 20 including a group of tubes 4A arranged in parallel (14 in this embodiment) are spaced by about 7 mm in the air ventilation direction. The heat exchanger cores adjacent to each other in the air ventilation direction are arranged at positions shifted from the air circulation direction. That is, the heat exchanger cores 20 and 22 are arranged so as to be in the same position in the stacking direction of the tubes 4A, and the heat exchanger cores 21 and 23 are more than the heat exchanger cores 20 and 22 in the stacking direction of the tubes 4A. Is also arranged so as to be lower by the amount of the shift.

  Further, the center line in the air ventilation direction of the tube 4A in the heat exchanger core 21 is made to coincide with the extension of the intermediate line of the pitch between the tubes constituting the heat exchanger cores 20 and 22 adjacent in the air ventilation direction. It is desirable to arrange the heat exchanger cores adjacent to each other in a shifted manner.

  Below, the process which manufactures the heat exchanger core of this embodiment is demonstrated.

  First, the tube 4A is formed by bending it into a desired mountain shape and valley shape in the flow direction of the refrigerant. In this step, the tube 4A before bending is cut into a necessary length in consideration of the number of bending, and bent one by one into a desired shape.

  In the step of bending the tube into a desired shape (referred to as a tube bending step), a mold prepared in advance so that the tube is in a shape to be bent is used. This mold is divided into two parts, and the tube is pressed from both sides. The tube 4A before molding is set on the base of the two divided molds, and this tube 4A is connected to another mold and a base. The mold is sandwiched between the molds and pressed until the tube 4A is plastically deformed into a desired shape.

  This mold is made of a material harder than the tube material such as iron or carbon steel in consideration of the fact that the tube is made of aluminum or copper. In general, a press machine is used for the press work, but when the tube 4A to be pressed is thin and thin, it can also be performed manually. If the mold is formed so that a plurality of tubes can be pressed at a time, this tube bending process can be performed in a large amount of tubes with a press machine.

  Then, when the pressing operation for the number of tubes 2 constituting the heat exchanger is completed, a step of connecting the plurality of tubes 2 and the header tank is performed (this is called a header tank connection step).

  First, a predetermined number of bent tubes 4A are arranged, and both end surfaces of these tubes 4A are aligned. And these tubes 4A and the refrigerant | coolant inflow header tank 9 are temporarily assembled and connected so that the refrigerant | coolant inflow port 35 of these tubes 4A and the inflow port 10 of the refrigerant | coolant inflow header tank 9 may be connected.

  Similarly, these tubes 4A and the refrigerant outflow header tank 30 are temporarily assembled and connected so that the refrigerant outflow port 35 of these tubes 4A and the outflow port 28 of the refrigerant outflow header tank 9 communicate with each other.

  Next, since the tube 4A and the header tanks 9 and 30 in the temporarily assembled state are in an unstable form, there is a high possibility that the tube 4A will be deformed in the manufacturing process leading to deterioration of the heat exchange performance. . And, in order to make the heat exchanger core easy to handle and stable in the subsequent steps, the tubes 4A temporarily assembled with both the header tanks 9 and 30 have a holding member 24 that secures a predetermined interval between the tubes 4A, 26, and a process of assembling the heat exchanger core 20 that is held in a temporary stable form as a whole is performed (this is called a tube holding process).

  In this tube holding step, each of the tubes 4A is held at a predetermined interval, and the entire predetermined number of tubes temporarily assembled with the header tanks 9 and 30 are integrally held. The holding members 24 and 26 may be configured to hold the bent tube 4A at any part. In particular, the configuration in which the holding members 24 and 26 hold the tube 4A in the valley bottom portions 31 and 33 of the tube 4A formed in a mountain shape or a valley shape in the direction in which the refrigerant flows is on the surface of the tube 4A. It is desirable from the viewpoint of drainage of the generated condensed water.

  When all the tubes 4A supported at both ends by the header tanks 9 and 30 are held by the holding member, all the tubes 4A are simultaneously applied to the openings of the slits from the direction parallel to the main surface of the tubes 4A. Then, the holding member is pushed in so that all the tubes 4A are accommodated in the slits. When the holding member is pushed, the lateral movement of the tube 4A is restricted when the side surface connecting the upper and lower main surfaces reaches the deep part of the groove-shaped slit. In this state, the upper and lower main surfaces of the tube 4A are held by the inner upper and lower surfaces of the groove-shaped slit, so that the vertical movement of the tube 4A is restricted.

  Next, a step of placing the heat exchanger core 20 in a temporarily stable form in the furnace and brazing the whole in the furnace is performed (this is called a brazing process). In this step, the tube 4A and the refrigerant inflow header tank 9 are fixed, the tube 4A and the refrigerant outflow header tank 30 are fixed, and the tube 4A and the holding members 24 and 26 are fixed.

  The heat exchanger core 20 of this embodiment will be manufactured by performing the above tube bending process, header tank connection process, tube holding process, and brazing process.

  Furthermore, the manufacturing method of a heat exchanger is demonstrated. This manufacturing method is a method in which heat exchanger cores 21, 22, and 23 having the same configuration as the heat exchanger core 20 are arranged in the air flow direction to integrate these heat exchanger cores.

  First, all the tubes 4A of the heat exchanger core 21 that are not integrated by the holding member are simultaneously applied to the openings of the slits of the holding members 24 and 26 from a direction parallel to the main surface of the tube 4A. Then, the heat exchanger core 21 is pushed in so that all the tubes 4A are accommodated in the slits. Then, the heat exchanger core 20 and the heat exchanger core 21 held by the holding members 24 and 26 are integrated via the holding members 24 and 26 (assembly process of the heat exchanger cores 20 and 21). ).

  Next, similarly to the assembly process of the heat exchanger cores 20 and 21, the heat exchanger core 22 and the heat exchanger core 23 having the same configuration as the heat exchanger core 20 are integrated via the holding members 25 and 27. (Assembly process of heat exchanger cores 22 and 23).

  As shown in FIG. 7, the heat exchanger cores 20 and 21 and the heat exchanger cores 22 and 23, which are assembled integrally with each other, have the holding member 24 and the holding member 25 abutted or overlapped with each other. The joint portion is brazed, and the holding member 26 and the holding member 27 are abutted or overlapped, and the joint portion is fixed integrally by brazing, and the four-stage heat exchanger core is integrated. An exchanger will be manufactured. Brazing is a method in which the entire heat exchanger is placed in a furnace and brazed in the furnace.

  Thus, according to this embodiment, when the shape of the plurality of tubes 4A on both sides of the holding members 24, 25, 26, and 27 is formed in a mountain shape or a valley shape in the direction in which the refrigerant flows, It is possible to further promote the tendency of the adhered moisture to flow down through the holding members 24, 25, 26, 27 or the tube 4A.

  Moreover, when it is set as the structure which hold | maintains the valley bottom parts 31 and 33 of the tube 4A bent by the holding members 24 and 26 in the shape of a mountain or a valley, the tube 4A in which the water | moisture adhering to the surface of the tube 4A was inclined. , It flows toward the holding members 24 and 26 and then flows down along the holding members 24 and 26, so that drainage can be improved. In addition, since the trough bottom portion of the tube, which is likely to be stressed by thermal contraction and expansion, is supported by the holding members 24 and 26, the burden on the tube can be reduced.

  Further, when the tube 4A is formed in a flat shape, the flat tube 4A that is easy to bend is stably held, so that the shape of the heat exchanger is stabilized and the handleability is improved, and the flat tube Since water that tends to accumulate on the upper surface also easily flows, drainage can be improved.

  In addition, a step of continuously forming a plurality of tubes 4A through which the refrigerant flows into a desired mountain shape and a valley shape with respect to the refrigerant flow direction, and a predetermined number of tubes continuously formed in a mountain shape and a valley shape A predetermined number of tubes 4A and the refrigerant inflow header tank 9 are connected so that the inlet 10 of the refrigerant inflow header tank 9 of the 4A communicates, and the refrigerant outflow port 36 and the refrigerant outflow of the predetermined number of tubes 4A are connected. A step of connecting a predetermined number of tubes 4A and the refrigerant outflow header tank 30 so that the outflow port 28 of the header tank 30 communicates, and the holding members 24 and 26 hold the respective intervals of the tubes 4A temporarily as a whole. A step of forming the heat exchanger core 20 having a stable form, a step of placing the heat exchanger core 20 having the temporary stable form into a furnace and brazing the whole in the furnace, By carrying out the production method of Ranaru heat exchanger core, reduction and form of assembly steps of the heat exchanger core can be realized stably improve handleability good workability during manufacturing.

  Moreover, in the process of forming the heat exchanger core 20 in the temporary stable form, the holding members 24 and 26 hold the tubes 4A at the valley bottom portions 31 and 33 of the plurality of tubes 4A formed in a mountain shape and a valley shape. The strength of the heat exchanger can be improved by holding the bent portion of the tube 4A, which is a portion that is easily subjected to stress due to cold shrinkage and is also a portion that is easily deformed by an external force, by the holding member.

  Further, in the case where a plurality of heat exchanger cores manufactured by the above method are arranged, a method of integrating the arranged heat exchanger cores by joining holding members together, a heat exchanger By increasing or decreasing the number of cores, a heat exchanger suitable for the required heat exchange capability can be easily supplied.

  In addition, since the flat tube 4A is integrated by the holding member of the comb-shaped aluminum plate, the flat tube having an elongated cross-sectional shape can be reliably held in the direction of the minor axis of the cross section, which is easy to deform. It is possible to prevent the tube from being deformed.

  In addition, when the heat exchanger cores that are integrally held by the holding members are stacked in a plurality of stages, it is easy to heat by adopting a configuration in which the holding members that hold adjacent heat exchanger cores are connected and fixed. The exchanger can be assembled and workability can be improved.

  In addition, the group of tubes 4A constituting the heat exchanger core are integrally held by the holding member at two locations between the refrigerant inflow header tank 9 and the refrigerant outflow header tank 30. During the work, it is possible to reduce the damage to the thin tube 4A that is easily deformed.

(Third embodiment)
The third embodiment will be described below. FIG. 8 is a plan view showing the configuration of the heat exchanger of the present embodiment. The same components as those of the heat exchanger shown in FIG. 2 of the first embodiment are denoted by the same reference numerals. FIG. 9 is a schematic diagram in the AA cross section of FIG.

  As shown in FIG. 8, the heat exchanger core includes a plurality of flat tubes 4B arranged in the top and bottom (10 in this embodiment), a refrigerant inflow header tank 9A provided at both ends of these flat tubes 4B, and a refrigerant outflow. The header tank 14A and all of the plurality of flat tubes 4B are configured by a holding member 19A that holds the interval between the flat tubes 4B.

  As shown in FIG. 9, the holding member 19 </ b> A is configured to incline the longitudinal direction in the flat cross section of the flat tube 4 </ b> B with respect to the horizontal direction, that is, the air flow direction, and hold an interval between adjacent flat tubes 4 </ b> B. .

  The holding member 19A is an aluminum rectangular plate. A plurality of slits penetrating in the thickness direction are formed in the holding member 19A. Each slit is formed to extend slightly obliquely upward from one side in the longitudinal direction of the holding member 19A along the width direction of the holding member 19A. Each slit is formed without reaching from one side in the longitudinal direction to the other side, and is formed in a comb shape in which teeth extend obliquely. The holding member 19 </ b> A has a connecting portion extending in the vertical direction on the other side, and is formed in a shape having a plurality of comb teeth extending obliquely from the connecting portion to one side thereof. The connecting portion provides a continuous wall surface extending in the vertical direction.

  The inclination angle θ with respect to the horizontal direction of the flat tube 4B that is inclined and held by the holding member 19A is the result of the experiment described in the first embodiment and the inclination angle of the public road is within 6 °. It is desirable to set in the range of 0-6 °.

  As described above, according to the present embodiment, the longitudinal direction in the flat cross section of the flat tube 4B is inclined with respect to the horizontal direction, and the holding member 19A that holds the interval between the adjacent flat tubes 4B is provided. Since the flat tube 4B is stably held, the shape of the heat exchanger is stable and the handleability is improved, and the flow of the external fluid flowing outside the flat tube 4B is utilized to easily collect on the upper surface of the flat tube 4B. Water can be drained.

It is a schematic perspective view which shows the structure at the time of mounting the heat exchanger of 1st Embodiment of this invention in a refrigeration vehicle. It is a front view which shows the structure of the tube of the heat exchanger in 1st Embodiment. It is a graph which shows the experimental data which examined the drainage property of the heat exchanger regarding 1st Embodiment. It is a front view which shows the structure of the heat exchanger in 1st Embodiment. It is the conceptual diagram which showed typically the structure of the tube of the heat exchanger in 2nd Embodiment. It is a perspective view which shows the structure of the heat exchanger in 2nd Embodiment. It is a schematic diagram which shows the relationship between the tube and holding member of the heat exchanger in 2nd Embodiment. It is a top view which shows the structure of the heat exchanger in 3rd Embodiment. It is a schematic diagram in the AA cross section of FIG.

Explanation of symbols

4, 4A tube 4B flat tube
7, 7A Refrigerant inflow part 8, 8A Refrigerant outflow part 9, 9A Refrigerant inflow header tank 10 Inlet 14, 14A, 30 Refrigerant outflow header tank 19, 19A Holding member 20 Heat exchanger core 24, 25, 26, 27 Holding member 28 Outlet 31, 33 Valley bottom 35 Refrigerant inlet 36 Refrigerant outlet

Claims (8)

A refrigerant flows through the inside and a plurality of adjacent tubes (4, 4A);
A refrigerant inflow header tank (9, 9A) and a refrigerant outflow header tank (14, 30) respectively disposed in the refrigerant inflow portion (7) and the refrigerant outflow portion (8) of the tube (4, 4A). ,
With respect to the direction in which the refrigerant flows, one side of the plurality of tubes (4, 4A) is disposed at a position lower than the other side, and the one side and the other side of the plurality of tubes (4, 4A) A heat exchanger comprising a holding member (19) for holding a gap between the adjacent tubes (4, 4A) in between.   2. The shape of the plurality of tubes (4 </ b> A) on both sides of the holding member (24, 25, 26, 27) in the direction in which the refrigerant flows is formed in a mountain shape or a valley shape. The described heat exchanger.   The holding member (24, 25, 26, 27) holds the tube (4A) at a valley bottom (31, 33) of a predetermined number of tubes (4A) formed in a mountain shape and a valley shape. The heat exchanger according to claim 2.   The heat exchanger according to claim 1, 2 or 3, wherein the tube (4, 4A) has a flat shape. A refrigerant flows through the inside, and a plurality of adjacent flat tubes (4B);
A refrigerant inflow header tank (9A) and a refrigerant outflow header tank (14A) arranged in each of the refrigerant inflow portion (7A) and the refrigerant outflow portion (8A) of the flat tube (4B),
A heat characterized by comprising a holding member (19A) that inclines the longitudinal direction of the flat cross section of the flat tube (4B) with respect to the horizontal direction and holds the interval between the adjacent flat tubes (4B). Exchanger. A step of continuously forming a plurality of tubes (4A) for flowing the refrigerant therein in a desired mountain shape and valley shape with respect to the refrigerant flow direction;
The predetermined number of tubes so that the refrigerant inlet (35) of the predetermined number of tubes (4A) continuously formed in a mountain shape and a valley shape communicate with the inlet (10) of the refrigerant inflow header tank (9). (4A) and the refrigerant inflow header tank (9) are connected so that the refrigerant outlet (36) of the predetermined number of tubes (4A) and the outlet (28) of the refrigerant outflow header tank (30) communicate with each other. Connecting the predetermined number of tubes (4A) and the refrigerant outflow header tank (30);
Forming a heat exchanger core (20) having a temporary stable form as a whole by holding each interval of the tubes (4A) by holding members (24, 26);
Placing the heat exchanger core (20) in the temporary stable form into a furnace and brazing in the furnace as a whole;
The manufacturing method of the heat exchanger core characterized by comprising.   In the step of forming the heat exchanger core (20) in the temporary stable form, the holding members (24, 26) are formed in the valley bottoms (31, 31) of the predetermined number of tubes (4A) formed in the peaks and valleys. The method of manufacturing a heat exchanger core according to claim 6, wherein the tube (4A) is held in (33).   A plurality of heat exchanger cores manufactured by the method for manufacturing a heat exchanger core according to claim 6 or 7, wherein the arrayed heat exchanger cores are joined by joining the holding members. A method for producing a heat exchanger, characterized by integrating.

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