KR100664537B1 - Plate for laminate type secondary heat exchanger of car air conditioner - Google Patents

Abstract

The present invention relates to a laminated type 2 of an automotive air conditioner, in which a plurality of plates are stacked together with the plates of an evaporator and bonded together through a single brazing process, thereby forming a laminated second heat exchanger of an automobile air conditioner integrated in the evaporator on the side of the evaporator. It relates to a plate for a primary heat exchanger.

Secondary heat exchanger plate 600 according to the present invention is a thin plate consisting of a low pressure surface 610 and a high pressure surface 620, the low pressure tank portion 611 and the high pressure tank portion 621, respectively, in the upper and lower parts in the same pair Kinds are formed so as to be arranged side by side, and there between a low pressure passage 65 and a high pressure passage 62 which form the high pressure passage 62 which connect the tanks of the same type therebetween, and the low pressure tank portion. Between the and the beads, the equalization portion 616 which induces a low pressure refrigerant from the low pressure tank portion and distributes evenly to each of the low pressure flow paths 65 is formed, the plate of this structure is 2 In the secondary heat exchanger, the low pressure side passage and the high pressure side passage of the high pressure side respectively induce low pressure refrigerant and high pressure refrigerant to mutual heat exchange, and have good balance of low pressure refrigerant flow, thereby greatly improving the heat exchange performance of the secondary heat exchanger. Can be.

Air Conditioning, Evaporator, Secondary Heat Exchange, Auxiliary Heat Exchanger, Heat Exchanger Plate

Description

Plate for secondary heat exchanger of car air conditioner {PLATE FOR LAMINATE TYPE SECONDARY HEAT EXCHANGER OF CAR AIR CONDITIONER}             

1 is a configuration diagram of a cooling system of a general automotive air conditioner;

2 is a configuration diagram of a cooling system of a vehicle air conditioner equipped with a secondary heat exchanger;

3 is an exploded perspective view of an evaporator provided with a stacked secondary heat exchanger of an automobile air conditioner;

4 is a schematic perspective view of a stacked secondary heat exchanger of an automobile air conditioner;

FIG. 5 is a front view of a low pressure surface of a plate for a laminated secondary heat exchanger of an automobile air conditioner applied as the same;

6 is a front view of a high pressure side of a plate for a laminated secondary heat exchanger of an automobile air conditioner applied as the same;

7A and 7B are cross-sectional views taken along lines A-A and B-B of FIG. 6,

8 is a cross-sectional view taken along the line VII-VII of the refrigerant channel formed by the stacked secondary heat exchanger of the automobile air conditioner;

9 is a flow chart of the low pressure refrigerant flowing along the low pressure surface of the plate for the laminated secondary heat exchanger of the automotive air conditioner filed as the same,                 

10 is a front view of a low pressure surface of a plate for a laminated secondary heat exchanger of a vehicle air conditioner according to an embodiment of the present invention;

11 is a high-pressure front view of a plate for a laminated secondary heat exchanger of a vehicle air conditioner according to an embodiment of the present invention, and

12 is a flow chart of a low pressure refrigerant flowing along a low pressure surface of a plate for a laminated secondary heat exchanger of a vehicle air conditioner according to an embodiment of the present invention.

Explanation of symbols on the main parts of the drawings

3: expansion valve 4: evaporator

61: high pressure refrigerant inlet chamber 62: high pressure flow path

63: high pressure refrigerant discharge chamber 64: low pressure refrigerant inlet chamber

65 low pressure flow path 66 low pressure refrigerant discharge chamber

7: Inlet access block 8: Outlet access block

9: refrigerant conduit 600: plate

610: low pressure surface 611: low pressure tank

612: low pressure tank ball 613: bead

614: Euro blocking unit 616: Uniform distribution

620: high pressure side 621: high pressure tank

622 high pressure tank ball

The present invention heat-exchanges the high-temperature, high-pressure liquid refrigerant before being throttled in the cooling system of the automobile air conditioner and the low-temperature low-pressure gaseous refrigerant discharged from the evaporator to supercool the refrigerant before being throttled and to optimize the superheat degree of the refrigerant discharged from the evaporator. The present invention relates to a plate used in the manufacture of a secondary heat exchanger, which stabilizes the refrigerant flow in the evaporator and reduces the overheating area of the evaporator, thereby improving the cooling performance of the air conditioner.

As shown in FIG. 1, a cooling system of a vehicle air conditioner generally includes a compressor 1 for compressing and delivering a refrigerant, and a condenser for condensing a high pressure refrigerant that is sent out from the compressor 1 ( 2) a throttling mechanism 3 such as an expansion valve for throttling a refrigerant condensed and liquefied in the condenser 2, and a low-pressure liquid refrigerant throttled by the throttling mechanism 3 for automobiles. It consists of a vapor compression refrigeration cycle consisting of an evaporator (4) for cooling the air discharged into the room by the endothermic action of the latent heat of the refrigerant by evaporating heat exchanged with the air blown to the room side, the cooling of the automotive air conditioner On (on) of the switch (not shown) to cool the interior of the vehicle through the refrigerant circulation process as follows.

First, while the compressor 1 is driven by the power of the engine, the low-temperature, low-pressure gaseous refrigerant is sucked and compressed and sent to the condenser 2 in a gaseous state of high temperature and high pressure, and the condenser 2 exchanges the gaseous refrigerant with outside air. Condensed into high temperature and high pressure liquid and sent out. Subsequently, the liquid refrigerant sent out from the condenser 2 is rapidly expanded by the throttling action of the throttling mechanism 3 and is sent to the evaporator 4 in a low temperature and low pressure wet state, and the evaporator 4 blows the refrigerant into a blower ( Heat exchange with the air blowing into the vehicle interior. Accordingly, the refrigerant is evaporated in the evaporator and discharged in a gas state of low temperature and low pressure, and is again sucked into the compressor 1 to recycle the refrigeration cycle as described above. In the above refrigerant circulation process, the cooling of the vehicle interior is cooled by the latent heat of evaporation of the liquid refrigerant circulating in the evaporator 4 while the air blown by the blower (not shown) passes through the evaporator 4 as described above. It is made by discharging the inside of the car in a cold state.

The cooling efficiency of the air conditioner that cools through the refrigeration cycle as described above is determined by various factors, among which the subcooling of the high-pressure refrigerant immediately before being throttled by the throttling mechanism 3 such as an expansion valve. The degree of superheat of the low pressure refrigerant discharged from the evaporator and the fluidity of the refrigerant, the pressure drop in the evaporator 4, the superheated region of the evaporator 4 (partial region of the refrigerant outlet side of the evaporator), and the volumetric efficiency of the compressor 1 are determined. This has a significant effect on the cooling efficiency of the air conditioner.

For example, if the subcooling of the refrigerant before the condensation increases, the specific volume of the refrigerant is reduced to stabilize the refrigerant flow, and the refrigerant pressure drop in the evaporator 4 is reduced, thereby increasing the cooling efficiency of the air conditioner and increasing the cooling efficiency of the compressor 1. Power consumption is reduced. On the other hand, if the superheat of the low-pressure refrigerant discharged from the evaporator 4 is not properly maintained, the superheated region of the evaporator 4 having a relatively high temperature at which the refrigerant is completely vaporized to prevent the compressor from entering the liquid refrigerant. Since this has to be enlarged, the cooling performance of the air conditioner is reduced. Therefore, automotive air conditioners generally increase the cooling performance before the overcooling of the refrigerant before being condensed and the superheat of the refrigerant discharged from the evaporator 4 is maintained.

Accordingly, in recent years, the air conditioner of a vehicle includes a high temperature and high pressure liquid refrigerant flowing into the throttling mechanism 3 and a low temperature low pressure gas phase refrigerant discharged from the evaporator 4 as shown in FIG. A secondary heat exchanger (6) capable of supercooling the high-temperature, high-pressure liquid refrigerant before throttling and optimizing the superheat degree of the low-pressure refrigerant discharged from the evaporator (4) is used.

In the cooling cycle of the automotive air conditioner, the secondary heat exchanger exchanges heat between the high temperature high pressure gaseous refrigerant before being throttled and the low temperature low pressure gaseous refrigerant evaporated in the evaporator 4 to supercool the refrigerant flowing into the evaporator and vaporize it in the evaporator. The superheat degree of the gaseous refrigerant discharged can be optimized. As a result, the amount of refrigerant pressure drop in the evaporator is reduced due to the decrease in the specific volume of the refrigerant flowing into the evaporator 4 so that the refrigerant flow in the evaporator is stabilized and the refrigerant is previously set in the evaporator to completely vaporize the refrigerant to prevent the liquid refrigerant from entering the compressor. The cooling temperature of the air conditioner can be greatly increased by allowing the refrigerant overheating zone, which reduces the cooling performance due to the relatively high temperature, to be drawn out of the discharge side of the evaporator. As a result, the compressor 1, the condenser 2 and the evaporator 4 can be made more efficient, contributing to the higher efficiency and smaller size of the air conditioner.

However, in spite of the advantages as described above, secondary heat exchangers of conventional automobile air conditioners such as secondary heat exchangers of Japanese Patent Application Laid-Open No. 6-185831 or secondary heat exchangers of Japanese Patent Application Laid-open No. Hei 6-185831, etc. Due to the large number of components and the complicated structure thereof, the manufacturing cost is high, and the refrigerant pipes are complicatedly intertwined, so that many connection parts are used to reduce the fluidity of the refrigerant. Therefore, there is a limit in improving the cooling performance of the air conditioner. In addition, many connections have various problems, such as the airtightness and durability of the refrigerant is weak, and the volume is too large to counteract the miniaturization of the cooling system.

In order to solve the problems of the conventional secondary heat exchangers as described above, the present inventors have laminated the evaporator plates together with the bonding of the evaporator plates through one brazing process, as shown in FIGS. 3 and 4. Composed of a laminated structure of a plurality of thin plate-like plate to be bonded at the same time, it is possible to assemble simultaneously with the evaporator (4), easy to assemble, simple structure and fewer connections to the refrigerant piping, excellent airtightness and durability of the refrigerant, small volume The laminated secondary heat exchanger 6 of the automobile air conditioner, which can contribute to the miniaturization of the air conditioner, has been developed and filed as the same as the present application.

The laminated secondary heat exchanger plate 600 of the automobile air conditioner used for assembling the secondary heat exchanger is vertically symmetrical having the low pressure side 610 of FIG. 5 and the high pressure side 620 of FIG. As a thin plate of a thermally conductive material having a structure, as can be seen from FIGS. 5, 6, 7A, and 7B, the upper and lower portions are respectively settled at the low pressure surface 610 and the low pressure tank hole 612 in the middle. The drilled low pressure tank 611 and the high pressure tank 621, which is settled down at the high pressure surface 620 and the high pressure tank hole 622 is drilled in the middle, are formed in pairs, and the upper and lower tank parts 611 and 621 ( A plurality of vertical beads 613 protruding from the low pressure surface 610 are formed side by side between the 611, 621. In the center thereof, the low pressure refrigerant flow path blocking part 614 protruding to the low pressure surface 610 and the high pressure refrigerant flow path blocking part 624 protruding to the high pressure surface 620 are respectively located on the upper and lower low pressure tank parts 611 and 611. And the high-pressure tank portions 621 and 621 are formed in the transverse direction so as to be offset, and the mixing portion 601 is formed above and below the blocking portions 614, 624, the molding of beads. In addition, a plurality of flow rate distribution beads 615 and 625 are formed on the region between the tank portions 611, 621 and the beads 613, and on the mixing portion 601. 620, each protruded.

The secondary secondary heat exchanger plate of the vehicle air conditioner of such a structure is laminated on the low pressure side 610 and the high pressure side 620 and up and down at the same time on one side of the evaporator plate laminated structure constituting the evaporator and then bonded to each other, As shown in FIG. 4, a stacked secondary heat exchanger 6 is formed, and the upper portion of the secondary heat exchanger has a low pressure tank 611 on each plate 600 as shown in FIGS. 3 and 4. Low-pressure refrigerant discharge chamber 66 and high-pressure refrigerant discharge chamber (63) formed by the side and the high-pressure tank unit 621, respectively, are formed side by side, corresponding to the lower pressure tank of the lower side of each plate 600 ( 611 and the low pressure refrigerant inlet chamber 64 and the high pressure refrigerant inlet chamber 61 formed by the high pressure tank portions 621 are formed in pairs, and the same type of tank portions 61, 63, 64 (up and down) 66 is a bead protruding to the low pressure surface (see 613 in Fig. 5) Through the low pressure side 610 and a high pressure side (620) the low-pressure passage (numeral 65 in Fig. 5) and the high-pressure flow path (reference numeral 62 in FIG. 6) to form respectively are connected to each other. In addition, the low pressure refrigerant inlet chamber 64 and the high pressure refrigerant inlet chamber 61, as shown in FIG. 3, the discharge side tank part 42 of the evaporator 4 and the discharge passage 20 of the condenser (not shown). Are connected to each other, and the low pressure refrigerant discharge chamber 66 and the high pressure refrigerant discharge chamber 63 in the upper portion of the throttle hole 30 of the throttling mechanism 3 in which the flow paths 81 and 31 and the expansion valves directed to the compressor are respectively built. Is connected to. A refrigerant conduit 9 is connected to the throttling hole 30, and the refrigerant conduit 9 passes through the high-pressure refrigerant inlet chamber 61 again and is inserted into the evaporator inlet side tank part 41. 40).

According to such a configuration, the stacked secondary heat exchanger, as can be seen in Figure 3, the high pressure refrigerant discharged from the condenser (not shown) and the low pressure refrigerant discharged from the evaporator (4) and the high pressure refrigerant inlet chamber 61 and Into the low pressure refrigerant inlet chamber (64) through the high pressure flow passage (see numeral 62 of Figs. 6 and 8) and the low pressure flow passage (see numeral 65 of Figs. 5 and 8) alternately with each plate 600 interposed therebetween. Next, the high pressure refrigerant and the low pressure refrigerant flow through the high pressure refrigerant discharge chamber 63 and the low pressure refrigerant discharge chamber 66 through the throttle mechanism 3 and the compressor (not shown), respectively. Heat exchange with each other while flowing along (65).

On the other hand, in the multilayer secondary heat exchanger of the automobile air conditioner which heat-exchanges the high pressure refrigerant and the low pressure refrigerant as described above, the heat exchange performance is dependent on the flow equalization of the refrigerant flowing along the low pressure side and the high pressure side of each plate. Bar flow of the high pressure refrigerant of the high pressure side 620 is a high pressure liquid refrigerant, so that it is uniformly distributed throughout the high pressure side 620 has little effect on the heat exchange performance, but the low pressure side ( Since the low pressure refrigerant flow of 610 is a low pressure refrigerant itself and is a flow of refrigerant mixed with gaseous phase and liquid phase, the flow uniformity of the entire low pressure surface 610 is greatly changed depending on various factors. It has a dominant influence on the heat exchange performance of the heat exchanger.

However, the plate for the secondary secondary heat exchanger of the air conditioner of the same application described above, as shown in Figure 5, the low pressure refrigerant inlet chamber (symbol 64 of FIG. 4) and the low pressure refrigerant for introducing and discharging the low pressure refrigerant up and down as shown in FIG. Although the low pressure tanks 611 and 611 on the upper and lower sides of the low pressure surface forming the discharge chambers (reference numeral 66 in FIG. 4) are biased to one side of the plate 600, the low pressure passages 65 are the upper and lower low pressure tank portions 611. As shown in FIG. 9, each of the inlets of substantially the same height formed by the tips of the same size beads 613 formed between the upper and lower sides, the low pressure of the low pressure close to the low pressure tank side of the high pressure refrigerant flow Since the flow uniformity flows to the flow paths 65 very poorly against the low pressure refrigerant, it is a factor that greatly reduces the heat exchange performance of the stacked secondary heat exchanger.

The present invention is to equalize the low pressure refrigerant flow having a dominant influence on the heat exchange performance of the secondary heat exchanger in order to solve the problem of the secondary heat exchanger according to the plate for the laminated secondary heat exchanger of the vehicle air conditioner as described above It is very good to provide a laminated secondary heat exchanger plate of a vehicle air conditioner that can greatly improve the heat exchange performance of the secondary heat exchanger.

Secondary thermal bridge ventilation plate of the air conditioner according to the present invention devised for the purpose as described above, consisting of a low pressure surface and a high pressure surface, a plurality of the low pressure surface and the high pressure surface alternately stacked at the same time up and down A vertically symmetrical thin plate bonded to each other to form a laminated secondary heat exchanger of an automobile air conditioner, the lower pressure tank part having a lower pressure surface in the upper and lower portions thereof, and the lower pressure tank hole drilled in the middle and the high pressure tank in the middle thereof. The high-pressure tank unit is formed to be paired with the same type to be arranged side by side to form a low-pressure refrigerant inlet chamber and a low-pressure refrigerant discharge chamber to be isolated up and down, and to form a high-pressure refrigerant inlet chamber and a high-pressure refrigerant discharge chamber to be isolated up and down, and Between the upper and lower tank portions, a plurality of vertical beads protruding from the low pressure surface side by side And a low pressure flow path is formed between the beads on the low pressure surface to connect the low pressure refrigerant inlet chamber and the low pressure refrigerant discharge chamber, and at the high pressure surface, the beads form a high pressure flow path and the high pressure refrigerant inlet chamber. In the laminated secondary heat exchanger plate of the vehicle air conditioner connecting the high-pressure refrigerant discharge chamber,

Between the low pressure tank portion and the beads, the equalization portion for inducing low pressure refrigerant from the low pressure tank portion forming the low pressure refrigerant inlet chamber and evenly distributed to each of the low pressure flow paths is formed. It is done.

According to a preferred feature of the laminated secondary heat exchanger plate of the vehicle air conditioner according to the present invention, the equalization portion is formed by excluding a portion of each tip of the low pressure tank side of the beads.

In addition, it is preferable that the top and bottom widths of the bactericidal portion are greatest in the width direction center of the plate and gradually decrease toward both sides thereof.

In addition, in the longitudinal center of the plate, the low pressure refrigerant flow path blocking portion protruding to the low pressure surface and the high pressure refrigerant flow path blocking portion protruding to the high pressure surface, respectively, on the same horizontal line, the upper and lower low pressure tank portions and the upper and lower high pressure tank portions, respectively. It is preferable that the mixing part is formed to be disposed to be offset from the upper part of the blocking part, and the mixing part which excludes molding of the bead is formed above and below the blocking parts.

The laminated secondary heat exchanger plates of the vehicle air conditioner according to the present invention having the above configuration are laminated together with the evaporator plates and then bonded together with the evaporator plates through a single brazing process to be integrated with the evaporator. A laminated secondary heat exchanger of the conditioner is achieved. That is, the high pressure tank part and the low pressure tank part formed by pairing up and down the laminated and joined plates form a high pressure refrigerant inlet chamber and a low pressure refrigerant inlet chamber, and are connected through the high pressure flow path and the low pressure flow path of each plate. The low pressure refrigerant inlet chamber and the high pressure refrigerant inlet chamber are formed, the high pressure refrigerant discharged from the condenser and the low pressure refrigerant discharged from the evaporator are respectively introduced into the high pressure refrigerant inlet chamber and the low pressure refrigerant inlet chamber, and alternately arranged with each plate therebetween. The high pressure refrigerant and the low pressure refrigerant flow through the high pressure refrigerant discharge chamber and the low pressure refrigerant discharge chamber through the high pressure flow passage and the low pressure refrigerant discharge chamber, respectively, to the throttling mechanism and the compressor, thereby mutually exchanging the high pressure refrigerant and the low pressure refrigerant.

As described above, the laminated secondary heat exchanger having a laminated structure of plates for the secondary secondary heat exchanger of the automobile air conditioner according to the present invention is assembled at the same time as the evaporator and integrated at one side of the evaporator, so that the assembly process is very simple, and the configuration and refrigerant piping are short. Due to its mildness and low number of connections, it is very excellent in terms of manufacturing cost, airtightness and durability, and its small volume can greatly contribute to the miniaturization of the cooling system. In addition, the low pressure refrigerant flow uniformity of the low pressure side which flows into the low pressure refrigerant inlet chamber and flows along the low pressure passages of the low pressure side of each plate is distributed evenly to each low pressure passage by the above-mentioned equalizing unit, which has a dominant influence on the heat exchange performance. Since the heat exchange performance is very good, the heat exchange performance is also very high.

Hereinafter, with reference to the accompanying drawings, the structural features and the effects of the laminated secondary heat exchanger plate of the vehicle air conditioner according to the present invention through a preferred embodiment of the present invention in more detail.

Laminated secondary heat exchanger made of a laminated structure of the plate for the secondary secondary heat exchanger of the vehicle air conditioner according to an embodiment of the present invention, as shown in Figure 3 attached to the side of the evaporator (4) evaporator (4) It is integrated in the high pressure refrigerant inlet chamber (61) and the low pressure refrigerant inlet chamber (64) in the lower portion, and the high pressure refrigerant discharge chamber (63) and low pressure in communication with the two inlet chambers (61, 64), respectively The refrigerant discharge chambers 66 are held in pairs.

The laminated secondary heat exchanger plate of the vehicle air conditioner according to the present invention used for assembling the laminated secondary heat exchanger having such a configuration is a thin plate having a size substantially the same as that of the evaporator plate, as shown in FIGS. 3 and 4. Likewise, they are stacked together with the evaporator plates 400 such that the evaporator plates 400 are joined together to form the evaporator 4 through a single brazing process, and at the same time, they are joined together to form the secondary heat exchanger 6. As described above, the multilayered secondary heat exchanger 6 having the laminated structure of the laminated secondary heat exchanger plates of the vehicle air conditioner according to the embodiment of the present invention is assembled together with the evaporator 4 through a single brazing process. The process is simpler.

10 and 11 are front and rear views showing the front (low pressure side) and the rear side (high pressure side) of the laminated secondary heat exchanger plate 600 of the vehicle air conditioner according to an embodiment of the present invention.

As shown, the plate 600 for the laminated secondary heat exchanger of the vehicle air conditioner according to an embodiment of the present invention, the front and rear symmetrical structure in which the front and rear surfaces of the low pressure surface 610 and the high pressure surface 620 A high-pressure surface 620, which is a thin plate of a thermally conductive material such as aluminum, for example, and is opposed to two tank portions 611, 621, 611, 621, ie, the low pressure tank portion 611 that is settled on the low pressure surface 610. High pressure tank portion 621 settled in the) is formed in pairs up and down, respectively, so that the same type of tank portion (611,611) (621, 621) are juxtaposed up and down, respectively. Between the upper and lower tank portions 611, 621, 611, 621, a plurality of vertical beads 613 protruding from the low pressure surface 610 are formed side by side, which are shown in FIG. 10. On the low pressure surface 610, a low pressure passage 65 is formed between the upper and lower low pressure tanks 612 and 612 between them, and on the high pressure surface 620, as shown in FIG. 613 is a recessed flow path to become a high pressure flow path 62 connecting the upper and lower high pressure tank portions 621 and 621 therebetween. The low pressure tank hole 612 and the high pressure tank hole 622 are drilled through the tank parts, that is, the low pressure tank part 611 and the high pressure tank part 621, respectively. In addition, as a preferred configuration, as shown in FIGS. 10 and 11, respectively, the low pressure refrigerant flow path blocking portion 614 and the high pressure surface 620 protruding toward the low pressure surface 610 at the center of the plate 600. The high pressure refrigerant flow path blocking part 624 of the plate 600 is disposed so as to be displaced with respect to the upper and lower low pressure tank parts 611 and 611 and the upper and lower high pressure tank parts 621 and 621 which are juxtaposed on the upper and lower sides, respectively. The mixing portions 601 are formed in the center in the transverse direction, respectively, and the blocking portions 614 and 624 are formed above and below the bead 613. In addition, a plurality of flow rate distribution beads 615 and 625 are formed on the region between the tank portions 611 and 621 and the beads 613 and on the mixing portion 601. Each is protruded to 620.

In particular, as shown in FIG. 10, the laminated secondary heat exchanger plate of the automotive air conditioner according to an embodiment of the present invention has a coolant flow between the low pressure tank 611 and the low pressure flow paths 65. A flow path 616 is further provided so that a portion of each tip of the beads 613 forming the low pressure passage 65 is removed as a space.

The bactericidal portion 616 is a low pressure and is installed to solve the problem of the homogenization of the low-pressure refrigerant flow in which the flow pattern changes frequently due to the mixture of the gaseous phase and the liquid phase, the low pressure refrigerant inlet chamber ubiquitous to one side of the plate 600 (Fig. 3). The low pressure refrigerant is evenly distributed along each low pressure passage 65 in the low pressure surface 610 by inducing low pressure refrigerant from the low pressure tank 611 and distributing it evenly to each low pressure passage 65. Allow it to flow in proportions. The shape of the equalizing portion 616 is a shape in which the vertical width H is the largest in the center and gradually decreases toward the both sides so that the refrigerant pressure is equally applied to each inlet of the low pressure flow paths 65, for example, as shown in FIG. 10. Likewise, the convex shape in the flow direction of the low pressure refrigerant is preferable.

Plate 600 according to the present invention of the above structure is the low pressure surface 610 and the high pressure surface 620 and the upper and lower at the same time so as to be opposed to each other in the structure between each other between the outermost end plate (not shown) After being alternately stacked, they are joined together to form a stacked secondary heat exchanger having the following configurations.

That is, as shown in Figures 3 and 4, the stack type secondary heat exchanger 6 is formed by stacking a plurality of plates 600 according to the present invention, the upper, lower low pressure tank of each of the plates 600 ( 611 and 621 communicate with each other through the tank holes 612 to form a closed space between the plates 600 facing the low pressure surface 610 to form a low pressure refrigerant discharge chamber 66 and a low pressure refrigerant inlet chamber. And each of the upper and lower high pressure tanks 621 of the plates 600 communicate with each other through the respective tank holes 622 and face the plate 600 facing the high pressure surface 620. By forming a sealed space to form a high pressure refrigerant discharge chamber (63) and a high pressure refrigerant inlet chamber (61), respectively, as shown in Figure 3, the low pressure refrigerant discharge chamber (66) and the high pressure refrigerant discharge chamber (63) at the top In the lower part, the low pressure refrigerant inlet chamber 64 and the high pressure refrigerant are arranged side by side with respect to the two discharge chambers 66, 63. It would control entrance (61).

The low pressure refrigerant discharge chamber 66 and the low pressure refrigerant inlet chamber 64 protrude from the low pressure surface 610 of each plate, as shown in FIG. 10, between the plates 600 joined to the low pressure surface 610. The high pressure refrigerant discharge chamber 63 and the high pressure refrigerant inlet chamber 61 are connected to the high pressure surface 620 through the low pressure passages 65 of each plate low pressure surface 610 formed between the bead 613. 11 are connected to each other through high pressure flow paths 62 formed by beads 613 recessed in the high pressure surface 620 of each plate, as shown in FIG. References 62 and 65).

In the structure of the stacked secondary heat exchanger, as shown in FIG. 3, the low pressure refrigerant inlet chamber 64 disposed below is directly connected to the discharge side tank part 42 of the evaporator 4, and the high pressure refrigerant The inlet chamber 61 is connected to the outlet passage 20 of the condenser through an inlet connecting block 7 attached to the opposite side of the evaporator. In addition, the high pressure refrigerant inlet chamber 61 has a flow rate distribution pipe 40 inserted through the high pressure refrigerant inlet chamber 61 on the opposite side of the evaporator 4 and inserted into the inlet tank part 41 of the evaporator 4. Is inserted. In addition, the low pressure passage (see reference numeral 62 of FIGS. 8 and 10) and the high pressure of the low pressure side 610 and the high pressure side 620 of each plate with respect to the low pressure refrigerant inlet chamber 64 and the high pressure refrigerant inlet chamber 61. The upper high pressure refrigerant discharge chamber 63 and the low pressure refrigerant discharge chamber 66 connected through the flow path (see reference numeral 65 in FIGS. 8 and 11), respectively, in the opposite directions to the evaporator 4, respectively, in the discharge ports 63a and 66a. A discharge connection block 8 and a throttling mechanism 3 are sequentially attached to the discharge ports 63a and 66a, and the high pressure refrigerant discharge chamber 63 is formed in the first of the discharge connection block 8. The evaporator inlet side tank part 41 penetrates through the high-pressure refrigerant inlet chamber 61 in the order of the through-hole 80, the throttling hole 30 of the throttling mechanism 3 having the expansion valve, and the refrigerant conduit 9 therein. It is connected to the flow distribution pipe 40 inserted in the, the low pressure refrigerant discharge chamber 66 is connected to the inlet side of the compressor (see 1 in Fig. 2) through the through hole 31 formed in the throttling mechanism (3) Is determined.

According to the refrigerant passage as described above, the high pressure refrigerant discharged from the condenser (see 2 in FIG. 2) is transferred to the stacked secondary heat exchanger 6 through the lower high pressure refrigerant inlet chamber 61 as shown in FIG. 3. Inflow and ascending along the high pressure flow paths (symbol 65 of FIGS. 8 and 11) on the high pressure side of each plate are discharged from the secondary heat exchanger through the high pressure refrigerant discharge chamber 63. Subsequently, the discharged high-pressure refrigerant is expanded while passing through the expansion valve of the throttle mechanism (3) and flows into the evaporator (4) through the flow distribution pipe (40) in a low pressure state, and then the refrigerant flow path formed by the evaporator (4). The heat is evaporated by heat exchange with the air blown into the evaporator 4 while being distributed and flowed. The vaporized refrigerant flows into the low pressure refrigerant inlet chamber 64 of the lower side of the secondary heat exchanger 6 from the discharge side tank 42 of the evaporator 4 and flows into the secondary heat exchanger 6 again. Next, the plates are raised along the low pressure flow paths (reference numeral 65 in FIG. 5) formed on the low pressure surfaces 610 of the plates, and are sent to the compressor via the low pressure refrigerant discharge chamber 66.

In the refrigerant flow process, the low pressure refrigerant inlet chamber 64 and the high pressure refrigerant inlet chamber 61 of the lower side of the secondary heat exchanger are introduced into the low pressure passages 65 and the high pressure passages 62 of each plate. The low pressure refrigerant and the high pressure refrigerant which are discharged through the upper low pressure refrigerant discharge chamber 66 and the high pressure refrigerant discharge chamber 63 after rising, respectively, rise along the low pressure passages 65 and the high pressure passages 62 of each plate. Each side, that is, the low pressure surface 610, by the flow path blocking portions 624 and 614 which are mixed with each other in the mixing portions 630 above and below the flow path blocking portions 624 and 614 and flowed and redistributed. On the high pressure surface 620 and flows in a direction crossing with each other. In the process, the equalization portion 616 between the low pressure tank 611 and the low pressure flow path 65 is ubiquitous on one side of each plate-forming a low pressure refrigerant inlet chamber 64, as shown in FIG. The low pressure refrigerant flows from the low pressure tank 611 into the respective low pressure flow paths 65 to distribute the low pressure refrigerant evenly from the low pressure tank part 611 to each of the low pressure flow paths 65.

On the other hand, the flow distribution pipe 40 for introducing the throttling refrigerant into the evaporator (4), through the high pressure refrigerant inlet chamber 61 as shown in Figure 3 to the inlet side tank portion 41 of the evaporator (4) It has a plurality of distribution holes (40a) is inserted into, and arranged in the longitudinal direction in the longitudinal direction and increasing toward the tip side where the refrigerant pressure is lowered, the refrigerant throttled in the throttling mechanism (3) through each of the distribution holes (40a) evaporator It serves to distribute evenly to each cooling tube (refer 400 of FIG. 8) of (4). In this way, the refrigerant flow path of the evaporator 4 can be simplified by the use of the flow rate distribution pipe 40 which allows the refrigerant to be distributed evenly in each refrigerant tube of the evaporator 4. In the case where the laminated secondary heat exchanger 6 according to the present invention is applied to a cooling system, an evaporator 4 having a simple U-shaped simple refrigerant passage is usually employed.

In the refrigerant flow of the evaporator 4, if the flow distribution of the refrigerant is inappropriate, there is a temperature deviation inside the evaporator core formed by each cooling tube of the evaporator, and when the pressure drop is large, two-phase flow (gas refrigerant and liquid refrigerant Temperature difference corresponding to the pressure difference of co-existing flow), for example, HFC134a refrigerant, a temperature difference of about 5 ° C. occurs when the pressure drop in the core is 0.5 kgf / cm ² . When the stacked secondary heat exchanger 6 according to the present invention is applied to an air conditioner, the evaporator 4 having a simple flow path as a flow distribution pipe 40 for evenly distributing the refrigerant flow rate to each evaporator tube as described above. ), The temperature deviation between the evaporator tubes and the pressure drop in the evaporator tube are greatly reduced, thereby improving the cooling performance of the air conditioner.

Secondary heat exchanger made of a laminated structure of a plate for the secondary type heat exchanger of the vehicle air conditioner according to an embodiment of the present invention having the configuration as described above is attached to the cooling system to the cooling cycle as shown in FIG. Configure. Thus, as shown in Figure 3, the medium-temperature high-pressure liquid refrigerant from the condenser flows into the high-pressure refrigerant inlet chamber 61 and the high-pressure flow paths 62 formed between the plates facing the high-pressure surface 620 The diesel fuel is discharged to the throttling mechanism 3 through the high pressure refrigerant discharge chamber 63, and at the same time, the low-temperature low-pressure liquid refrigerant discharged from the evaporator 4 flows into the low pressure refrigerant inlet chamber 64 to the high pressure flow path 62. By discharging the low pressure flow paths 65 isolated with each plate 600 therebetween through the diesel low pressure refrigerant discharge chamber 66, the high temperature high pressure refrigerant immediately before being throttled and the low temperature low pressure refrigerant vaporized in the evaporator 4. Heat exchange each plate 600 with a heat transfer medium. In this process, as shown in FIG. 12, the low pressure refrigerant of the low pressure tank 611 ubiquitous on one side of each plate is equally distributed between the low pressure tank 611 and the low pressure flow path 65. By uniformly flowing in the flow path (65), the low pressure refrigerant flow uniformity of the low pressure surface (610) having a dominant influence on the heat exchange performance is improved, thereby greatly improving the heat exchange performance of the stacked secondary heat exchanger.

 As described above, the stacked secondary heat exchanger heat-exchanges the high-temperature high-pressure refrigerant just before being throttled and the low-temperature low-pressure refrigerant vaporized in the evaporator with the heat transfer medium to supercool the liquid refrigerant in the high-temperature and high-pressure state and discharge it from the evaporator. Therefore, it is possible to optimize the superheat degree of the gas phase refrigerant flowing into the compressor. As a result, it is possible to stabilize the flow by reducing the specific volume of the high-temperature and high-pressure gaseous refrigerant before it is throttled, and to reduce the evaporator superheating zone set to completely vaporize the refrigerant to prevent the compressor from entering the liquid refrigerant.

Therefore, the laminated secondary heat exchanger reduces the amount of refrigerant pressure drop in the evaporator in the refrigerant flow from the evaporator to the compressor and allows the air to be reduced by reducing the superheated region of the evaporator, which has a relatively high temperature and lowers the cooling performance of the air conditioner. The cooling performance of the conditioner can be greatly increased. Accordingly, the compressor, the condenser and the evaporator can be made efficient, contributing to the high efficiency and miniaturization of the air conditioner.

Particularly, in the case of the laminated secondary heat exchanger assembled by the laminated secondary heat exchanger plate of the automobile air conditioner according to the present invention, the low pressure tank in which the semicircular equalization between the low pressure tank portion and the low pressure flow path is localized on one side of each plate The low pressure refrigerant flows from the low pressure tank part evenly along each low pressure flow path as the low pressure refrigerant flows from the portion to the low pressure flow paths, and thus the heat exchange efficiency between the low pressure refrigerant and the high pressure refrigerant is very high. That is, the plate for the secondary secondary heat exchanger of the automobile air conditioner according to the present invention is a low pressure, and the gas and liquid phases are mixed so that the pressure change is severe, so that the flow is poor, even the low pressure side low pressure refrigerant flow that caused the heat exchange performance deterioration Since the problem can be solved, it can greatly contribute to improving the heat exchange performance of the secondary heat exchanger.

The laminated secondary heat exchanger plate of the automotive air conditioner according to the present invention as described in detail above consists of a low pressure side and a high pressure side, and a plurality of low pressure side and the high pressure side are alternately stacked together with the evaporator plates, and then a single brazing process. The evaporator plates form an evaporator and at the same time form a stacked secondary heat exchanger integrated with the evaporator. The laminated secondary heat exchanger can be assembled at the same time as the evaporator, so that the assembly process is simple, the configuration and the refrigerant piping are simple, and there are few connections. Not only is it low in manufacturing cost, it is also very good in terms of airtightness and durability, and can be integrated in one side of the evaporator to contribute greatly to the miniaturization of the air conditioner.

In the laminated secondary heat exchanger of the automobile air conditioner as described above, the plate for the laminated secondary heat exchanger of the automobile air conditioner according to the present invention induces a low pressure refrigerant and a high pressure refrigerant to the low pressure side and the high pressure side, respectively, to mutually heat exchange them. It is a low pressure, mixed with gaseous phase and liquid refrigerant, so that the flow multiplication is very poor. The equalization portion between the distribution of the low-pressure refrigerant in the low-pressure tank unit evenly distributed to each low-pressure flow path to solve the heat exchange performance of the secondary heat exchanger can be significantly improved.

On the other hand, while the above has been shown and described with respect to preferred embodiments of the present invention, the present invention is not limited to the above-described embodiment, the field to which the invention belongs without departing from the spirit of the invention claimed in the claims below. Of course, anyone skilled in the art can make various modifications, as well as such modifications are within the scope of the claims.

Claims (4)

It is composed of a low pressure side and a high pressure side, the plurality of low pressure side and the high pressure side is alternately stacked at the same time, the upper and lower sides are alternately stacked up and down symmetrical thin plate to form a laminated secondary heat exchanger of the automotive air conditioner, respectively The low pressure tank section with the low pressure tank hole settled in the plane and the low pressure tank hole in the middle and the high pressure tank part settled at the high pressure surface with the high pressure tank hole in the center formed in pairs to be arranged side by side to form the low pressure refrigerant inlet chamber and the low pressure refrigerant discharge chamber. And the high pressure refrigerant inlet chamber and the high pressure refrigerant discharge chamber are formed to be separated up and down, and a plurality of vertical beads protruding from the low pressure surface are formed side by side between the upper and lower tank portions to form the low pressure surface. A low pressure flow path is formed between the beads in And the low-pressure connecting the refrigerant discharge chamber, as well as in the laminate type secondary heat exchanger plates in the high-pressure side automotive air conditioning system in which the beads are connected to the high-pressure refrigerant inlet chamber and the high-pressure refrigerant discharge chamber to form a high-pressure flow path, Between the low pressure tank portion and the beads, the equalization portion for inducing low pressure refrigerant from the low pressure tank portion forming the low pressure refrigerant inlet chamber and evenly distributed to each of the low pressure flow paths is formed. Plate for secondary type heat exchanger of automobile air conditioner. The method of claim 1 The spreading part is a plate for the secondary heat exchanger of the vehicle air conditioner, characterized in that the low pressure tank side of the bead portion of each of the front end portion is formed is excluded. The method according to claim 1 or 2 The upper and lower widths of the spreading portion is the maximum in the center of the width direction of the plate and the secondary secondary heat exchanger plate of the vehicle air conditioner, characterized in that it is gradually reduced. The method of claim 1, The low pressure refrigerant flow path blocking portion projecting to the low pressure surface and the high pressure refrigerant flow path blocking portion projecting to the high pressure surface are shifted from the upper and lower portions of the low pressure tank portion and the high pressure tank portions of the upper and lower portions on the same horizontal line. Laminated secondary heat exchanger of the vehicle air conditioner, which is formed to be arranged, and the upper and lower parts of the blocking portion is further formed with a mixed portion in which the molding of the beads is excluded.

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