CN206638065U - Double-dryness split-flow heat-exchanging evaporator - Google Patents

Abstract

The utility model relates to a double dryness shunt heat exchange evaporator, comprising a first header connected with an inlet pipe, a second header connected with an outlet pipe, and a connection between the first header and the second header And several heat exchange tubes arranged in parallel, the first header and the second header are equipped with porous partitions and non-porous partitions arranged at intervals in sequence, and the porous partitions and non-porous partitions divide the first header The interior of the second header and the second header are divided into several split chambers, and the heat exchange tubes arranged next to the perforated partition and close to the side of the inlet pipe are low-quality split heat-exchange tubes, and the inlet section of the low-quality split heat-exchange tubes It protrudes into the distribution chamber and has a gap with the inner wall of the distribution chamber. In the heat exchange process of the multi-tube evaporator, the "high and low dryness separation split heat transfer" evaporation of the two-phase fluid is realized. The high dryness flow significantly enhances heat transfer and can greatly reduce the flow resistance. According to the flow rate, a certain The dryness of the two-phase working fluid entering the high-dryness shunt heat exchange tube is automatically adjusted to a certain degree.

Description

Double dryness split flow heat exchange evaporator

technical field

The utility model relates to the technical field of evaporator split flow heat exchange, in particular to a double dryness split flow heat exchange evaporator.

Background technique

The existing heat exchange tube evaporator is basically arranged in a serpentine tube flow arrangement or in a multi-tube parallel flow arrangement with a number of non-porous partitions. At the same time, due to the low heat exchange efficiency of the heat exchange tube in the low-quality evaporation process, and when the serpentine tube heat exchange arrangement is used, the evaporator has serious disadvantages such as serious pressure loss in the tube due to the large proportion of gas phase working medium and fast flow rate in the later stage of evaporation. For the multi-tube parallel flow evaporator, because the number of heat exchange tubes in the tube pass increases appropriately with the deepening of the evaporation process, the pressure loss in the tube is small. However, based on the evaporation heat transfer law, the parallel flow evaporator still exists The heat exchange efficiency is low when the dryness is evaporated, and the heat exchange efficiency drops obviously due to the parallel flow arrangement when the high dryness is evaporated. Finally, since the evaporative heat transfer has the highest heat transfer efficiency in the nucleate boiling region with high dryness, the heat transfer effect of the serpentine tube and parallel flow evaporators is significantly enhanced in the later stage of the evaporative heat transfer, resulting in the overall The heat transfer is obviously uneven, and the heat transfer effect of the evaporator is thus limited

Utility model content

The purpose of the utility model is to provide a double dryness shunt heat exchange evaporator, which can improve resistance pressure drop and heat exchange performance.

For realizing the purpose of this utility model, the technical scheme that takes is:

A double dryness split heat exchange evaporator, comprising a first header communicated with an inlet pipe, a second header communicated with an outlet pipe, and connected between the first header and the second header and arranged in parallel A number of heat exchange tubes, the first header and the second header are provided with porous partitions and non-porous partitions arranged at intervals in sequence, and the porous partitions and non-porous partitions connect the first header and the second header. The interior of the box is divided into several split chambers, and the heat exchange tubes adjacent to the perforated partition and near the inlet pipe are low-quality split heat-exchange tubes, and the inlet section of the low-quality split heat-exchange tube extends into the split chamber , and there is a gap with the inner wall of the distribution cavity.

The liquid or low-dryness working fluid enters the evaporator from the inlet pipe, and after repeated heat exchange between the first header and the second header, it is discharged from the outlet pipe of the second header. In the process of evaporative heat exchange, every time the working fluid passes through the heat exchange tubes of a tube side, a two-phase working medium with low dryness will be formed, and then enter one of the headers, and the incoming two-phase working fluid enters one of the headers After the splitter chamber is installed, the flow rate decreases rapidly. Due to the obvious difference in the density of the working fluid gas and liquid phase, the two-phase working fluid in the splitter chamber will undergo phase separation and phase stratification to a certain extent, in which the gas phase is mainly at the top and the liquid phase is mainly at the bottom. . The double-baffle tube-side structure is composed of non-porous baffles and porous baffles. Since the inlet section of the low-quality shunt heat exchange tube extends into the shunt chamber, it can effectively prevent the gas-phase working medium from directly passing through the low-quality shunt due to motion inertia. The heat exchange tube is discharged, and the low-quality split heat exchange tube is arranged next to the perforated partition and close to the inlet tube side, while the non-porous partition adjacent to the perforated partition and close to the outlet tube side and the perforated partition are arranged The heat exchange tubes between the perforated partitions are high-quality shunt heat transfer tubes. Through the pressure difference between two adjacent split chambers in the header, most of the gas phase will mix with part of the liquid phase, and enter the phase through the perforated partitions. Then enter the high-quality split heat exchange tube connected with the adjacent split cavity to continue evaporation and heat exchange, and the low-quality working medium enters the low-quality split heat exchange tube to continue evaporation and heat exchange, so that The flow of high dryness flow and low dryness flow is completed in this header. After heat exchange in one tube side, the low dryness flow and high dryness flow enter the split cavity of another header through the heat exchange tube and Mix and proceed to the double dryness shunt heat exchange of the next tube pass. Due to the continuous increase of the gas-phase working medium and the continuous decrease of the liquid-phase working medium during the evaporation process, along the flow direction, when the number of tube passes increases, the number of high-dryness shunt heat exchange tubes in the tube pass tends to increase, while the number of low-dryness split heat exchange tubes in the tube pass tends to increase. The number of splitter tubes tends to be reduced, and the high-quality nucleate boiling is used to efficiently transfer heat away from it, and the overall heat transfer initiated by the enhancement is strengthened, and the parallel flow multi-heat exchange tube splitting arrangement is adopted to improve the flow performance of the evaporator and improve the multi-tube The uniformity of the working medium distribution of the evaporator can be greatly reduced, the flow resistance can be greatly reduced, and the resistance pressure drop and heat transfer performance of the evaporator can be improved.

The technical scheme is further described below:

Further, the perforated partition is provided with a through hole, and an adjusting tube is sleeved in the through hole, and the adjusting tube extends into the split cavity towards the end of the low quality split flow heat exchange tube. By controlling the length of the regulating tube, the two-phase working fluid with different dryness is discharged into the next split cavity, and the dryness of the two-phase working medium entering the high-quality split heat exchange tube is adjusted to improve the split heat exchange effect.

Further, there are at least two through holes, and each through hole is sleeved with an adjusting tube, and the length of each adjusting tube protruding into the split chamber toward the end of the low-quality split heat exchange tube is different. The two-phase working fluid with different dryness is discharged to the next split cavity through different regulating tubes, and the dryness of the two-phase working medium entering the high-quality split heat exchange tube is further adjusted.

Furthermore, the apertures of each through hole are different. Through-holes with different apertures pass through different flow rates of working fluid. The through-holes with different apertures, plus the length of the regulating tube corresponding to each through-hole extending into the split chamber towards the end of the low-quality split heat exchange tube, can be adjusted according to the flow rate. To a certain extent, the dryness of the two-phase working medium that enters the high-quality split heat exchange tube is automatically adjusted to divert most of the gas-phase working medium and a small part of the liquid-phase working medium into the high-quality split heat exchange tube section.

Further, the projection of the end of the low-quality split flow heat exchange tube extending into the flow split cavity and the adjustment tube adjacent to it along the central axis of the adjustment tube does not overlap. Since there is no hindrance of the heat exchange tube under the through hole, the diameter of the through hole and the length of the regulating tube on it can be optimized in a wide range.

Further, the position where each heat exchange tube communicates with the first header is close to the first side wall of the first header, and the through holes in the first header are close to the first side wall of the first header. Two side walls, the first side wall is arranged opposite to the second side wall, the position where each heat exchange tube communicates with the second header is close to the third side wall of the second header, and the through hole in the second header They are all close to the fourth side wall of the second header, and the third side wall is arranged opposite to the fourth side wall. The heat exchange tube row is installed sideways, and is connected to the inner chamber of the header at one side, and the through hole on the perforated partition is dug on the other side close to the non-connected heat exchange tube, and the through hole is connected to the through adjustment The tube further ensures that there is no obstruction of the heat exchange tube under the through hole, so that the diameter of the through hole and the length of the adjustment tube on it can be optimized in a wide range.

Further, the position where each heat exchange tube communicates with the first header is located on the first inner wall of the first header, and the first header is also provided with a second inner wall parallel to the first inner wall, and the first inner wall The distance between the second inner wall and the second inner wall is H, and the length of the low dryness shunt heat exchange tube extending into the first header is h, where 2H/3≤h<H; each heat exchange tube communicates with the second header The positions are all located on the third inner wall of the second header, and the second header is also provided with a fourth inner wall parallel to the third inner wall, the distance between the third inner wall and the fourth inner wall is T, and the low dryness shunt The length of the heat exchange tube extending into the second header is t, where 2T/3≤t<T. In order to ensure that the incoming working medium can enter the low-quality split tube for evaporative heat exchange, it is better to prevent the gas-phase working medium from being discharged directly through the low-quality split heat exchange tube due to the inertia of motion.

Further, both ends of each heat exchange tube communicate with the first installation surface of the first header and the second installation surface of the second header respectively, and both the first installation surface and the second installation surface are plane. The plane is used as the installation surface of the heat exchange tube, which is convenient for production, installation and positioning, and simplifies the production process.

Further, the outer peripheries of the porous partition and the non-porous partition are both rectangular, and the four corners of the porous partition and the non-porous partition are all rounded. It is beneficial to promote the flow of working fluid in the header and prevent stagnant liquid at the corners.

Further, the side of the first header near the bottom is connected with an inlet pipe, and the side of the second header near the top is connected with an outlet pipe. Further increase the gas-phase working fluid diverted into the high-quality diversion heat-exchange pipe section, and improve the heat-exchange efficiency.

Compared with the prior art, the utility model has the following beneficial effects:

The utility model improves the heat transfer and flow performance of the evaporator, realizes the evaporation of the original two-phase fluid in the heat exchange process of the multi-tube evaporator by "separating high and low dryness split flow heat exchange", and maintains heat exchange through the low dryness flow High efficiency, high dryness flow significantly enhances heat transfer, and can greatly reduce flow resistance; the inlet section of low dryness splitter heat exchange tubes extends deep into the header splitter cavity, preventing the gas phase in the header from entering the low flow rate with inertia. Dryness split heat exchange tube; through the length and diameter of the adjustment tube installed on the through hole of the perforated partition, the dryness of the two-phase working medium entering the high dryness split heat exchange tube can be automatically adjusted to a certain extent according to the flow rate.

Description of drawings

Fig. 1 is a schematic structural view of a double dryness shunt heat exchange evaporator according to an embodiment of the present invention;

Figure 2 is an enlarged view of the I place of Figure 1;

Fig. 3 is the A direction view of Fig. 2;

Fig. 4 is a schematic diagram of a partial structure of a double dryness split heat exchange evaporator according to an embodiment of the present invention.

Explanation of reference signs:

10. inlet pipe, 20. first header, 210. first inner wall, 220. second inner wall, 230. first side wall, 240. second side wall, 30. outlet pipe, 40. second header, 410. The third inner wall, 420. The fourth inner wall, 430. The third side wall, 440. The fourth side wall, 50. Heat exchange tube, 510. Low dryness split heat exchange tube, 511. Inlet section, 520. High Dryness shunt heat exchange tube, 60. porous partition, 610. through hole, 70. non-porous partition, 80. split cavity, 90. regulating tube.

detailed description

Embodiment of the utility model is described in detail below in conjunction with accompanying drawing:

As shown in Figure 1, a double dryness split heat exchange evaporator includes a first header 20 connected with an inlet pipe 10, a second header 40 connected with an outlet pipe 30, and a second header 40 connected with the first header 20. A number of heat exchange tubes 50 arranged in parallel between the second header 40, the first header 20 and the second header 40 are provided with porous partitions 60 and non-porous partitions 70 arranged at intervals in sequence, there are The perforated partition 60 and the non-porous partition 70 divide the interior of the first header 20 and the second header 40 into a number of distribution chambers 80, which are arranged next to the perforated partition 60 and close to the heat exchange chamber on the side of the inlet pipe 10. The tube 50 is a low-quality diversion heat exchange tube 510. The inlet section 511 of the low-quality diversion heat exchange tube 510 extends into the distribution chamber 80, and there is a gap with the inner wall of the distribution chamber 80. The perforated partition 60 is placed on the The front of the non-porous partition 70 according to the flow direction.

The liquid or low dryness working fluid enters the evaporator from the inlet pipe 10, and after repeated heat exchange between the first header 20 and the second header 40, it is discharged from the outlet pipe 30 of the second header 40. When the inlet When the working fluid is in single-phase liquid state, the first group of partitions in the first header 20 where the inlet pipe 10 is located is only the non-porous partitions 70. In addition, the non-porous partitions 70 and porous partitions in each subsequent tube pass 60 are used in combination. In the evaporation heat exchange process, every time the working fluid passes through the heat exchange tube 50 of a tube side for heat exchange, a two-phase working medium with low dryness will be formed, and then enter one of the headers, and the incoming two-phase working fluid enters one of the headers. After the split chamber 80 of the box, the flow rate decreases rapidly. Due to the obvious difference in the density of the working fluid gas and the liquid phase, the two-phase working fluid in the split chamber 80 will undergo phase separation and phase stratification to a certain extent, in which the gas phase is mainly at the top, and the liquid phase Mainly below. A double-baffle tube-side structure is composed of a non-porous partition 70 and a porous partition 60. As shown in Figure 2, since the inlet section 511 of the low-quality split heat exchange tube 510 extends into the split chamber 80, it can effectively block the gas phase. The working fluid is directly discharged through the low-quality split heat exchange tube 510 due to the inertia of motion, and the low-quality split heat exchange tube 510 is arranged next to the perforated partition 60 and is close to the side of the inlet pipe 10, and is connected to the perforated partition 60 The heat exchange tube 50 between the non-porous partition 70 adjacent to the side of the outlet pipe 30 and the perforated partition 60 is a high-quality split flow heat exchange tube 520, which passes through two adjacent split flow tubes in the header. Due to the pressure difference in the cavity 80, most of the gas phase will mix with a part of the liquid phase, and enter the adjacent split cavity 80 through the perforated partition 60, and then enter the high-quality split flow heat exchange tube 520 communicating with the adjacent split cavity 80 Continue evaporating heat exchange, the low-quality working fluid enters the low-quality split heat exchange tube 510 to continue evaporating and heat-exchanging, so that the incoming working medium completes the split flow of the high-quality flow and the low-quality flow in the header, and passes through a After the tube-side heat exchange, the low-quality flow and the high-quality flow pass through the heat exchange tube 50 and enter into the split chamber 80 of another header, where they are mixed, and continue to perform double-quality split heat exchange in the next tube pass. Due to the continuous increase of the gas-phase working medium and the continuous decrease of the liquid-phase working medium during the evaporation process, along the flow direction, when the number of tube passes increases, the number of high-quality shunt heat exchange tubes 520 in the tube pass tends to increase, while the number of low-quality tube passes in the tube pass tends to increase. The number of dryness shunt pipes tends to decrease, and the high-dryness nucleate boiling is used to transfer heat efficiently away from, strengthen and enhance the overall heat transfer initiated, and adopt parallel flow multi-heat exchange tubes with 50 split flow arrangements to improve the flow performance of the evaporator and increase The uniform distribution of working fluid in the multi-tube evaporator greatly reduces the flow resistance and improves the resistance pressure drop and heat transfer performance of the evaporator.

In this embodiment, the side of the first header 20 near the bottom is connected with the inlet pipe 10, and the side of the second header 40 near the top is connected with the outlet pipe 30, which further improves the diversion into the high-quality diversion heat exchange tube. The gas phase working medium in the 520 section improves the heat exchange efficiency.

As shown in Figure 4, the first header 20 and the second header 40 are designed with a large cross-sectional area, so that the fluid entering the header is significantly decelerated, and the separation of gas and liquid phases is realized, and the Reynolds number in the pipe is ≤ 10000 as a constraint; And both ends of each heat exchange tube 50 are connected with the first installation surface of the first header 20 and the second installation surface of the second header 70 respectively, the first installation surface and the second installation surface are both plane, adopt The plane is used as the installation surface of the heat exchange tube, which is convenient for production, installation and positioning, and simplifies the production process. In this embodiment, the cross-sections of the first header 20 and the second header 40 are rectangular, and the cross-sections of the first header 20 and the second header 40 can also be cylindrical, D-shaped, trapezoidal, etc. according to actual needs. shape.

As shown in Figure 4, the outer periphery of the perforated partition 60 and the non-porous partition 70 cooperate with the cross-section of the header, and are also rectangular, and the four corners of the perforated partition 60 and the non-porous partition 70 are all Rounded corners, the four corners of the cross-sections of the first header 20 and the second header 40 are also rounded, which is conducive to promoting the flow of working fluid in the headers and preventing stagnant liquid at the corners.

As shown in FIGS. 1 and 4 , the first header 20 is provided with a first inner wall 210 connected to the heat exchange tubes, and a second inner wall 220 arranged parallel to the first inner wall 210 . Between the first inner wall 210 and the second inner wall 220 The distance between them is H, and the length of the low dryness shunt heat exchange tube 510 extending into the first header 20 is h, wherein, 2H/3≤h<H; the second header 40 is provided with a The third inner wall 410, the fourth inner wall 420 arranged parallel to the third inner wall 410, the position where each heat exchange tube communicates with the second header 40 is located on the third inner wall 410 of the second header 40, the second header 40 is also provided with a fourth inner wall 420 parallel to the third inner wall 410, the distance between the third inner wall 410 and the fourth inner wall 420 is T, and the low-quality split heat exchange tube 510 extends into the length of the second header 40 is t, where 2T/3≤t<T. In order to ensure that the incoming working medium can enter the low-quality split pipe for evaporative heat exchange, it is better to prevent the gas-phase working medium from being discharged directly through the low-quality split heat-exchange pipe 510 due to the inertia of motion. The length of the low-quality split heat exchange tube 510 protruding into the split cavity 80 can also be set to other values according to actual needs.

As shown in Figure 2 and Figure 4, the perforated partition 60 is provided with a through hole 610, and the through hole 610 is sleeved with a regulating tube 90, and the regulating tube 90 extends into the split chamber 80 toward the end of the low dryness split heat exchange tube 510 Inside. By controlling the length of the regulating tube 90, the two-phase working medium with different dryness is discharged into the next split chamber 80, and the dryness of the two-phase working medium entering the high-quality split heat exchange tube 520 is adjusted to improve the split heat exchange effect .

In this embodiment, there are three through holes 610, and each through hole 610 is sleeved with an adjustment tube 90, and each adjustment tube 90 extends into the split cavity 80 toward the end of the low-quality split heat exchange tube 510. different, and the diameter of each through hole 610 is different, the diameter of the through hole 610 can be optimally combined within the range of 3-10 mm. Through different regulating tubes 90, the two-phase working fluid with different dryness is discharged into the next distribution chamber 80. The flow rate of the working fluid passing through the through holes 610 with different apertures is different. The through holes 610 with different apertures, plus each through hole 610 The length of the corresponding adjustment tube 90 protruding into the split chamber 80 toward the end of the low-quality split heat-exchange tube 510 is different, and the dryness of the two-phase working fluid entering the high-quality split heat-exchange tube 520 can be automatically adjusted to a certain extent according to the flow rate. , so as to divert most of the gas-phase working medium and a small part of the liquid-phase working medium into the high-quality split heat exchange tube section 520 . More than one through-hole 610 can be set according to actual needs, and the aperture can also be set to other values according to actual needs. The aperture of the through-hole 610 and the length of the regulating tube 90 can be optimally designed into other combinations according to the design flow and load of the evaporator.

One end of the low-quality split heat exchange tube 510 extending into the split cavity 80 and the projection of the adjacent adjustment tube 90 along the central axis of the adjustment tube 90 do not overlap. Since there is no hindrance of the heat exchange tube under the through hole 610, it is convenient to pass through. The diameter of the hole 610 and the length of the regulating tube 90 thereon can be optimized in a wide range.

In this embodiment, as shown in FIGS. 3 and 4 , the first header 20 further includes a first side wall 230 and a second side wall 240 disposed between the first inner wall 210 and the second inner wall 220 , each The positions where the heat exchange tubes 50 communicate with the first header 20 are all close to the first side wall 230 of the first header 20 , and the through holes 610 located in the first header 20 are all close to the second side wall of the first header 20 . The side wall 240, the first side wall 230 and the second side wall 240 are arranged oppositely; referring to the arrangement of the heat exchange tubes and the through holes 610 in the first header 20, the second header 40 also includes the third inner wall 410 and the Between the third side wall 430 and the fourth side wall 440 between the fourth inner wall 420, the position where each heat exchange tube communicates with the second header 40 is close to the third side wall 430 of the second header 40, located in the second The through holes 610 in the header box 40 are close to the fourth side wall 440 of the second header box 40 , and the third side wall 430 is arranged opposite to the fourth side wall 440 . The heat exchange tube row is installed sideways, and is connected to the inner chamber of the header at one side, and the through hole 610 on the perforated partition 60 is excavated on the other side close to the non-connected heat exchange tube, and the through hole 610 is connected to The penetrating regulating tube 90 further ensures that there is no obstruction of the heat exchange tube under the through hole 610 , so that the diameter of the through hole 610 and the length of the regulating tube 90 thereon can be optimally designed in a wide range. The heat exchange tube row can also adopt other installation methods according to actual needs, so as to ensure that the end of the low-quality split heat exchange tube 510 protruding into the split cavity 80 and the projection of the adjacent adjustment tube 90 along the central axis of the adjustment tube 90 are staggered. .

The utility model overcomes the low heat exchange efficiency in the low-dryness evaporation process that co-exists in the serpentine tube flow arrangement or the common multi-tube parallel flow arrangement evaporator, and the heat exchange effect is obviously enhanced due to the later stage of the evaporation process, so that The shortcoming of uneven heat transfer between the tubes of the evaporator; and the shortcomings of the serious pressure loss in the tube caused by the serpentine flow arrangement of the serpentine tube flow arrangement evaporator; the improvement of the parallel flow evaporator due to The parallel flow arrangement leads to the decrease of the flow rate of the working medium in the high-quality nucleate boiling area, and the obvious decrease of the heat transfer efficiency. Compared with the prior art, the utility model adopts a plane as the installation surface of the heat exchange tube, which is convenient for production, installation and positioning, and simplifies the production process; it adopts a multi-tube pass double-dryness evaporation heat transfer method, and utilizes the high-dryness nucleate boiling high-efficiency heat transfer principle , to strengthen the overall heat transfer of the evaporator; the parallel flow multi-tube split flow arrangement is adopted to improve the flow performance of the evaporator, improve the uniformity of the working medium distribution of the multi-tube evaporator, and greatly reduce the flow resistance; the low dryness split tube The inlet section 511 extends deep into the header splitter cavity 80, preventing the gas phase in the header from entering the low-quality flow heat exchange tubes in large quantities with inertia; According to the flow rate, the dryness of the two-phase working fluid entering the high-dryness split heat exchange tube 520 can be automatically adjusted to a certain extent to ensure the enhanced heat transfer effect.

The technical features of the above-mentioned embodiments can be combined arbitrarily. To make the description concise, all possible combinations of the technical features in the above-mentioned embodiments are not described. However, as long as there is no contradiction in the combination of these technical features, should be considered as within the scope of this specification.

The above-mentioned embodiments only express several implementation modes of the utility model, and the description thereof is relatively specific and detailed, but it should not be understood as limiting the scope of the utility model patent. It should be noted that those skilled in the art can make several modifications and improvements without departing from the concept of the present invention, and these all belong to the protection scope of the present invention. Therefore, the scope of protection of the utility model patent should be based on the appended claims.

Claims (10)

1. A double dryness split heat exchange evaporator is characterized in that it comprises a first header communicated with an inlet pipe, a second header communicated with an outlet pipe, and communicated with said first header and said first header. A number of heat exchange tubes arranged in parallel between the second headers, the first header and the second header are provided with porous partitions and non-porous partitions arranged at intervals in sequence, the porous partitions The partition and the non-porous partition divide the inside of the first header and the second header into a number of distribution chambers, and all the parts adjacent to the porous partition and close to the inlet pipe The heat exchange tubes are low-quality split heat-exchange tubes, and the inlet section of the low-quality split heat-exchange tubes extends into the split cavity and has a gap with the inner wall of the split cavity. 2. The double dryness shunt heat exchange evaporator according to claim 1, characterized in that, the perforated partition is provided with a through hole, and an adjusting tube is sleeved in the through hole, and the adjusting tube faces to the One end of the low-quality split flow heat exchange tube extends into the split cavity. 3. The double dryness split heat exchange evaporator according to claim 2, characterized in that there are at least two said through holes, each of said through holes is sleeved with said regulating tube, and each of said through holes The lengths of the adjustment tubes extending into the split cavity toward the end of the low-quality split heat exchange tube are different. 4. The double dryness split flow heat exchange evaporator according to claim 3, characterized in that the diameters of each of the through holes are different. 5. The double dryness split flow heat exchange evaporator according to claim 2, characterized in that, one end of the low dryness split flow heat exchange tube extending into the split cavity and the regulating tube adjacent to it are along the The projections in the direction of the central axis of the adjustment tube do not overlap. 6. The double dryness split flow heat exchange evaporator according to claim 5, characterized in that the position where each of the heat exchange tubes communicate with the first header is close to the first header of the first header. side walls, the through holes in the first header are close to the second side walls of the first header, the first side walls are arranged opposite to the second side walls, and each of the The position where the heat exchange tube communicates with the second header is close to the third side wall of the second header, and the through holes in the second header are close to the first side wall of the second header. Four side walls, the third side wall is arranged opposite to the fourth side wall. 7. The double dryness split flow heat exchange evaporator according to claim 1, characterized in that the position where each of the heat exchange tubes communicate with the first header is located in the first section of the first header. On the inner wall, the first header is also provided with a second inner wall parallel to the first inner wall, the distance between the first inner wall and the second inner wall is H, and the low dryness splitter The length of the heat pipe extending into the first header is h, where 2H/3≤h<H; the position where each of the heat exchange tubes communicate with the second header is located in the second header On the third inner wall, the second header is also provided with a fourth inner wall parallel to the third inner wall, the distance between the third inner wall and the fourth inner wall is T, and the low stem The length of the split heat exchange tube extending into the second header is t, where 2T/3≤t<T. 8. The double dryness split flow heat exchange evaporator according to any one of claims 1 to 7, characterized in that, both ends of each of the heat exchange tubes are respectively connected to the first joint of the first header. The surface and the second installation surface of the second header are connected, and the first installation surface and the second installation surface are both planes. 9. The double dryness split heat exchange evaporator according to claim 8, characterized in that, the outer peripheries of the porous partition and the non-porous partition are rectangular, and the porous partition and the The four corners of the non-porous partition are all rounded. 10. The double dryness split flow heat exchange evaporator according to any one of claims 1 to 7, characterized in that, the side of the first header close to the bottom communicates with the inlet pipe, and the second header The side of the tank close to the top is communicated with the outlet pipe.