Flow divider, air conditioning system and flow dividing control method

Abstract

The invention provides a flow divider, an air conditioning system and a flow dividing control method.The flow divider is internally provided with a flow dividing cavity, a first flow dividing hole and a second flow dividing hole, the flow dividing cavity is connected to a throttling element through a liquid inlet pipe, and the first flow dividing hole is connected to a middle-layer flow path of a fin type heat exchanger through a capillary tube; the second shunting hole is connected to an edge layer flow path of the fin type heat exchanger through a capillary tube; a flow dividing cone is arranged in the flow dividing cavity and divides the flow dividing cavity into a first flow dividing sub-cavity communicating with the first flow dividing hole and a second flow dividing sub-cavity communicating with the second flow dividing hole, and the volume of the first flow dividing sub-cavity is larger than that of the second flow dividing sub-cavity. According to the fin type heat exchanger, the requirement of each flow path of the fin type heat exchanger for refrigerants can be better met, and therefore the overall heat exchange performance of the fin type heat exchanger is improved.

Description

Technical Field

[0001] The present invention belongs to the technical field of air conditioners, and more specifically, relates to a flow divider, an air conditioning system, and a flow division control method. Background Art

[0002] In current mainstream air conditioning systems, capillary tubes are usually used inside the unit to connect the flow divider and each flow path of the fin heat exchanger. Usually, the fin heat exchanger is vertically placed, and a fan is installed at the middle position thereof. When the fan operates, the air volume in the middle layer of the fin heat exchanger is significantly greater than that in the upper and lower edge layers, which makes the heat transfer efficiency in the middle layer of the fin heat exchanger higher. Therefore, the demand for refrigerant in the edge layers of the fin heat exchanger is much lower than that in the middle layer. Given the differences in the refrigerant demand of each flow path of the fin heat exchanger, the prior art adjusts the flow resistance by selecting capillary tubes with different lengths to control the amount of refrigerant entering each flow path. However, the adjustment ability of the capillary tubes is limited, and there is still room for improvement in the overall heat transfer performance of the fin heat exchanger. Summary of the Invention

[0003] The object of the present invention is to provide a flow divider, an air conditioning system, and a flow division control method, aiming to better meet the refrigerant demand of each flow path of the fin heat exchanger, thereby improving the overall heat transfer performance of the fin heat exchanger.

[0004] To achieve the above object, the technical solution adopted by the present invention is:

[0005] The present invention provides a flow divider applied to an air conditioning system. A flow division cavity, a first flow division hole, and a second flow division hole are formed inside the flow divider. The flow division cavity is connected to a throttling element through a liquid inlet pipe. The first flow division hole is connected to the middle layer flow path of the fin heat exchanger through a capillary tube. The second flow division hole is connected to the edge layer flow path of the fin heat exchanger through a capillary tube;

[0006] A flow division cone is provided inside the flow division cavity. The flow division cone divides the flow division cavity into a first flow division sub-cavity communicating with the first flow division hole and a second flow division sub-cavity communicating with the second flow division hole, and the volume of the first flow division sub-cavity is greater than the volume of the second flow division sub-cavity.

[0007] Further, a first electromagnetic coil is provided outside the flow divider. A first magnetic rotor and a stator are provided on the flow dividing cone. The first magnetic rotor has a first alignment hole group corresponding to the first flow dividing cavity and a second alignment hole group corresponding to the second flow dividing cavity. The stator has a first fixing hole group corresponding to the first flow dividing cavity and a second fixing hole group corresponding to the second flow dividing cavity. When the first electromagnetic coil is energized, the first magnetic rotor rotates by electromagnetic force, changing the alignment state between the first alignment hole group and the first fixing hole group and between the second alignment hole group and the second fixing hole group, thereby adjusting the refrigerant amount of the first flow dividing hole and the second flow dividing hole.

[0008] Further, a second electromagnetic coil is provided outside the flow divider. The stator is provided with a rotor installation groove in the area located in the second flow dividing cavity. A second magnetic rotor is rotatably installed in the rotor installation groove. The second magnetic rotor has a third alignment hole group corresponding to the second flow dividing cavity. When the second electromagnetic coil is energized, the second magnetic rotor rotates by electromagnetic force, changing the alignment state between the third alignment hole group and the second fixing hole group, thereby adjusting the refrigerant amount of the second flow dividing hole.

[0009] Further, a pressure relief pipeline for connecting the second flow dividing cavity and the vapor-liquid separator is provided outside the flow divider. A pressure regulating elastic element for balancing the internal pressure of the vapor-liquid separator is provided in the pressure relief pipeline.

[0010] Further, a sealing element is provided between the first magnetic rotor and the stator and between the second magnetic rotor and the stator.

[0011] The present invention also provides an air conditioning system, including a water circulation loop and a refrigerant circulation loop. A compressor, a four-way reversing valve, a fin heat exchanger, a throttling element, and a plate heat exchanger are provided on the refrigerant circulation loop. The refrigerant circulation loop is also provided with the flow divider as described above.

[0012] Further, a vapor-liquid separator and a reversing assembly are also provided on the refrigerant circulation loop. The reversing assembly includes a first three-way reversing valve and a second three-way reversing valve sequentially arranged between the throttling element and the flow divider. The inlet of the vapor-liquid separator is connected to the first three-way reversing valve, the liquid outlet of the vapor-liquid separator is connected to the second three-way reversing valve, and the gas outlet of the vapor-liquid separator is respectively connected to the enthalpy-increasing port of the compressor and the pressure relief pipeline of the flow divider.

[0013] The present invention also provides a flow dividing control method, which is applied to the air conditioning system as described above. The flow dividing control method includes:

[0014] When the air conditioning system is in the heating mode, determine the amount of refrigerant currently required by the fin heat exchanger, and control the amount of refrigerant in the diversion holes in the diverter according to the amount of refrigerant currently required by the fin heat exchanger.

[0015] Further, the amount of refrigerant currently required by the fin heat exchanger is determined according to the current ambient temperature and the current compressor operating frequency of the air conditioning system; the control of the amount of refrigerant in the diversion holes in the diverter according to the amount of refrigerant currently required by the fin heat exchanger is as follows:

[0016] According to the temperature range where the current ambient temperature is located and the frequency range where the current compressor operating frequency is located, adjust the current parameter of the first electromagnetic coil, so as to control the amount of refrigerant in the first diversion hole and the second diversion hole in the diverter.

[0017] Further, the amount of refrigerant currently required by the fin heat exchanger is determined according to the load state of the air conditioning system, and the control of the amount of refrigerant in the diversion holes in the diverter according to the amount of refrigerant currently required by the fin heat exchanger is as follows:

[0018] When the air conditioning system is in the first load state, adjust the current parameter of the second electromagnetic coil according to the set current parameter, so that all the third alignment hole groups of the second magnetic rotor are misaligned with the second fixed hole groups of the stator, thereby cutting off the refrigerant supply to the second diversion hole in the diverter;

[0019] When the air conditioning system is in the second load state, control the current parameter of the second electromagnetic coil to be consistent with the current parameter of the first electromagnetic coil.

[0020] Further, determine whether the air conditioning system is in the first load state or the second load state according to the current ambient temperature, the current compressor operating frequency and the current outlet water temperature of the plate heat exchanger of the air conditioning system.

[0021] Compared with the prior art, the beneficial effects of the diverter, the air conditioning system and the diversion control method provided by the present invention are as follows: In the diverter of the present invention, since the volume of the first diversion sub-chamber is larger than the volume of the second diversion sub-chamber, when the refrigerant flows through the diversion cone, it will preferentially enter the first diversion sub-chamber. Subsequently, the refrigerant is transported to the middle layer flow path of the fin heat exchanger through the first diversion hole and the corresponding capillary tube. Since the middle layer flow path usually has a relatively large demand for refrigerant, this design can ensure that it obtains sufficient refrigerant supply. At the same time, the remaining refrigerant will flow into the second diversion sub-chamber and enter the edge layer flow path of the fin heat exchanger through the second diversion hole and the corresponding capillary tube. Since the edge layer flow path has a relatively small demand for refrigerant, this diversion method can effectively avoid excessive cooling, thereby improving the heat exchange efficiency of the entire fin heat exchanger. Description of the Drawings

[0022] To more clearly illustrate the technical solutions in the embodiments of the present invention, the following will briefly introduce the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings in the following description are only some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on these drawings.

[0023] Figure 1 Schematic cross-sectional view of the inside of the flow divider in the present invention;

[0024] Figure 2 For Figure 1 in Schematic cross-sectional view;

[0025] Figure 3 For Figure 1 Schematic cross-sectional view of the A-B section in;

[0026] Figure 4 Schematic external view of the flow divider in the present invention;

[0027] Figure 5 Schematic partial view of the air-conditioning system in the present invention;

[0028] Figure 6 Schematic view of the air-conditioning system in the heating mode in the present invention;

[0029] Figure 7 Schematic view of the air-conditioning system in the cooling mode in the present invention;

[0030] Figure 8 Flow chart of the movement of the first magnetic rotor in the present invention;

[0031] Figure 9 Flow chart of the movement of the second magnetic rotor in the present invention;

[0032] Among them, the main reference signs in the drawings are as follows:

[0033] 1. Compressor; 2. Four-way reversing valve; 3. Finned heat exchanger; 4. Flow divider; 5. Plate heat exchanger; 6. Gas-liquid separator; 7. Main throttle valve; 8. Auxiliary throttle valve; 9. First three-way reversing valve; 10. Second three-way reversing valve;

[0034] 40. Flow dividing cavity; 41. First flow dividing sub-cavity; 42. Second flow dividing sub-cavity; 43. Flow dividing cone; 44. Capillary tube; 45. Stator; 46. First magnetic rotor; 47. Second magnetic rotor; 451. Positioning magnet; 461. First pair of alignment hole groups; 462. Second pair of alignment hole groups; 471. Third pair of alignment hole groups; 48. Pressure relief pipeline; 49. Pressure regulating elastic element; 410. Sealing element;

[0035] 51. Whole machine control module; 52. First relay; 53. Second relay; 54. First electromagnetic coil; 55. Second electromagnetic coil. Detailed implementation manners

[0036] In order to make the technical problems, technical solutions and beneficial effects to be solved by the present invention more clear and understandable, the present invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not used to limit the present invention.

[0037] In the current mainstream air conditioning system, a capillary tube is usually used inside the unit to connect the flow divider and each flow path of the fin heat exchanger. Usually, the fin heat exchanger is vertically placed, and a blower is installed at the middle position thereof. When the blower operates, the air volume in the middle layer of the fin heat exchanger is significantly larger than that in the upper and lower edge layers, which makes the heat exchange efficiency of the middle layer of the fin heat exchanger higher. Therefore, the demand for refrigerant in the edge layer of the fin heat exchanger is much lower than that in the middle layer. In view of the difference in the refrigerant demand of each flow path of the fin heat exchanger, the prior art adjusts the flow resistance by selecting capillary tubes with different lengths, so as to control the amount of refrigerant entering each flow path. However, the adjustment ability of the capillary tube is limited, and there is still room for improvement in the overall heat exchange performance of the fin heat exchanger. In addition, the prior art cannot adjust the amount of refrigerant in each flow path in real time during the operation of the unit, and under ultra-low temperature conditions, the amount of refrigerant required by the fin heat exchanger is much lower than that under normal temperature conditions. In addition, the prior art also has problems such as low heat exchange efficiency of the fins caused by the two-phase coexistence when the refrigerant enters the fin heat exchanger, and the problem of retention of excess gaseous refrigerant inside the fin heat exchanger.

[0038] Therefore, the present invention proposes a flow divider, an air conditioning system and a flow control method. The present invention can more effectively adapt to the difference in the refrigerant demand of each flow path of the fin heat exchanger, and can also change the amount of refrigerant in each flow path of the fin heat exchanger according to the unit state. In addition, the amount of liquid refrigerant inside the fin heat exchanger can be increased, thereby improving the heat exchange efficiency of the fin heat exchanger. In addition, it can also guide the excess gaseous refrigerant inside the system to the compressor end for enthalpy increase, thereby improving the thermal efficiency of the compressor.

[0039] Please refer to Figures 1 to 4 simultaneously, the present invention provides a flow divider 4, which is applied to an air conditioning system and includes:

[0040] A flow dividing cavity 40, a first flow dividing hole and a second flow dividing hole are formed inside the flow divider 4. The flow dividing cavity 40 is connected to a throttling element through a liquid inlet pipe. The first flow dividing hole is connected to the middle layer flow path of the fin heat exchanger 3 through a capillary tube 44, and the second flow dividing hole is connected to the edge layer flow path of the fin heat exchanger 3 through a capillary tube 44;

[0041] The flow splitting cavity 40 is provided with a flow splitting cone 43. The flow splitting cone 43 divides the flow splitting cavity 40 into a first flow splitting sub-cavity 41 communicating with the first flow splitting hole and a second flow splitting sub-cavity 42 communicating with the second flow splitting hole, and the volume of the first flow splitting sub-cavity 41 is larger than that of the second flow splitting sub-cavity 42.

[0042] When the air-conditioning system operates, the refrigerant flows into the flow splitting cavity 40 of the flow splitter 4 from the throttling element. Since the volume of the first flow splitting sub-cavity 41 is larger than that of the second flow splitting sub-cavity 42, under the action of the flow splitting cone 43, the refrigerant will preferentially flow into the first flow splitting sub-cavity 41 and enter the middle laminar flow path of the fin heat exchanger 3 through the first flow splitting hole and the corresponding capillary 44. Since the middle laminar flow path usually has a relatively large demand for the refrigerant, such a design can ensure sufficient refrigerant supply for the middle laminar flow path. At the same time, the remaining refrigerant will flow into the second flow splitting sub-cavity 42 and enter the edge laminar flow path of the fin heat exchanger 3 through the second flow splitting hole and the corresponding capillary 44. The edge laminar flow path has a relatively small demand for the refrigerant, so such a flow splitting method can avoid excessive cooling of the edge laminar flow path, thereby improving the heat exchange efficiency of the entire fin heat exchanger 3.

[0043] As Figure 1 shown, when the flow splitter 4 is horizontally placed, the first flow splitting sub-cavity 41 is located below the flow splitting cone 43, while the second flow splitting sub-cavity 42 is located above the flow splitting cone 43. By arranging the flow splitting cone 43 at a relatively upper position in the flow splitting cavity 40, it can be ensured that the volume of the first flow splitting sub-cavity 41 is larger than that of the second flow splitting sub-cavity 42. Combined with the capillary 44 with different lengths, the difference in the refrigerant demand of each flow path of the fin heat exchanger 3 can be more effectively met.

[0044] As Figure 1 、 Figure 2 and Figure 4 shown, in a further preferred embodiment of the present invention, a first electromagnetic coil 54 is provided outside the flow splitter 4, a first magnetic rotor 46 and a stator 45 are provided on the flow splitting cone 43. The first magnetic rotor 46 has a first alignment hole group 461 corresponding to the first flow splitting sub-cavity 41 and a second alignment hole group 462 corresponding to the second flow splitting sub-cavity 42. The stator 45 has a first fixing hole group corresponding to the first flow splitting sub-cavity 41 and a second fixing hole group corresponding to the second flow splitting sub-cavity 42. When the first electromagnetic coil 54 is energized, the first magnetic rotor 46 rotates by electromagnetic force to change the alignment state between the first alignment hole group 461 and the first fixing hole group and between the second alignment hole group 462 and the second fixing hole group, thereby adjusting the refrigerant amounts of the first flow splitting hole and the second flow splitting hole.

[0045] This design enables real-time regulation of the refrigerant volume in each flow path of the fin heat exchanger 3 during the operation of the air conditioning system. This regulation mechanism has high flexibility and can automatically or manually adjust the refrigerant distribution according to different operating conditions and load requirements. For example, when the refrigerant volume required by the fin heat exchanger 3 increases, the system adjusts the current parameters of the first electromagnetic coil 54 to increase the alignment degree between the first alignment hole group 461 and the first fixed hole group, and between the second alignment hole group 462 and the second fixed hole group; conversely, when the refrigerant volume required by the fin heat exchanger 3 decreases, the system correspondingly adjusts the current parameters of the first electromagnetic coil 54 to reduce the alignment degree between the first alignment hole group 461 and the first fixed hole group, and between the second alignment hole group 462 and the second fixed hole group. Through this design, the system can accurately control the refrigerant volume entering each flow path of the fin heat exchanger 3, ensuring that the fin heat exchanger 3 can maintain the best heat exchange efficiency under various working conditions.

[0046] It should be noted that the overall control module 51 of the air conditioning system adjusts the power-on and power-off of the first electromagnetic coil 54 by controlling the opening and closing state of the first relay 52. When the first electromagnetic coil 54 is powered off, the first magnetic rotor 46 rotates to the initial position under the action of the positioning magnet 451 of the stator 45. At this time, the first alignment hole group 461 of the first magnetic rotor 46 is completely aligned with the first fixed hole group of the stator 45, and the second alignment hole group 462 of the first magnetic rotor 46 is completely aligned with the second fixed hole group of the stator 45. When the first electromagnetic coil 54 is powered on, it drives the first magnetic rotor 46 to rotate. In addition, by adjusting the current parameters (including current intensity, power-on duration, and phase) of the first electromagnetic coil 54, the offset amplitude, offset residence time, and offset direction of the first magnetic rotor 46 can be accurately controlled, thereby changing the hole position matching relationship between the first magnetic rotor 46 and the stator 45.

[0047] As Figure 1 、 Figure 3 and Figure 4 shown, in a further preferred embodiment of the present invention, a second electromagnetic coil 55 is provided outside the diverter 4. The stator 45 is provided with a rotor installation groove in the area located in the second diverter chamber 42. A second magnetic rotor 47 is rotatably installed in the rotor installation groove. The second magnetic rotor 47 has a third alignment hole group 471 corresponding to the second diverter chamber 42. The second magnetic rotor 47 rotates by electromagnetic force when the second electromagnetic coil 55 is powered on, changing the alignment state between the third alignment hole group 471 and the second fixed hole group, thereby regulating the refrigerant volume of the second diverter hole.

[0048] This design further enhances the shunt control ability of the air conditioning system, enabling the system to perform multi-level regulation of the refrigerant distribution according to more refined regulation requirements. The change in the alignment state between the third alignment hole group 471 and the second fixing hole group makes the refrigerant distribution of the fin heat exchanger 3 more flexible. When the air conditioning system needs to be finely adjusted according to specific working conditions or load requirements, the alignment degree between the third alignment hole group 471 and the second fixing hole group can be precisely adjusted by controlling the current parameters of the second electromagnetic coil 55, so as to achieve precise control of the refrigerant volume of the second shunt hole. This refrigerant distribution adjustment mechanism enables the air conditioning system to maintain the best heat exchange efficiency and operating performance under various working conditions.

[0049] It should be noted that the whole machine control module 51 controls the opening and closing state of the second relay 53, and then regulates the power on and off of the second electromagnetic coil 55. When the second electromagnetic coil 55 is powered off, the second magnetic rotor 47 rotates to the initial position under the action of the positioning magnet 451 of the stator 45. At this time, the third alignment hole group 471 of the second magnetic rotor 47 is completely aligned with the second fixing hole group of the stator 45. When the second electromagnetic coil 55 is powered on, it will drive the second magnetic rotor 47 to rotate. By adjusting the current parameters of the second electromagnetic coil 55 (including current intensity, power-on duration, and phase), the offset amplitude, offset residence time, and offset direction of the second magnetic rotor 47 can be precisely controlled, and then the hole position matching relationship between the second magnetic rotor 47 and the stator 45 can be changed.

[0050] As Figure 1 shown, in a further preferred embodiment of the present invention, a pressure relief pipeline 48 for connecting the second shunt sub-chamber 42 and the gas-liquid separator 6 is provided outside the shunt 4. A pressure regulating elastic element 49 for balancing the internal pressure of the gas-liquid separator 6 is provided in the pressure relief pipeline 48. For example, the pressure regulating elastic element 49 is a one-way reed, and the pressure relief threshold is 1.8 Mpa.

[0051] When the internal pressure of the gas-liquid separator 6 exceeds the set pressure relief threshold (for example, 1.8 Mpa), the pressure regulating elastic element 49 will be compressed due to pressure, thereby opening the pressure relief pipeline 48. This process will guide the gaseous refrigerant to the shunt 4, effectively preventing the internal pressure of the gas-liquid separator 6 from being too high while ensuring that the gaseous refrigerant maintains sufficient pressure.

[0052] As Figure 1 shown, in a further preferred embodiment of the present invention, a sealing element 410 is provided between the first magnetic rotor 46 and the stator 45, and between the second magnetic rotor 47 and the stator 45. The setting of the sealing element 410 effectively prevents the leakage of the refrigerant between the first and second magnetic rotors 47 and the stator 45, thereby improving the sealing performance of the shunt 4.

[0053] Please refer toFigures 5 to 7 , the present invention also provides an air conditioning system, including a water circulation loop and a refrigerant circulation loop. A compressor 1, a four-way reversing valve 2, a fin heat exchanger 3, a throttling element, and a plate heat exchanger 5 are provided on the refrigerant circulation loop. Meanwhile, a shunt device 4 as described above is also provided on the refrigerant circulation loop. Since the shunt device 4 can better meet the refrigerant requirements of each flow path of the fin heat exchanger 3, the overall heat exchange performance of the fin heat exchanger 3 is improved.

[0054] As Figure 5 shown, in a further preferred embodiment of the present invention, a gas-liquid separator 6 and a reversing assembly are further provided on the refrigerant circulation loop. The reversing assembly includes a first three-way reversing valve 9 and a second three-way reversing valve 10 sequentially arranged between the throttling element and the shunt device 4. The inlet of the gas-liquid separator 6 is connected to the first three-way reversing valve 9, the liquid outlet of the gas-liquid separator 6 is connected to the second three-way reversing valve 10, and the gas outlet of the gas-liquid separator 6 is respectively connected to the enthalpy-increasing port of the compressor 1 and the pressure relief pipeline 48 of the shunt device 4.

[0055] This design further takes into account that, under the same heat exchange medium state, the latent heat exchange amount generated by the complete evaporation of a unit mass of liquid refrigerant is much greater than the sensible heat exchange amount of gaseous refrigerant. Therefore, in order to further improve the efficiency of the shunt device 4 in the air conditioning system, it is necessary to combine the gas-liquid separator 6 to perform a more refined separation process on the refrigerant entering the shunt device 4. Only in this way can the fin heat exchange space be utilized more fully, thereby improving the operating efficiency of the whole machine.

[0056] For the convenience of understanding, the refrigerant circulation loop in the air conditioning system will be described in detail below with reference to the accompanying drawings.

[0057] As Figure 5 shown, a compressor 1, a four-way reversing valve 22, a fin heat exchanger 3, a shunt device 4, a plate heat exchanger 5, a gas-liquid separator 6, a main throttling valve 7, an auxiliary throttling valve 8, a first three-way reversing valve 9, and a second three-way reversing valve 10 are provided on the refrigerant circulation loop. Among them, the main throttling valve 7 and the auxiliary throttling valve 8 are electronic expansion valves.

[0058] As Figure 6As shown in the figure, when the air-conditioning system is in the heating mode, after the refrigerant is discharged from the compressor 1, it passes through the plate heat exchanger 5 and the main throttle valve 7 in sequence, and then enters the gas-liquid separator 6 through the first three-way reversing valve 9. The gas-liquid separator 6 separates the two-phase refrigerant after passing through the main throttle valve 7. The liquid refrigerant enters the shunt 4 through the liquid refrigerant branch and the main throttle valve 7, and naturally flows through the first shunt sub-chamber to the first shunt hole under the action of gravity, and then enters the intermediate laminar flow path of the fin heat exchanger 3 through the capillary 44 for heat exchange; the gaseous refrigerant flows through the gaseous refrigerant branch to the auxiliary throttle valve 8, or enters the shunt 4 through the pressure relief pipeline 48, and then participates in heat exchange through the second shunt hole to the edge laminar flow path of the fin heat exchanger 3.

[0059] Meanwhile, the gaseous refrigerant in the gas-liquid separator 6 can be used to increase the enthalpy of the compressor 1, thereby improving the efficiency of the compressor 1. To ensure that the gaseous refrigerant has sufficient pressure to enter the compressor 1, an action reed with a specific pressure needs to be installed inside the gas-liquid separator 6. This design can not only ensure sufficient pressure of the gaseous refrigerant, but also effectively prevent the internal pressure of the gas-liquid separator 6 from being too high.

[0060] When the compressor 1 is operating at a low frequency, the refrigerant circulation volume of the entire system is small. At this time, the refrigerant does not need to pass through the gas-liquid separator 6. At this time, the first three-way reversing valve 9 should be controlled to switch to the refrigeration flow path, so that the refrigerant directly flows to the shunt 4 for shunting.

[0061] The present invention also provides a shunt control method, which is applied to the air-conditioning system as described above. The shunt control method includes:

[0062] When the air-conditioning system is in the heating mode, judge the current refrigerant amount required by the fin heat exchanger, and control the refrigerant amount of the shunt hole in the shunt according to the current refrigerant amount required by the fin heat exchanger.

[0063] Such a design can realize the real-time regulation of the refrigerant amount entering each flow path of the fin heat exchanger during the operation of the air-conditioning system. This regulation mechanism has high flexibility and can automatically or manually adjust the distribution of the refrigerant according to the current refrigerant amount required by the fin heat exchanger. By precisely regulating the refrigerant amount, not only the heat exchange efficiency of the fin heat exchanger is optimized, but also the waste of the refrigerant is reduced, and the energy efficiency ratio of the entire air-conditioning system is improved.

[0064] In a further preferred embodiment of the present invention, the current refrigerant amount required by the fin heat exchanger is judged according to the current ambient temperature and the current compressor operating frequency of the air-conditioning system; controlling the refrigerant amount of the shunt hole in the shunt according to the current refrigerant amount required by the fin heat exchanger is:

[0065] Adjust the current parameter of the first electromagnetic coil according to the temperature range where the current ambient temperature is located and the frequency range where the current compressor operating frequency is located, so as to control the refrigerant amounts in the first shunt hole and the second shunt hole in the diverter.

[0066] Such a design can achieve a more refined adjustment of the refrigerant distribution. At different ambient temperatures and compressor operating frequencies, the demand for refrigerant by the fin heat exchanger will be different. By comprehensively considering these two factors and adjusting the current parameter of the first electromagnetic coil accordingly, it can be ensured that the refrigerant amount can accurately match the actual demand of the fin heat exchanger. This can not only further improve the heat exchange efficiency, but also avoid over-supply or shortage of refrigerant, thus achieving a higher energy efficiency ratio and more stable system performance.

[0067] As Figure 8 shown, detect the current ambient temperature T 环 and the current compressor operating frequency P 压 , and determine the temperature range where the current ambient temperature T 环 is located and the frequency range where the current compressor operating frequency P 压 is located;

[0068] When T 环 < -20°C, change the current intensity of the first electromagnetic coil to align the first alignment hole group of the first magnetic rotor with the first fixed hole group of the stator to the 1 / 2 position, and at the same time align the second alignment hole group of the first magnetic rotor with the second fixed hole group of the stator to the 1 / 2 position, so as to change the offset amplitude of the first magnetic rotor, and further effectively control the refrigerant amounts entering each flow path of the fin heat exchanger.

[0069] When -20°C ≤ T 环 < -5°C, change the current intensity of the first electromagnetic coil to align the first alignment hole group of the first magnetic rotor with the first fixed hole group of the stator to the 2 / 3 position, and at the same time align the second alignment hole group of the first magnetic rotor with the second fixed hole group of the stator to the 2 / 3 position, so as to change the offset amplitude of the first magnetic rotor, and further effectively control the refrigerant amounts entering each flow path of the fin heat exchanger.

[0070] When T 环 ≥ -5°C, change the current intensity of the first electromagnetic coil to completely align the first alignment hole group of the first magnetic rotor with the first fixed hole group of the stator, and at the same time completely align the second alignment hole group of the first magnetic rotor with the second fixed hole group of the stator, so as to change the offset amplitude of the first magnetic rotor, and further effectively control the refrigerant amounts entering each flow path of the fin heat exchanger.

[0071] When P 压When the frequency is less than 60 Hz, the energization duration and phase of the first electromagnetic coil are changed so that the first magnetic rotor deviates per second for a unit time of movement to be consistent with the compressor frequency, thereby changing the deviation residence time of the first magnetic rotor, and further controlling the amount of refrigerant flowing into each flow path of the fin heat exchanger.

[0072] When P 压 ≥ 60 Hz, the energization duration and phase of the first electromagnetic coil are changed so that the first magnetic rotor deviates per 1.5 seconds for a unit time of movement to be consistent with the compressor frequency, thereby changing the deviation residence time of the first magnetic rotor, and further controlling the amount of refrigerant flowing into each flow path of the fin heat exchanger.

[0073] In a further preferred embodiment of the present invention, the amount of refrigerant currently required by the fin heat exchanger is judged according to the load state of the air-conditioning system, and the amount of refrigerant in the diversion holes in the diverter is controlled according to the amount of refrigerant currently required by the fin heat exchanger as follows:

[0074] When the air-conditioning system is in the first load state, the current parameter of the second electromagnetic coil is adjusted according to the set current parameter, so that all the third alignment hole groups of the second magnetic rotor are misaligned with the second fixed hole groups of the stator, thereby cutting off the refrigerant supply to the second diversion holes in the diverter;

[0075] When the air-conditioning system is in the second load state, the current parameter of the second electromagnetic coil is controlled to be consistent with the current parameter of the first electromagnetic coil.

[0076] Such a design can effectively adjust the distribution of the refrigerant according to the load state of the air-conditioning system, realizing more refined control. In the first load state, by completely misaligning the third alignment hole groups of the second magnetic rotor and the second fixed hole groups of the stator, it can be ensured that the refrigerant supply to the second diversion holes is completely cut off, avoiding unnecessary refrigerant loss and improving energy efficiency. And in the second load state, maintaining the consistency of the current parameters of the second electromagnetic coil and the first electromagnetic coil can ensure the coordination of the offset movements of the two magnetic rotors, further realizing the precise control of the refrigerant flow rate. Such a design not only improves the operating efficiency of the air-conditioning system, but also enhances its ability to adapt to different load states, providing a more comfortable use experience for users.

[0077] In a further preferred embodiment of the present invention, it is judged whether the air-conditioning system is in the first load state or the second load state according to the current ambient temperature, the current compressor operating frequency and the current outlet water temperature of the plate heat exchanger of the air-conditioning system.

[0078] Designed in this way, considering multiple factors such as ambient temperature, compressor operating frequency, and the outlet water temperature of the plate heat exchanger, the system can judge its load status in real time and adjust the current parameters of the second electromagnetic coil accordingly, so as to achieve precise control of the refrigerant quantity. This design helps to maintain the stability of the internal pressure of the air-conditioning system, avoid the adverse effects caused by too high or too low pressure on the system, further extend the service life of the air-conditioning system, and improve the overall operating efficiency.

[0079] As Figure 9 shown, it is judged whether the air-conditioning system is in the defrost mode; if so, the current parameters of the second electromagnetic coil are adjusted according to the first set current parameters, so that the third alignment hole group of the second magnetic rotor is completely aligned with the second fixed hole group of the stator, thereby ensuring that the refrigerant can smoothly enter the edge laminar flow path of the fin heat exchanger; if not, the outlet water temperature T 出水 of the plate heat exchanger and the current ambient temperature T 环 of the air-conditioning system are detected.

[0080] It is judged whether T 环 ≤ 10°C and T 出水 ≥ 40°C; if so, the current parameters of the second electromagnetic coil are made consistent with those of the first electromagnetic coil to ensure the synchronous movement of the second magnetic rotor and the first magnetic rotor. If not, the current operating frequency P 压 of the compressor and the maximum frequency P 最大 of the compressor in the current ambient temperature range are detected.

[0081] It is judged whether P 压 / P 最大 ≥ 50%; if so, the current parameters of the second electromagnetic coil are made consistent with those of the first electromagnetic coil to ensure the synchronous movement of the second magnetic rotor and the first magnetic rotor. If not, the outlet water temperature T 出水 of the plate heat exchanger and the maximum outlet water temperature T 最大 in the current ambient temperature range are detected.

[0082] It is judged whether T 出水 / T 最大 ≥ 95%; if so, the current parameters of the second electromagnetic coil are made consistent with those of the first electromagnetic coil to ensure the synchronous movement of the second magnetic rotor and the first magnetic rotor. If not, the current ambient temperature T 环 of the air-conditioning system is continuously detected.

[0083] It is judged whether T 环≥25°C; if yes, make the current parameter of the second electromagnetic coil consistent with that of the first electromagnetic coil to ensure the synchronous movement of the second magnetic rotor and the first magnetic rotor. If no, it is determined that the air-conditioning system is in the first load state, and then adjust the second electromagnetic coil according to the second set current parameter to make the third alignment hole group of the second magnetic rotor completely misaligned with the second fixed hole group of the stator, thereby blocking the refrigerant from entering the edge laminar flow path of the fin heat exchanger.

[0084] It should be clear that the control process of the first magnetic rotor and the second magnetic rotor in the present invention is only effective in the heating mode. Among them, the first magnetic rotor can be used to control the refrigerant volume of each flow path of the fin heat exchanger, while the second magnetic rotor works in cooperation with the first magnetic rotor and the stator to further control the refrigerant volume of the edge laminar flow path of the fin heat exchanger. Usually, the fan is located in the middle position of the fin heat exchanger. When it operates, the air volume at the middle position of the fin heat exchanger is much larger than that at the edge position, which results in the refrigerant demand at the edge position of the fin heat exchanger being much lower than that at the middle position. By reasonably controlling the refrigerant volume entering different positions of the fin heat exchanger, the efficient utilization of the fin heat exchanger can be achieved. In addition, when the air-conditioning system is operating at a partial load, the edge laminar flow path of the fin heat exchanger can also be closed by controlling the second magnetic rotor, and only the middle laminar flow path is used. This not only improves the utilization efficiency of the fin heat exchanger but also reduces the frosting and defrosting problems of the bottom fin heat exchanger in a low-temperature and high-humidity environment.

[0085] In the description of the present invention, it should be understood that unless otherwise clearly specified and limited, when an element is referred to as "fixed to" or "disposed on" another element, it can be directly on the other element or indirectly on the other element. When an element is referred to as "connected to" another element, it can be directly connected to the other element or indirectly connected to the other element.

[0086] In addition, the orientation or positional relationship indicated by terms such as "center", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation to the present invention.

[0087] In addition, the terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, "a plurality" means two or more unless otherwise clearly and specifically defined.

[0088] In addition, the terms "installed", "connected", and "coupled" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two components or the interaction relationship between two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0089] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent replacements, and improvements made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A shunt, applied to an air conditioning system, characterized in that A flow divider is internally formed with a flow dividing chamber, a first flow dividing hole, and a second flow dividing hole. The flow dividing chamber is connected to a throttling element through a liquid inlet pipe. The first flow dividing hole is connected to the middle laminar flow path of a fin heat exchanger through a capillary tube. The second flow dividing hole is connected to the edge laminar flow path of the fin heat exchanger through a capillary tube. A flow dividing cone is provided in the flow dividing chamber. The flow dividing cone divides the flow dividing chamber into a first flow dividing sub-chamber communicating with the first flow dividing hole and a second flow dividing sub-chamber communicating with the second flow dividing hole, and the volume of the first flow dividing sub-chamber is larger than that of the second flow dividing sub-chamber.

2. The diverter according to claim 1, characterized in that, A first electromagnetic coil is provided outside the flow divider. A first magnetic rotor and a stator are provided on the flow dividing cone. The first magnetic rotor has a first alignment hole group corresponding to the first flow dividing sub-chamber and a second alignment hole group corresponding to the second flow dividing sub-chamber. The stator has a first fixing hole group corresponding to the first flow dividing sub-chamber and a second fixing hole group corresponding to the second flow dividing sub-chamber. The first magnetic rotor rotates by electromagnetic force when the first electromagnetic coil is energized, changing the alignment state between the first alignment hole group and the first fixing hole group and between the second alignment hole group and the second fixing hole group, so as to adjust the refrigerant amount of the first flow dividing hole and the second flow dividing hole.

3. The diverter according to claim 2, characterized in that, A second electromagnetic coil is provided outside the flow divider. A rotor installation groove is formed in the area of the stator located in the second flow dividing sub-chamber. A second magnetic rotor is rotatably installed in the rotor installation groove. The second magnetic rotor has a third alignment hole group corresponding to the second flow dividing sub-chamber. The second magnetic rotor rotates by electromagnetic force when the second electromagnetic coil is energized, changing the alignment state between the third alignment hole group and the second fixing hole group, so as to adjust the refrigerant amount of the second flow dividing hole.

4. The diverter according to claim 2, characterized in that, A pressure relief pipeline for communicating the second flow dividing sub-chamber with a gas-liquid separator is provided outside the flow divider. A pressure regulating elastic element for balancing the internal pressure of the gas-liquid separator is provided in the pressure relief pipeline.

5. The diverter according to claim 3, characterized in that, Sealing elements are provided between the first magnetic rotor and the stator and between the second magnetic rotor and the stator.

6. An air conditioning system, comprising a water circulation loop and a refrigerant circulation loop. A compressor, a four-way reversing valve, a fin heat exchanger, a throttling element and a plate heat exchanger are provided on the refrigerant circulation loop, and it is characterized in that, The refrigerant circulation loop is further provided with a flow divider as described in any one of claims 1-5.

7. The air conditioning system according to claim 6, characterized in that, The refrigerant circulation loop is further provided with a gas-liquid separator and a commutation assembly. The commutation assembly includes a first three-way commutation valve and a second three-way commutation valve sequentially arranged between the throttling element and the flow divider. The inlet of the gas-liquid separator is communicated with the first three-way commutation valve. The liquid outlet of the gas-liquid separator is communicated with the second three-way commutation valve. The gas outlet of the gas-liquid separator is respectively communicated with the enthalpy-increasing port of the compressor and the pressure relief pipeline of the flow divider.

8. A shunt control method, characterized in that, Applied to the air-conditioning system as described in claim 6 or 7, the flow dividing control method includes: When the air-conditioning system is in the heating mode, determine the current required refrigerant amount of the fin heat exchanger, and control the refrigerant amount of the flow dividing holes in the flow divider according to the current required refrigerant amount of the fin heat exchanger.

9. The flow control method according to claim 8, characterized in that, The required amount of refrigerant for the fin heat exchanger currently is determined according to the current ambient temperature and the current compressor operating frequency of the air conditioning system; controlling the refrigerant amount in the shunt holes in the diverter according to the required amount of refrigerant for the fin heat exchanger currently is as follows: According to the temperature range where the current ambient temperature is located and the frequency range where the current compressor operating frequency is located, adjust the current parameter of the first electromagnetic coil, so as to control the refrigerant amounts in the first shunt hole and the second shunt hole in the diverter.

10. The shunt control method according to claim 9, wherein, The required amount of refrigerant for the fin heat exchanger currently is determined according to the load state of the air conditioning system, and controlling the refrigerant amount in the shunt holes in the diverter according to the required amount of refrigerant for the fin heat exchanger currently is as follows: When the air conditioning system is in the first load state, adjust the current parameter of the second electromagnetic coil according to the set current parameter, so that all the third alignment hole groups of the second magnetic rotor are misaligned with the second fixed hole groups of the stator, thereby cutting off the refrigerant supply to the second shunt hole in the diverter; When the air conditioning system is in the second load state, control the current parameter of the second electromagnetic coil to be consistent with the current parameter of the first electromagnetic coil.

11. The flow control method according to claim 10, wherein Judge whether the air conditioning system is in the first load state or the second load state according to the current ambient temperature, the current compressor operating frequency and the current outlet water temperature of the plate heat exchanger of the air conditioning system.

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