Heat exchangers, flow path control methods for heat exchangers, storage media, and household appliances

Abstract

This invention discloses a heat exchanger, a flow path control method for the heat exchanger, a storage medium, and a household appliance. The heat exchanger includes an inlet pipe, an outlet pipe, a gas-liquid separator, a separable module, a variable flow path module, and a throttling device. The gas end of the gas-liquid separator is connected to a first pipe. One end of the first heat exchange tube group of the variable flow path module is connected to another liquid end via a fourth pipe. Both ends of the second heat exchange tube group are connected to another liquid end and the outlet pipe via fifth and sixth pipes, respectively. A first control valve is located on the fifth pipe. The first end of a switching valve group is connected to the outlet pipe, the second end is connected to the end of the first heat exchange tube group away from the other liquid end, and the third end is connected to the end of the second heat exchange tube group near the first control valve. A throttling device is located on either the first or second pipe, and is situated between the gas-liquid separator and the other end of the separable module. This invention enables switching between different numbers of heat exchange flow paths depending on different load changes.

Description

Technical Field

[0001] This invention relates to the field of household appliance technology, and in particular to a heat exchanger, a flow path control method for the heat exchanger, a storage medium, and a household appliance using the heat exchanger. Background Technology

[0002] The optimal flow path for indoor and outdoor heat exchangers in air conditioners or water heaters differs depending on their operating frequency. When operating under low load or low frequency conditions, the pressure loss is small, requiring fewer branch paths to increase refrigerant velocity and thus the heat transfer coefficient. However, when operating under high load or medium-to-high frequency conditions, the decrease in logarithmic mean temperature difference due to pressure loss has a more significant impact on heat transfer than the effect of flow velocity on the heat transfer coefficient; in this case, more branch paths are needed to maximize heat transfer.

[0003] Existing technologies include heat exchangers that can change flow paths for different high-frequency and low-frequency modes. However, these existing heat exchangers are highly specific, have low modularity, and are difficult to adapt to large-capacity air conditioners with large heat exchange areas. When the flow path is changed, it is limited to adding or removing a few flow paths, resulting in limited options and weak adaptability to load changes. At the same time, in a single heat exchange process, the gaseous (liquid) refrigerant still degrades the evaporation (condensation) heat transfer coefficient, limiting the performance of the heat exchanger and heat pump (hot air blower, heat pump water heater). Summary of the Invention

[0004] The main objective of this invention is to propose a heat exchanger that aims to improve the problem of deteriorated heat transfer coefficient of gaseous refrigerants or the problem of deteriorated heat transfer coefficient of liquid refrigerants, and can improve the heat exchange effect under different load conditions.

[0005] To achieve the above objectives, the heat exchanger proposed in this invention includes an inlet pipe;

[0006] Outflow tube;

[0007] A gas-liquid separator, comprising a gas end and two liquid ends, wherein the gas end is connected to a first pipeline;

[0008] A separable module is disposed between the gas-liquid separator and the inlet pipe or outlet pipe;

[0009] A variable flow path module, comprising a first heat exchange tube group, a second heat exchange tube group, a first control valve and a switching valve group, wherein one end of the first heat exchange tube group is connected to the other liquid end through a fourth pipeline;

[0010] One end of the second heat exchange tube assembly is connected to the other liquid end through the fifth pipe, and the other end is connected to the outflow pipe or inflow pipe through the sixth pipe. The first control valve is located in the fifth pipe or the sixth pipe.

[0011] The switching valve assembly has a first end, a second end, and a third end. The first end is connected to the outlet pipe or the fourth pipeline. The second end is connected to the end of the first heat exchange tube assembly that is away from or near the other liquid end. The third end is connected to the end of the second heat exchange tube assembly that is near the first control valve.

[0012] Throttling device;

[0013] When the end of the first pipeline away from the gas end is connected to the outflow pipe, one end of the separable module is connected to the liquid end through the second pipeline, and the other end is connected to the inflow pipe through the third pipeline, and the throttling device is provided in the first pipeline;

[0014] Alternatively, when the end of the first pipeline away from the gas end is connected to one end of the separable module, the liquid end is connected to the inflow pipe through the second pipeline, and the other end of the separable module is connected to the second pipeline; the throttling element is provided in the second pipeline and is located between the gas-liquid separator and the other end of the separable module.

[0015] Optionally, the throttling element is an electronic expansion valve or a capillary tube;

[0016] Alternatively, the throttling element may be a one-way valve, wherein the one-way valve is directed from one of the liquid ends to the outlet pipe, or the one-way valve is directed from the gas end to the outlet pipe.

[0017] Optionally, the separable module includes a plurality of first separable flow paths and second separable flow paths, wherein the plurality of first separable flow paths are arranged in parallel, and the second separable flow paths are arranged in series with the first separable flow paths, wherein the number of flow paths of the first separable flow paths is less than the total number of flow paths of the variable flow path module.

[0018] Optionally, the switching valve assembly is a three-way valve.

[0019] Optionally, both the first heat exchange tube group and the second heat exchange tube group are provided with at least two, with at least two first heat exchange tube groups and at least two second heat exchange tube groups connected in parallel;

[0020] And / or, the first heat exchanger tube group includes two first heat exchanger lines arranged in parallel, and the second heat exchanger tube group includes at least two second heat exchanger lines arranged in parallel.

[0021] Optionally, the switching valve group is provided such that the end of each first heat exchange tube group near the outlet pipe is connected to the second end; and the end of each second heat exchange tube group near the first control valve is connected to the third end.

[0022] Optionally, the heat exchanger further includes a common heat exchange tube assembly, one end of which is connected to the fourth pipeline and the other end of which is connected to the sixth pipeline.

[0023] The present invention also provides a flow path control method for a heat exchanger, wherein the heat exchanger is any of the heat exchangers described above, and the first pipeline is connected to the outlet pipe at one end away from the gas end, one end of the separable module is connected to the liquid end through a second pipeline, and the other end is connected to the inlet pipe through a third pipeline, the throttling element is provided in the first pipeline, and the heat exchanger is used as an evaporator;

[0024] Alternatively, when the end of the first pipeline away from the gas end is connected to one end of the separable module, and the liquid end is connected to the inflow pipe through the second pipeline, and the other end of the separable module is connected to the second pipeline; the throttling element is provided in the second pipeline and is located between the gas-liquid separator and the other end of the separable module, and the heat exchanger is used as a condenser;

[0025] The flow path control method for the heat exchanger includes:

[0026] Control the throttling element to conduct and obtain the operating status of the heat exchanger;

[0027] When the heat exchanger is in the first load operating state, the first control valve is opened and the first end of the switching valve group is connected to the second end.

[0028] When the heat exchanger is in the second load operating state, the first control valve is controlled to close, and the third end of the switching valve group is controlled to be connected to the second end; wherein, the first load is greater than the second load.

[0029] Optionally, the heat exchanger is applied to the outdoor unit of a heating system, the outdoor unit of the heating system further includes a compressor, the compressor is connected to the heat exchanger, and the heat exchanger acts as an evaporator; the step of controlling the throttling element to conduct and obtaining the operating status of the heat exchanger includes:

[0030] The outdoor temperature is T3 and the compressor frequency is F1.

[0031] When the outdoor temperature T3 is less than the first preset value a; or when the outdoor temperature is less than the second preset value b and greater than the first preset value a, and the compressor frequency F1 ≥ k*(Fmax+Fmin); or when the outdoor temperature is greater than the second preset value b, and the compressor frequency F1 ≥ m*(Fmax+Fmin), the heating system is set to the first load mode.

[0032] When the outdoor temperature T3 is greater than the first preset value a and less than or equal to the second preset value b, and the compressor frequency F1 < k*(Fmax+Fmin); or, when the outdoor temperature T3 is greater than the second preset value b, and the compressor frequency F1 < m*(Fmax+Fmin), the heating system is set to the second load mode.

[0033] Where b is greater than a, k ranges from 1 / 3 to 5 / 8, m ranges from 5 / 8 to 7 / 8, Fmax is the maximum operating frequency of the compressor, Fmin is the minimum operating frequency of the compressor, the first preset value a ranges from 0℃ to 6℃, and the second preset value b ranges from 6℃ to 20℃.

[0034] Optionally, when the throttling element is an electronic expansion valve, it further includes:

[0035] Obtain the target operating frequency Fr of the heating system;

[0036] Determine the magnitude of the target operating frequency Fr and the third preset value c;

[0037] If Fr≤c, the initial opening of the electronic expansion valve is set to the first opening A, and the holding time is t1; if Fr>c, the initial opening of the electronic expansion valve is set to the second opening B, and the holding time is t2.

[0038] Where c = l*(Fmax + Fmin), l ranges from 0.45 to 0.75, A is less than B, Fmax is the maximum operating frequency of the compressor, and Fmin is the minimum operating frequency of the compressor;

[0039] After initialization, the coil temperature of the heat exchanger and the suction temperature of the compressor are checked every first preset time interval;

[0040] Determine the difference between the coil temperature and the intake temperature, and adjust the opening value of the electronic expansion valve according to the magnitude of the difference.

[0041] Optionally, the step of determining the difference between the coil temperature and the suction temperature, and adjusting the opening adjustment value of the electronic expansion valve according to the magnitude of the difference, specifically includes:

[0042] Let the difference be ΔT. If ΔT < -1.5, then the opening degree of the electronic expansion valve is increased by a first opening degree value n; if -1.5 < ΔT ≤ -0.5, then the opening degree of the electronic expansion valve is increased by a second opening degree value E.

[0043] If -0.5 < ΔT ≤ 0.5, then the opening degree of the electronic expansion valve remains unchanged;

[0044] If 0.5 < ΔT ≤ 1.5, then the opening degree of the electronic expansion valve is reduced by the third opening value -(E+1);

[0045] If ΔT > 1.5, then the opening degree of the electronic expansion valve is reduced by the fourth opening degree value -(F+1);

[0046] Where F > E.

[0047] Optionally, the first preset time ranges from 30s to 300s, E ranges from 2P to 15P, and F ranges from 4P to 30P;

[0048] And / or, the range of A is 20P to 100P, the range of t1 is 2min to 15min, the range of B is 50P to 150P, and the range of t2 is 1min to 15min.

[0049] Optionally, the heat exchanger is applied to the outdoor unit of a refrigeration system, and the outdoor unit of the heating system further includes a compressor, the compressor being connected to the heat exchanger, and the heat exchanger acting as a condenser; the step of controlling the throttling element to conduct and obtaining the operating status of the heat exchanger includes:

[0050] Obtain the outdoor temperature T4 and compressor frequency F2;

[0051] When the outdoor temperature T4 is greater than the fourth preset value d; or when the outdoor temperature is less than the fourth preset value d and greater than the fifth preset value g, and the compressor frequency F2 ≥ k*(Fmax+Fmin); or when the outdoor temperature is less than the fifth preset value g, and the compressor frequency F2 ≥ m*(Fmax+Fmin), the refrigeration system is set to the first load mode.

[0052] When the outdoor temperature T4 is less than the fourth preset value d and greater than or equal to the fifth preset value g, and the compressor frequency F2 < k*(Fmax+Fmin); or, when the outdoor temperature is less than the fifth preset value g, and the compressor frequency F2 < m*(Fmax+Fmin), the refrigeration system is set to the second load mode.

[0053] Where d is greater than g, k ranges from 1 / 3 to 5 / 8, m ranges from 5 / 8 to 7 / 8, Fmax is the maximum operating frequency of the compressor, and Fmin is the minimum operating frequency of the compressor;

[0054] The fourth preset value d ranges from 26℃ to 35℃, and the fifth preset value g ranges from 10℃ to 25℃.

[0055] The present invention also provides a storage medium storing a flow path control program for a heat exchanger, wherein when the flow path control program for the heat exchanger is executed by a processor, the flow path control program for the heat exchanger implements the steps of the above-described flow path control method for the heat exchanger.

[0056] The present invention also proposes a household appliance comprising any of the heat exchangers described above.

[0057] Optionally, the household appliance is a single-function air conditioner or a water heater.

[0058] In this invention, when the heat exchanger is used as an evaporator, the liquid phase change working fluid enters from the inlet pipe. It first undergoes preliminary evaporation through a separable module, and then enters a gas-liquid separator through the liquid end for gas-liquid separation. The separated gas enters the first pipeline through the gas end, and after passing through a throttling device, it can enter the outlet pipe. The liquid part enters the variable flow path module through another liquid end. In this way, the gaseous working fluid can be separated in time at the point where heat exchange is in the initial stage and the heat transfer coefficient deteriorates, resulting in a higher heat transfer coefficient for the subsequent liquid working fluid and effectively enhancing the heating effect of the heat exchanger. When the heat exchanger is used as a condenser, the gaseous phase change working fluid enters through the inlet pipe. It first undergoes most of the condensation and heat exchange through the variable flow path module, and then enters the gas-liquid separator through the liquid end for gas-liquid separation. The separated gas enters the first pipeline through the gas end, and then undergoes condensation and heat exchange again through the separable module. The liquid part mixes with the working fluid after the second condensation and heat exchange through the second pipeline and flows out through the outlet pipe. In this way, the liquid working fluid can be separated in time at the point where the heat transfer coefficient deteriorates, resulting in a higher heat transfer coefficient for the subsequent gaseous working fluid and effectively enhancing the cooling effect of the heat exchanger.

[0059] In the variable flow path module, the heat exchange can be adjusted according to the state of the heat exchanger. When in a medium-to-high frequency state, by opening the first control valve and connecting the first and second ends, the phase change working fluid flowing from the liquid end flows to the first and second heat exchange tube groups respectively. The phase change working fluid passing through the first heat exchange tube group flows to the first and second ends, while the phase change working fluid from the second heat exchange tube group flows to the sixth pipe. The phase change working fluid flowing from the first end and from the sixth pipe merge into the outlet pipe and then flows out. Alternatively, the gaseous working fluid enters the gas-liquid separator via the first heat exchange tube group and the switching valve group, and the first control valve and the second heat exchange tube group respectively. In this state, the number of flow paths for the phase change working fluid is the sum of the first and second heat exchange tube groups, i.e., a larger number of flow paths, thereby improving the heat exchange capacity in medium-to-high frequency states and achieving better heat exchange performance. When the heat exchanger is in a low-frequency state, by closing the first control valve and connecting the second and third ends, the phase change working fluid flows along the fourth pipeline to the first heat exchange tube group, then through the switching valve group to the second heat exchange tube group, and finally through the sixth pipeline to the outlet pipe; alternatively, the working fluid enters the second heat exchange tube group after heat exchange via the first heat exchange tube group and the switching valve group, and then flows into the gas-liquid separator. In this state, the first and second heat exchange tube groups are connected in series to form a single flow path, thereby reducing the number of flow paths and increasing the flow rate of the phase change working fluid in the low-frequency state, thus increasing the heat transfer coefficient and achieving a better heat exchange effect. The heat exchanger in this invention can improve the heat exchange effect in both medium- and high-frequency states and low-frequency states. Attached Figure Description

[0060] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0061] Figure 1 This is a schematic diagram of the flow path structure in one embodiment of the present invention when the heat exchanger is used as an evaporator and is in a medium-high frequency operation state (i.e., the first load operation state).

[0062] Figure 2 for Figure 1 The diagram shows the flow path structure when the heat exchanger is used as an evaporator and is in a low-frequency operation state (i.e., the second load operation state).

[0063] Figure 3 This is a schematic diagram of the flow path structure of another embodiment of the heat exchanger of the present invention when it is used as an evaporator;

[0064] Figure 4This is a schematic diagram of the flow path structure of another embodiment of the heat exchanger of the present invention when it is used as an evaporator;

[0065] Figure 5 This is a schematic diagram of the structure of the heat exchanger in the household appliance of the present invention, which is in a medium-to-high frequency operating state when it is used as an evaporator.

[0066] Figure 6 for Figure 5 The diagram shows the structure of a heat exchanger in a household appliance operating at low frequency when it functions as an evaporator.

[0067] Figure 7 This is a schematic diagram of the flow path structure of one embodiment of the heat exchanger of the present invention when it is used as a condenser.

[0068] Figure 8 This is a schematic diagram of the flow path structure of another embodiment of the heat exchanger of the present invention when it is used as a condenser;

[0069] Figure 9 This is a schematic diagram of the flow path structure of another embodiment of the heat exchanger of the present invention when it is used as a condenser;

[0070] Figure 10 This is a schematic diagram of the heat exchanger in the household appliance of the present invention, which operates at a medium-to-high frequency as a condenser.

[0071] Figure 11 for Figure 5 The diagram shows the structure of a heat exchanger in a household appliance operating at low frequency when it functions as a condenser.

[0072] Explanation of icon numbers:

[0073] label name label name 100 Inflow pipe 620 Second pipeline 200 Outflow tube 630 Third pipeline 300 First heat exchanger tube assembly 640 Fourth pipeline 301 First heat exchange pipe 650 Fifth pipeline 400 Second heat exchanger tube assembly 660 Sixth pipeline 401 Second heat exchange pipe 700 gas-liquid separator 510 First control valve 701 Gas end 520 Switching valve group 702，703 Liquid end 521 First end 800 Detachable module 522 Second end 801 First separation flow path 523 Third end 802 Second separation flow path 530 Throttling device 900 Common heat exchanger tube assemblies 610 First pipeline 2000 compressor

[0074] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0075] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0076] It should be noted that if the embodiments of the present invention involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a certain specific posture (as shown in the figure). If the specific posture changes, the directional indicators will also change accordingly.

[0077] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. If the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0078] This invention proposes a heat exchanger.

[0079] In the embodiments of the present invention, please refer to the reference. Figure 1 and Figure 2 The heat exchanger includes an inlet pipe 100, an outlet pipe 200, a gas-liquid separator 700, a separable module 800, a variable flow path module, and a throttling device 530. The gas-liquid separator 700 includes a gas end 701 and two liquid ends (702, 703). The gas end 701 is connected to a first pipe 610. The separable module 800 is disposed between the gas-liquid separator 700 and the inlet pipe 100 or the outlet pipe 200.

[0080] The variable flow path module includes a first heat exchange tube group 300, a second heat exchange tube group 400, a first control valve 510, and a switching valve group 520. One end of the first heat exchange tube group 300 is connected to the other liquid end 703 through a fourth pipe 640. One end of the second heat exchange tube group 400 is connected to the other liquid end 703 through a fifth pipe 650, and the other end is connected to the outlet pipe 200 or outlet pipe 200 through a sixth pipe 660. The first control valve 510 is located in the fifth pipe 650 or the sixth pipe 660. The switching valve group 520 has a first end 521, a second end 522, and a third end 523. The first end 521 is connected to the outlet pipe 200 or the fourth pipe 640. The second end 522 is connected to the end of the first heat exchange tube group 300 that is away from or close to the other liquid end 703. The third end 523 is connected to the end of the second heat exchange tube group 400 that is close to the first control valve 510.

[0081] When the end of the first pipeline 610 away from the gas end 701 is connected to the outflow pipe 200, one end of the separable module 800 is connected to the liquid end 702 through the second pipeline 620, and the other end is connected to the inflow pipe 100 through the third pipeline 630, and the throttling device 530 is provided in the first pipeline 610.

[0082] Alternatively, when the end of the first pipeline 610 away from the gas end 701 is connected to one end of the separable module 800, the liquid end 702 is connected to the inflow pipe 100 through the second pipeline 620, and the other end of the separable module 800 is connected to the second pipeline 620; the throttling element 530 is provided in the second pipeline 620 and is located between the gas-liquid separator 700 and the other end of the separable module 800.

[0083] It should be noted that the heat exchanger in the technical solution of this invention can be used as an evaporator or a condenser, and is suitable for single-mode household appliances, such as being used as an evaporator in the outdoor unit of a single-cooling air conditioner, or as a condenser in the outdoor unit of a single-heating air conditioner. It is understood that when the heat exchanger is adapted to a single-mode air conditioner, it can only allow the phase change working fluid to flow from the inlet pipe 100 to the outlet pipe 200, and not from the outlet pipe 200 to the inlet pipe 100.

[0084] For the refrigerant evaporation process inside a circular tube, the refrigerant flow pattern, with increasing dryness, is as follows: single-phase liquid flow, bubbly flow, slug flow, annular flow, mist flow, and single-phase gas flow. In the bubbly, slug, and annular flow regions, as the refrigerant dryness increases, the heat transfer coefficient on the inner surface of the tube increases due to the increase in the average flow velocity inside the tube. However, in the mist flow region, due to excessive refrigerant dryness, the liquid film on the inner surface of the tube is destroyed, leading to deteriorated heat transfer and a sharp decrease in the heat transfer coefficient, which greatly affects the heat exchange performance of the evaporator. Applying gas bypass evaporation technology can effectively reduce the area of ​​the mist flow region, thereby increasing the effective heat exchange area of ​​the heat exchanger. In the technical solution of this invention, the phase separation evaporator technology can reduce the average flow velocity of the refrigerant, thereby reducing the refrigerant-side resistance loss and improving the overall performance of the heat exchanger. Therefore, when the heat exchanger is in evaporation mode, a portion of the phase change refrigerant can be evaporated first through the separable module 800. Then, at the point where heat exchange efficiency deteriorates, the gaseous refrigerant after heat exchange is separated by the gas-liquid separator 700. The remaining liquid refrigerant continues to evaporate, thereby improving the problem of deteriorated evaporation heat transfer coefficient of the gaseous refrigerant and improving heat exchange effect and efficiency. That is, during heating, gaseous refrigerant can be extracted to improve the evaporation heat transfer coefficient, thereby improving the overall heat exchange efficiency. At the same time, the heat exchanger can achieve the effect of switching different numbers of flow paths when in different operating states.

[0085] Similarly, for the refrigerant condensation process inside a circular tube, the refrigerant flow pattern decreases with decreasing dryness as follows: single-phase gas flow, mist flow, annular flow, slug flow, bubbly flow, and single-phase liquid flow. As the condensation process progresses and the refrigerant dryness decreases, liquid refrigerant accumulates inside the heat exchanger tubes, hindering the condensation of the gaseous refrigerant, thus worsening the condensation heat transfer coefficient and increasing the flow resistance loss of the refrigerant inside the tubes. Adding a separable module to the lower part of the heat exchanger enables liquid-liquid separation and condensation. The liquid refrigerant first condenses in the upper variable flow path module, and then, at the location where heat exchange efficiency deteriorates, the gaseous refrigerant is removed and further condensed into liquid, before being combined with the original liquid refrigerant for subcooling, thereby improving the heat exchange efficiency of the refrigeration heat exchanger. In other words, during heating, gaseous refrigerant can be extracted to increase the evaporation heat transfer coefficient, thereby improving the overall heat exchange efficiency of the unit.

[0086] It is understandable that when the heat exchanger is used as an evaporator or a condenser, and the outdoor unit is used to connect multiple indoor units, the indoor unit is in a medium-to-high frequency operating state, that is, the heat exchanger in the outdoor unit is in a medium-to-high frequency operating state (i.e., a high load state). Compared with the influence of flow rate on the heat transfer coefficient, the decrease in logarithmic mean temperature difference caused by pressure loss has a dominant influence on the heat transfer. At this time, we hope to use more flow paths to increase the heat transfer. Therefore, when using the heat exchanger in this invention, the number of heat exchange flow paths can be increased.

[0087] Please refer to Figure 1 Specifically, when the heat exchanger is an evaporator and is operating at medium to high frequency, by opening the first control valve 510, the phase change working fluid will first be divided into two streams for flow, and the first heat exchange tube group 300 is connected to the other liquid end 703. One stream will flow through the fourth pipe 640 and the first heat exchange tube group 300 in sequence; the other stream will flow through the first control valve 510, the fifth pipe 650 and the second heat exchange tube group 400. Next, by connecting the first end 521 of the switching valve assembly 520 to the second end 522, with the first end 521 connected to the outlet pipe 200, and the second heat exchange tube assembly 400 connected to the outlet pipe 200 via the sixth pipe 660, the phase change working fluid after heat exchange in the first heat exchange tube assembly 300 will sequentially enter the outlet pipe 200 via the second end 522 and the first end 521; simultaneously, the phase change working fluid after heat exchange in the second heat exchange tube assembly 400 will sequentially enter the sixth pipe 660 and the outlet pipe 200, and flow out from the outlet pipe 200. Please refer to... Figure 7When the heat exchanger is a condenser and is operating at medium to high frequency, by opening the first control valve 510 and connecting the first end 521 and the second end 522 of the switching valve group 520, the phase change working fluid will first be divided into two streams. One stream will flow through the first heat exchange tube group 300, the switching valve group 520 and the fourth pipe 640 in sequence, and enter the other liquid end 703. The other stream will flow through the sixth pipe 660, the first control valve 510, the second heat exchange tube group 400 and the fifth pipe 650, and merge with the first stream into the other liquid end 703.

[0088] Therefore, when the heat exchanger is in a medium-to-high frequency operating state, if both the first heat exchange tube group 300 and the second heat exchange tube group 400 have N units, the phase change working fluid can flow through 2N flow paths simultaneously.

[0089] When the heat exchanger functions as an evaporator or a condenser, and the outdoor unit is used to connect to a single indoor unit or a small number of indoor units, the indoor unit operates at a low frequency. This means the heat exchanger within the outdoor unit is also operating at a low frequency (i.e., under low load). In this case, the flow rate of the phase change medium has a more dominant effect on the heat transfer coefficient than the flow rate. Therefore, we aim to increase the heat transfer coefficient by using fewer flow paths. When using the heat exchanger of this invention, the number of heat transfer flow paths can be reduced, thereby increasing the flow rate of the phase change medium and thus increasing the heat transfer coefficient. Specifically, when the heat exchanger is an evaporator and operates at low frequency, by closing the first control valve 510, the phase change working fluid flows sequentially through the fourth pipe 640 and the first heat exchange tube group 300. Then, by connecting the second end 522 and the third end 523 of the switching valve group 520, the phase change working fluid after heat exchange in the first heat exchange tube group 300 flows sequentially through the second end 522 and the third end 523 into the second heat exchange tube group 400, and from the second heat exchange tube group 400 into the sixth pipe 660, finally flowing out from the outlet pipe 200. When the heat exchanger is a condenser and operates at low frequency, by closing the first control valve 510, the phase change working fluid flows through the first heat exchange tube group 300 and, through the second end 522 and the third end 523 of the switching valve group 520, enters the second heat exchange tube group 400 for further condensation, and then enters the other liquid end 703 through the fifth pipe 650. Therefore, when the heat exchanger is in a low-frequency operating state, if both the first heat exchange tube group 300 and the second heat exchange tube group 400 have N tubes, the phase change working fluid can flow through N main heat exchange channels simultaneously.

[0090] The technical solution of this invention, by simply adding the aforementioned first control valve 510 and switching valve group 520 to the heat exchanger, achieves different flow paths for the phase change working fluid in medium- and high-frequency operating states and low-frequency operating states. Furthermore, by controlling the first control valve 510 and switching valve group 520, it achieves the effect of having more flow paths in medium- and high-frequency operating states and fewer flow paths in low-frequency operating states, thus enabling the heat exchanger to have good heat exchange performance under different operating states, thereby improving the heat exchanger's adaptability to load changes. Simultaneously, the inclusion of the separable module 800 and the gas-liquid separator 700 further improves the problem of evaporative heat transfer coefficient deterioration of the liquid working fluid by the gaseous working fluid, or improves the problem of condensative heat transfer coefficient deterioration of the gaseous working fluid by the liquid working fluid, thereby improving heat exchange efficiency. Here, the first control valve 510 can be a one-way valve or a solenoid valve, without limitation. The first control valve 510 in the figure is a solenoid valve, which enables more precise control and can be used for switching between one-way cooling and one-way heating, making control simple and convenient. The throttling device 530 allows the gaseous working fluid to be appropriately depressurized and returned to the compressor 2000, thereby improving the protection of the compressor 2000 and extending its service life.

[0091] Furthermore, the first heat exchange tube group 300 and the second heat exchange tube group 400 in the heat exchanger of the present invention can both be modularized. That is, when a large heat exchange area is required under high load mode, the number of the first heat exchange tube group 300 and / or the second heat exchange tube group 400 can be increased by simply connecting them in parallel, without adding additional valves, so that different heat exchange flow paths can be achieved in different operating modes. Therefore, the heat exchanger of the present invention has strong modularity and versatility, can adapt to various different operating states, and can flexibly increase the number of the first heat exchange tube group 300 and / or the second heat exchange tube group 400.

[0092] In this invention, when the heat exchanger is used as an evaporator, the liquid phase change working fluid enters from the inlet pipe 100. It first undergoes preliminary evaporation through the separable module 800, and then enters the gas-liquid separator 700 through the liquid end 702 for gas-liquid separation. The separated gas enters the first pipeline 610 through the gas end 701, and after passing through the throttling device 530, it can enter the outlet pipe 200. The liquid part enters the variable flow path module through another liquid end 703. In this way, the gaseous working fluid can be separated in time at the point where the heat exchange is in the initial stage and the heat exchange coefficient deteriorates, so that the heat exchange coefficient of the subsequent liquid working fluid is higher, effectively enhancing the heating effect of the heat exchanger. When the heat exchanger is used as a condenser, the gaseous phase change working fluid enters through the inlet pipe 100. It first undergoes most of the condensation and heat exchange through the variable flow path module, and then enters the gas-liquid separator 700 through the liquid end 703 for gas-liquid separation. The separated gas enters the first pipe 610 through the gas end 701, and then undergoes condensation and heat exchange again through the separable module 800. The liquid part mixes with the working fluid after condensation and heat exchange again through the second pipe 620 and flows out through the outlet pipe. In this way, the liquid working fluid can be separated in time at the point where the heat transfer coefficient deteriorates, so that the heat transfer coefficient of the subsequent gaseous working fluid is higher, effectively enhancing the cooling effect of the heat exchanger.

[0093] In the variable flow path module, the flow path can be changed according to the state of the heat exchanger. When in the medium-high frequency state, by opening the first control valve 510 and connecting the first end 521 and the second end 522, the phase change working fluid flowing out from the liquid end 703 flows to the first heat exchange tube group 300 and the second heat exchange tube group 400 along the fourth pipe 640 and the fifth pipe 650, respectively. The phase change working fluid passing through the first heat exchange tube group 300 then flows to the first end 521 of the switching valve group 520, and the phase change working fluid of the second heat exchange tube group 400 then flows to the sixth pipe 660. The phase change working fluid flowing out from the first end 521 and the phase change working fluid flowing out from the sixth pipe 660 merge into the outlet pipe 200 and then flow out. Alternatively, the gaseous working fluid enters the gas-liquid separator 700 through the first heat exchange tube group 300 and the switching valve group 520, and the first control valve 510 and the second heat exchange tube group 400, respectively. In this state, the number of flow paths for the phase change working fluid is the sum of the first heat exchange tube group 300 and the second heat exchange tube group 400, meaning there are a relatively large number of flow paths. This increases the heat exchange capacity at medium and high frequencies, achieving a better heat exchange effect. When the heat exchanger is in a low-frequency state, by closing the first control valve 510 and connecting the second section and the third end, the phase change working fluid flows along the fourth pipe 640 to the first heat exchange tube group 300, and then flows through the second section and the third end 523 connected by the switching valve group 520, before flowing to the second heat exchange tube group 400, and finally through the sixth pipe 660 to the outlet pipe 200; alternatively, the working fluid enters the second heat exchange tube group after heat exchange via the first heat exchange tube group and the switching valve group, and then flows into the gas-liquid separator. In this state, the first heat exchange tube group 300 and the second heat exchange tube group 400 are connected in series to form a single flow path, thereby reducing the number of flow paths at low frequencies, increasing the flow rate of the phase change working fluid, and thus increasing the heat transfer coefficient, achieving a better heat exchange effect. The heat exchanger in the technical solution of this invention can improve the heat exchange effect under both medium and high frequency and low frequency conditions.

[0094] Please refer to Figure 1 and Figure 7 Optionally, the throttling element 530 is an electronic expansion valve or a capillary tube. Alternatively, the throttling element 530 is a one-way valve, wherein the one-way valve is open from the liquid end 702 to the outlet pipe 200, or the one-way valve is open from the gas end 701 to the outlet pipe 200.

[0095] In this embodiment, when the throttling element 530 is an electronic expansion valve, it is activated when the heat exchanger is used as an evaporator and adjusted to a suitable opening degree. This allows the gaseous working fluid separated from the gas-liquid separator 700 to be appropriately depressurized by the electronic expansion valve before entering the outlet pipe 200 and returning to the compressor 2000 for suction. This enables precise control for different load changes, improving control accuracy and further protecting the compressor 2000, extending its service life. When the heat exchanger is used as a condenser, the electronic expansion valve is installed on the second pipeline 620. The gas end 701 of the gas-liquid separator 700 is connected to one end of the separable module 800 through the first pipe 610. After gas-liquid separation of the working fluid, the gaseous working fluid undergoes heat exchange again through the separable module 800 and mixes with the liquid working fluid after being appropriately depressurized by the electronic expansion valve before flowing out from the outlet pipe 200. When the throttling element 530 is a capillary tube, the capillary tube is low in cost and easy to control, and there is no need to set up a control program for regulation, making it more suitable for stable low-load conditions.

[0096] Of course, the throttling element 530 can also be a one-way valve. When the heat exchanger is used as a condenser, the one-way valve is directed from the liquid end 702 to the outlet pipe 200. Alternatively, when the heat exchanger is used as a condenser, the one-way valve is directed from the gas end 701 to the outlet pipe 200, thereby achieving flow rate regulation of the corresponding working fluid and improving product performance.

[0097] Please continue to refer to Figure 1 and Figure 7 Optionally, the separable module 800 includes a plurality of first separable flow paths 801 and second separable flow paths 802, wherein the plurality of first separable flow paths are arranged in parallel, and the second separable flow paths 802 are arranged in series with the first separable flow paths 801, wherein the number of flow paths of the first separable flow paths 801 is less than the total number of flow paths of the variable flow path module.

[0098] To further improve heat exchange efficiency, in this embodiment, the separable module 800 includes several parallel first separation flow paths 801 and a second separation flow path 802 connected in series with them. When the heat exchanger is used as an evaporator, the working fluid flow rate is reduced by increasing the flow path. After heat exchange through the second separation flow path 802, it can be heat exchanged again through the first separation flow path 801. The gas-liquid mixed phase change working fluid enters the gas-liquid separator 700, so that part of the evaporated gas can be separated and enter the outlet pipe 200 from the throttling element 530. The remaining liquid part continues to enter the variable flow path module for further evaporation, thereby improving the location of heat exchange coefficient deterioration and timely separating gas to improve heat exchange efficiency. When the heat exchanger is used as a condenser, the phase change working fluid can be separated by the gas-liquid separator 700, and then flow through the first separation flow path 801 and the second separation flow path 802 for heat exchange before flowing to the outlet pipe 200. This can further improve the heat exchange efficiency and the heat exchange effect, and ensure that the phase change working fluid receives sufficient heat exchange, thereby improving the heat exchange efficiency.

[0099] As a module for improving the heat transfer coefficient at the deterioration point of the gas phase working fluid, the number of flow paths of the separable module 800 should not be too large. The total number of flow paths of the separable module 800 is set to be less than the maximum number of flow paths of the variable flow path module. For example, the separable module 800 includes two first separation flow paths 801, which is less than the maximum number of flow paths of 4 when the variable flow path module is set with two first heat exchange tube groups 300 and two second heat exchange tube groups 400.

[0100] Of course, based on the above reasons, the length of a single flow path in the separable module 800 should not be too large, and cannot exceed the length of a single flow path in the variable flow path module, which serves as the main heat exchange function. Conversely, its single flow path length should not be too small either, otherwise it will not effectively reduce the flow velocity and improve the heat transfer coefficient. Therefore, the single flow path length of the separable module 800 is 0.15 to 0.55 times that of the variable flow path module, for example, 0.15, 0.2, 0.3, 0.4, or 0.5 times, which allows it to work in conjunction with the variable flow path module to achieve better heat exchange performance. Here, the optional single flow path length of the separable module 800 is 0.5 times that of the variable flow path module.

[0101] Optionally, the switching valve assembly 520 is a three-way valve.

[0102] By selecting a three-way valve for the switching valve assembly 520, the entire heat exchanger can switch between different heat exchange flow paths under different operating conditions using only one three-way valve and one solenoid valve. The three-way valve configuration reduces the number of valves used in the entire module, thereby saving costs and simplifying control.

[0103] Of course, in other embodiments, the three-way valve can also be replaced by three solenoid valves.

[0104] Please continue to refer to Figure 3 and Figure 8 Optionally, at least two of the first heat exchange tube group 300 and the second heat exchange tube group 400 are provided, with at least two of the first heat exchange tube groups 300 connected in parallel and at least two of the second heat exchange tube groups 400 connected in parallel.

[0105] And / or, the first heat exchange tube group 300 includes two first heat exchange tubes 301 arranged in parallel, and the second heat exchange tube group 400 includes at least two second heat exchange tubes 401 arranged in parallel.

[0106] In one embodiment described above, at least two of each of the first heat exchange tube group 300 and the second heat exchange tube group 400 are provided. This arrangement allows the heat exchanger in the present invention to be modularly configured; that is, one first heat exchange tube group 300 is a first module, and one second heat exchange tube group 400 is a second module. The number of first modules and the number of second modules can be increased or decreased. When a higher frequency of operation is required, the number of first and second modules can be increased to increase the heat exchange flow path. When a lower frequency of operation is required, the number of first and second modules can be decreased to reduce the heat exchange flow path and increase the flow rate, thereby improving the heat exchange effect.

[0107] Of course, when modularizing, the first heat exchanger tube group 300 and the second heat exchanger tube group 400 can also be treated as a single module. Similarly, when a higher frequency of operation is required, the number of this module can be increased to increase the heat exchange flow path. When a lower frequency of operation is required, the number of this module can be reduced to decrease the heat exchange flow path and increase the flow rate, thereby improving the heat exchange effect. In this case, the number of the first heat exchanger tube group 300 and the second heat exchanger tube group 400 is always the same. Specifically, the number of both the first heat exchanger tube group 300 and the second heat exchanger tube group 400 can be 2, 3, 4, or more.

[0108] To further increase the heat exchange flow paths, based on the above structure, the first heat exchange tube group 300 includes two parallel first heat exchange tubes 301, and the second heat exchange tube group 400 includes two parallel second heat exchange tubes 401. Thus, the total number of flow paths in the variable flow path module under high load mode is also four, achieving the effect of increasing the heat exchange flow paths. This is equivalent to designating the first heat exchange tube group 300 as the first module, and setting up two first modules and two second modules.

[0109] Of course, when there is only one first heat exchange tube group 300 and one second heat exchange tube group 400, the first heat exchange tube group 300 can be configured to include two parallel first heat exchange tubes 301, or two or more parallel first heat exchange tubes 301, and the second heat exchange tube group 400 can include two parallel second heat exchange tubes 401, or two or more parallel second heat exchange tubes 401, thereby increasing the number of heat exchange flow paths.

[0110] Optionally, the switching valve group 520 is provided such that the end of each first heat exchange tube group 300 near the outlet pipe 200 is connected to the second end 522; and the end of each second heat exchange tube group 400 near the first control valve 510 is connected to the third end 523.

[0111] In this embodiment, when there is only one three-way valve, the end of each first heat exchange tube group 300 away from the other liquid end 703 is connected to the second end 522 of the three-way valve; the end of each second heat exchange tube group 400 near the first control valve 510 is connected to the third end 523 of the three-way valve. At this time, by setting a three-way valve, the number of heat exchange flow paths can be changed in different operating modes without adding more valves, by arbitrarily adding the first heat exchange tube group 300 and / or the second heat exchange tube group 400.

[0112] In another embodiment, the switching valve group 520 may further include two solenoid valves, each solenoid valve having two interconnected ends. The two ends of one solenoid valve are respectively connected to the end of the first heat exchange tube group 300 near the other liquid end 703 and the end of the second heat exchange tube group 400 near the outlet pipe 200. The two ends of the other solenoid valve are respectively connected to the end of the second heat exchange tube group 400 away from the first control valve 510 and the outlet pipe 200, thereby realizing operation under high load and low load conditions.

[0113] Please combine Figure 4 and Figure 9 Optionally, the heat exchanger further includes a common heat exchange tube assembly 900, one end of which is connected to the fourth pipe 640 and the other end of which is connected to the sixth pipe 660.

[0114] Alternatively, one end of the commonly used heat exchange tube assembly 900 is connected to the fifth pipeline 640, and the other end is connected to the inflow pipe 200.

[0115] When the heat exchanger functions as an evaporator, since the first control valve 510 is located in the fifth pipe 650, one end of the commonly used heat exchange tube assembly 900 is connected to the fourth pipe 640, and the other end is connected to the sixth pipe 660. When the heat exchanger functions as a condenser, since the first control valve 510 is located in the sixth pipe 650, one end of the commonly used heat exchange tube assembly 900 is connected to the fifth pipe 640, and the other end is connected to the inflow pipe 200. This ensures that the commonly used heat exchange tube assembly 900 is in a constantly flowing state and is not affected by the opening and closing of the first control valve 510, the switching valve assembly 520, etc. In other words, regardless of whether the first control valve 510 and / or the switching valve assembly 520 are open or closed, the commonly used heat exchange tube assembly 900 can supply the phase change working fluid, allowing the phase change working fluid to flow from the inflow pipe 100 to the outflow pipe 200.

[0116] Understandably, there can be one, two, or more commonly used heat exchanger tube groups 900. Let M be the number of commonly used heat exchanger tube groups 900, and A and B be the number of the first heat exchanger tube group 300 and the second heat exchanger tube group 400, respectively. Then, under medium- and high-frequency operation, the number of heat exchanger flow paths through which the phase change working fluid flows is (A+B+M); under low-frequency operation, the number of heat exchanger flow paths through which the phase change working fluid flows is (A+M), and under low-frequency operation, the phase change working fluid also flows through B subcooling flow paths. The values ​​of at least any two of A, B, and M can be the same or different.

[0117] Furthermore, in the technical solution of this invention, the first heat exchanger tube group 300 can be a double-row heat exchanger tube group or a single-row heat exchanger tube group; and / or, the second heat exchanger tube group 400 can be a double-row heat exchanger tube group or a single-row heat exchanger tube group. Regardless of whether the first heat exchanger tube group 300 is a double-row or single-row heat exchanger tube group, it has two interconnected ports, each a conduit through which the phase change working fluid enters from one port and exits from the other. It is understood that when the first heat exchanger tube group 300 is a double-row heat exchanger tube group, it can be connected to the outlet of one of the two single-row heat exchanger tube groups arranged side-by-side and the inlet of the other through an intermediate conduit. Of course, the type of the second heat exchanger tube group 400 can be the same as or different from the type of the first heat exchanger tube group 300; the second heat exchanger tube group 400 can also be a double-row or single-row heat exchanger tube group.

[0118] Please refer to Figure 5 and Figure 6 , Figure 10 and Figure 11 The present invention also proposes a household appliance, which includes a heat exchanger. The specific structure of the heat exchanger is as described in the above embodiments. Since the present household appliance adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0119] By incorporating a heat exchanger into a household appliance, the appliance may operate at medium to high frequencies or low frequencies when cooling or heating is required. When the appliance is operating at medium to high frequencies, the first control valve 510 of the heat exchanger can be opened, and the first end 521 of the switching valve assembly 520 can be connected to the second end 522, thereby increasing the number of heat exchange flow paths and thus increasing the heat exchange capacity and improving the heat exchange effect. When the appliance is operating at low frequencies, the first control valve 510 of the heat exchanger can be closed, and the second end 522 of the switching valve assembly 520 can be connected to the third end 523, thereby reducing the number of heat exchange flow paths while increasing the flow rate of the phase change working fluid, thus still improving the heat exchange effect. Furthermore, when the heat exchanger is an evaporator or a condenser, the gas-liquid mixture can be separated in a timely manner by the gas-liquid separator 700, so that the gas flows from the throttling element 530 to the outlet pipe 200 or the liquid flows from the second pipe 620 to the outlet pipe 200, thereby improving the heat transfer coefficient at the location where the heat transfer coefficient deteriorates, and thus improving the overall heat exchange efficiency.

[0120] The household appliance can be a single-mode air conditioner or a water heater, etc.

[0121] When the household appliance is a single-mode air conditioner, it can be an outdoor unit for heating only, in which case the heat exchanger functions as an evaporator; or it can be an outdoor unit for cooling only, in which case the heat exchanger functions as a condenser. Specifically, when the outdoor unit of the single-cooling air conditioner is connected to multiple indoor units, the heat exchanger operates at a medium-to-high frequency. In this case, the first control valve 510 can be opened, and the first end 521 and the second end 522 of the switching valve assembly 520 can be connected, thereby increasing the heat exchange path of the phase change refrigerant and thus increasing the heat exchange capacity and improving the heat exchange effect. When the outdoor unit of the single-cooling air conditioner is connected to a single indoor unit, the heat exchanger operates at a low frequency. In this case, the first control valve 510 can be closed, and the second end 522 and the third end 523 of the switching valve assembly 520 can be connected, thereby reducing the heat exchange path of the phase change refrigerant but increasing the flow rate of the phase change refrigerant, which also improves the heat exchange effect. Furthermore, by combining the gas-liquid separator 700 and the separable module 800, the gas-liquid mixture after heat exchange is separated in a timely manner, resulting in a relatively pure gaseous working fluid that is then further condensed, thus improving the heat exchange effect. Additionally, this single-mode air conditioner can be the outdoor unit of a single-heating air conditioner, in which case the heat exchanger functions as an evaporator. The specific control method described above also improves the heat exchange effect.

[0122] When the household appliance is a water heater, the heat exchanger can be used as an evaporator to absorb low-temperature heat energy from the air. Specifically, when the water heater is operating at medium to high frequencies, the first control valve 510 can be opened, and the first end 521 and the second end 522 of the switching valve group 520 can be connected. This increases the heat exchange flow path of the phase change working fluid through the heat exchanger, thereby increasing the heat exchange capacity and improving the heat exchange effect. When the water heater is operating at low frequencies, the first control valve 510 can be closed, and the second end 522 and the third end 523 of the switching valve group 520 can be connected. This reduces the heat exchange flow path of the phase change working fluid through the heat exchanger, but increases the flow rate of the phase change working fluid, which also improves the heat exchange effect.

[0123] Please continue to refer to the reference. Figure 5 and Figure 6 The present invention also provides a flow path control method for a heat exchanger, wherein the heat exchanger is any of the heat exchangers described above, and will not be described in detail here. When the end of the first pipe 610 away from the gas end 701 is connected to the outlet pipe 200, one end of the separable module 800 is connected to the liquid end 702 through the second pipe 620, and the other end is connected to the inlet pipe 100 through the third pipe 630, the throttling element 530 is provided in the first pipe 610, and the heat exchanger is used as an evaporator;

[0124] Alternatively, when the end of the first pipeline 610 away from the gas end 701 is connected to one end of the separable module 800, and one of the liquid ends is connected to the inflow pipe 100 through the second pipeline 620, and the other end of the separable module 800 is connected to the second pipeline 620; the throttling element is disposed in the second pipeline 620 and located between the gas-liquid separator 700 and the other end of the separable module 800, and the heat exchanger is used as a condenser; the flow path control method of the heat exchanger includes:

[0125] S1: Control the throttling element 530 to be turned on, and obtain the operating status of the heat exchanger;

[0126] S2: When the heat exchanger is in the first load operating state, control the first control valve 510 to open, and control the first end 521 of the switching valve group 520 to connect with the second end 522.

[0127] S3: When the heat exchanger is in the second load operating state, control the first control valve 510 to close, and control the third end 523 of the switching valve group 520 to connect with the second end 522; wherein, the first load is greater than the second load.

[0128] In this control method, the heat exchanger is applied to single-mode air conditioners, including those for cooling, heating, and heating water heaters; it can also be used in refrigerators. When the heat exchanger is used in the outdoor unit of a cooling-only air conditioner, it functions as a condenser; when used in the outdoor unit of a heating-only air conditioner, it functions as an evaporator. Taking the heat exchanger as an evaporator as an example, combined with the separable module 800, gas-liquid separator 700, and throttling device 530, the gas-liquid mixture after initial heat exchange can be separated in a timely manner, and the gaseous working fluid can be separated out and enter the outlet pipe 200 from the throttling device 530. This allows the subsequent pure liquid working fluid to further improve the heat transfer coefficient in the variable flow path module, thereby achieving a better heat exchange effect. When the heat exchanger functions as a condenser, the gaseous working fluid can also achieve sufficient heat exchange through the separable module 800 and the variable flow path module, improving heat exchange efficiency.

[0129] Whether the heat exchanger functions as an evaporator or a condenser, it operates under a first load and a second load, with the first load being greater than the second load. When the heat exchanger operates under the first load, by controlling the first control valve 510 to open and the first end 521 of the switching valve group 520 to connect with the second end 522 (which can be understood as the third end 523 of the switching valve group 520 being closed), the phase change working fluid can simultaneously exchange heat through the first heat exchange tube group 300 and the second heat exchange tube group 400. This results in a larger number of heat exchange flow paths, thereby increasing the heat exchange capacity under higher load operating conditions and meeting the requirement for better heat exchange performance under heavy load conditions. As long as the heat exchanger operates under the second load condition, by controlling the first control valve 510 to close and controlling the third end 523 of the switching valve group 520 to connect with the second end 522 (which can be understood as the first end 521 of the switching valve group 520 being in a closed state), the phase change working fluid can exchange heat in the heat exchanger by passing through the first heat exchange tube group 300 and the second heat exchange tube group 400 in sequence. At this time, the number of heat exchange flow paths is reduced by half compared to the high load operating state, thereby improving the heat exchange coefficient under the low load operating mode, and can also meet the requirement of achieving better heat exchange effect under the low load operating state.

[0130] Specifically, please refer to Figure 5When the heat exchanger is used as an evaporator, and the heat exchanger is in the first load operating state, by controlling the opening of the first control valve 510, the first end 521 and the second end 522 of the switching valve group 520 are connected. Then the phase change working fluid flows out from the inlet pipe 100, passes through the separable module 800 and the gas-liquid separator 700, and flows into the first heat exchange tube group 300 through the fourth pipe 640 and into the second heat exchange tube group 400 through the fifth pipe 650 respectively. The phase change working fluid flowing out of the first heat exchange tube group 300 flows into the outlet pipe 200 through the second end 522 and the first end 521 of the switching valve group 520 in sequence. The phase change working fluid flowing out of the second heat exchange tube group 400 flows directly into the outlet pipe 200.

[0131] Please refer to Figure 6 When the heat exchanger is operating under the second load, by closing the first control valve 510 and only connecting the third end 523 of the switching valve group 520 to the second end 522, the phase change working fluid flows out from the inlet pipe 100, passes through the separable module 800 and the gas-liquid separator 700, and then flows into the outlet pipe 200 in sequence through the fourth pipe 640, the first heat exchange tube group 300, the second end 522 and the third end 523 of the switching valve group 520, and the second heat exchange tube group 400. At this time, the number of flow paths is reduced by half compared to the first load operating state, which can still meet the requirement of increasing the heat transfer coefficient under a smaller load operating state and achieve better heat exchange effect.

[0132] Please refer to Figure 10 When the heat exchanger is used as a condenser, when the heat exchanger is in the first load operating state, the gaseous working fluid flows in from the inlet pipe 100. By controlling the opening of the first control valve 510, the first end 521 and the second end 522 of the switching valve group 520 are connected. The working fluid flows in two paths. One path passes through the first heat exchange tube group 300 for heat exchange and the switching valve group 520 before entering the fourth pipe 640. The other path passes through the first control valve 510 for heat exchange with the second heat exchange tube group 400 before entering the fifth pipe. The working fluids in the fourth pipe 640 and the fifth pipe 650 merge and enter the gas-liquid separator 700.

[0133] When the heat exchanger is operating under the second load, by closing the first control valve 510 and only connecting the third end 523 of the switching valve group 520 with the second end 522, the gaseous working fluid flows in through the inlet pipe 100, first exchanges heat through the first heat exchange tube group 300, and then enters the second heat exchange tube group 400 through the switching valve group, thereby realizing the series connection of the two heat exchange tube groups, which meets the requirement of increasing the heat transfer coefficient under the lower load operating condition and achieves better heat exchange effect.

[0134] In addition, the technical solution of the present invention can realize the modularization of the first heat exchange tube group 300 and the second heat exchange tube group 400, and flexibly increase or decrease multiple heat exchange flow paths without increasing the number of control valves.

[0135] Optionally, the heat exchanger is applied to the outdoor unit of a heating system, the outdoor unit of which further includes a compressor 2000 connected to the heat exchanger; the step of controlling the throttling element 530 to be turned on and obtaining the operating status of the heat exchanger includes:

[0136] S11: Obtain the outdoor temperature as T3 and the compressor frequency as F1 (2000).

[0137] S12: When the outdoor temperature T3 is less than the first preset value a; or when the outdoor temperature is less than the second preset value b and greater than the first preset value a, and the frequency F1 of the compressor 2000 is greater than k*(Fmax+Fmin); or when the outdoor temperature is greater than the second preset value b, and the frequency F1 of the compressor 2000 is greater than m*(Fmax+Fmin), the heating system is set to the first load mode;

[0138] S13: When the outdoor temperature T3 is greater than the first preset value a and less than or equal to the second preset value b, and the frequency F1 of the compressor 2000 is less than k*(Fmax+Fmin); or, when the outdoor temperature T3 is greater than the second preset value b, and the frequency F1 of the compressor 2000 is less than m*(Fmax+Fmin), the heating system is set to the second load mode.

[0139] Where b is greater than a, k ranges from 1 / 3 to 5 / 8, m ranges from 5 / 8 to 7 / 8, Fmax is the maximum operating frequency of compressor 2000, and Fmin is the minimum operating frequency of compressor 2000.

[0140] The load state of a heat exchanger is related to the external environment and the quantity of loads it carries. The harsher the ambient temperature, the heavier the load on the heat exchanger. An increased load leads to a higher compressor 2000 frequency; therefore, monitoring the compressor 2000 frequency can indirectly determine whether the heat exchanger load is high or low. For example, when a heat exchanger is used in an air conditioner outdoor unit, if the ambient temperature is low when the air conditioner is in heating mode, the environment is harsher, and the heat exchanger will operate under a higher load. Alternatively, a higher compressor 2000 frequency indicates a heavier load, and the heat exchanger will operate under a higher load. Conversely, the heat exchanger will operate under a lower load. In this invention, if the first load operating state is greater than the second load operating state, it indicates that the first load operating state is a higher load operating state, and the second load operating state is a lower load operating state. This invention simultaneously acquires the outdoor temperature T3 and the compressor 2000 frequency F1, comprehensively considering both conditions to determine the heat exchanger's operating state, thus making the determination more accurate.

[0141] When the heat exchanger is determined to be in the first load operating state, a first signal is sent to the heat exchanger to control the first control valve 510 to open and control the first end 521 and the second end 522 of the switching valve group 520 to connect, so that there are more heat exchange flow paths when the heat exchange is in the high load operating state, thereby increasing the heat exchange capacity and improving the heat exchange effect.

[0142] When it is determined that the heat exchanger is in the second load operation state, a second signal is sent to the heat exchanger to control the first control valve 510 to close and control the first end 521 and the third end 523 of the switching valve group 520 to connect. This results in fewer heat exchange flow paths when the heat exchanger is in the low load operation state. On the one hand, this can meet the stable operation state under this load operation state. On the other hand, it can also increase the flow rate of the refrigerant in the heat exchange flow path, thereby increasing the heat transfer coefficient and improving the heat exchange effect.

[0143] In this invention, when the heat exchanger is applied to the outdoor unit of an air conditioner and acts as an evaporator, the air conditioner is in heating mode. Specifically, when the outdoor temperature T3 is less than a (where 0 ≤ a ≤ 6℃, and a can be 0, 1℃, 2℃, 3℃, 4℃, 5℃, or 6℃, and preferably 5℃), it indicates that the ambient temperature is very low. That is, when the air conditioner is in heating mode, regardless of whether the compressor 2000 operates at a high or low frequency, it indicates that the environmental conditions are very harsh. Therefore, the heat exchanger must be under a large load during operation, thus it can be determined that the heat exchanger is in the first load operating state. When the outdoor temperature a ≤ T3 < b (where 6℃ ≤ b ≤ 20℃, and b can be 6℃, 7℃, 8℃, 9℃, 10℃, 11℃, 12℃, 13℃, 14℃, 15℃, 16℃, 17℃, 18℃, 19℃, or 20℃, and preferably 16℃), it indicates that the ambient temperature has improved. At this point, combined with the obtained compressor 2000 frequency F1, the operating status of the heat exchanger can be further determined. If the compressor 2000 frequency F1 ≥ k*(Fmax + Fmin), where 1 / 3 ≤ k ≤ 5 / 8, for example, k can be 1 / 3, 3 / 8, 1 / 2, or 5 / 8, and preferably 1 / 2; Fmax is the maximum allowable operating frequency of compressor 2000, and Fmin is the minimum allowable operating frequency of compressor 2000, it proves that the compressor 2000 frequency is high, and the heat exchanger is still operating under high load. Therefore, the heat exchanger is determined to be operating under the first load condition. When the outdoor temperature T3 > b, the outdoor temperature has further improved. If the compressor 2000 frequency F1 ≥ m*(Fmax + Fmin), where 5 / 8 ≤ m ≤ 7 / 8, for example, m can be 5 / 8, 2 / 3, 3 / 4, or 7 / 8. Furthermore, m can preferably be 2 / 3. This proves that the compressor 2000 frequency has further increased, thus proving that the load is too heavy. At this time, regardless of the outdoor temperature, the heat exchanger is in a high-load operating state. Therefore, it is determined that the heat exchanger is in the first load operating state.

[0144] When the heat exchanger is used as an evaporator and is operating under the first load condition, the specific control flow path is as described above. In this way, the number of flow paths for the phase change working fluid is the sum of the first heat exchange tube group 300 and the second heat exchange tube group 400. The large number of heat exchange flow paths increases the heat exchange capacity under the higher load operating mode, thus achieving a better heat exchange effect.

[0145] In this invention, when the heat exchanger is applied to the outdoor unit of an air conditioner as an evaporator, if the outdoor temperature is not too harsh and the compressor frequency (2000 rpm) is not too high, the heat exchanger is operating under a low load. Specifically, when a ≤ T3 < b and F1 < k*(Fmax + Fmin), the outdoor temperature is not too low, indicating that the environment is not too harsh, and the compressor frequency (2000 rpm) is also low, thus the heat exchanger can be determined to be operating under a low load, i.e., the second load operating state mentioned above. When T3 > b and F1 < m*(Fmax + Fmin), the outdoor temperature is very high, providing a naturally favorable environment for the operation of the heat exchanger. Simultaneously, the compressor frequency (2000 rpm) is not too high, therefore, the load on the heat exchanger is not too large, and the heat exchanger can also be determined to be operating under a low load.

[0146] When the heat exchanger is in the second load operating state, the specific control method is as above. At this time, the number of flow paths is reduced by half compared with the first load operating state. This can still meet the requirement of increasing the heat transfer coefficient under a smaller load operating state and achieve better heat exchange effect.

[0147] Of course, please refer to Figure 10 and Figure 11 The heat exchanger is applied to the outdoor unit of a refrigeration system, and the outdoor unit of the heating system further includes a compressor 2000, which is connected to the heat exchanger, and the heat exchanger is used as a condenser; the step of controlling the throttling element 530 to be turned on and obtaining the operating status of the heat exchanger includes:

[0148] Obtain the outdoor temperature T4 and the compressor frequency F2 at 2000 RPM;

[0149] When the outdoor temperature T4 is greater than the fourth preset value d; or when the outdoor temperature is less than the fourth preset value d but greater than the fifth preset value g, and the frequency F2 of the compressor 2000 is greater than k*(Fmax+Fmin); or when the outdoor temperature is less than the fifth preset value g, and the frequency F2 of the compressor 2000 is greater than m*(Fmax+Fmin), the refrigeration system is set to the first load mode.

[0150] When the outdoor temperature T4 is less than the fourth preset value d and greater than or equal to the fifth preset value g, and the frequency F2 of the compressor 2000 is less than k*(Fmax+Fmin); or, when the outdoor temperature is less than the fifth preset value g, and the frequency F2 of the compressor 2000 is less than m*(Fmax+Fmin), the refrigeration system is set to the second load mode.

[0151] Where d is greater than g, k ranges from 1 / 3 to 5 / 8, m ranges from 5 / 8 to 7 / 8, Fmax is the maximum operating frequency of compressor 2000, and Fmin is the minimum operating frequency of compressor 2000;

[0152] The first preset value d ranges from 26℃ to 35℃, and the second preset value g ranges from 10℃ to 25℃.

[0153] When a heat exchanger is used in the outdoor unit of an air conditioner, and the heat exchanger acts as a condenser, the air conditioner is in cooling mode. When the air conditioner is in cooling mode, a higher ambient temperature indicates a harsher environment, causing the heat exchanger to operate under a higher load. Alternatively, a higher compressor frequency (e.g., 2000 rpm) indicates a greater load, resulting in the heat exchanger operating under a higher load. Conversely, a lower load will result in the heat exchanger operating under a lower load.

[0154] Specifically, when the outdoor temperature T4 is greater than a certain preset value, it indicates that the ambient temperature is very high. That is, when the air conditioner is in cooling mode, regardless of whether the compressor 2000's operating frequency is high or low, it indicates that the environmental conditions are very harsh. Therefore, the heat exchanger will inevitably operate under a high load, thus determining that the heat exchanger is in its first load operating state. When the outdoor temperature is moderate, it indicates that the ambient temperature has improved. At this point, combined with the compressor 2000's frequency F2, the operating state of the heat exchanger is further determined. If the compressor 2000's frequency F2 is greater than a certain preset value, it proves that the compressor 2000's frequency is high, and the heat exchanger is still operating under a high load, thus determining that the heat exchanger is in its first load operating state. When the outdoor temperature T4 is less than the preset value, the outdoor temperature has further improved. If the compressor 2000's frequency F2 further increases, it proves that the load is too heavy. At this time, regardless of the outdoor temperature, the heat exchanger is operating under a high load, thus determining that the heat exchanger is in its first load operating state. When the outdoor temperature is not too high, it indicates that the environment is not too harsh, and the compressor frequency of 2000 is also relatively low. Therefore, it can be determined that the heat exchanger is operating under low load, which is the second load operating state mentioned above. Alternatively, when the outdoor temperature is very low, it provides a naturally favorable environment for the operation of the heat exchanger. At the same time, the compressor frequency of 2000 will not be too high, so the load on the heat exchanger will not be too large. In this case, it can also be determined that the heat exchanger is operating under low load.

[0155] When the outdoor temperature T4 is greater than or equal to d (where 26℃≤d≤35℃, for example, d can be 26℃, 27℃, 28℃, 29℃, 30℃, 31℃, 32℃, 33℃, 34℃ or 35℃, and d is preferably recommended to be 33℃), it indicates that the ambient temperature is very high. That is, when the air conditioner is in cooling mode, regardless of whether the compressor 2000's operating frequency is high or low, it indicates that the environmental conditions are very harsh. Therefore, the heat exchanger must be under a large load when it is running, and thus it can be determined that the heat exchanger is in the first load mode. When the outdoor temperature g ≤ T4 < d (where 10℃ ≤ g ≤ 25℃, for example, b can be 10℃, 11℃, 12℃, 13℃, 14℃, 15℃, 16℃, 17℃, 18℃, 19℃, 20℃, 21℃, 22℃, 23℃, 24℃ or 25℃, and g is preferably recommended to be 16℃), it indicates that the ambient temperature has improved. At this time, combined with the obtained compressor 2000 frequency F2, the mode of the heat exchanger is further determined. If F1 ≥ k*(Fmax + Fmin), where 1 / 3 ≤ k ≤ 5 / 8, for example, k can be 1 / 3, 3 / 8, 1 / 2, 5 / 8, and k is preferably 1 / 2; Fmax is the maximum allowable operating frequency of compressor 2000, and Fmin is the minimum allowable operating frequency of compressor 2000, it proves that the frequency of compressor 2000 is relatively high, so the heat exchanger is still in the high load mode. Therefore, it is determined that the heat exchanger is in the first load mode. When the outdoor temperature T4 < g, the outdoor temperature has further improved. If F2 ≥ m * (Fmax + Fmin), where 5 / 8 ≤ m ≤ 7 / 8, for example, m can be 5 / 8, 2 / 3, 3 / 4, or 7 / 8. Furthermore, m can preferably be 2 / 3. This proves that the compressor frequency of 2000 has further increased, thus proving that the load is too heavy. At this time, regardless of the outdoor temperature, the heat exchanger is in a high-load mode. Therefore, it is determined that the heat exchanger is in the first load mode.

[0156] When the heat exchanger is used as a condenser and is in the first load mode, the heat exchanger enters the full flow path mode. In this way, the number of flow paths of the phase change working fluid is the sum of the first heat exchange tube group 300 and the second heat exchange tube group 400. The large number of heat exchange flow paths increases the heat exchange capacity under the larger load operation mode and achieves better heat exchange effect.

[0157] Meanwhile, when the heat exchanger is used in the outdoor unit of an air conditioner as a condenser, if the outdoor temperature is not too harsh and the compressor frequency (2000 rpm) is not too high, it indicates that the heat exchanger is operating under a low load mode. Specifically, when g ≤ T4 < d and F2 < k*(Fmax + Fmin), the outdoor temperature is not too high, indicating that the environment is not too harsh, and the compressor frequency (2000 rpm) is also low, thus it can be determined that the heat exchanger is in a low load mode, i.e., the second load mode mentioned above. When T4 < g and F2 < m*(Fmax + Fmin), the outdoor temperature is very low, providing a naturally favorable environment for the operation of the heat exchanger. At the same time, the compressor frequency (2000 rpm) is not too high, therefore, the load on the heat exchanger is not too large, and it can also be determined that the heat exchanger is in the second load mode.

[0158] When the heat exchanger is in the second load mode, the semi-flow path mode is selected. At this time, the number of flow paths is reduced by half compared to the first load mode, which can meet the requirement of increasing the heat transfer coefficient under a smaller load mode and achieve better heat exchange effect.

[0159] Optionally, when the throttling element 530 is an electronic expansion valve, it further includes:

[0160] S4: Obtain the target operating frequency Fr of the heating system;

[0161] S5: Determine the magnitude of the target operating frequency Fr and the third preset value c;

[0162] S6: If Fr≤c, then the initial opening of the electronic expansion valve is set to the first opening A, and the holding time is t1; if Fr>c, then the initial opening of the electronic expansion valve is set to the second opening B, and the holding time is t2.

[0163] Where c = l*(Fmax + Fmin), l ranges from 0.45 to 0.75, A is less than B, Fmax is the maximum operating frequency of compressor 2000, and Fmin is the minimum operating frequency of compressor 2000;

[0164] S7: After initialization, the coil temperature of the heat exchanger and the suction temperature of the compressor 2000 are detected every first preset time.

[0165] S8: Determine the difference between the coil temperature and the intake temperature, and adjust the opening adjustment value of the electronic expansion valve according to the magnitude of the difference.

[0166] Here, when the throttling element 530 is an electronic expansion valve, in order to enhance the heating effect, the electronic expansion valve is opened when the heat exchanger is in evaporation mode. The initial opening degree and holding time of the electronic expansion valve are set according to the target operating frequency of the refrigeration system, thereby effectively saving energy and improving the efficiency of gas-liquid separation.

[0167] Specifically, the target operating frequency is compared with a third preset value c. Here, the third preset value is the ratio of the sum of the maximum and minimum operating frequencies of the compressor 2000. The ratio coefficient l ranges from 0.45 to 0.75, for example, 0.5, 0.6, or 0.7. In a preferred embodiment, the ratio coefficient is selected as 0.5, so that the target operating frequency is compared with half of the sum of Fmax and Fmin, which can best reflect the load mode of the refrigeration system. This allows for more accurate initial control of the opening and holding time of the electronic expansion valve, thereby improving heat exchange efficiency.

[0168] Specifically, the heat exchanger is in heating mode. Combined with the obtained frequency Fr of compressor 2000, the operating mode of the heat exchanger is further determined. If the target operating frequency Fr of compressor 2000 is ≤ c, it indicates that the target operating frequency of compressor 2000 is low, meaning the heat exchanger may be operating under low load. Therefore, the opening degree of the electronic expansion valve can be set to a relatively small first opening degree A. Here, A ranges from 20P to 100P, for example, 30P, 40P, 50P, 60P, 70P, 80P, 90P, etc., preferably 50P. The maintenance time is t1, ranging from 2min to 15min, for example, 3min, 4min, 5min, 6min, 8min, 10min, 12min, etc. In a preferred embodiment, t1 is set to 5min, thereby effectively saving energy and improving heat exchange efficiency while meeting low load requirements. If Fr > c, it indicates that the compressor 2000 target operating frequency is high, and the heat exchanger may be operating under high load. Therefore, the initial opening of the electronic expansion valve is set to the second opening B, where B ranges from 50P to 150P, for example, 50P, 60P, 70P, 80P, 90P, 100P, 120P, 140P, etc. In a preferred embodiment, the second opening B is selected as 80P, and the holding time is t2, which ranges from 1min to 15min, for example, 2min, 3min, 4min, 5min, 6min, 8min, 10min, 12min, etc. Preferably, t2 is selected as 2min, thereby ensuring the heat exchange effect while meeting the high load requirements.

[0169] Optionally, the step of determining the difference between the coil temperature and the suction temperature, and adjusting the opening adjustment value of the electronic expansion valve according to the magnitude of the difference, specifically includes:

[0170] S81: Let the difference be ΔT. If ΔT < -1.5, then increase the opening of the electronic expansion valve by a first opening value n; if -1.5 < ΔT ≤ -0.5, then increase the opening of the electronic expansion valve by a second opening value E.

[0171] S82: If -0.5 < ΔT ≤ 0.5, then the opening degree of the electronic expansion valve remains unchanged;

[0172] S83: If 0.5 < ΔT ≤ 1.5, then control the opening of the electronic expansion valve to decrease by the third opening value - (E+1);

[0173] S84: If ΔT > 1.5, then control the opening of the electronic expansion valve to decrease by the fourth opening value - (F+1);

[0174] Where F > E.

[0175] Optionally, the first preset time ranges from 30s to 300s, E ranges from 2P to 15P, and F ranges from 4P to 30P;

[0176] And / or, the range of A is 20P to 100P, the range of t1 is 2min to 15min, the range of B is 50P to 150P, and the range of t2 is 1min to 15min.

[0177] To further improve the throttling accuracy, in this embodiment, the difference between the coil temperature and the suction temperature is set to ΔT. If ΔT < -1.5, it means that the coil temperature of the heat exchanger is lower than the suction temperature and the difference between the two is large. At this time, the suction superheat is large. Therefore, it is necessary to increase the opening of the electronic expansion valve. The corresponding first opening value is E (E can be selected from 4P to 30P, for example, 5P, 6P, 7P, 8P, 10P, 15P, 20P, 25P, 30P, etc., preferably 8P). This makes the refrigerant at the outlet of the evaporator saturated, the evaporation temperature increases, the suction temperature decreases, and the effective suction superheat decreases, thereby improving the heat exchange effect. Of course, if -1.5 < ΔT ≤ -0.5, then the corresponding intake superheat is not very large. The opening of the electronic expansion valve can be increased by a second opening value F. Here, the value of F is less than E, and its range can be 2P to 15P, for example, 4P, 5P, 7P, 8P, 10P, 15P, etc., preferably 4P, so as to ensure an effective and appropriate intake superheat and improve the heat exchange effect.

[0178] Understandably, when the difference between the two is equal, i.e. -0.5 < ΔT ≤ 0.5, the opening of the electronic expansion valve can be kept constant.

[0179] Of course, when 0.5 < ΔT ≤ 1.5, or ΔT > 1.5, it means that the coil temperature of the heat exchanger is greater than the suction temperature, and the difference between the two is large. In this case, it is necessary to reduce the opening of the electronic expansion valve. In the former case, the reduction value is smaller than that in the latter case. That is, when 0.5 < ΔT ≤ 1.5, the opening of the electronic expansion valve is reduced by the third opening value (F+1), preferably 5P. When ΔT > 1.5, the opening of the electronic expansion valve is reduced by the fourth opening value (E+1), preferably 9P, so as to ensure an effective and appropriate suction superheat and improve the heat exchange effect.

[0180] The present invention also provides a storage medium storing a flow path control program for a heat exchanger, wherein when the flow path control program for the heat exchanger is executed by a processor, the steps of the flow path control method for the heat exchanger described above are implemented.

[0181] The specific implementation of the storage medium of the present invention can be referred to the various embodiments of the flow path control method of the heat exchanger described above, and will not be repeated here.

[0182] The above description is merely a preferred embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent structural transformations made using the contents of the present invention's specification and drawings under the inventive concept of the present invention, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present invention.

Claims

1. A flow path control method for a heat exchanger, characterized in that, The heat exchanger includes: Inflow pipe; Outflow tube; A gas-liquid separator, comprising a gas end and two liquid ends, wherein the gas end is connected to a first pipeline; A separable module is disposed between the gas-liquid separator and the inlet pipe or outlet pipe; A variable flow path module, comprising a first heat exchange tube group, a second heat exchange tube group, a first control valve and a switching valve group, wherein one end of the first heat exchange tube group is connected to the other liquid end through a fourth pipeline; One end of the second heat exchange tube assembly is connected to the other liquid end through the fifth pipe, and the other end is connected to the outflow pipe or inflow pipe through the sixth pipe. The first control valve is located in the fifth pipe or the sixth pipe. The switching valve assembly has a first end, a second end, and a third end. The first end is connected to the outlet pipe or the fourth pipeline. The second end is connected to the end of the first heat exchange tube assembly that is away from or near the other liquid end. The third end is connected to the end of the second heat exchange tube assembly that is near the first control valve. Throttling device; When the end of the first pipeline away from the gas end is connected to the outflow pipe, one end of the separable module is connected to the liquid end through the second pipeline, and the other end is connected to the inflow pipe through the third pipeline, and the throttling device is provided in the first pipeline; Alternatively, when the end of the first pipeline away from the gas end is connected to one end of the separable module, and the liquid end is connected to the inflow pipe through a second pipeline, and the other end of the separable module is connected to the second pipeline; the throttling element is provided in the second pipeline and is located between the gas-liquid separator and the other end of the separable module; When the end of the first pipeline away from the gas end is connected to the outlet pipe, one end of the separable module is connected to the liquid end through the second pipeline, and the other end is connected to the inlet pipe through the third pipeline, the throttling element is provided in the first pipeline, and the heat exchanger is used as an evaporator; Alternatively, when the end of the first pipeline away from the gas end is connected to one end of the separable module, and the liquid end is connected to the inflow pipe through the second pipeline, and the other end of the separable module is connected to the second pipeline; the throttling element is provided in the second pipeline and is located between the gas-liquid separator and the other end of the separable module, and the heat exchanger is used as a condenser; The flow path control method for the heat exchanger includes: Control the throttling element to conduct and obtain the operating status of the heat exchanger; When the heat exchanger is in the first load operating state, the first control valve is opened and the first end of the switching valve group is connected to the second end. When the heat exchanger is in the second load operating state, the first control valve is closed, and the third end of the switching valve group is connected to the second end; wherein, the first load is greater than the second load; The heat exchanger is used in the outdoor unit of a heating system, the outdoor unit of which also includes a compressor. The compressor is connected to the heat exchanger, and the heat exchanger functions as an evaporator. The steps of controlling the throttling element to conduct and obtaining the operating status of the heat exchanger include: The outdoor temperature is T3 and the compressor frequency is F1. When the outdoor temperature T3 is less than the first preset value a; or when the outdoor temperature is less than the second preset value b and greater than the first preset value a, and the compressor frequency F1 ≥ k*(Fmax+Fmin); or when the outdoor temperature is greater than the second preset value b, and the compressor frequency F1 ≥ m*(Fmax+Fmin), the heating system is set to the first load mode. When the outdoor temperature T3 is greater than the first preset value a and less than or equal to the second preset value b, and the compressor frequency F1 < k*(Fmax+Fmin); or, when the outdoor temperature T3 is greater than the second preset value b, and the compressor frequency F1 < m*(Fmax+Fmin), the heating system is set to the second load mode. Where b is greater than a, k ranges from 1 / 3 to 5 / 8, m ranges from 5 / 8 to 7 / 8, Fmax is the maximum operating frequency of the compressor, and Fmin is the minimum operating frequency of the compressor; The first preset value a ranges from 0℃ to 6℃, and the second preset value b ranges from 6℃ to 20℃; When the throttling element is an electronic expansion valve, it also includes: Obtain the target operating frequency Fr of the heating system; Determine the magnitude of the target operating frequency Fr and the third preset value c; If Fr≤c, the initial opening of the electronic expansion valve is set to the first opening A, and the holding time is t1; if Fr>c, the initial opening of the electronic expansion valve is set to the second opening B, and the holding time is t2. Where c = l * (Fmax + Fmin), l ranges from 0.45 to 0.75, A is less than B, Fmax is the maximum operating frequency of the compressor, and Fmin is the minimum operating frequency of the compressor; After initialization, the coil temperature of the heat exchanger and the suction temperature of the compressor are checked every first preset time interval; Determine the difference between the coil temperature and the intake temperature, and adjust the opening value of the electronic expansion valve according to the magnitude of the difference.

2. The flow path control method for a heat exchanger as described in claim 1, characterized in that, The throttling device is an electronic expansion valve or a capillary tube; Alternatively, the throttling element may be a one-way valve, wherein the one-way valve is directed from one of the liquid ends to the outlet pipe, or the one-way valve is directed from the gas end to the outlet pipe.

3. The flow path control method for a heat exchanger as described in claim 1, characterized in that, The separable module includes a plurality of first separable flow paths and second separable flow paths. The plurality of first separable flow paths are arranged in parallel, and the second separable flow paths are arranged in series with the first separable flow paths. The number of flow paths of the first separable flow paths is less than the total number of flow paths of the variable flow path module.

4. The flow path control method for a heat exchanger as described in claim 1, characterized in that, The switching valve assembly is a three-way valve.

5. The flow path control method for a heat exchanger as described in claim 1, characterized in that, The first heat exchange tube group and the second heat exchange tube group are each provided with at least two, with at least two first heat exchange tube groups and at least two second heat exchange tube groups being arranged in parallel; And / or, the first heat exchanger tube group includes two first heat exchanger lines arranged in parallel, and the second heat exchanger tube group includes at least two second heat exchanger lines arranged in parallel.

6. The flow path control method for a heat exchanger as described in claim 5, characterized in that, The switching valve group is provided with one end of each first heat exchange tube group near the outlet tube connected to the second end; and one end of each second heat exchange tube group near the first control valve connected to the third end.

7. The flow path control method for a heat exchanger as described in any one of claims 1 to 6, characterized in that, The heat exchanger also includes a common heat exchange tube assembly, one end of which is connected to the fourth pipeline and the other end of which is connected to the sixth pipeline.

8. The flow path control method for a heat exchanger as described in any one of claims 1 to 6, characterized in that, The step of determining the difference between the coil temperature and the suction temperature, and adjusting the opening adjustment value of the electronic expansion valve according to the magnitude of the difference, specifically includes: Let the difference be ∆T. If ∆T < -1.5, then the opening degree of the electronic expansion valve is increased by a first opening degree value F; if -1.5 < ∆T ≤ -0.5, then the opening degree of the electronic expansion valve is increased by a second opening degree value E. If -0.5 < ∆T ≤ 0.5, then the opening degree of the electronic expansion valve remains unchanged; If 0.5 < ∆T ≤ 1.5, then the opening degree of the electronic expansion valve is reduced by the third opening value - (E+1). If ∆T>1.5, then the opening degree of the electronic expansion valve is reduced by the fourth opening degree value - (F+1). Where F > E.

9. The flow path control method for a heat exchanger as described in claim 8, characterized in that, The first preset time ranges from 30s to 300s, E ranges from 2P to 15P, and F ranges from 4P to 30P. And / or, the range of A is 20P~100P, the range of t1 is 2min~15min, the range of B is 50P~150P, and the range of t2 is 1min~15min.

10. The flow path control method for a heat exchanger as described in any one of claims 1 to 6, characterized in that, The heat exchanger is used in the outdoor unit of a refrigeration system, the outdoor unit of which also includes a compressor. The compressor is connected to the heat exchanger, and the heat exchanger functions as a condenser. The steps of controlling the throttling element to conduct and obtaining the operating status of the heat exchanger include: Obtain the outdoor temperature T4 and compressor frequency F2; When the outdoor temperature T4 is greater than the fourth preset value d; or when the outdoor temperature is less than the fourth preset value d but greater than the fifth preset value g, and the compressor frequency F2 ≥ k*(Fmax+Fmin); or when the outdoor temperature is less than the fifth preset value g, and the compressor frequency F2 ≥ m*(Fmax+Fmin), the refrigeration system is set to the first load mode. When the outdoor temperature T4 is less than the fourth preset value d and greater than or equal to the fifth preset value g, and the compressor frequency F2 < k*(Fmax+Fmin); or, when the outdoor temperature is less than the fifth preset value g, and the compressor frequency F2 < m*(Fmax+Fmin), the refrigeration system is set to the second load mode. Where d is greater than g, k ranges from 1 / 3 to 5 / 8, m ranges from 5 / 8 to 7 / 8, Fmax is the maximum operating frequency of the compressor, and Fmin is the minimum operating frequency of the compressor; The fourth preset value d ranges from 26℃ to 35℃, and the fifth preset value g ranges from 10℃ to 25℃.

11. A storage medium, characterized in that, The storage medium stores a flow path control program for a heat exchanger, which, when executed by a processor, implements the steps of the flow path control method for a heat exchanger as described in any one of claims 1 to 10.

12. A household appliance, characterized in that, The household appliance includes a heat exchanger capable of performing the flow path control method for a heat exchanger as described in any one of claims 1 to 10.

13. The household appliance as described in claim 12, characterized in that, The household appliance is a single-function air conditioner or a water heater.

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