Air conditioner, control method and controller thereof, air conditioning system, and storage medium

Abstract

The application provides an air conditioner, a control method and controller thereof, an air conditioner system and a storage medium. The air conditioner comprises: a circulation loop for realizing circulation flow of refrigerant to perform refrigeration or heating, wherein a compressor, an outdoor heat exchanger and a gas-liquid separator are arranged on the circulation loop; a deicing flow path connected with an outlet of the compressor and an inlet of the gas-liquid separator and coupled with the outdoor heat exchanger in heat to utilize high-temperature refrigerant flowing out of the compressor to deice the outdoor heat exchanger; and a bypass branch connected with the deicing flow path and an inlet of the compressor to lead the refrigerant in the deicing flow path back to the compressor. Thus, the working reliability of the air conditioner can be improved.

Description

Technical Field

[0001] This application relates to the field of air conditioning technology, and in particular to an air conditioner and its control method, controller, air conditioning system and storage medium. Background Technology

[0002] In actual use of air conditioners, users may add less refrigerant than designed for the unit in order to reduce costs. In addition, there may be problems such as leakage during the operation of the air conditioner. All of these may result in insufficient refrigerant in the unit, affecting its reliability. Summary of the Invention

[0003] One of the technical problems this application aims to solve is: improving the operational reliability of air conditioners.

[0004] To solve the above-mentioned technical problems, this application provides an air conditioner, which includes:

[0005] The circulation loop is used to realize the circulation of refrigerant for cooling or heating. The circulation loop is equipped with a compressor, an outdoor heat exchanger and a gas-liquid separator.

[0006] The de-icing flow path connects the compressor outlet and the gas-liquid separator inlet, and is thermally coupled to the outdoor heat exchanger to utilize the high-temperature refrigerant flowing from the compressor to de-ic the outdoor heat exchanger; and

[0007] A bypass branch connects the defrosting flow path and the compressor inlet to return the refrigerant in the defrosting flow path to the compressor.

[0008] In some embodiments, a de-icing valve is provided on the de-icing flow path, which controls the opening and closing of the de-icing flow path. Along the direction of refrigerant flow through the de-icing flow path, the connection point between the bypass branch and the de-icing flow path is located upstream of the de-icing valve; and / or, a de-icing throttling device is provided on the de-icing flow path, which throttles the refrigerant in the de-icing flow path. Along the direction of refrigerant flow through the de-icing flow path, the connection point between the bypass branch and the de-icing flow path is located downstream of the de-icing valve.

[0009] In some embodiments, a de-icing valve and a de-icing throttling device are provided on the de-icing flow path. The de-icing throttling device and the de-icing valve are arranged sequentially along the direction in which the refrigerant flows through the de-icing flow path. The connection point between the bypass branch and the de-icing flow path is located between the de-icing valve and the de-icing throttling device.

[0010] In some embodiments, a bypass branch is connected to the de-icing flow path located between the outdoor heat exchanger and the gas-liquid separator.

[0011] In some embodiments, a bypass throttling element is provided on the bypass branch to throttle the refrigerant flowing back to the compressor via the bypass branch; and / or, a bypass valve is provided on the bypass branch to control the opening and closing of the bypass branch.

[0012] In some embodiments, an oil separator is also provided in the circulation loop. The oil separator is connected to the outlet of the compressor to separate the lubricating oil in the refrigerant flowing out of the compressor. A cold oil heat exchanger for cooling the lubricating oil is provided on the bypass branch. The cold oil heat exchanger is connected to the oil separator and the compressor through a cold oil flow path so that the lubricating oil separated by the oil separator is cooled by the refrigerant in the bypass branch and flows back to the compressor.

[0013] In some embodiments, the air conditioner is configured to be at least one of the following:

[0014] The cold oil heat exchanger is located downstream of the bypass throttling element on the bypass branch, along the direction in which the refrigerant flows through the bypass branch.

[0015] A cold oil valve is installed in the cold oil flow path, which controls the opening and closing of the cold oil flow path;

[0016] A cold oil throttling device is provided in the cold oil flow path to throttle the lubricating oil flowing back to the compressor through the cold oil flow path.

[0017] In some embodiments, the cold oil valve is disposed upstream of the cold oil heat exchanger along the direction of the lubricating oil flow through the cold oil flow path; and / or, the cold oil throttling element is disposed downstream of the cold oil heat exchanger along the direction of the lubricating oil flow through the cold oil flow path.

[0018] In addition, this application also provides a control method for an air conditioner based on any embodiment, which includes:

[0019] Determine whether the air conditioner is cooling or heating;

[0020] When the air conditioner is cooling or heating, a bypass branch is used to return the refrigerant in the defrosting path to the compressor.

[0021] In some embodiments, during the process of returning the refrigerant in the defrosting flow path to the compressor using the bypass branch when the air conditioner is cooling or heating, the opening of the bypass throttling device on the bypass branch is adjusted.

[0022] In some embodiments, during air conditioning cooling or heating, when the refrigerant in the defrosting flow path is returned to the compressor via a bypass branch without passing through the gas-liquid separator, adjusting the opening of the bypass throttling element on the bypass branch includes at least one of the following:

[0023] When the air conditioner is cooling, the opening of the bypass throttling device on the bypass branch is adjusted according to the compressor's exhaust temperature.

[0024] When the air conditioner is in heating mode, the opening of the bypass throttling device on the bypass branch is adjusted according to the low pressure value of the compressor.

[0025] In some embodiments, during air conditioning cooling, adjusting the opening of the bypass throttling device on the bypass branch according to the compressor's discharge temperature includes at least one of the following:

[0026] When T < a, the opening degree of the bypass throttling device is set to 0;

[0027] When a≤T<b, make the opening degree of the bypass throttling device A;

[0028] When b≤T<c, make the opening of the bypass throttling device B;

[0029] When T≥c, the opening degree of the bypass throttling device is C;

[0030] Where T is the compressor's exhaust temperature, a < b < c, 0 < A < B < C.

[0031] In some embodiments, 85℃; and / or, 90℃; and / or, 95℃; and / or, ; and / or, 300 steps; and / or, 350 steps.

[0032] In some embodiments, when the air conditioner is in heating mode, adjusting the opening of the bypass throttling device on the bypass branch according to the low pressure value of the compressor includes at least one of the following:

[0033] When L < m, the opening degree of the bypass throttling device is D;

[0034] When m≤L<n, the opening degree of the bypass throttling device is E;

[0035] When n≤L<p, make the opening degree of the bypass throttling device F;

[0036] When L≥p, the opening of the bypass throttling device is set to 0;

[0037] Where L is the saturation temperature of the refrigerant corresponding to the low pressure value of the compressor, m < n < p, D > E > F > 0.

[0038] In some embodiments, ; and / or, ; and / or, ; and / or, ; and / or, ; and / or, .

[0039] In some embodiments, during the cooling process of the air conditioner, the refrigerant in the defrosting flow path is disconnected from the gas-liquid separator during the process of returning the refrigerant in the defrosting flow path to the compressor via a bypass branch; and / or, during the heating process of the air conditioner, the defrosting flow path is connected to the gas-liquid separator during the process of returning the refrigerant in the defrosting flow path to the compressor via a bypass branch, so that the refrigerant is returned to the compressor via the gas-liquid separator through the defrosting flow path.

[0040] In some embodiments, during the air conditioning cooling or heating process, when the refrigerant in the de-icing flow path is led back to the compressor using the bypass branch, the oil heat exchanger located on the bypass branch is also connected to the compressor and the oil separator so that the lubricating oil flowing back to the compressor from the oil separator is cooled by the refrigerant in the bypass branch.

[0041] Furthermore, this application also provides a controller including a memory and a processor coupled to the memory, the processor being configured to execute the control method of any embodiment based on instructions stored in the memory.

[0042] In addition, this application also provides an air conditioning system, which includes an air conditioner of any embodiment and a controller of any embodiment.

[0043] In addition, this application also provides a storage medium storing computer instructions, which are executed by a processor using the control method of any embodiment.

[0044] By setting up a bypass branch to return the refrigerant in the defrosting flow path to the compressor, the refrigerant in the compressor can be quickly replenished. Therefore, the adverse effects of insufficient refrigerant on the overall reliability of the unit can be effectively reduced, thereby effectively improving the reliability of the air conditioner.

[0045] Other features and advantages of this application will become clear from the following detailed description of exemplary embodiments with reference to the accompanying drawings. Attached Figure Description

[0046] To more clearly illustrate the technical solutions in the embodiments of this application 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 this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0047] Figure 1 This is a schematic diagram illustrating the working principle of an air conditioner in one embodiment of this application.

[0048] Figure 2 This is a schematic diagram illustrating the working principle of an air conditioner in another embodiment of this application.

[0049] Explanation of reference numerals in the attached figures

[0050] 100. Air conditioning;

[0051] 1. Circulation loop; 11. Compressor; 12. Oil separator; 13. Four-way valve; 14. Outdoor heat exchanger; 15. Subcooler; 16. First valve; 17. Indoor heat exchanger; 18. Second valve; 19. Gas-liquid separator;

[0052] 2. Return oil flow path; 21. Return oil valve; 22. Return oil throttling element;

[0053] 3. De-icing flow path; 31. Filter; 32. De-icing throttling element; 33. De-icing valve; 34. De-icing heat exchange tube;

[0054] 4. Bypass branch; 41. Bypass throttling device; 42. Cold oil heat exchanger;

[0055] 5. Cold oil flow path; 51. First oil passage; 52. Second oil passage; 53. Cold oil throttling device; 54. Cold oil valve;

[0056] 6. Capillary tube;

[0057] 7. Throttling valve. Detailed Implementation

[0058] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit this application or its application or use. All other embodiments obtained by those skilled in the art based on the embodiments of this application without creative effort are within the scope of protection of this application.

[0059] Techniques, methods, and equipment known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and equipment should be considered part of the specification.

[0060] In the description of this application, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is usually based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this application and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this application; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0061] In the description of this application, it should be understood that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this application.

[0062] In this application, unless otherwise stated, “multiple” means at least two, that is, including cases of two and at least three.

[0063] Furthermore, the technical features involved in the different embodiments of this application described below can be combined with each other as long as they do not conflict with each other.

[0064] In practice, it has been found that insufficient refrigerant in air conditioners can cause many reliability problems for the unit, and may even cause the unit to fail to work properly.

[0065] For example, during cooling, if the amount of refrigerant in the unit is too low, less refrigerant will return to the compressor, which will not be able to effectively cool the compressor motor and other components. As a result, the heat cannot be effectively dissipated, leading to excessively high compressor discharge temperature. This will cause the compressor to operate under fatigue for a long time, making it prone to damage, shortening its lifespan, and affecting the reliability of the air conditioner.

[0066] For example, if the amount of refrigerant in the unit is too low when heating, it will result in a low low pressure value of the compressor, poor heating capacity stability, rapid degradation, and affect the reliability of the air conditioner.

[0067] It is evident that insufficient refrigerant, whether in cooling or heating mode, will affect the reliability of the air conditioner.

[0068] In view of the above, this application provides an air conditioner.

[0069] Figure 1 and Figure 2 An air conditioner is illustrated as an example in this application.

[0070] See Figure 1 and Figure 2 In this application, the air conditioner 100 includes a circulation loop 1 and a de-icing flow path 3.

[0071] In this circuit, loop 1 is used to circulate the refrigerant for cooling or heating. For example... Figure 1 and Figure 2 As shown, the circulation loop 1 is equipped with a compressor 11, an outdoor heat exchanger 14, and a gas-liquid separator 19.

[0072] The de-icing flow path 3 is used to de-ice the outdoor heat exchanger 14 to prevent icing and frost buildup from affecting its normal operation. For example... Figure 1 and Figure 2As shown, the de-icing flow path 3 connects the outlet of the compressor 11 and the inlet of the gas-liquid separator 19, and is thermally coupled to the outdoor heat exchanger 14 to de-ice the outdoor heat exchanger 14 using the high-temperature refrigerant flowing from the compressor 11. The thermal coupling between the de-icing flow path 3 and the outdoor heat exchanger 14 means that heat exchange is possible between them, with the refrigerant in the de-icing flow path 3 de-icing the outdoor heat exchanger 14. As another method of thermal coupling between the de-icing flow path 3 and the outdoor heat exchanger 14, the de-icing flow path 4 is thermally coupled to the outdoor heat exchanger 14 through a de-icing heat exchange pipe 34 located at the bottom of the outdoor heat exchanger 14. During operation, a portion of the high-temperature refrigerant flowing from the compressor 11 outlet flows into the defrosting flow path 3 and passes through the defrosting heat exchange tube 34 at the bottom of the outdoor heat exchanger 14, releasing heat to defrost the outdoor heat exchanger 14. Afterward, it flows through the gas-liquid separator 19 and back to the compressor 11. This defrosting effect is achieved by allowing the high-temperature refrigerant to flow directly from the high-pressure side through the outdoor heat exchanger 14. The defrosting flow path 3 typically operates in heating mode but not in cooling mode.

[0073] To prevent insufficient refrigerant from affecting the reliability of air conditioner 100, please refer to... Figure 1 and Figure 2 In this application, the air conditioner 100 includes not only the circulation loop 1 and the defrosting flow path 3, but also a bypass branch 4. The bypass branch 4 connects the defrosting flow path 3 and the inlet of the compressor 11 to return the refrigerant in the defrosting flow path 3 to the compressor 11.

[0074] By adding a bypass branch 4 to the defrosting flow path 3, the refrigerant in the defrosting flow path 3 can be directly returned to the compressor 11. This allows at least a portion of the refrigerant in the defrosting flow path 3 to flow back to the compressor 11 without passing through the gas-liquid separator 19. This shortens the path and time for the refrigerant to return to the compressor 11, enabling the refrigerant to flow back to the compressor 11 more quickly and increasing the amount of refrigerant in the compressor 11 more promptly. This effectively prevents the air conditioner 100 from being affected by insufficient refrigerant.

[0075] For example, in cooling mode, by using the bypass branch 4 to directly return the refrigerant in the defrosting flow path 3 to the compressor 11, the refrigerant can quickly return to the compressor 11, increasing the amount of refrigerant in the compressor 11, enhancing the cooling of the motor and other components of the compressor 11, alleviating the problem of insufficient cooling and high exhaust temperature caused by insufficient refrigerant in the compressor 11, and thus effectively reducing the risk of damage to the compressor 11 and extending its lifespan. In this way, the operational reliability of the air conditioner 100 can be effectively improved.

[0076] Moreover, in cooling mode, the defrosting flow path 3 is not working. The refrigerant entering the defrosting flow path 3 does not flow back to the compressor 11, but accumulates in the defrosting flow path 3, resulting in refrigerant waste. By drawing a bypass branch 4 from the defrosting flow path 3, the refrigerant originally left in the defrosting flow path 3 is returned to the compressor 11, which can reduce refrigerant waste, improve refrigerant utilization, and will not, or at least will not, affect the normal cooling process, thus achieving stable operation of the whole unit.

[0077] It can be seen that, in the cooling state, by using the bypass branch 4 to return the refrigerant in the defrosting flow path 3 to the compressor 11, the waste of refrigerant can be reduced and the utilization rate of refrigerant can be improved without affecting the normal cooling operation. This also alleviates the problem of the compressor 11 running under fatigue for a long time due to insufficient refrigerant and high exhaust temperature, effectively improving the working reliability of the air conditioner 100.

[0078] For example, in heating mode, the refrigerant in the defrosting flow path 3 flows back to the compressor 11 via the gas-liquid separator 19 to defrost the outdoor heat exchanger 14. At the same time, a portion of the refrigerant in the defrosting flow path 3 is directly led back to the compressor 11 without passing through the gas-liquid separator 19 using the bypass branch 4. This allows the refrigerant to return to the compressor 11 closer to the suction port, which not only allows this portion of refrigerant to return to the compressor 11 quickly and increase the amount of refrigerant in the compressor 11 in time, but also reduces refrigerant loss caused by deposits at the bottom of the gas-liquid separator 19 and reduces pressure loss caused by the refrigerant flowing through the gas-liquid separator 19. Therefore, it is beneficial to improve the low pressure value of the compressor 11 and effectively solve the problem of poor heating capacity stability and rapid heating capacity decay caused by low low pressure value. In this way, the working reliability of the air conditioner 100 can be effectively improved.

[0079] The refrigerant in the defrosting flow path 3 returns to the compressor 11 only after passing through the gas-liquid separator 19. This does not significantly increase the low pressure of the compressor 11 during heating because some liquid refrigerant is separated and stored at the bottom of the gas-liquid separator 19 when it returns to the compressor 11, resulting in a refrigerant loss and less refrigerant returning to the compressor 11. Moreover, the gas-liquid separator 19 is a large-volume cavity, and there will be a relatively large pressure loss when the refrigerant passes through it. In particular, during heating, the refrigerant stored in the gas-liquid separator 19 is returned directly from the outdoor heat exchanger 14, and the temperature of the entire gas-liquid separator 19 is relatively low, while the refrigerant in the defrosting flow path 3 is at a higher temperature and enters the gas-liquid separator 19, resulting in a large pressure loss.

[0080] By using the bypass branch 4 to guide a portion of the refrigerant in the defrosting flow path 3 back to the compressor 11 closer to the compressor 11 inlet, the problems of refrigerant quantity and pressure loss caused by all the refrigerant in the defrosting flow path 3 returning to the compressor 11 through the gas-liquid separator 19 can be effectively mitigated. This effectively increases the low pressure value of the compressor 11, improves the stability of the heating capacity of the air conditioner 100, delays the decay of the heating capacity, and thus effectively improves the working reliability of the air conditioner 100.

[0081] Furthermore, during heating, the defrosting flow path 3 can still operate according to normal logic without being affected by the bypass branch 4. Therefore, using the bypass branch 4 to guide a portion of the refrigerant in the defrosting flow path 3 back to the compressor 11 at a location closer to the compressor 11 inlet does not affect the normal heating and defrosting process, thus enabling stable operation of the entire unit.

[0082] It can be seen that in heating mode, by using the bypass branch 4 to return the refrigerant in the defrosting flow path 3 to the compressor 11, the low pressure value of the compressor 11 can be effectively increased without affecting the normal heating and defrosting process, thus delaying the decline in heating capacity and improving the working reliability of the air conditioner 100.

[0083] As can be seen from the above analysis, whether in cooling mode or heating mode, using the bypass branch 4 to return the refrigerant in the defrosting flow path 3 to the compressor 11 can effectively reduce the adverse effects of insufficient refrigerant on the unit's operational reliability, thereby effectively improving the operational reliability of the air conditioner 100.

[0084] The connection position of the bypass branch 4 on the de-icing flow path 3 can be varied.

[0085] For example, the connection point of the bypass branch 4 on the de-icing flow path 3 can be located on the flow path of the de-icing flow path 3 between the outdoor heat exchanger 14 and the compressor 11 outlet, or on the flow path of the de-icing flow path 3 between the outdoor heat exchanger 14 and the gas-liquid separator 19. See also... Figure 1 and Figure 2When the bypass branch 4 is connected to the de-icing flow path 3 at the point where the de-icing flow path 3 is located between the outdoor heat exchanger 14 and the gas-liquid separator 19, the bypass branch 4 is connected to the portion of the de-icing flow path 3 between the outdoor heat exchanger 14 and the gas-liquid separator 19. The connection point of the bypass branch 4 on the de-icing flow path 3 is downstream of the de-icing heat exchange tube 34 along the direction of refrigerant flow through the de-icing flow path 3. This facilitates the bypass branch 4 in cooling mode to return the refrigerant deposited in the de-icing heat exchange tube 34 to the compressor 1. 1. Since the defrosting flow path 3 does not work in the cooling mode, the refrigerant in the defrosting flow path 3 is mainly deposited in the defrosting heat exchange tube 34. Therefore, the bypass branch 4 is connected to the flow path of the defrosting flow path 3 located between the outdoor heat exchanger 14 and the gas-liquid separator 19. In the cooling mode, the refrigerant deposited in the defrosting heat exchange tube 34 is led back to the compressor 11, which makes it easier to lead more refrigerant back to the compressor 11, more effectively increase the amount of refrigerant in the compressor 11, increase the exhaust temperature of the compressor 11, and improve the working reliability of the air conditioner 100.

[0086] For example, see Figure 1 and Figure 2 In some embodiments, a defrosting valve 33 is provided on the defrosting flow path 3. The defrosting valve 33 is used to control the opening and closing of the defrosting flow path 3. Along the direction of refrigerant flow through the defrosting flow path 3, the connection position of the bypass branch 4 and the defrosting flow path 3 is located upstream of the defrosting valve 33. At this time, the defrosting valve 33 only controls the opening and closing of the defrosting flow path 3, but does not control the opening and closing of the bypass branch 4. The operation of the bypass branch 4 is not affected by whether the defrosting flow path 3 is working. Therefore, in the cooling mode, simply closing the defrosting valve 33 will prevent the defrosting flow path 3 from working, but will not affect the operation of the bypass branch 4. The bypass branch 4 can still draw out the refrigerant in the defrosting flow path 3 and bring it back to the compressor 11. Therefore, it can effectively meet the different requirements of the defrosting flow path 3 not working and the bypass branch 4 working in the cooling mode, effectively improve the compressor exhaust temperature in the cooling mode, and effectively improve the working reliability of the air conditioner 100.

[0087] For example, see Figure 1 and Figure 2 In some embodiments, the de-icing flow path 3 is provided with a de-icing throttling device 32, which throttles the refrigerant in the de-icing flow path 3. Along the direction of refrigerant flow through the de-icing flow path 3, the connection position of the bypass branch 4 and the de-icing flow path 3 is located downstream of the de-icing throttling device 32. In this way, the refrigerant drawn from the de-icing flow path 3 by the bypass branch 4 can be throttled by the de-icing throttling device 32, resulting in a decrease in temperature and pressure. This can better meet the refrigerant return requirements of the compressor 11, and thus is more conducive to improving the working reliability of the air conditioner 100.

[0088] For example, see Figure 1 and Figure 2In some embodiments, the defrosting flow path 3 is equipped with both a defrosting valve 33 and a defrosting throttling device 32. The defrosting throttling device 32 and the defrosting valve 33 are arranged sequentially along the direction of refrigerant flow through the defrosting flow path 3. The bypass branch 4 is connected to the defrosting flow path 3 between the defrosting valve 33 and the defrosting throttling device 32. In this way, the refrigerant led to the compressor 11 by the bypass branch 4 is refrigerant that has been throttled by the defrosting throttling device 32, which better meets the refrigerant return requirements of the compressor 11. Furthermore, in cooling mode, the defrosting flow path 3 can be shut down by closing the defrosting valve 33, and the bypass branch 4 can be operated. This increases the discharge temperature of the compressor 11 without affecting the normal operation of the cooling system, thus effectively improving the operational reliability of the air conditioner 100.

[0089] As a further improvement to the foregoing embodiments, see Figure 2 The bypass branch 4 is equipped with a bypass throttling device 41 to throttle the refrigerant flowing back to the compressor 11 via the bypass branch 4. In this way, the refrigerant flowing into the bypass branch 4 can be throttled by the bypass throttling device 41, so that the refrigerant flowing back to the compressor 11 via the bypass branch 4 is a low-temperature, low-pressure gaseous refrigerant, which better meets the refrigerant return requirements of the compressor 11, more effectively improves the working reliability of the compressor 11, and thus improves the working reliability of the air conditioner 100. In particular, when the connection point between the bypass branch 4 and the de-icing flow path 3 is located downstream of the de-icing throttling device 32 along the direction of refrigerant flow through the de-icing flow path 3, a bypass throttling device 41 is further provided on the bypass branch 4. The de-icing throttling device 32 and the bypass throttling device 41 together can throttle the refrigerant flowing back to the compressor 11 through the bypass branch 4 twice, making it more reliable that the refrigerant flowing back to the compressor 11 is a low-temperature, low-pressure gaseous refrigerant, better meeting the refrigerant return requirements of the compressor 11, and more effectively improving the working reliability of the air conditioner 100.

[0090] The bypass throttling device 41 can be any structure capable of throttling, such as a throttling orifice plate, capillary tube 6, or throttling valve 7. When the bypass throttling device 41 includes a throttling valve 7, it offers higher precision and stronger controllability, which is beneficial for more accurate control of the refrigerant flowing back to the compressor 11 via the bypass branch 4. This more effectively alleviates the problem of low reliability caused by insufficient refrigerant and improves the operational reliability of the air conditioner 100.

[0091] In some embodiments, a bypass valve (not shown) is provided on the bypass branch 4 to control the opening and closing of the bypass branch 4. This allows for convenient control of whether the bypass branch 4 is working by controlling the opening and closing of the bypass valve, so that the bypass branch 4 is only opened and operated when needed.

[0092] See also Figure 2As a further improvement to the aforementioned embodiments, a cold oil heat exchanger 42 for cooling lubricating oil is provided on the bypass branch 4. The cold oil heat exchanger 42 is connected to the compressor 11 and the oil separator 12 (connected to the outlet of the compressor 11 to separate the lubricating oil in the refrigerant flowing out of the compressor 11) through the cold oil flow path 5, so that the lubricating oil separated by the oil separator 12 is cooled by the refrigerant in the bypass branch 4 and flows back to the compressor 11. In this way, on the one hand, the temperature of the lubricating oil flowing back to the compressor 11 is lower, which can achieve a better cooling effect and more effectively prevent the lubricating oil from overheating; on the other hand, the lubricating oil separated by the oil separator 12 inevitably contains some gaseous refrigerant, which cools the lubricating oil and helps the gaseous refrigerant to contract, reduce its specific volume, and increase the amount of oil flowing back to the compressor 11 per unit time, effectively enhancing the oil return effect; furthermore, after the refrigerant in the bypass branch 4 cools the lubricating oil, its temperature can be increased to a certain extent. The corresponding temperature increase is beneficial to increasing the low pressure value of the compressor 11 in heating mode and improving the stability of the heating capacity. All of these factors contribute to further improving the operational reliability of the air conditioner 100.

[0093] It can be seen that by further installing a cold oil heat exchanger 42 on the bypass branch 4 to achieve the cooling of the lubricating oil flowing back to the compressor 11 by the refrigerant in the bypass branch 4, the working reliability of the air conditioner 100 can be further improved.

[0094] The location of the cold oil heat exchanger 42 on the bypass branch 4 can vary. For example, see... Figure 2 When a bypass throttling element 41 is provided on the bypass branch 4, the cold oil heat exchanger 42 can be located upstream or downstream of the bypass throttling element 41 on the bypass branch 4 along the direction in which the refrigerant flows through the bypass branch 4. When the oil heat exchanger 42 is located downstream of the bypass throttling device 41 along the direction of refrigerant flow through the bypass branch 4, it is more conducive to improving the working reliability of the air conditioner 100. This is because, on the one hand, the refrigerant in the bypass branch 4 flows into the oil heat exchanger 42 only after passing through the bypass throttling device 41. The refrigerant flowing into the oil heat exchanger 42 has already undergone the throttling effect of the bypass throttling device 41, and its temperature is lower, which is conducive to more fully absorbing the heat of the lubricating oil and achieving a better cooling effect on the lubricating oil. On the other hand, after cooling the lubricating oil, the refrigerant flowing out of the oil heat exchanger 42 does not need to go through the throttling and cooling effect of the bypass throttling device 41 again and can flow directly back to the compressor 11. In this way, the temperature of the refrigerant flowing back to the compressor 11 from the bypass branch 4 is relatively high, which is conducive to increasing the low pressure value of the compressor 11 in the heating mode. All of these factors are conducive to further improving the working reliability of the air conditioner 100. It is understandable that although the temperature of the lubricating oil increases to some extent after the refrigerant cools it, the refrigerant is still a low-temperature, low-pressure gaseous refrigerant, and therefore can still meet the refrigerant return requirements of compressor 11.

[0095] In the case where a cold oil heat exchanger 42 is installed on the bypass branch 4, see Figure 2 In some embodiments, the cold oil flow path 5, which connects the cold oil heat exchanger 42 to the compressor 11 and the oil separator 12, is provided with a cold oil valve 54 and / or a cold oil throttling element 53.

[0096] The cooling oil valve 54 controls the opening and closing of the cooling oil flow path 5. This allows for convenient control over whether to activate the cooling oil flow path 5 and whether to utilize the cooling oil heat exchanger 42 to cool the lubricating oil using the refrigerant in the bypass branch 4, improving the unit's operational flexibility. The cooling oil valve 54 can be positioned in various ways on the cooling oil flow path 5; for example, it can be positioned upstream or downstream of the cooling oil heat exchanger 42 along the direction of lubricating oil flow through the cooling oil flow path 5. When the cooling oil valve 54 is positioned upstream of the cooling oil heat exchanger 42 along the direction of lubricating oil flow through the cooling oil flow path 5, closing the cooling oil valve 54 prevents lubricating oil from entering the cooling oil heat exchanger 42, thus facilitating more reliable control over whether the cooling oil heat exchanger 42 stops cooling the lubricating oil.

[0097] The oil throttling device 53 throttles the lubricating oil flowing back to the compressor 11 via the oil cooling path 5. In this way, the oil throttling device 53, together with the oil cooling heat exchanger 42, can achieve two-stage cooling of the lubricating oil, thus further improving the cooling effect of the lubricating oil and enhancing the operational reliability of the air conditioner 100. The oil throttling device 53 can be positioned in various ways on the oil cooling path 5; for example, it can be positioned upstream or downstream of the oil cooling heat exchanger 42 along the direction of lubricating oil flow through the oil cooling path 5. When the oil throttling element 53 is positioned downstream of the oil heat exchanger 42 along the direction of the lubricating oil flow through the oil flow path 5, the lubricating oil flowing through the oil heat exchanger 42 has not yet undergone the throttling effect of the oil throttling element 53, and its temperature is relatively high. This allows for better heat exchange with the refrigerant in the bypass branch 4, thus fully utilizing the function of the oil heat exchanger 42 and achieving a better heat exchange effect. While effectively cooling the lubricating oil, it further increases the temperature of the refrigerant flowing back to the compressor 11 via the bypass branch 4, improving the stability of the heating capacity. Furthermore, the lubricating oil flowing out of the oil heat exchanger 42 can undergo further throttling by the oil throttling element 53, further reducing its temperature. This results in an even lower temperature of the lubricating oil returning to the compressor 11, more effectively preventing the lubricating oil from overheating, thereby further improving the operational reliability of the air conditioner 100.

[0098] The cold oil throttling device 53 can be any structural form capable of throttling, such as a throttling orifice plate, capillary tube 6, or throttling valve 7. Since the precision requirements of the throttling process for lubricating oil are relatively low, when the cold oil throttling device 53 includes a capillary tube 6, the throttling requirements of the lubricating oil can be met, and it is beneficial to reduce costs and simplify the control process.

[0099] The air conditioner 100 in the foregoing embodiments can be of various types. For example, in some embodiments, the air conditioner 100 is a multi-split air conditioner. Multi-split air conditioners are more prone to refrigerant shortages during operation. Therefore, when the air conditioner 100 is a multi-split air conditioner, the bypass branch 4 is more effective and can more effectively improve operational reliability.

[0100] Based on the air conditioner 100 of the foregoing embodiments, this application also provides a control method, which includes:

[0101] Determine whether the air conditioner is cooling or heating;

[0102] When the air conditioner 100 is cooling or heating, the refrigerant in the defrosting flow path 3 is returned to the compressor 11 by using the bypass branch 4.

[0103] Based on the above steps, in cooling or heating mode, at least a portion of the refrigerant in the defrosting flow path 3 can be drawn back to the compressor 11 from a position closer to the compressor 11 inlet by the bypass branch 4, thereby achieving rapid replenishment of the compressor refrigerant and effectively alleviating the problem of insufficient refrigerant during cooling or heating. Therefore, the working reliability of the air conditioner 100 can be effectively improved.

[0104] Furthermore, in some embodiments, when the air conditioner 100 is cooling or heating, during the process of the refrigerant in the defrosting flow path 3 being returned to the compressor 11 via the bypass branch 4 without passing through the gas-liquid separator 19, the opening degree of the bypass throttling device 41 on the bypass branch 4 is adjusted. This allows for real-time adjustment of the throttling effect of the bypass throttling device 41 on the refrigerant in the bypass branch 4 according to actual conditions, making the amount of refrigerant flowing back to the compressor 11 via the bypass branch 4 more consistent with actual needs, thereby more effectively improving the operational reliability of the air conditioner 100.

[0105] For example, in some embodiments, when the air conditioner 100 is cooling, the opening of the bypass throttling device 41 on the bypass branch 4 is adjusted according to the discharge temperature of the compressor 11. In this way, the amount of refrigerant returning to the compressor 11 via the bypass branch 4 in cooling mode can be adjusted according to the actual magnitude of the compressor discharge temperature, which is more consistent with the actual demand for refrigerant in cooling mode, thereby more effectively regulating the discharge temperature and more reliably improving the operational reliability of the air conditioner 100.

[0106] Specifically, in some embodiments, when the air conditioner 100 is cooling, adjusting the opening of the bypass throttling element 41 on the bypass branch 4 according to the exhaust temperature of the compressor 11 includes at least one of the following:

[0107] When T < a, the opening degree of the bypass throttling element 41 is set to 0;

[0108] When a≤T<b, the opening degree of the bypass throttling device 41 is set to A;

[0109] When b≤T<c, the opening degree of the bypass throttling device 41 is B;

[0110] When T≥c, the opening degree of the bypass throttling device 41 is C;

[0111] Where T is the exhaust temperature of compressor 11, a < b < c, 0 < A < B < C.

[0112] In the above steps, the opening of the bypass throttling device 41 increases as the discharge temperature of the compressor 11 increases. Thus, the higher the discharge temperature of the compressor 11, the more refrigerant flows back to the compressor 11 through the bypass branch 4, which can effectively increase the amount of refrigerant in the compressor 11, reduce the discharge temperature of the compressor 11, and prevent the compressor 11 from operating under fatigue for a long time. Therefore, it is more conducive to improving the working reliability of the air conditioner 100.

[0113] In the above steps, the values ​​of a, b, c, A, B, and C can be varied. As an example, in some embodiments, 85℃; and / or, 90℃; and / or, 95℃; and / or, ; and / or, 300 steps; and / or, 350 steps. In this way, the adjustment gradient of the bypass throttling device 41 opening degree is more reasonable in cooling mode, which is more conducive to improving the working reliability of air conditioner 100.

[0114] In some embodiments, when the air conditioner 100 is in heating mode, the opening degree of the bypass throttling device 41 on the bypass branch 4 is adjusted according to the low pressure value of the compressor 11. This allows the amount of refrigerant returning to the compressor 11 via the bypass branch 4 in heating mode to be adjusted according to the actual value of the compressor's low pressure, making it more consistent with the actual refrigerant demand in heating mode. This more effectively regulates the low pressure value of the compressor 11 and reliably improves the operational reliability of the air conditioner 100.

[0115] Specifically, in some embodiments, when the air conditioner 100 is heating, adjusting the opening of the bypass throttling element 41 on the bypass branch 4 according to the low pressure value of the compressor 11 includes at least one of the following:

[0116] When L < m, the opening degree of the bypass throttling element 41 is set to D;

[0117] When m≤L<n, the opening degree of the bypass throttling device 41 is set to E;

[0118] When n≤L<p, the opening degree of the bypass throttling device 41 is F;

[0119] When L≥p, the opening degree of the bypass throttling element 41 is set to 0;

[0120] Where m < n < p, D > E > F > 0, and L is the saturation temperature of the refrigerant corresponding to the low pressure value of compressor 11. It can be understood that L is directly proportional to the low pressure value of compressor 11; the higher L is, the higher the low pressure value of compressor 11.

[0121] In the above steps, the opening of the bypass throttling device 41 decreases as the low pressure of the compressor 11 increases. Thus, the lower the low pressure of the compressor 11, the more refrigerant flows back to the compressor 11 through the bypass branch 4, which can effectively increase the amount of refrigerant in the compressor 11, improve the low pressure of the compressor 11, and prevent the heating capacity from rapidly decreasing. Therefore, it is more conducive to improving the working reliability of the air conditioner 100.

[0122] In the above steps, the values ​​of m, n, p, D, E, and F can be varied. As an example, in some embodiments, ; and / or, ; and / or, ; and / or, ; and / or, ; and / or, In this way, the adjustment gradient of the bypass throttling device 41 opening degree is more reasonable in heating mode, which is more conducive to improving the working reliability of air conditioner 100.

[0123] In the foregoing embodiments, during the cooling process of the air conditioner 100, the bypass branch 4 can be used to return the refrigerant in the defrosting flow path 3 to the compressor 11, thereby disconnecting the defrosting flow path 3 from the gas-liquid separator 19. In this way, during cooling, the bypass branch 4 operates while the defrosting flow path 3 does not, which can reduce the exhaust temperature of the compressor 11 without affecting the normal cooling process, thus improving the operational reliability of the air conditioner 100.

[0124] Furthermore, when the air conditioner 100 is in heating mode, during the process of using the bypass branch 4 to return the refrigerant in the defrosting flow path 3 to the compressor 11, the defrosting flow path 3 can be connected to the gas-liquid separator 19, so that the refrigerant can be returned to the compressor 11 via the gas-liquid separator 19 through the defrosting flow path 3. In this way, during heating, both the bypass branch 4 and the defrosting flow path 3 are working, which can effectively defrost the outdoor heat exchanger 14 while increasing the low pressure value of the compressor 11, thereby improving the operational reliability of the air conditioner 100.

[0125] Furthermore, when the bypass branch 4 is equipped with an oil heat exchanger 42, during the cooling or heating operation of the air conditioner 100, when the refrigerant in the defrosting flow path 3 is returned to the compressor 11 via the bypass branch 4, the oil heat exchanger 42 located on the bypass branch 4 can be connected to the compressor 11 and the oil separator 12. This allows the refrigerant in the bypass branch 4 to cool the lubricating oil flowing back to the compressor 11 from the oil separator 12. This reduces the temperature of the lubricating oil flowing back to the compressor 11, enhances the oil return effect, and helps to increase the low-pressure value of the compressor 11 in heating mode. Therefore, it effectively improves the operational reliability of the air conditioner 100.

[0126] The control methods of the foregoing embodiments can be performed under the control of a controller. The controller includes a memory and a processor coupled to the memory, and the processor is configured to execute the control method of any embodiment based on instructions stored in the memory.

[0127] In addition, this application also provides an air conditioning system, which includes an air conditioner 100 of any embodiment and a controller of any embodiment.

[0128] In addition, this application also provides a storage medium storing computer instructions, which are executed by a processor using the control method of any embodiment.

[0129] Next, combine Figure 1 and Figure 2 The present application will be further described through embodiments thereof.

[0130] First, let's introduce Figure 1 The example shown.

[0131] like Figure 1 As shown, in this embodiment, the air conditioner 100 is a multi-split air conditioner and includes a circulation loop 1, an oil return path 2, a de-icing path 3, and a bypass branch 4.

[0132] In this system, circulation loop 1 is used to circulate the refrigerant, thereby enabling the air conditioner 100 to perform its cooling or heating functions. For example... Figure 1As shown, in this embodiment, the circulation loop 1 is equipped with a compressor 11, an oil separator 12 (referred to as oil separator), a four-way valve 13, an outdoor heat exchanger 14, a first valve 16, an indoor heat exchanger 17, a second valve 18, and a gas-liquid separator 19 (referred to as gas separator) connected in sequence. The compressor 11 is used to compress the refrigerant, so as to compress the low-temperature, low-pressure refrigerant into a high-temperature, high-pressure gaseous refrigerant. The four-way valve 13 is set between the outlet of the compressor 11 and the indoor heat exchanger 17 and the outdoor heat exchanger 14 to control the refrigerant flow direction, thereby realizing the switching between different modes such as cooling and heating. The oil separator 12 is set between the outlet of the compressor 11 and the four-way valve 13 to separate the oil and gas of the high-temperature refrigerant flowing out of the compressor 11, separating the lubricating oil in the refrigerant. The oil separator 12 is connected to the compressor 11 through the oil return path 2, so that the lubricating oil separated by the oil separator 12 can return to the compressor 11 through the oil return path 2, so as to ensure that the oil quantity in the compressor 11 is sufficient. The outdoor heat exchanger 14 is used to exchange heat between outdoor air and refrigerant, acting as a condenser during cooling and an evaporator during heating. The indoor heat exchanger 17 is used to exchange heat between indoor air and refrigerant, acting as an evaporator during cooling and a condenser during heating. The gas-liquid separator 19 is used to separate the refrigerant flowing back into the compressor 11 into gas and liquid components, preventing a large amount of liquid refrigerant from returning to the compressor 11, causing liquid slugging and damaging the compressor 11.

[0133] During refrigeration, the refrigerant flows as follows: compressor 11 — oil separator 12 — four-way valve 13 — outdoor heat exchanger 14 — first valve 16 — indoor heat exchanger 17 — second valve 18 — four-way valve 13 — gas-liquid separator 19 — back to compressor 11.

[0134] During heating, the refrigerant flows as follows: compressor 11 — oil separator 12 — four-way valve 13 — second valve 18 — indoor heat exchanger 17 — first valve 16 — outdoor heat exchanger 14 — four-way valve 13 — gas-liquid separator 19 — back to compressor 11.

[0135] The oil return path 2 connects the oil separator 12 and the compressor 11, and is used to return the lubricating oil separated by the oil separator 12 to the compressor 11 to ensure sufficient oil level in the compressor 11. Figure 1 As shown, in this embodiment, a return oil valve 21 is provided on the return oil flow path 2. The return oil valve 21 is used to control the opening and closing of the return oil flow path 2, so as to control whether the lubricating oil separated by the oil separator 12 is returned to the compressor 11 via the return oil flow path 2. In addition, a return oil throttling element 22 is also provided on the return oil flow path 2. The return oil throttling element 22 is located upstream of the return oil valve 21 along the direction of lubricating oil flow through the return oil flow path 2, and is used to throttle the lubricating oil flowing back to the compressor 11 via the return oil flow path 2, so as to reduce the temperature of the lubricating oil flowing back to the compressor 11 and prevent the lubricating oil from overheating.

[0136] The de-icing flow path 3 connects the outlet of the compressor 11 and the inlet of the gas-liquid separator 19, and passes through the de-icing heat exchange tube 34 at the bottom of the outdoor heat exchanger 14. This allows the high-temperature refrigerant to flow directly from the high-pressure side through the outdoor heat exchanger 14 and release heat to the outdoor heat exchanger 14, thereby de-icing the outdoor heat exchanger 14 and preventing icing and frost from affecting the normal operation of the outdoor heat exchanger 14.

[0137] like Figure 1 As shown, in this embodiment, one end of the de-icing flow path 3 is connected to the portion of the circulation loop 1 located between the compressor 11 outlet and the four-way valve 13 to achieve connection with the compressor 11 outlet, and the other end is connected to the portion of the circulation loop 1 located between the four-way valve 13 and the gas-liquid separator 19 to achieve connection with the gas-liquid separator 19 inlet.

[0138] And, as Figure 1 As shown, in this embodiment, the de-icing flow path 3 is equipped with a filter 31, a de-icing throttling device 32, and a de-icing valve 33. The filter 31, de-icing throttling device 32, and de-icing valve 33 are all located in the flow path of the de-icing flow path 3 between the outdoor heat exchanger 14 and the gas-liquid separator 19, and are arranged sequentially along the refrigerant flow direction, respectively for filtration, throttling, and on / off control. Thus, when the de-icing valve 33 is open, the refrigerant flowing from the compressor 11 into the de-icing flow path 3 can, after de-icing the outdoor heat exchanger 14, flow sequentially through the filter 31, the de-icing throttling device 32, and the de-icing valve 33, before flowing into the gas-liquid separator 19 and finally returning to the compressor 11. When flowing through the filter 31, the refrigerant is filtered to prevent blockage of the downstream de-icing throttling device 32 and the de-icing valve 33. When flowing through the de-icing throttling device 32, the refrigerant is throttled. In this embodiment, the de-icing throttling device 32 includes a capillary tube 6 to meet the throttling requirements of the refrigerant in the de-icing flow path 3 based on a simpler structure.

[0139] In this embodiment, the defrosting flow path 3 does not operate in cooling mode but only in heating mode. Correspondingly, the defrosting valve 33 is closed in cooling mode and opened in heating mode. In cooling mode, the refrigerant flowing from the compressor 11 into the defrosting flow path 3 is mainly deposited in the defrosting heat exchange tube 34.

[0140] Bypass branch 4 is led out from the defrost flow path 3 and connected to the inlet of compressor 11. By allowing the refrigerant in the defrost flow path 3 to flow back to compressor 11 without passing through gas-liquid separator 19, the refrigerant in compressor 11 is quickly replenished. This solves the problem of excessively high exhaust temperature of compressor 11 during cooling and low low pressure value during heating caused by insufficient refrigerant, effectively improving the working reliability of air conditioner 100.

[0141] like Figure 1As shown, in this embodiment, one end of the bypass branch 4 is connected to the portion of the defrosting flow path 3 located between the defrosting throttling element 32 and the defrosting valve 33, and the other end is connected to the inlet of the compressor 11, so as to connect the defrosting flow path 3 and the inlet of the compressor 11, so that refrigerant can be drawn out from the defrosting flow path 3 and the corresponding refrigerant can flow back to the compressor 11.

[0142] Since the bypass branch 4 is connected to the portion of the defrost flow path 3 located between the defrost throttling element 32 and the defrost valve 33, the connection point between the bypass branch 4 and the defrost flow path 3 is downstream of the defrost throttling element 32 and upstream of the defrost valve 33. In this way, the bypass branch 4 can return the refrigerant after being throttled by the defrost throttling element 32 to the compressor 11. Moreover, the opening and closing of the defrost valve 33 only controls the on / off state of the defrost flow path 3, and does not control the on / off state of the bypass branch 4. This not only meets the requirement that both the defrost flow path 3 and the bypass branch 4 work in the heating mode, but also meets the requirement that only the bypass branch 4 works and the defrost flow path 3 does not work in the cooling mode.

[0143] Bypass branch 4 operates in both cooling and heating modes. During operation, if... Figure 1 As shown by the solid arrow, the bypass branch 4 draws out the refrigerant after it has been throttled by the de-icing throttling device 32 in the de-icing flow path 3, so that the corresponding refrigerant can quickly flow back to the compressor 11, thereby quickly replenishing the refrigerant in the compressor 11, effectively increasing the amount of refrigerant in the compressor 11, alleviating the phenomenon of excessively high exhaust temperature when the compressor 11 is cooling and excessively low low pressure value when heating due to insufficient refrigerant, and effectively improving the working reliability of the air conditioner 100.

[0144] As can be seen, this embodiment adds a bypass branch 4 after the de-icing throttling element 32 in the de-icing flow path 3, so that the refrigerant does not pass through the gas-liquid separator 19 and quickly returns to the compressor 11. This can alleviate the problem of excessively high exhaust temperature caused by insufficient refrigerant during cooling, and also alleviate the problem of excessively low pressure caused by insufficient refrigerant during heating. Therefore, it can effectively improve the working reliability of the air conditioner 100.

[0145] Next, we will introduce... Figure 2 The example shown.

[0146] Depend on Figure 2 It can be seen that this embodiment is similar to the one described above. Figure 1 The main difference in the embodiment shown is that, in this embodiment, a subcooler 15 is provided on the circulation loop 1, and a bypass throttling device 41 and a cold oil heat exchanger 42 are arranged sequentially along the refrigerant flow direction on the bypass branch 4. At the same time, a cold oil flow path 5 is provided in the air conditioner 100.

[0147] The subcooler 15 is located between the outdoor heat exchanger 14 and the first valve 16 to recool the liquid refrigerant, thereby reducing throttling losses and improving the coefficient of performance (COP).

[0148] The bypass throttling device 41 includes a throttling valve 7, specifically an expansion valve, such as an electronic expansion valve. This allows for throttling of the refrigerant via the bypass branch 4, and by adjusting the opening of the bypass throttling device 41, the flow rate, pressure, and temperature of the refrigerant flowing back to the compressor 11 via the bypass branch 4 can be more precisely adjusted. This makes the flow rate, pressure, and temperature of the refrigerant flowing back to the compressor 11 via the bypass branch 4 more consistent with actual needs, and more precisely adjusts the discharge temperature of the compressor 11 during cooling and the low pressure value during heating, thereby more effectively improving the operational reliability of the air conditioner 100.

[0149] The oil heat exchanger 42 is arranged downstream of the bypass throttling element 41 along the refrigerant flow direction and is connected to the return oil flow path 2 and the compressor 11 through the oil flow path 5. This allows for heat exchange between the refrigerant in the bypass branch 4 and the lubricating oil separated by the oil separator 12. The refrigerant in the bypass branch 4 cools the lubricating oil, preventing it from overheating, and the lubricating oil raises the temperature of the refrigerant flowing back to the compressor 11 via the bypass branch 4, improving the stability of the heating capacity. In this embodiment, the oil heat exchanger 42 is a tubular heat exchanger, with refrigerant flowing through the tubes and lubricating oil flowing through the shell.

[0150] The cold oil flow path 5 connects the cold oil heat exchanger 42 with the return oil flow path 2 and the compressor 11, so that the lubricating oil flows back to the compressor 11 via the cold oil heat exchanger 42. Figure 2 As shown, in this embodiment, the cold oil flow path 5 includes a first oil path 51 and a second oil path 52. The first oil path 51 connects the return oil flow path 2 and the cold oil heat exchanger 42, and the second oil path 52 connects the cold oil heat exchanger 42 and the compressor 11, so as to realize the connection between the cold oil heat exchanger 42 and the return oil flow path 2 and the compressor 11.

[0151] And, as Figure 2 As shown, in this embodiment, a cooling oil valve 54 is provided on the first oil passage 51, and a cooling oil throttling device 53 is provided on the second oil passage 52. Thus, the cooling oil valve 54 and the cooling oil throttling device 53 are located upstream and downstream of the cooling oil heat exchanger 42, respectively, along the flow direction of the lubricating oil, for on / off control and throttling. Specifically, in this embodiment, the cooling oil throttling device 53 includes a capillary tube 6 to throttle the lubricating oil based on a relatively simple structure.

[0152] In this embodiment, both the bypass branch 4 and the cold oil flow path 5 operate in both cooling and heating modes. During operation, such as... Figure 2As shown by the solid arrow, bypass branch 4 draws out the refrigerant from the defrosting flow path 3 after it has been throttled by the defrosting throttling device 32. This allows the refrigerant to pass through the bypass throttling device 41 again, then through the oil heat exchanger 42, and back to the compressor 11. This rapidly replenishes the refrigerant in the compressor 11, effectively increasing the amount of refrigerant in the compressor 11. This alleviates the problem of excessively high exhaust temperature during cooling and excessively low pressure during heating caused by insufficient refrigerant, effectively improving the operational reliability of the air conditioner 100. Furthermore, as... Figure 2 As shown by the dashed arrow, when the oil cooling valve 54 is opened, the lubricating oil separated by the oil separator 12 flows into the oil cooling heat exchanger 42, exchanges heat with the refrigerant flowing through the oil cooling heat exchanger 42, and after cooling, flows through the oil cooling throttling element 53. After being throttled, it returns to the compressor 11, ensuring that the oil quantity in the compressor 11 is sufficient.

[0153] The bypass throttling device 41, acting as a throttling component of the bypass branch 4, further throttles the refrigerant after it has been throttled by the de-icing throttling device 32, ensuring that the refrigerant returning to the compressor 11 is a low-temperature, low-pressure refrigerant. During operation, the opening of the bypass throttling device 41 is adjusted according to the discharge temperature and low pressure of the compressor 11, so that the amount of refrigerant flowing back to the compressor 11 via the bypass branch 4 varies under different compressor discharge temperatures and low pressure conditions. This provides the compressor 11 with refrigerant replenishment that better meets actual needs, thus more effectively improving the operational reliability of the air conditioner 100.

[0154] Specifically, in this embodiment, during refrigeration, the defrosting valve 33 is closed, and the opening of the bypass throttling device 41 is adjusted as follows:

[0155] When T < a, the bypass throttling element 41 is closed, and the opening degree is 0.

[0156] When a≤T<b, the opening degree of the bypass throttling device 41 is A;

[0157] When b≤T<c, the opening degree of the bypass throttling device 41 is B;

[0158] When T≥c, the opening degree of the bypass throttling device 41 is C;

[0159] Where T is the exhaust temperature of compressor 11, a < b < c, 0 < A < B < C, for example, a is 81, 82, 83 or 84℃, b is 86, 87, 88 or 89℃, c is 91, 92, 93 or 94℃, A is 210, 220, 230 or 240 steps, B is 260, 270, 280 or 290 steps, and C is 310, 320, 330 or 340 steps.

[0160] By adopting the above method, the opening degree of the bypass throttling device 41 can be reasonably and gradually adjusted during cooling. This means that the higher the discharge temperature of the compressor 11, the larger the opening degree of the bypass throttling device 41. As a result, when the discharge temperature of the compressor 11 is higher, more refrigerant can be drawn back to the compressor 11 more quickly through the bypass branch 4, thereby increasing the amount of refrigerant in the compressor 11 more quickly and cooling it more rapidly. This effectively prevents the discharge temperature from being too high and affecting the working reliability of the air conditioner 100.

[0161] During heating, the defrosting valve 33 opens according to normal logic control, and the opening degree of the bypass throttling device 41 is controlled according to the low pressure value of the compressor 11; the two do not affect each other. The opening degree of the bypass throttling device 41 is adjusted as follows:

[0162] When L < m, the opening degree of the bypass throttling element 41 is set to D;

[0163] When m≤L<n, the opening degree of the bypass throttling device 41 is set to E;

[0164] When n≤L<p, the opening degree of the bypass throttling device 41 is F;

[0165] When L≥p, the opening degree of the bypass throttling element 41 is set to 0;

[0166] Where L is the saturation temperature of the refrigerant corresponding to the low pressure value of compressor 11, m < n < p, D > E > F > 0, for example, m is -15, -14 or -13℃, n is -9, -10 or -11℃, p is -7, -6 or -5℃, D is 470, 460, 450, 440, 430, 420 or 410 steps, E is 310, 320, 330, 340, 350, 360, 370, 380 or 390 steps, and F is 210, 220, 230, 240, 250, 260, 270, 280 or 290 steps.

[0167] By adopting the above method, the opening degree of the bypass throttling device 41 can be reasonably and gradually adjusted during heating. This means that when the low pressure value of the compressor 11 is low, the opening degree of the bypass throttling device 41 is larger. As a result, when the low pressure value of the compressor 11 is low, more refrigerant can be drawn back to the compressor 11 more quickly through the bypass branch 4, thereby increasing the amount of refrigerant in the compressor 11 more quickly and raising the low pressure value more quickly. This effectively prevents the low pressure value from being too low and affecting the working reliability of the air conditioner 100.

[0168] As can be seen, this embodiment further improves the operational reliability of the air conditioner 100 by further throttling the refrigerant flowing back to the compressor 11 via the bypass branch 4 by providing a bypass throttling element 41 and a cold oil heat exchanger 42 on the bypass branch 4, and by using the refrigerant flowing back to the compressor 1 via the bypass branch 4 to cool the lubricating oil separated by the oil separator 12.

[0169] The above description is merely an exemplary embodiment of this application and is not intended to limit this application. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. An air conditioner (100), characterized in that, include: The circulation loop (1) is used to realize the circulation of refrigerant for cooling or heating. The circulation loop (1) is equipped with a compressor (11), an outdoor heat exchanger (14) and a gas-liquid separator (19). The de-icing flow path (3) is connected to the outlet of the compressor (11) and the inlet of the gas-liquid separator (19), and is thermally coupled to the outdoor heat exchanger (14) to de-ic the outdoor heat exchanger (14) using the high-temperature refrigerant flowing from the compressor (11). The de-icing flow path (3) is provided with a de-icing throttling device (32), which throttles the refrigerant in the de-icing flow path (3). and A bypass branch (4) is connected to the inlet of the de-icing flow path (3) and the compressor (11) to draw the refrigerant in the de-icing flow path (3) back to the compressor (11).

2. The air conditioner (100) according to claim 1, characterized in that, The de-icing flow path (3) is provided with a de-icing valve (33), which controls the opening and closing of the de-icing flow path (3). Along the direction of refrigerant flow through the de-icing flow path (3), the connection position of the bypass branch (4) and the de-icing flow path (3) is located upstream of the de-icing valve (33); and / or, along the direction of refrigerant flow through the de-icing flow path (3), the connection position of the bypass branch (4) and the de-icing flow path (3) is located downstream of the de-icing throttling device (32).

3. The air conditioner (100) according to claim 2, characterized in that, The de-icing flow path (3) is provided with the de-icing valve (33) and the de-icing throttling device (32). The de-icing throttling device (32) and the de-icing valve (33) are arranged sequentially along the direction of refrigerant flow through the de-icing flow path (3). The connection position of the bypass branch (4) and the de-icing flow path (3) is located between the de-icing valve (33) and the de-icing throttling device (32).

4. The air conditioner (100) according to claim 1, characterized in that, The bypass branch (4) is connected to the de-icing flow path (3) located between the outdoor heat exchanger (14) and the gas-liquid separator (19).

5. The air conditioner (100) according to claim 1, characterized in that, The bypass branch (4) is provided with a bypass throttling device (41) to throttle the refrigerant flowing back to the compressor (11) via the bypass branch (4); and / or, the bypass branch (4) is provided with a bypass valve to control the opening and closing of the bypass branch (4).

6. The air conditioner (100) according to any one of claims 1-5, characterized in that, An oil separator (12) is also provided on the circulation loop (1). The oil separator (12) is connected to the outlet of the compressor (11) to separate the lubricating oil in the refrigerant flowing out of the compressor (11). A cold oil heat exchanger (42) for cooling the lubricating oil is provided on the bypass branch (4). The cold oil heat exchanger (42) is connected to the oil separator (12) and the compressor (11) through the cold oil flow path (5) so that the lubricating oil separated by the oil separator (12) is cooled by the refrigerant in the bypass branch (4) and flows back to the compressor (11).

7. The air conditioner (100) according to claim 6, characterized in that, The air conditioner (100) is configured to be at least one of the following: The cold oil heat exchanger (42) is located downstream of the bypass throttling element (41) on the bypass branch (4) along the direction of the refrigerant flow through the bypass branch (4); The cold oil flow path (5) is provided with a cold oil valve (54), which controls the opening and closing of the cold oil flow path (5); The cold oil flow path (5) is provided with a cold oil throttling device (53), which throttles the lubricating oil flowing back to the compressor (11) through the cold oil flow path (5).

8. The air conditioner (100) according to claim 7, characterized in that, The cold oil valve (54) is located upstream of the cold oil heat exchanger (42) along the direction of the lubricating oil flowing through the cold oil flow path (5); and / or, the cold oil throttling element (53) is located downstream of the cold oil heat exchanger (42) along the direction of the lubricating oil flowing through the cold oil flow path (5).

9. A control method for an air conditioner (100) as described in any one of claims 1-8, characterized in that, include: Determine whether the air conditioner (100) is cooling or heating; When the air conditioner (100) is cooling or heating, the refrigerant in the de-icing flow path (3) is returned to the compressor (11) by means of the bypass branch (4).

10. The control method according to claim 9, characterized in that, When the air conditioner (100) is cooling or heating, the opening degree of the bypass throttling device (41) on the bypass branch (4) is adjusted during the process of using the bypass branch (4) to return the refrigerant in the defrosting flow path (3) to the compressor (11).

11. The control method according to claim 10, characterized in that, When the air conditioner (100) is cooling or heating, during the process of using the bypass branch (4) to return the refrigerant in the de-icing flow path (3) to the compressor (11) without passing through the gas-liquid separator (19), adjusting the opening degree of the bypass throttling device (41) on the bypass branch (4) includes at least one of the following: When the air conditioner (100) is cooling, the opening degree of the bypass throttling device (41) on the bypass branch (4) is adjusted according to the exhaust temperature of the compressor (11); When the air conditioner (100) is heating, the opening degree of the bypass throttling device (41) on the bypass branch (4) is adjusted according to the low pressure value of the compressor (11).

12. The control method according to claim 11, characterized in that, When the air conditioner (100) is cooling, adjusting the opening of the bypass throttling device (41) on the bypass branch (4) according to the exhaust temperature of the compressor (11) includes at least one of the following: When T < a, the opening degree of the bypass throttling device (41) is set to 0; When a≤T<b, the opening degree of the bypass throttling device (41) is set to A; When b≤T<c, the opening degree of the bypass throttling device (41) is set to B; When T≥c, the opening degree of the bypass throttling device (41) is C; Where T is the exhaust temperature of the compressor (11), a < b < c, 0 < A < B < C.

13. The control method according to claim 12, characterized in that, 85℃; and / or, 90℃; and / or, 95℃; and / or, ; and / or, 300 steps; and / or, 350 steps.

14. The control method according to claim 11, characterized in that, When the air conditioner (100) is heating, adjusting the opening of the bypass throttling device (41) on the bypass branch (4) according to the low pressure value of the compressor (11) includes at least one of the following: When L < m, the opening degree of the bypass throttling device (41) is set to D; When m≤L<n, the opening degree of the bypass throttling device (41) is set to E; When n≤L<p, the opening degree of the bypass throttling device (41) is F; When L≥p, the opening degree of the bypass throttling device (41) is set to 0; Where L is the saturation temperature of the refrigerant corresponding to the low pressure value of the compressor (11), m < n < p, D > E > F > 0.

15. The control method according to claim 14, characterized in that, ; and / or, ; and / or, ; and / or, ; and / or, ; and / or, .

16. The control method according to claim 9, characterized in that, When the air conditioner (100) is cooling, during the process of using the bypass branch (4) to return the refrigerant in the de-icing flow path (3) to the compressor (11), the de-icing flow path (3) is disconnected from the gas-liquid separator (19); and / or, when the air conditioner (100) is heating, during the process of using the bypass branch (4) to return the refrigerant in the de-icing flow path (3) to the compressor (11), the de-icing flow path (3) is connected to the gas-liquid separator (19) so that the refrigerant is returned to the compressor (11) via the gas-liquid separator (19) by the de-icing flow path (3).

17. The control method according to claim 9, characterized in that, When the air conditioner (100) is cooling or heating, during the process of using the bypass branch (4) to return the refrigerant in the de-icing flow path (3) to the compressor (11), the oil heat exchanger (42) located on the bypass branch (4) is also connected to the compressor (11) and the oil separator (12) so that the refrigerant in the bypass branch (4) cools the lubricating oil flowing back to the compressor (11) from the oil separator (12).

18. A controller, characterized in that, The system includes a memory and a processor coupled to the memory, the processor being configured to execute the control method as described in any one of claims 11-17 based on instructions stored in the memory.

19. An air conditioning system, characterized in that, Includes the air conditioner (100) as described in any one of claims 1-10, and the controller as described in claim 18.

20. A storage medium storing computer instructions, the computer instructions being executed by a processor using the control method as described in any one of claims 11-17.

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