Compressor pressure relief structure, compressor, air conditioner and control method

Abstract

The application provides a compressor pressure relief structure, a compressor, an air conditioner and a control method, wherein the compressor pressure relief structure comprises a flange, a pressure relief hole and a pressure relief assembly are arranged on the flange, and the pressure relief assembly is used for opening or closing the pressure relief hole. Before a compressor stops, the pressure relief assembly opens the pressure relief hole for a preset time. According to the application, the technical problem that gas still exists in the cylinder of the compressor during the stopping process in the prior art, leading to noise of the compressor, can be solved.

Description

Technical Field

[0001] This invention belongs to the field of air conditioner technology, specifically relating to a compressor pressure relief structure, a compressor, an air conditioner, and a control method. Background Technology

[0002] With the development of the air conditioning industry, the compressor, as the main noise and excitation source of the air conditioning system, has increasingly stringent noise requirements. Currently, when an air conditioner stops, the compressor vibrates significantly during shutdown, causing large vibrations in the pipes and the outdoor unit panel, as well as transient exhaust noise transmitted into the room, greatly affecting the user experience. The main reason for this problem is that gas still exists in the compressor cylinder during shutdown, and during the compression process, the pressure inside the cylinder cannot quickly reach equilibrium with the pressure outside the cylinder.

[0003] Because gas still exists inside the compressor cylinder during shutdown in existing technologies, the pressure inside the cylinder cannot be quickly balanced with that outside, resulting in technical problems such as noise generated by the compressor. Therefore, this invention studies and designs a compressor pressure relief structure, a compressor, an air conditioner, and a control method. Summary of the Invention

[0004] Therefore, the present invention provides a compressor pressure relief structure, a compressor, an air conditioner, and a control method, which can solve the technical problem in the prior art that gas still exists in the compressor cylinder during shutdown, causing the compressor to generate noise.

[0005] To address the aforementioned problems, the present invention provides a compressor pressure relief structure, comprising: a flange, wherein a pressure relief hole and a pressure relief assembly are provided on the flange, the pressure relief assembly being used to open or close the pressure relief hole, and the pressure relief assembly opening the pressure relief hole after a preset time before the compressor stops.

[0006] In some implementations, the preset time is 0.3s-2s.

[0007] In some embodiments, the flange is provided with a first groove, the pressure relief hole is located at the bottom of the first groove, the pressure relief assembly includes a baffle and a valve plate, the baffle and the valve plate are installed on the flange by a connector, the valve plate is used to open or close the pressure relief hole, and an electromagnet is provided on the side of the baffle facing the valve plate.

[0008] In some embodiments, the flange is provided with a second groove, the sidewall of the second groove is connected to the first groove, and the baffle is provided with a connection hole.

[0009] In some embodiments, the flange is provided with a fourth groove, the bottom of the fourth groove is provided with a vent hole, and a vent valve assembly is provided at the fourth groove. The flange is provided with a plurality of third grooves, one end of the third groove is connected to the fourth groove along the extension direction of the third groove, and the other end of the third groove is connected to the first groove.

[0010] The present invention also provides a compressor, including the compressor pressure relief structure described above.

[0011] In some embodiments, the compressor includes a cylinder, a flange is disposed on the cylinder, the cylinder has an intake chamber and an exhaust chamber, and when the flange is provided with a fourth groove, the bottom of the fourth groove is provided with an exhaust hole, and an exhaust valve assembly is provided at the fourth groove, the exhaust hole, the pressure relief hole and the pressure relief assembly are arranged opposite to the exhaust chamber, a portion of the exhaust valve assembly is arranged opposite to the exhaust chamber, and the remaining portion of the exhaust valve assembly is arranged opposite to the intake chamber.

[0012] The present invention also provides an air conditioner, including the compressor described above.

[0013] In some implementation methods, the following steps are specifically followed: The judgment step is to determine the status of the compressor motor.

[0014] The control procedure is as follows: 0.3s-2s before the compressor motor is powered off, the pressure relief assembly is controlled to open the pressure relief hole; otherwise, the pressure relief assembly is controlled to maintain its current state.

[0015] In some implementation methods, the following steps are specifically followed: The judgment step involves determining the relationship between the real-time current of the compressor motor and the rated current of the compressor motor.

[0016] The control procedure is as follows: when the real-time current of the compressor motor exceeds 120% of the rated current, the pressure relief component is controlled to open the pressure relief hole; otherwise, the pressure relief component is controlled to maintain the current state.

[0017] In some embodiments, when the pressure relief assembly opens the pressure relief port, the following step is further included: The judgment step involves determining the time when the pressure relief assembly opens the pressure relief hole and the pressure difference between the pressure relief hole and the compressor exhaust port. The control procedure is as follows: when the pressure relief component opens the pressure relief hole for no less than 3-5 seconds, and the pressure difference between the pressure relief hole and the compressor exhaust port is less than or equal to 0.3 MPa, the pressure relief component is controlled to close the pressure relief hole; otherwise, the pressure relief component is controlled to maintain the current state.

[0018] The compressor pressure relief structure, compressor, air conditioner, and control method provided by this invention have the following beneficial effects: By pre-setting a time before the compressor stops, the pressure relief component opens the pressure relief hole to release the high-pressure gas in the compressor cylinder in advance. This achieves active and stable release of cylinder pressure during shutdown, effectively suppressing compressor mechanical vibration during shutdown, significantly reducing low-frequency vibration and transient exhaust noise transmitted from the outdoor unit to the indoor unit, and providing active pressure relief protection under abnormal operating conditions. This comprehensively improves the stability of compressor operation and the reliability of the entire unit, significantly enhancing the user experience. Attached Figure Description

[0019] To more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the accompanying drawings used in the description of the embodiments or the prior art will be briefly introduced below. The drawings described below are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

[0020] Figure 1 This is a schematic diagram of the compressor pressure relief structure of the present invention. Figure 1 ; Figure 2 This is a schematic diagram of the compressor pressure relief structure of the present invention. Figure 2 ; Figure 3 yes Figure 2 A magnified view of a portion of the image; Figure 4 This is a schematic diagram of the compressor pressure relief structure of the present invention. Figure 3 ; Figure 5 yes Figure 4 Enlarged view of point A in the middle; Figure 6 yes Figure 4 Enlarged view of point B in the middle; Figure 7 This is a gas flow diagram of the compressor pressure relief structure of the present invention.

[0021] The attached figures are labeled as follows: 1. Flange; 2. Pressure relief valve assembly; 3. Exhaust valve assembly; 4. Baffle; 5. Valve plate; 6. Connection hole; 7. Connector; 8. Pressure relief hole; 9. First groove; 10. Electromagnet; 11. Second groove; 12. Fourth groove; 13. Third groove. Detailed Implementation

[0022] 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 some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0023] In the description of this invention, 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 generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention 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 invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0024] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0025] Furthermore, it should be noted 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 invention.

[0026] See also Figure 1-7As shown in the embodiment of the present invention, a compressor pressure relief structure is provided, comprising: a flange 1, on which a pressure relief hole 8 and a pressure relief assembly 2 are provided. The pressure relief assembly 2 is used to open or close the pressure relief hole 8. A preset time is elapsed before the compressor stops, and the pressure relief assembly 2 opens the pressure relief hole 8. In this technical solution, by opening the pressure relief hole 8 a preset time before the compressor stops, the high-pressure gas in the compressor cylinder is depressurized in advance, realizing the active and stable release of cylinder pressure during shutdown. This effectively suppresses compressor mechanical vibration during shutdown, significantly reduces low-frequency vibration and transient exhaust noise transmitted from the outdoor unit of the air conditioner to the indoor unit, and provides active pressure relief protection under abnormal operating conditions, comprehensively improving the stability of compressor operation and overall reliability, and significantly improving the user experience.

[0027] In some implementations, the preset time is 0.3s-2s.

[0028] In this technical solution, the pressure relief valve automatically opens 0.3s-2s before the main motor is powered off, realizing active pressure relief before shutdown and effectively eliminating the risk of "liquid slamming" or "reverse impact" caused by the instantaneous release of high-pressure gas.

[0029] The current air conditioner shutdown logic is generally such that when the user presses the power button, the indoor unit immediately shuts down, and the outdoor unit compressor stops simultaneously. Referring to the table below, if the compressor remains running for an extended period after receiving the shutdown command, the indoor unit, already shut down, will not exchange heat and may experience frost buildup. Therefore, the delay should not be too long.

[0030]

[0031] The compressor pressure relief structure of this invention provides active pressure relief protection, comprehensively improving the stability of compressor operation and the overall reliability of the machine, thus solving user pain points. During compressor shutdown, it effectively controls the pressure and load inside the cylinder, avoiding mechanical vibration, low-frequency vibration, and transient noise caused by the inability to quickly balance the pressure load. It also achieves active pressure relief protection under abnormal operating conditions, thereby improving the compressor's operational stability, overall reliability, and user experience.

[0032] In some embodiments, the flange 1 is provided with a first groove 9, the pressure relief hole 8 is provided at the bottom of the first groove 9, the pressure relief assembly 2 includes a baffle 4 and a valve plate 5, the baffle 4 and the valve plate 5 are installed on the flange 1 by a connector 7, the valve plate 5 is used to open or close the pressure relief hole 8, and an electromagnet 10 is provided on the side of the baffle 4 facing the valve plate 5.

[0033] In this technical solution, the valve plate 5 can be actively closed or opened using an electromagnet 10. The opening and closing can be precisely controlled by a control module, achieving rapid response and reliable opening. It should be noted that the valve plate 5 is made of ferromagnetic iron metal, which can be attracted by the electromagnet 10.

[0034] In some embodiments, the flange 1 is provided with a second groove 11, the sidewall of the second groove 11 is connected to the first groove 9, and the baffle 4 is provided with a connection hole 6.

[0035] In this technical solution, the sidewall of the second groove 11 is connected to the first groove 9, meaning the sidewall of the first groove 9 penetrates the sidewall of the second groove 11, effectively creating an opening in the sidewall of the second groove 11 that connects to it. A resonant cavity is formed through the second groove 11, which meets the 2000Hz resonant cavity noise reduction requirement, further reducing transient exhaust noise during shutdown. The compressor pressure relief structure of this invention integrates a 2000Hz resonant cavity noise reduction channel, namely the second groove 11, in the valve port area of ​​the pressure relief valve. Its noise reduction frequency precisely matches the main frequency band of exhaust noise during shutdown, 1800–2200Hz, effectively suppressing high-frequency transient noise and significantly reducing transient exhaust noise.

[0036] In some embodiments, the pressure relief assembly 2 is in a closed state under normal operating conditions, not affecting the compressor's operation. The connection hole 6 facilitates electrical connection between the electromagnet and the external control module. When the pressure relief valve is open, upon receiving a stop command from the control module, the electromagnet 10 is energized, lifting the valve plate 5 and opening the pressure relief valve. At this time, the gas inside the cylinder can directly communicate with the inner cavity of the housing through this valve, achieving rapid pressure relief without waiting for the gas to reach exhaust pressure before being discharged from the upper flange exhaust valve.

[0037] In some embodiments, the flange 1 is provided with a fourth groove 12, the bottom of the fourth groove 12 is provided with an exhaust hole, the fourth groove 12 is provided with an exhaust valve assembly 3, the flange 1 is provided with a plurality of third grooves 13, one end of the third groove 13 is connected to the fourth groove 12 along the extending direction of the third groove 13, and the other end of the third groove 13 is connected to the first groove 9.

[0038] In this technical solution, one end of the third groove 13 is connected to the fourth groove 12, and the other end of the third groove 13 is connected to the first groove 9. That is, both ends of the third groove 13 penetrate the sidewalls of the fourth groove 12 and the first groove 9, respectively. Multiple third grooves 13 are arranged radially. Through the third grooves 13, the high-speed depressurization airflow is evenly dispersed, effectively suppressing airflow turbulence and local impact, and improving the stability of the depressurization process.

[0039] The compressor pressure relief structure of this invention, in order to achieve smooth airflow release and reduce turbulence and impact noise during shutdown, provides multiple radial third grooves 13 in the area near the valve port of the pressure relief valve seat. These third grooves 13 extend radially from the center of the valve port to the surrounding areas and communicate with the flange exhaust valve seat. Under this design, in addition to upward exhaust, the high-speed pressure relief airflow can also be evenly dispersed to multiple directions at the upper flange exhaust valve seat, avoiding local concentrated impact and significantly improving airflow stability. The exhaust groove plays the role of dispersing high-pressure airflow. During the pressure relief process, in addition to the conventional upward discharge, the gas can also enter the exhaust groove through the guide groove for buffering, thereby dispersing the high-pressure airflow.

[0040] It should be noted that in the compressor pressure relief structure of the present invention, the structures of the exhaust valve assembly 3 and the pressure relief assembly 2 are the same as those of the existing valve plate baffle structure. However, unlike the prior art, in the compressor pressure relief structure of the present invention, the pressure relief assembly 2 is provided with a solenoid valve 10 on the baffle 4.

[0041] The present invention also provides a compressor, including the compressor pressure relief structure described above.

[0042] In some embodiments, the compressor includes a cylinder, and the flange 1 is disposed on the cylinder. The cylinder has an intake chamber and an exhaust chamber. When the flange 1 is provided with a fourth groove 12, the bottom of the fourth groove 12 is provided with an exhaust hole, and an exhaust valve assembly 3 is provided at the fourth groove 12, the exhaust hole, the pressure relief hole 8, and the pressure relief assembly 2 are arranged opposite to the exhaust chamber, a portion of the exhaust valve assembly 3 is arranged opposite to the exhaust chamber, and the remaining portion of the exhaust valve assembly 3 is arranged opposite to the intake chamber.

[0043] In this technical solution, the original flange exhaust port position remains unchanged, the exhaust valve plate tail seat is changed to be set in the intake area, and a pressure relief valve assembly is added in the exhaust area to achieve rapid and direct pressure relief of the gas in the cylinder when the machine stops, avoiding reliance on the original exhaust valve.

[0044] During the operation of the rotary compressor, the motor drives the rotor to rotate, and the rotor and the inner wall of the cylinder form a periodically changing sealed volume. As the rotor rotates, the suction chamber gradually expands, and gas is drawn in through the intake port; as the rotor continues to rotate, the gas is compressed, the volume decreases, and the pressure increases; when the discharge pressure is reached, the gas is discharged through the exhaust port of the upper flange. In the compressor, the rotor rotates clockwise, the area clockwise past the exhaust port is the suction area, and the area counterclockwise past the exhaust port is the discharge area. Existing exhaust valve plates are generally located in the discharge area. Compared with the integrated exhaust valve and pressure relief valve of the prior art, the pressure relief of the compressor of this invention relies on the opening path of the original exhaust valve. Due to limitations in ensuring operational performance, the design of the exhaust passage often needs to be coordinated with the compressor volume, cylinder parameters, etc., while the separate pressure relief valve is not subject to this limitation and can accelerate the pressure relief efficiency while ensuring the strength of the upper flange. The compressor of this invention separates the exhaust function and the pressure relief function, avoiding mutual interference caused by the complex structure of the integrated valve body. The exhaust valve focuses on exhaust control during operation, while the pressure relief valve is specifically designed for pressure relief during shutdown. This modular design reduces the failure rate and improves the overall stability and reliability of the system. In traditional integrated designs, pressure relief is often achieved by forcibly opening the exhaust valve, which can easily cause fatigue damage to the valve components due to frequent opening and closing. This solution uses an independent pressure relief valve to handle the pressure relief task, eliminating the need for the exhaust valve to operate during shutdown. This effectively reduces mechanical stress and wear in its non-operating state, extending its overall service life.

[0045] As shown in the table below, the compressor of the present invention significantly reduces the vibration of the pipeline and outdoor unit at the moment of shutdown compared to the prior art.

[0046]

[0047] The present invention also provides an air conditioner, including the compressor described above.

[0048] The present invention also provides a control method for the above-mentioned air conditioner, which is implemented according to the following steps: The judgment step is to determine the status of the compressor motor.

[0049] The control procedure is as follows: 0.3s-2s before the compressor motor is de-energized, the pressure relief component 2 is controlled to open the pressure relief hole 8; otherwise, the pressure relief component 2 is controlled to maintain its current state.

[0050] In this technical solution, 0.3s-2s before the compressor motor is de-energized, the pressure relief component 2 is controlled to open the pressure relief hole 8; otherwise, the pressure relief component 2 is controlled to maintain its current state until 0.3s-2s before the compressor motor is de-energized.

[0051] The pressure relief valve adopts an electromagnetic drive and valve plate reset control structure. Its opening action is linked to the compressor main motor shutdown process: it automatically opens 0.3 seconds before the main motor is powered off, realizing the safe shutdown logic of first depressurizing and then powering off, eliminating the risk of liquid slugging or reverse impact caused by the high pressure in the exhaust chamber at the moment of shutdown.

[0052] In some implementation methods, the following steps are specifically followed: The judgment step involves determining the relationship between the real-time current of the compressor motor and the rated current of the compressor motor.

[0053] The control procedure is as follows: when the real-time current of the compressor motor exceeds 120% of the rated current, the pressure relief component 2 is controlled to open the pressure relief hole 8; otherwise, the pressure relief component 2 is controlled to maintain the status quo.

[0054] In this technical solution, when the real-time current of the compressor motor exceeds 120% of the rated current, the pressure relief component 2 is controlled to open the pressure relief port 8; otherwise, the pressure relief component 2 remains unchanged until it meets the conditions for opening. Simultaneously, the system collects the main motor operating current in real time and dynamically compares it with the rated value. Real-time monitoring of the main motor current is crucial; if an abnormal increase in current is detected, such as exceeding 120% of the rated value, the system immediately identifies it as a potential fault risk, such as compressor seizure, liquid slugging, or motor overload, even without a shutdown command. At this time, the control system forcibly triggers the electromagnet to open the pressure relief channel, providing active protection to prevent seizure, liquid slugging, and other faults.

[0055] It should be noted that when the system detects an abnormal increase in the main motor current, such as exceeding 120% of the rated value, it may indicate liquid slugging, cylinder jamming, condenser blockage, or fan malfunction, leading to increased exhaust resistance. In the event of such a fault, the high-pressure gas in the cylinder or exhaust chamber should be quickly released through the pressure relief valve to reduce the load, control the temperature rise, and prevent motor overcurrent and further wear on internal mechanical components.

[0056] In some embodiments, when the pressure relief assembly 2 opens the pressure relief port 8, the following step is further included: The judgment step is to determine the time when the pressure relief component 2 opens the pressure relief hole 8, and the pressure difference between the pressure relief hole 8 and the compressor exhaust port; In the control steps, when the pressure relief component 2 opens the pressure relief hole 8 for no less than 3-5 seconds, and the pressure difference between the pressure relief hole 8 and the compressor exhaust port is less than or equal to 0.3 MPa, the pressure relief component 2 is controlled to close the pressure relief hole 8; otherwise, the pressure relief component 2 is controlled to maintain the current state.

[0057] In this technical solution, the pressure relief component 2 opens the pressure relief port 8 for no less than 3-5 seconds. When the pressure difference between the pressure relief port 8 and the compressor discharge port is less than or equal to 0.3 MPa, the pressure relief component 2 is controlled to close the pressure relief port 8. Otherwise, the pressure relief component 2 is controlled to maintain its current state until it meets the conditions for opening. The pressure relief valve must close simultaneously, with a 3-5 second delay after opening, and the pressure difference between the valve port and the discharge pressure must be ≤0.3 MPa to ensure sufficient pressure relief and system safety. Discharge pressure refers to the air pressure at the compressor discharge port, and valve port pressure is the air pressure at the pressure relief port. The pressure relief valve will not close if only one condition is met. If the pressure difference is not met, it indicates that the system pressure is not sufficiently balanced, so a delay is required to ensure reliability and safety. The time requirement for meeting the pressure difference is primarily for safety redundancy design, avoiding misjudgments due to instantaneous pressure fluctuations or measurement noise, and ensuring sufficient release of residual energy.

[0058] It will be readily understood by those skilled in the art that, without conflict, the advantageous technical features of the above-mentioned methods can be freely combined and superimposed.

[0059] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention. The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. A compressor pressure relief structure, characterized in that: include: Flange (1), the flange (1) is provided with a pressure relief hole (8) and a pressure relief assembly (2), the pressure relief assembly (2) is used to open or close the pressure relief hole (8), and the pressure relief assembly (2) opens the pressure relief hole (8) at a preset time before the compressor stops. The flange (1) is provided with a first groove (9), and the pressure relief hole (8) is provided at the bottom of the first groove (9). The pressure relief assembly (2) includes a baffle (4) and a valve plate (5). The baffle (4) and the valve plate (5) are installed on the flange (1) through a connector (7). The valve plate (5) is used to open or close the pressure relief hole (8). An electromagnet (10) is provided on the side of the baffle (4) facing the valve plate (5). The flange (1) is provided with a fourth groove (12). The bottom of the fourth groove (12) is provided with an exhaust hole, and an exhaust valve assembly (3) is provided at the fourth groove (12). Multiple third grooves (13) are provided on the flange (1). Along the extension direction of the third groove (13), one end of the third groove (13) is connected to the fourth groove (12), and the other end of the third groove (13) is connected to the first groove (9). The multiple third grooves (13) are arranged radially, and the high-speed depressurization airflow is evenly dispersed through the third grooves (13).

2. The compressor pressure relief structure according to claim 1, characterized in that: The preset time is 0.3s-2s.

3. The compressor pressure relief structure according to claim 1, characterized in that: The flange (1) is provided with a second groove (11), the side wall of the second groove (11) is connected to the first groove (9), and the baffle (4) is provided with a connection hole (6).

4. A compressor, characterized in that, The compressor pressure relief structure includes any one of claims 1 to 3.

5. The compressor according to claim 4, characterized in that: The compressor includes a cylinder, and the flange (1) is disposed on the cylinder. The cylinder has an intake chamber and an exhaust chamber. When the flange (1) is provided with a fourth groove (12), the bottom of the fourth groove (12) is provided with an exhaust hole, and an exhaust valve assembly (3) is provided at the fourth groove (12), the exhaust hole, the pressure relief hole (8) and the pressure relief assembly (2) are arranged opposite to the exhaust chamber, part of the exhaust valve assembly (3) is arranged opposite to the exhaust chamber, and the remaining part of the exhaust valve assembly (3) is arranged opposite to the intake chamber.

6. An air conditioner, characterized in that, Includes the compressor described in claims 4 to 5.

7. The control method for an air conditioner according to claim 6, characterized in that: The specific steps are as follows: The judgment step is to determine the status of the compressor motor; The control steps are as follows: 0.3s-2s before the compressor motor is de-energized, the pressure relief component (2) is controlled to open the pressure relief hole (8); otherwise, the pressure relief component (2) is controlled to maintain the status quo.

8. The control method for an air conditioner according to claim 6, characterized in that: The specific steps are as follows: The judgment step is to determine the relationship between the real-time current of the compressor motor and the rated current of the compressor motor. The control procedure is as follows: when the real-time current of the compressor motor exceeds 120% of the rated current, the pressure relief component (2) is controlled to open the pressure relief hole (8); otherwise, the pressure relief component (2) is controlled to maintain the status quo.

9. The control method for an air conditioner according to any one of claims 7 or 8, characterized in that: When the pressure relief assembly (2) opens the pressure relief hole (8), the following steps are also included: The judgment step is to determine the time when the pressure relief component (2) opens the pressure relief hole (8) and the pressure difference between the pressure relief hole (8) and the compressor exhaust port; In the control steps, when the pressure relief component (2) opens the pressure relief hole (8) for no less than 3-5 seconds, and the pressure difference between the pressure relief hole (8) and the compressor exhaust port is less than or equal to 0.3 MPa, the pressure relief component (2) is controlled to close the pressure relief hole (8); otherwise, the pressure relief component (2) is controlled to maintain the status quo.

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