Compressor and air conditioner

Abstract

The application discloses a compressor and an air conditioner. The compressor is provided with a compression mechanism for compressing refrigerant in an inner cavity. The compression mechanism comprises a cylinder, a bearing connected to the cylinder, a bearing exhaust hole on the bearing and communicating with a compression cavity of the cylinder, an exhaust valve plate and a lift limiter. The exhaust valve plate is used for closing or opening the bearing exhaust hole. The lift limiter is arranged above the exhaust valve plate and is used for limiting the displacement of the exhaust valve plate. A driving part is used for generating relative movement between the exhaust valve plate and the lift limiter to adjust the effective length of the exhaust valve plate. The effective length of the exhaust valve plate of the compressor can be self-adaptively adjusted at different rotating frequencies of the compressor, thereby avoiding the problems of abnormal sound at low frequency and delayed closing at high frequency of the compressor.

Description

Technical Field

[0001] This invention relates to the field of air conditioner technology, and more particularly to a compressor and an air conditioner. Background Technology

[0002] Currently, compressor development has reached a bottleneck. As the operating range of compressors expands, some problems are gradually emerging. On the one hand, as the operating frequency of the compressor increases, its performance does not increase linearly; instead, it gradually approaches a certain value, or even deteriorates compared to low-frequency performance. On the other hand, when the compressor operates at low frequencies, a noticeable "ticking" or "clattering" noise occurs. After investigation, it was determined that the optimal operating frequency of the valve plates and lift limiters is determined simultaneously after the boundary parameter design. If the compressor operates at low frequencies, it is prone to flutter and repeated clattering of the lift limiters and upper bearing surfaces, resulting in the "ticking" noise and affecting auditory perception. If the compressor operates at high frequencies, the valve plates may fail to close properly, significantly reducing compressor performance.

[0003] The information disclosed in this background section is only intended to enhance the understanding of the background technology of this application, and therefore may include prior art that is not known to those skilled in the art. Summary of the Invention

[0004] In response to the problems mentioned in the background art, the present invention proposes a compressor and an air conditioner that enables the effective length of the compressor exhaust valve plate to be adaptively adjusted at different compressor rotation frequencies, thereby avoiding abnormal noise at low frequencies and delayed shutdown at high frequencies.

[0005] To achieve the above-mentioned objectives, the present invention employs the following technical solution:

[0006] In some embodiments of this application, a compressor is provided. The compressor cavity is provided with a compression mechanism for compressing refrigerant. The compression mechanism includes a cylinder, a bearing connected to the cylinder, and a bearing exhaust port communicating with the compression chamber of the cylinder. The compression mechanism also includes an exhaust valve and a lift limiter. The exhaust valve is used to close or open the bearing exhaust port. The lift limiter is located above the exhaust valve and is used to limit the displacement of the exhaust valve. A drive unit is used to generate relative movement between the exhaust valve and the lift limiter to adjust the effective length of the exhaust valve. This enables the effective length of the compressor exhaust valve to be adaptively adjusted at different compressor rotation frequencies, avoiding abnormal noise at low frequencies and delayed closing at high frequencies.

[0007] In some embodiments of this application, the drive unit drives the lift limiter and the exhaust valve plate to generate relative movement according to the rotational frequency of the compressor;

[0008] When the compressor experiences low-frequency knocking, the drive unit drives the lift limiter and the exhaust valve plate to move away from each other to increase the effective length of the exhaust valve plate.

[0009] When the compressor experiences a high-frequency delayed shutdown, the drive unit drives the lift limiter and the exhaust valve plate to move closer to each other to reduce the effective length of the exhaust valve plate.

[0010] The compressor in this application achieves adaptive control of the effective length of the exhaust valve plate by obtaining the compressor's rotational frequency, as well as the necessary structural parameters of the exhaust valve plate, the lift limiter, and the cylinder, and then combining this with the drive unit's drive of the exhaust valve plate and / or the lift limiter, thereby resolving the compressor's performance and abnormal noise.

[0011] In some embodiments of this application, the system calculates the airflow thrust of the compressor at the operating frequency based on the compressor rotation frequency;

[0012] The system calculates the elastic force of the exhaust valve plate based on the initial structural parameters of the exhaust valve plate and the lift limiter.

[0013] The system calculates the running trajectory of the exhaust valve plate at this operating frequency based on the airflow thrust and the elastic force of the exhaust valve plate;

[0014] The system determines whether the compressor exhibits low-frequency knocking or high-frequency delayed shutdown based on the running trajectory of the exhaust valve plate.

[0015] If present, the drive unit drives the lift limiter to generate relative movement between the exhaust valve plate;

[0016] If it does not exist, the drive unit will not move.

[0017] In some embodiments of this application, during the process of the drive unit driving the lift limiter and the exhaust valve plate to generate relative movement, the system iteratively calculates the optimal effective length of the exhaust valve plate, and then the drive unit stops.

[0018] In some embodiments of this application, the control process by which the drive unit drives the lift limiter and the exhaust valve plate to generate relative motion includes a coarse adjustment control process and a fine adjustment control process, wherein the coarse adjustment control process is executed first, and the fine adjustment control process is executed later.

[0019] During the coarse adjustment control process, the system calculates the approximate effective length of the exhaust valve plate at different compressor speeds based on the structural parameters of the exhaust valve plate and the lift limiter. The drive unit drives the lift limiter to generate relative movement between the exhaust valve plate and the exhaust valve plate so that the exhaust valve plate reaches the state of the approximate effective length.

[0020] In some embodiments of this application, the fine-tuning control process includes:

[0021] The system calculates the airflow thrust of the compressor at the operating frequency based on the compressor's rotational frequency;

[0022] The system calculates the elastic force of the exhaust valve plate based on the initial structural parameters of the exhaust valve plate and the lift limiter.

[0023] The system calculates the running trajectory of the exhaust valve plate at this operating frequency based on the airflow thrust and the elastic force of the exhaust valve plate;

[0024] The system determines whether the compressor exhibits low-frequency knocking or high-frequency delayed shutdown based on the running trajectory of the exhaust valve plate.

[0025] If present, the drive unit drives the lift limiter to generate relative movement between the exhaust valve plate;

[0026] If it does not exist, the drive unit will not move.

[0027] In some embodiments of this application, the drive unit drives the lift limiter to move forward or backward relative to the exhaust valve plate to adjust the effective length of the exhaust valve plate.

[0028] In some embodiments of this application, the bearing is provided with a first limiting part, and one end of the lift limiter is provided with a second limiting part. The first limiting part and the second limiting part are slidably engaged so that the lift limiter moves along the bearing under the drive of the drive part.

[0029] In some embodiments of this application, one end of the exhaust valve plate is fixedly mounted on the bearing, and one end of the lift limiter has a plurality of spaced rolling portions on the bottom surface facing the exhaust valve plate, the rolling portions being in rolling contact with the exhaust valve plate.

[0030] The present invention also provides an air conditioner, including the compressor described above.

[0031] Other features and advantages of the present invention will become clearer after reading the detailed embodiments of the invention in conjunction with the accompanying drawings. Attached Figure Description

[0032] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0033] Figure 1 This is a schematic diagram of the exhaust valve plate, lift limiter, and drive unit according to an embodiment;

[0034] Figure 2 This is a control flowchart of the compressor according to an embodiment;

[0035] Figure 3 This is a diagram of the low-frequency tapping signal of the compressor according to an embodiment;

[0036] Figure 4 This is a diagram of the high-frequency delayed shutdown signal of the compressor according to an embodiment;

[0037] Figure 5 This is a low-frequency airflow thrust diagram of the compressor according to an embodiment;

[0038] Figure 6 This is a high-frequency airflow thrust diagram of the compressor according to an embodiment;

[0039] Figure 7 This is a diagram showing the optimal operating trajectory of the exhaust valve plate according to the embodiment;

[0040] Figure 8 This is a schematic diagram of the motion mechanism of a rotary compressor according to an embodiment;

[0041] Figure 9 The curves showing the volume changes of the compressor's intake and exhaust chambers according to the embodiment;

[0042] Figure 10 The instantaneous flow velocity versus time curve according to the embodiment;

[0043] Figure 11 The curve showing the instantaneous airflow thrust versus time / angle according to the embodiment;

[0044] Figure 12 This is a schematic diagram of the exhaust valve plate wrapping model according to an embodiment;

[0045] Figure 13 The curves showing the effective length, elasticity, and mass of the exhaust valve plate as a function of angle / time according to the embodiment are shown.

[0046] Figure 14 This is a reference design scheme for the coarse-tuning process according to the embodiments;

[0047] Figure label:

[0048] 100 - Exhaust valve plate, 200 - Lift limit switch, 300 - Bearing, 400 - Drive unit. Detailed Implementation

[0049] 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. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0050] In the description of this application, it should be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description, and 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. Therefore, they should not be construed as limitations on this application.

[0051] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, unless otherwise stated, "a plurality of" means two or more.

[0052] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection between two components. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0053] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0054] The following disclosure provides many different embodiments or examples for implementing various structures of the invention. To simplify the disclosure, specific examples of components and arrangements are described below. These are merely examples and are not intended to limit the invention. Furthermore, reference numerals and / or letters may be repeated in different examples; such repetition is for simplification and clarity and does not in itself indicate a relationship between the various embodiments and / or arrangements discussed. In addition, examples of various specific processes and materials are provided in this invention, but those skilled in the art will recognize the application of other processes and / or the use of other materials.

[0055] In this application, the air conditioner performs a refrigeration cycle by using a compressor, condenser, expansion valve, and evaporator. The refrigeration cycle includes a series of processes involving compression, condensation, expansion, and evaporation to cool or heat an indoor space.

[0056] Low-temperature, low-pressure refrigerant enters the compressor, which compresses it into a high-temperature, high-pressure refrigerant gas and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed refrigerant into a liquid phase, and the heat is released to the surrounding environment through the condensation process.

[0057] The expansion valve expands the high-temperature, high-pressure liquid refrigerant that condenses in the condenser into a low-pressure liquid refrigerant. The evaporator evaporates the expanded refrigerant in the expansion valve and returns the low-temperature, low-pressure refrigerant gas to the compressor. The evaporator achieves its cooling effect by utilizing the latent heat of refrigerant evaporation to exchange heat with the material being cooled. Throughout the cycle, the air conditioner regulates the temperature of the indoor space.

[0058] The outdoor unit of an air conditioner refers to the part of the refrigeration cycle that includes the compressor and the outdoor heat exchanger. The indoor unit of an air conditioner includes the indoor heat exchanger, and an expansion valve can be provided in either the indoor or outdoor unit.

[0059] The indoor and outdoor heat exchangers function as either condensers or evaporators. When the indoor heat exchanger is used as a condenser, the air conditioner functions as a heater in heating mode; when the indoor heat exchanger is used as an evaporator, the air conditioner functions as a cooler in cooling mode.

[0060] The compressor in this embodiment is a rotary compressor, including a housing, with a closed inner cavity formed inside the housing. The inner cavity is equipped with a motor and a compression mechanism. The motor provides power to the compressor mechanism, and the compression mechanism is used to compress the refrigerant.

[0061] The motor includes a stator and a rotor. The stator is fixedly connected to the inner wall of the housing to achieve fixed installation of the motor in the compressor cavity.

[0062] The compression mechanism includes an eccentric crankshaft, cylinder, piston, and bearings.

[0063] The eccentric crankshaft includes a main shaft section, an eccentric shaft section, and a secondary shaft section. The main shaft section is fixedly connected to the rotor. A piston is installed in the compression chamber of the cylinder, and the piston is sleeved on the eccentric shaft section. The bearing is fixedly connected to the cylinder, and the bearing has a bearing exhaust hole, which communicates with the compression chamber. The cylinder has a vane groove 325, and a vane is installed in the vane groove. The eccentric crankshaft drives the piston to move circumferentially in the compression chamber, and the vane reciprocates along the vane groove. The vane always abuts against the piston, and the vane and piston divide the compression chamber into a high-pressure chamber and a low-pressure chamber.

[0064] The working principle of the compressor is as follows: After the stator of the motor is energized, it generates a magnetic pull. The rotor of the motor rotates under the action of the magnetic pull of the stator, and drives the eccentric crankshaft to rotate together. The rotation of the eccentric crankshaft drives the piston sleeved on its eccentric shaft section to make eccentric circular motion in the compression chamber of the cylinder. The sliding vane makes reciprocating motion in the sliding vane groove. The sliding vane and the piston divide the compression chamber of the cylinder into a high-pressure chamber and a low-pressure chamber. When the eccentric crankshaft drives the piston to rotate one revolution, it draws in air from the low-pressure chamber and exhausts air from the high-pressure chamber, completing one exhaust cycle. This realizes the compression of gas by the compressor. The compressed gas is discharged through the bearing exhaust port.

[0065] Reference Figure 1 The shaft 300 is equipped with a lift limiter 200 and an exhaust valve plate 100. The exhaust valve plate 100 is used to close or open the bearing exhaust hole, and the lift limiter 200 is used to limit the displacement of the exhaust valve plate 100.

[0066] During exhaust, the exhaust valve plate 100 opens under the force of the compressed air, and the compressed air is discharged. After exhaust is completed, the exhaust valve plate 100 automatically resets.

[0067] For variable frequency compressors, on the one hand, as the compressor's operating frequency increases, its performance does not increase linearly; instead, it gradually approaches a certain value, or even deteriorates compared to its low-frequency performance. On the other hand, when the compressor operates at low frequencies, it exhibits a noticeable "ticking" or "slapping" noise. After investigation, it was determined that this is because the optimal operating frequency of the exhaust valve and the lift limit switch is simultaneously determined after the boundary parameter design. If the compressor operates at low frequencies, it is prone to fluttering and repeated slapping of the lift limit switch and upper bearing surface, resulting in the "ticking" noise and affecting auditory perception. If the compressor operates at high frequencies, the exhaust valve may fail to close properly, significantly reducing compressor performance.

[0068] To solve this technical problem, this application uses a drive unit 400 to cause relative movement between the lift limiter 200 and the exhaust valve plate 100, thereby adjusting the effective length of the exhaust valve plate 100. This enables the effective length of the compressor exhaust valve plate 100 to be adaptively adjusted at different compressor rotation frequencies, avoiding abnormal noise at low frequencies and delayed closing at high frequencies.

[0069] Specifically, refer to Figure 2 The drive unit 400 drives the lift limiter 200 and the exhaust valve plate 100 to generate relative movement according to the compressor's rotation frequency.

[0070] When the compressor experiences low-frequency knocking, the drive unit 400 drives the lift limiter 200 and the exhaust valve plate 100 to move away from each other, thereby increasing the effective length of the exhaust valve plate 100, which means increasing the flexibility of the exhaust valve plate 100, or in other words, reducing the stiffness of the exhaust valve plate 100, thus reducing the elasticity of the exhaust valve plate 100 and preventing knocking from occurring when the compressor is running at low frequency.

[0071] When the compressor experiences a high-frequency delayed shutdown, the drive unit 400 drives the lift limiter 200 and the exhaust valve plate 100 to move closer to each other, thereby reducing the effective length of the exhaust valve plate 100, that is, reducing the flexibility of the exhaust valve plate 100, or in other words, increasing the stiffness of the exhaust valve plate 100. This increases the stiffness of the exhaust valve plate 100, allowing it to fall back normally and resolving the high-frequency delayed shutdown phenomenon.

[0072] The compressor in this application achieves adaptive control of the effective length of the exhaust valve 100 by obtaining the compressor's rotational frequency, as well as the necessary structural parameters of the exhaust valve 100, the lift limiter 200, and the cylinder, and then combining this with the drive unit 400 to drive the exhaust valve 100 and / or the lift limiter 200, thereby solving the problems of compressor performance and abnormal noise.

[0073] In some embodiments of this application, the system calculates the airflow thrust of the compressor at the operating frequency based on the compressor rotation frequency; the system calculates the elastic force of the exhaust valve plate 100 based on the initial structural parameters of the exhaust valve plate 100 and the lift limiter 200; the system calculates the running trajectory of the exhaust valve plate 100 at the operating frequency based on the airflow thrust and the elastic force of the exhaust valve plate 100; the system determines whether the compressor exhibits low-frequency knocking or high-frequency delayed shutdown based on the running trajectory of the exhaust valve plate 100; if so, the drive unit 400 drives the lift limiter 200 and the exhaust valve plate 100 to generate corresponding relative motion, specifically, mutual approach or mutual distance; if not, the drive unit 400 does not move.

[0074] The calculation process for the airflow thrust experienced by the exhaust valve plate 100 at a specific frequency is as follows:

[0075] The compressor airflow thrust calculation process is as follows: (Refer to...) Figure 8 The working volume of a cylinder is the product of the crescent-shaped area formed between the inner wall of the cylinder and the outer circle of the piston and the length of the piston. The sliding vane divides the working volume of the cylinder into two parts: the intake volume and the compression volume. Therefore...

[0076] V p =V s +V d =π(R) 2 -r 2 )L

[0077] To simplify the parsing expression, in Figure 8 In the diagram, S1 represents the area of ​​sector OBT, S2 represents the area of ​​sector O1AT, and S3 represents the area of ​​△OAO1.

[0078]

[0079]

[0080]

[0081] The intake volume V can be obtained by combining the two equations. S for:

[0082]

[0083] Exhaust volume V d for:

[0084]

[0085] Calculate the compressor's suction and discharge volume change curves as follows: Figure 9 As shown.

[0086] The formula for calculating instantaneous flow velocity is:

[0087]

[0088] In the above formula, Δv represents the change in cavity volume over a time interval of Δt, such as the instantaneous flow velocity c at 60Hz. v like Figure 10 As shown.

[0089] The formula for calculating airflow thrust Fg is as follows:

[0090]

[0091]

[0092]

[0093] Where ε is the drag coefficient, the value of which is related to the airflow coefficient a. v It is inversely proportional to the square of ρ, where ρ is the refrigerant density, and the coefficient β is determined to be 0.88 based on reference empirical values.

[0094] The curve of airflow thrust versus time / angle is shown below. Figure 11 As shown.

[0095] The calculation process for the elastic force of the exhaust valve plate 100 is as follows, combined with... Figure 12 The exhaust valve plate 100 has two stages of movement: the free movement stage of the exhaust valve plate 100 and the wrapping stage of the exhaust valve plate 100.

[0096] At the moment of opening, the radius of curvature of the root of the exhaust valve plate 100 approaches infinity. As the exhaust valve plate 100 opens, the radius of curvature of its root gradually decreases, but does not decrease to the same level as the radius of curvature of the lift limiter. At this time, the exhaust valve plate 100 and the lift limiter are not wrapped together, and the free segment length of the exhaust valve plate 100 remains unchanged, which is the initial effective length of the exhaust valve plate 100. When the curvature of the root of the exhaust valve plate 100 is equal to the radius of curvature of the arc-shaped lift limiter 200, the valve plate begins to wrap together. According to the mechanics of materials, this moment is the starting displacement of the wrapping point of the exhaust valve plate 100.

[0097]

[0098] In the above formula, L0 is the initial effective length of the exhaust valve plate 100, and R is the radius of curvature of the lift limiter.

[0099] Since the exhaust valve plate 100 does not come into contact with the lift limiter, its effective working mass, elasticity, and effective working mass remain unchanged and are its initial parameters. Therefore, at this time:

[0100]

[0101]

[0102] L = L0

[0103] During the wrapping stage of exhaust valve plate 100: When the displacement h of exhaust valve plate 100 is greater than h0, the two begin to wrap together. This can be derived from the formula:

[0104]

[0105] The curves showing the effective mass, elasticity, and length of the exhaust valve plate 100 as a function of angle / time are as follows: Figure 13 As shown.

[0106] The solution process for the kinematic differential equation of exhaust valve plate 100 is as follows:

[0107] When the exhaust chamber reaches the required pressure difference for exhaust, the exhaust valve plate 100 opens. During its movement, it mainly relies on the thrust of the airflow and its own elastic force to complete the opening and closing. The differential equation of motion of the exhaust valve plate 100 is established according to Newton's second law:

[0108]

[0109] In the above formula, θ is the rotation angle, ω is the rotor angular velocity, and Fg is the airflow thrust.

[0110] The initial displacement and velocity when the exhaust valve plate 100 is not open are the initial conditions for calculation:

[0111]

[0112] After the exhaust valve plate 100 opens, as the displacement increases, the exhaust valve plate 100 will collide with the lift limiter and rebound. This moment of impact is taken as the boundary condition, that is:

[0113]

[0114] In the above formula: C R The rebound coefficient is the ratio of the speeds of the exhaust valve plate 100 before and after it collides with the lift limiter. The subscript reb indicates rebound and the subscript imp indicates impact.

[0115] The motion equation of the exhaust valve plate 100 is solved using the Euler method to obtain the motion trajectory of the exhaust valve plate 100.

[0116] Figure 3 The image shown is a low-frequency tapping signal diagram, also known as a multi-cycle tapping signal. Figure 4 The diagram shown is a high-frequency delayed shutdown signal diagram. Figure 5 The diagram shown is a low-frequency airflow thrust diagram. Figure 6 This is a high-frequency airflow thrust diagram. Figure 7This is the optimal operating trajectory diagram for the exhaust valve plate 100.

[0117] In some embodiments of this application, during the relative motion between the drive unit 400 and the lift limiter 200 and the exhaust valve plate 100, the system iteratively calculates the optimal effective length of the exhaust valve plate 100. At this time, the exhaust valve plate 100 can obtain the optimal running trajectory. Then the drive unit 400 stops, and the lift limiter 200 and the exhaust valve plate 100 remain in this optimal relative position to avoid the problems of low-frequency tapping and high-frequency delayed closing.

[0118] In some embodiments of this application, the control process for generating relative motion between the drive unit 400 and the drive lift limiter 200 and the exhaust valve plate 100 includes a coarse adjustment control process and a fine adjustment control process, with the coarse adjustment control process executed first and the fine adjustment control process executed later.

[0119] During the coarse adjustment control process, the system calculates the approximate effective length of the exhaust valve plate 100 at different compressor speeds based on the structural parameters of the exhaust valve plate 100 and the lift limiter 200. The drive unit 400 drives the lift limiter 200 to generate relative movement between it and the exhaust valve plate 100, so that the exhaust valve plate 100 reaches the state of approximate effective length. Figure 14 The image shows a reference design.

[0120] After the compressor is turned on, the system first moves relative to the lift limiter 200 and the exhaust valve plate 100 under the action of the drive unit 400, based on the compressor's rotation frequency, so that the exhaust valve plate 100 reaches the optimal coarse effective length. Then, a fine-tuning control process is performed. The fine-tuning control logic is iterated to achieve the optimal selection of the elasticity of the exhaust valve plate 100, ultimately realizing that the exhaust valve plate 100 has no chatter when operating at low frequency and closes with minimal delay when operating at high frequency.

[0121] The fine-tuning control process includes: the system calculating the airflow thrust of the compressor at the operating frequency based on the compressor rotation frequency; the system calculating the elastic force of the exhaust valve plate 100 based on the initial structural parameters of the exhaust valve plate 100 and the lift limiter 200; the system calculating the running trajectory of the exhaust valve plate 100 at the operating frequency based on the airflow thrust and the elastic force of the exhaust valve plate 100; the system determining whether the compressor exhibits low-frequency knocking or high-frequency delayed shutdown based on the running trajectory of the exhaust valve plate 100; if so, the drive unit 400 drives relative movement between the lift limiter 200 and the exhaust valve plate 100; if not, the drive unit 400 remains stationary.

[0122] Specifically, under fine-tuning control, the compressor frequency is first obtained through the controller, and necessary structural parameters are input, such as the thickness and width of the exhaust valve plate.

[0123] Then, the airflow thrust at this operating frequency and the effective elastic force, effective mass, and effective length of the valve plate under the structural parameters are determined by theoretical derivation and calculation results.

[0124] Then, the operating trajectory of the exhaust valve plate 100 under the initial design parameters is calculated using the differential equations in the controller to determine whether it conforms to the low-frequency no-beating (i.e., only one periodic signal exists, while beaters have multiple periodic signals, such as...) Figure 3 (As shown); High-frequency delayed shutdown (i.e., the theoretical shutdown angle is 336°, but in practice it needs to be delayed by a lot, such as...) Figure 4 As shown in the figure, if there is neither a multi-cycle signal nor a delayed shutdown, then no change is needed;

[0125] If an undesirable trajectory exists, there are two scenarios. Scenario 1: When a low-frequency, multi-cycle signal is present, it is considered that the exhaust valve plate stiffness is too high (100°), resulting in insufficient airflow thrust (see [link to low-frequency airflow thrust]). Figure 5 If the first case is a delayed closing angle, then the stiffness of the exhaust valve plate 100 needs to be reduced, that is, the effective length of the exhaust valve plate 100 needs to be increased to reduce the elasticity of the exhaust valve plate 100; if the second case is a delayed closing angle, then the stiffness of the exhaust valve plate 100 is considered insufficient, and the stiffness of the exhaust valve plate 100 needs to be increased, that is, the elasticity of the exhaust valve plate 100 needs to be increased by reducing the effective length of the exhaust valve plate 100 to achieve normal return of the exhaust valve plate 100.

[0126] Finally, after iteration, the effective length of the exhaust valve plate 100 is determined, thus obtaining the optimal exhaust valve plate 100 running trajectory diagram, as shown below. Figure 7 As shown.

[0127] In some embodiments of this application, the drive unit 400 drives the lift limiter 200 to move forward or backward relative to the exhaust valve plate 100 to adjust the effective length of the exhaust valve plate 100.

[0128] The drive unit 400 can be a power source such as a motor. When the drive unit 400 drives the lift limiter 200 to move forward relative to the exhaust valve plate 100, that is, when the lift limiter 200 moves closer to the free end of the exhaust valve plate 100, the lift limiter 200 and the exhaust valve plate 100 move closer to each other, increasing the stiffness of the exhaust valve plate 100 and reducing the effective length of the exhaust valve plate 100. When the drive unit 400 drives the lift limiter 200 to move backward relative to the exhaust valve plate 100, that is, when the lift limiter 200 moves away from the free end of the exhaust valve plate 100, the lift limiter 200 and the exhaust valve plate 100 move further apart, reducing the stiffness of the exhaust valve plate 100 and increasing the effective length of the exhaust valve plate 100.

[0129] In some embodiments of this application, one end of the exhaust valve plate 100 is fixedly mounted on the bearing 300, and one end of the lift limiter 200 has a plurality of spaced rolling parts, such as rolling shafts, on the bottom surface facing the exhaust valve plate 100. The rolling parts are in rolling contact with the exhaust valve plate 100.

[0130] The rolling part is designed so that when the lift limiter 200 moves relative to the exhaust valve plate 100, the rolling part rolls along one end surface of the exhaust valve plate 100, reducing sliding friction and improving the smoothness of the movement of the lift limiter 200.

[0131] In some embodiments of this application, the bearing 300 is provided with a first limiting part, and one end of the lift limiter 200 is provided with a second limiting part. The first limiting part and the second limiting part are slidably engaged so that the lift limiter 200 moves along the bearing 300 under the drive of the drive part 400.

[0132] In one specific embodiment, the first limiting part is a groove, and the second limiting part is a protrusion. The protrusion is slidably disposed in the groove and plays a guiding role in the movement of the lift limiter 200 relative to the exhaust valve plate 100.

[0133] In the description of the above embodiments, specific features, structures, materials, or characteristics may be combined in any suitable manner in one or more embodiments or examples.

[0134] The above are merely specific embodiments of the present invention, but the scope of protection of the present invention is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in the present invention should be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. A compressor, wherein a compression mechanism for compressing refrigerant is provided in its internal cavity, the compression mechanism comprising a cylinder, the cylinder being connected to a bearing, the bearing having a bearing exhaust port communicating with the compression chamber of the cylinder, characterized in that, The compression mechanism further includes: An exhaust valve plate, used to close or open the bearing exhaust port; A lift limiter is located above the exhaust valve plate and is used to limit the displacement of the exhaust valve plate. A drive unit is used to generate relative movement between the exhaust valve plate and the lift limiter to adjust the effective length of the exhaust valve plate; The drive unit drives the lift limiter and the exhaust valve plate to generate relative movement according to the rotation frequency of the compressor; When the compressor experiences low-frequency knocking, the drive unit drives the lift limiter and the exhaust valve plate to move away from each other to increase the effective length of the exhaust valve plate. When the compressor experiences a high-frequency delayed shutdown, the drive unit drives the lift limiter and the exhaust valve plate to move closer to each other to reduce the effective length of the exhaust valve plate. The system calculates the airflow thrust of the compressor at that compressor frequency based on the compressor's rotational frequency. The system calculates the elastic force of the exhaust valve plate based on the initial structural parameters of the exhaust valve plate and the lift limiter. The system calculates the running trajectory of the exhaust valve plate at this rotational frequency based on the airflow thrust and the elastic force of the exhaust valve plate; The system determines whether the compressor exhibits low-frequency knocking or high-frequency delayed shutdown based on the running trajectory of the exhaust valve plate. If present, the drive unit drives the lift limiter to generate relative movement between the exhaust valve plate; If it does not exist, the drive unit will not move.

2. The compressor according to claim 1, characterized in that, During the relative motion between the lift limiter and the exhaust valve plate driven by the drive unit, the system iteratively calculates the optimal effective length of the exhaust valve plate, and then the drive unit stops.

3. The compressor according to claim 1 or 2, characterized in that, The control process for the drive unit to drive the relative motion between the lift limiter and the exhaust valve plate includes a coarse adjustment control process and a fine adjustment control process. The coarse adjustment control process is executed first, followed by the fine adjustment control process. During the coarse adjustment control process, the system calculates the approximate effective length of the exhaust valve plate at different compressor speeds based on the structural parameters of the exhaust valve plate and the lift limiter. The drive unit drives the lift limiter to generate relative movement between the exhaust valve plate and the exhaust valve plate so that the exhaust valve plate reaches the state of the approximate effective length.

4. The compressor according to claim 3, characterized in that, The fine-tuning control process includes: The system calculates the airflow thrust of the compressor at that compressor frequency based on the compressor's rotational frequency. The system calculates the elastic force of the exhaust valve plate based on the initial structural parameters of the exhaust valve plate and the lift limiter. The system calculates the running trajectory of the exhaust valve plate at this rotational frequency based on the airflow thrust and the elastic force of the exhaust valve plate; The system determines whether the compressor exhibits low-frequency knocking or high-frequency delayed shutdown based on the running trajectory of the exhaust valve plate. If present, the drive unit drives the lift limiter to generate relative movement between the exhaust valve plate; If it does not exist, the drive unit will not move.

5. The compressor according to claim 1 or 2, characterized in that, The drive unit drives the lift limiter to move forward or backward relative to the exhaust valve plate to adjust the effective length of the exhaust valve plate.

6. The compressor according to claim 5, characterized in that, The bearing is provided with a first limiting part, and one end of the lift limiter is provided with a second limiting part. The first limiting part and the second limiting part are slidably engaged so that the lift limiter moves along the bearing under the drive of the drive part.

7. The compressor according to claim 5, characterized in that, One end of the exhaust valve plate is fixed on the bearing, and one end of the lift limiter has a plurality of spaced rolling parts on the bottom surface facing the exhaust valve plate, and the rolling parts are in rolling contact with the exhaust valve plate.

8. An air conditioner, characterized in that, Includes the compressor as described in any one of claims 1 to 7.

Images