Compressor damping structure, compressor and compressor damping method

Abstract

The application discloses a compressor damping structure, a compressor and a compressor damping method. The damping structure comprises a stud, a piezoelectric ceramic assembly, a supporting damping part, an annular damping part, an axial damping pad and a nut. The middle section of the stud is provided with an annular groove. The stud is provided with the supporting damping part, the piezoelectric ceramic assembly, the annular damping part, the axial damping pad and the nut from bottom to top along the axial direction. The piezoelectric ceramic assembly is attached to the annular groove. The annular damping part is sleeved on the outer periphery of the piezoelectric ceramic assembly. The upper and lower ends of the annular damping part abut against the axial damping pad and the supporting damping part respectively. The piezoelectric ceramic assembly is electrically connected to an external control circuit. The application can effectively overcome the technical defects of the existing passive damping technology, such as poor adaptability under multiple working conditions, narrow damping frequency band and resonance amplification, and realizes an intelligent control mechanism of passive-active collaborative damping, thereby improving the vibration suppression capability and operation reliability of the compressor in the full working condition range.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a compressor vibration reduction structure, a compressor, and a compressor vibration reduction method. Background Technology

[0002] In existing technologies, rotary compressors, as core power components, are widely used in air conditioning systems and various refrigeration equipment. Their working principle relies on the high-speed rotation of the rotor to compress and transport gas. However, during actual operation, due to the high-speed rotation of the rotor, periodic gas pulsation, and frequent switching of operating conditions (such as start-stop, variable frequency speed regulation, and high-load operation, which are non-steady-state operations), the compressor inevitably generates significant vibration. This vibration not only increases the overall noise level of the machine, affecting the user experience, but also causes structural fatigue damage, thereby reducing equipment reliability and shortening its service life.

[0003] To address these issues, current mainstream vibration reduction technologies mostly employ passive solutions, such as introducing rubber pads, metal springs, or viscoelastic damping elements into the compressor support structure to absorb or dissipate some vibration energy. While these passive vibration reduction structures offer advantages such as simple design, low cost, and convenient maintenance, their vibration reduction performance is fixed after manufacturing, lacking adaptability to different operating conditions. Especially under complex and variable operating conditions, passive vibration reduction systems struggle to effectively suppress vibrations across a wide frequency range or multiple excitation frequencies. Furthermore, they may amplify the vibration response due to resonance effects within specific frequencies or load ranges, thereby weakening the overall vibration reduction effect and limiting their application prospects in high-performance, high-reliability compressor systems.

[0004] Therefore, there is an urgent need to develop a new vibration reduction technology that can adjust the vibration reduction characteristics in real time according to the operating conditions, so as to improve the vibration control capability and operating stability of the rotary compressor in the entire operating range. Summary of the Invention

[0005] The purpose of this invention is to overcome the shortcomings of the prior art and provide a compressor vibration reduction structure, a compressor, and a compressor vibration reduction method.

[0006] To solve the above-mentioned technical problems, the present invention adopts the following technical solution: In a first aspect, embodiments of the present invention provide a compressor vibration damping structure, comprising: a stud, a piezoelectric ceramic assembly, a support damping element, an annular damping element, an axial damping pad, and a nut. The stud has an annular groove in its middle section. The support damping element, the piezoelectric ceramic assembly, the annular damping element, the axial damping pad, and the nut are mounted on the stud axially from bottom to top. The piezoelectric ceramic assembly is fitted into the annular groove. The annular damping element is sleeved on the outer periphery of the piezoelectric ceramic assembly, and the upper and lower ends of the annular damping element abut against the axial damping pad and the support damping element, respectively. The piezoelectric ceramic assembly is electrically connected to an external control circuit.

[0007] In one specific embodiment, the piezoelectric ceramic assembly consists of a plurality of piezoelectric ceramic sheets arranged in a circumferential direction.

[0008] In one specific embodiment, the piezoelectric ceramic sheet has a concave curved surface, and the curvature of the surface is consistent with the curvature of the inner wall of the annular groove.

[0009] In one specific embodiment, the upper end of the stud is provided with an external thread, and the nut is matched with the external thread.

[0010] In one specific embodiment, the axial damping pad is made of rubber.

[0011] In one specific embodiment, the supporting damping element and the annular damping element are made of nitrile rubber or neoprene rubber.

[0012] The compressor vibration reduction structure of the present invention has the following advantages compared with the prior art: it can effectively overcome the technical defects of existing passive vibration reduction technology, such as poor adaptability under multiple working conditions, narrow vibration reduction frequency band, and possible resonance amplification. It realizes the intelligent control mechanism of "passive-active" coordinated vibration reduction, and improves the vibration suppression capability and operational reliability of the compressor in the entire working range. Specifically, when the compressor is in stable operation or low vibration condition, the vibration reduction structure effectively absorbs and dissipates the conventional vibration energy caused by rotor rotation through a multi-stage passive damping system consisting of support damping components, annular damping components, and axial damping pads, maintaining the low-noise and stable operation of the entire unit. However, under non-steady-state high vibration conditions such as start-up, variable frequency speed regulation, or high load, when the detected vibration amplitude reaches a preset threshold, the external control circuit, based on the air conditioner's built-in operating status signal, drives the piezoelectric ceramic components in real time to generate an active excitation torque that is opposite in phase and matches the amplitude of the disturbance torque. This torque acts on the stud structure and is transmitted to the compressor base through the annular damping component and support damping component, precisely canceling the radial and tangential vibration components excited by rotor eccentricity, mass imbalance, and installation constraints, thereby achieving active suppression of key vibration modes. Compared to traditional passive solutions that rely solely on fixed-parameter damping elements, this design integrates piezoelectric ceramic components into the annular groove of the stud, forming a closed-loop force transmission system with the annular damping element and axial damping pad. This not only results in a compact and easy-to-assemble structure but also achieves integrated control of vibration sensing, judgment, and response. This design combines the advantages of wide-bandwidth passive vibration absorption with high-precision active cancellation under specific operating conditions, effectively avoiding performance failures and even resonance amplification issues in passive systems at specific frequencies. It significantly reduces the vibration level and structural fatigue risk of the compressor in complex operating environments, thereby improving overall noise performance, service life, and energy efficiency stability.

[0013] Secondly, embodiments of the present invention provide a compressor, including: a compressor body and a compressor vibration damping structure as described above. The compressor body includes a housing and a foot base. The studs of the compressor vibration damping structure pass through the housing and the foot base from bottom to top to achieve a fixed connection.

[0014] In one specific embodiment, the stud passes through the housing, the support damping member, the foot, and the axial damping pad sequentially from bottom to top, and is connected to the nut; the upper and lower ends of the support damping member abut against the lower surface of the foot and the inner surface of the housing, respectively, and the annular damping member is located on the inner side of the foot.

[0015] In one specific embodiment, the foot is provided with a mounting hole, the inner diameter of which matches the outer diameter of the annular damping element.

[0016] The compressor of the present invention has the following advantages compared with the prior art: by applying the compressor vibration reduction structure mentioned above, it can effectively overcome the technical defects of existing passive vibration reduction technology, such as poor adaptability under multiple working conditions, narrow vibration reduction frequency band, and possible resonance amplification. It realizes the intelligent control mechanism of "passive-active" coordinated vibration reduction, and improves the vibration suppression capability and operational reliability of the compressor in the entire working condition range. Specifically, when the compressor is in stable operation or low vibration condition, the vibration reduction structure effectively absorbs and dissipates the conventional vibration energy caused by rotor rotation through a multi-stage passive damping system consisting of support damping components, annular damping components, and axial damping pads, maintaining the low-noise and stable operation of the entire unit. However, under non-steady-state high vibration conditions such as start-up, variable frequency speed regulation, or high load, when the detected vibration amplitude reaches a preset threshold, the external control circuit, based on the air conditioner's built-in operating status signal, drives the piezoelectric ceramic components in real time to generate an active excitation torque that is opposite in phase and matches the amplitude of the disturbance torque. This torque acts on the stud structure and is transmitted to the compressor base through the annular damping component and support damping component, precisely canceling the radial and tangential vibration components excited by rotor eccentricity, mass imbalance, and installation constraints, thereby achieving active suppression of key vibration modes. Compared to traditional passive solutions that rely solely on fixed-parameter damping elements, this design integrates piezoelectric ceramic components into the annular groove of the stud, forming a closed-loop force transmission system with the annular damping element and axial damping pad. This not only results in a compact and easy-to-assemble structure but also achieves integrated control of vibration sensing, judgment, and response. This design combines the advantages of wide-bandwidth passive vibration absorption with high-precision active cancellation under specific operating conditions, effectively avoiding performance failures and even resonance amplification issues in passive systems at specific frequencies. It significantly reduces the vibration level and structural fatigue risk of the compressor in complex operating environments, thereby improving overall noise performance, service life, and energy efficiency stability.

[0017] Thirdly, embodiments of the present invention provide a compressor vibration reduction method, applied to the compressor described above, the vibration reduction method comprising: Read the compressor's status information and the piezoelectric voltage of all piezoelectric ceramic plates; The total bending moment is calculated based on the state information and piezoelectric voltage. Determine whether the total bending moment exceeds a preset threshold; If the total bending moment does not exceed the preset threshold, the compressor will perform passive vibration reduction. If the total bending moment exceeds the preset threshold, the target reverse bending moment is calculated, and the driving voltage of each piezoelectric ceramic sheet is calculated based on the target reverse bending moment. Each piezoelectric ceramic sheet outputs deformation force according to its corresponding driving voltage to counteract vibration.

[0018] The vibration reduction method of this invention has the following advantages compared with the prior art: By using an intelligent vibration reduction structure based on piezoelectric ceramic components, it achieves real-time perception, dynamic evaluation, and active response to the vibration state of the compressor. This effectively solves the key problems of poor adaptability and limited suppression capability of traditional passive vibration reduction technology under varying operating conditions, thus improving the intelligence level and overall performance of the machine's vibration control. Specifically, this method first reads the compressor's operating status information (such as speed, load, start / stop signals, frequency conversion commands, etc.) and the piezoelectric voltage output by each piezoelectric ceramic plate (reflecting the strain or bending moment response caused by the current vibration), and integrates multi-source sensor data to accurately calculate the total bending moment acting on the compressor base. This total bending moment characterizes the radial and tangential vibration resultant torque caused by factors such as rotor eccentricity, unbalanced mass, and installation constraints, and is a key basis for determining whether an active vibration reduction mechanism needs to be activated. When the total bending moment does not exceed the preset threshold, the system maintains a passive vibration reduction mode, relying on a mechanical damping network composed of support damping components, ring damping components, and axial damping pads to absorb conventional vibration energy, ensuring low power consumption and high reliability of the foundation vibration reduction effect. However, once the total bending moment exceeds the threshold (usually corresponding to non-steady-state high vibration conditions such as start-stop, rapid frequency conversion, or high load), the system immediately activates the active vibration reduction logic: based on the amplitude and direction of the total bending moment, the system calculates the required target offset bending moment in reverse, and further decouples and distributes it to each piezoelectric ceramic sheet, generating the corresponding driving voltage command. Under the action of the driving voltage, each piezoelectric ceramic sheet generates a controllable deformation force, which is transmitted through the stud structure to form a reverse torque that is opposite in phase and matches the amplitude of the disturbance bending moment, thereby achieving effective offsetting of the vibration source. Compared with the existing passive schemes that only rely on fixed parameter damping elements, this method achieves adaptive switching of the vibration reduction strategy under operating conditions through "sensing-judgment-response" closed-loop control: it retains the advantages of simple and maintenance-free passive vibration reduction structure, while introducing high-response speed and high-precision active intervention capability under key high vibration conditions. This method not only effectively suppresses random vibrations over a wide frequency band, but also specifically eliminates resonance peaks in specific modes, avoiding vibration amplification caused by impedance mismatch in traditional passive systems at certain frequencies. Ultimately, overall system noise is reduced, structural fatigue damage is mitigated, and reliability and service life are substantially improved, making it particularly suitable for high-end air conditioning and refrigeration equipment with stringent vibration and noise control requirements.

[0019] The present invention will be further described below with reference to the accompanying drawings and specific embodiments. Attached Figure Description

[0020] To more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0021] Figure 1 This is a partial cross-sectional schematic diagram of the compressor vibration reduction structure provided by the present invention; Figure 2 This is an exploded view of the compressor vibration reduction structure provided by the present invention; Figure 3 This is a schematic diagram of the compressor provided by the present invention; Figure 4 This is a schematic flowchart of a compressor vibration reduction method provided in an embodiment of the present invention.

[0022] Figure label: Stud 10, annular groove 11, external thread 12, piezoelectric ceramic component 20, support damping component 30, annular damping component 40, axial damping pad 50, nut 60, compressor body 70, housing 71, foot 72. Detailed Implementation

[0023] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0024] 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. 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.

[0025] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," and "counterclockwise," 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 invention 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 invention.

[0026] Furthermore, 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. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0027] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a connection, a detachable connection, or an integral part; 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; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0028] 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.

[0029] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the invention. The illustrative expressions of the above terms in this specification should not be construed as necessarily referring to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. In addition, those skilled in the art can combine and integrate the different embodiments or examples described in this specification.

[0030] See Figures 1 to 2 As shown, this invention discloses a specific embodiment of a compressor vibration reduction structure, including: a stud 10, a piezoelectric ceramic assembly 20, a support damping element 30, an annular damping element 40, an axial damping pad 50, and a nut 60. The stud 10 has an annular groove 11 in its middle section. The support damping element 30, the piezoelectric ceramic assembly 20, the annular damping element 40, the axial damping pad 50, and the nut 60 are installed on the stud 10 from bottom to top along the axial direction. The piezoelectric ceramic assembly 20 is fitted into the annular groove 11. The annular damping element 40 is sleeved on the outer periphery of the piezoelectric ceramic assembly 20, and the upper and lower ends of the annular damping element 40 respectively abut against the axial damping pad 50 and the support damping element 30. The piezoelectric ceramic assembly 20 is electrically connected to an external control circuit.

[0031] Specifically, the vibration damping structure mainly consists of a stud 10, a piezoelectric ceramic component 20, a support damping element 30, an annular damping element 40, an axial damping pad 50, and a nut 60. The stud 10, as the core load-bearing and force-transmitting element, has the support damping element 30, piezoelectric ceramic component 20, annular damping element 40, axial damping pad 50, and nut 60 sequentially installed along its axial direction from bottom to top. In particular, the stud 10 has an annular groove 11 in its middle section. This groove is used to precisely accommodate and position the piezoelectric ceramic component 20, ensuring its stable radial fit against the stud 10 body, while preventing performance degradation due to assembly misalignment or operational vibration.

[0032] The piezoelectric ceramic assembly 20 typically consists of one or more annular or arc-shaped piezoelectric ceramic sheets. Its inner surface is tightly fitted to the wall of the annular groove 11 of the stud 10, while its outer periphery is completely covered by an annular damping element 40. The annular damping element 40 can be made of high-damping rubber, polyurethane, or viscoelastic composite material. Its upper and lower end faces respectively abut against the upper axial damping pad 50 and the lower support damping element 30, thus forming a continuous mechanical transmission path in both axial and radial dimensions. The support damping element 30 is located at the bottom of the entire structure, directly contacting the compressor base, bearing the main static load and providing initial passive damping. The axial damping pad 50 is located above the piezoelectric ceramic assembly 20, used to isolate high-frequency axial impacts and work with the annular damping element 40 to achieve multi-directional energy dissipation. The entire assembly is pre-tightened and fixed at the top by a nut 60, ensuring reliable contact and pre-pressure between components under long-term vibration conditions, preventing loosening or gaps.

[0033] The piezoelectric ceramic component 20 is electrically connected to an external control circuit via leads. This control circuit is integrated into the main control board of the air conditioning system or a separate vibration control module, and can acquire real-time operating status information of the compressor, including but not limited to speed signals, frequency conversion commands, start / stop status, current load, and temperature parameters. Simultaneously, the piezoelectric ceramic component 20 itself has dual sensing and driving functions: in the absence of active excitation, the piezoelectric voltage generated by structural vibration can serve as a vibration response acquisition signal; when active intervention is required, a driving voltage is applied according to the control command to produce controllable deformation.

[0034] During actual operation, when the compressor is in a stable operating state (such as constant-speed cooling / heating) or a low-vibration condition, the system only activates the passive vibration reduction mode. At this time, the multi-stage damping network composed of the support damping component 30, the annular damping component 40, and the axial damping pad 50 effectively absorbs and dissipates the conventional vibration energy caused by rotor rotation, especially the periodic disturbances in the low-to-medium frequency range, through material internal friction, interface slippage, and viscoelastic hysteresis effects, thereby maintaining the stable and low-noise operation of the entire machine.

[0035] When the compressor enters unsteady, high-vibration operating conditions such as start-stop, rapid frequency conversion speed regulation, or high load, the rotor experiences significantly enhanced tangential and radial vibrations due to acceleration / deceleration, increased airflow pulsation, or sudden changes in unbalanced forces. At this time, the vibration is transmitted through the compressor housing to the mounting base, forming an equivalent bending moment (i.e., total bending moment) at the stud 10. This bending moment causes a slight bending deformation in the stud 10, which in turn generates a corresponding piezoelectric charge (i.e., piezoelectric voltage) inside the piezoelectric ceramic assembly 20. The control circuit synchronously reads this voltage signal and the compressor's operating status to comprehensively determine the current vibration intensity. Once the calculated total bending moment exceeds a preset safety threshold (this threshold can be calibrated according to different models, installation environments, and user noise requirements), the system immediately triggers an active vibration reduction mechanism. Based on the amplitude, direction, and frequency characteristics of the total bending moment, the control algorithm calculates the target reverse bending moment to be applied and uses a force-electric coupling model to calculate the required driving voltage for each piezoelectric ceramic element. Subsequently, the control circuit applies a precisely controlled voltage signal to the piezoelectric ceramic assembly 20, causing it to undergo directional reverse deformation, thereby generating an excitation torque on the stud 10 that is equal in magnitude and opposite in direction to the disturbance bending moment. This torque is transmitted to the compressor base through the annular damper 40, effectively counteracting the original vibration source and suppressing radial and tangential vibration disturbances caused by rotor eccentricity, mass imbalance, assembly errors, or asymmetric constraint stiffness.

[0036] In other words, this vibration reduction structure can effectively overcome the technical defects of existing passive vibration reduction technology, such as poor adaptability under multiple working conditions, narrow vibration reduction frequency band, and potential resonance amplification. It realizes an intelligent control mechanism of "passive-active" coordinated vibration reduction, which improves the vibration suppression capability and operational reliability of the compressor in the entire working condition range. Specifically, when the compressor is in stable operation or low vibration condition, the vibration reduction structure effectively absorbs and dissipates the conventional vibration energy caused by rotor rotation through a multi-stage passive damping system consisting of a support damping component 30, an annular damping component 40, and an axial damping pad 50, maintaining the low-noise and stable operation of the entire unit. However, under non-steady-state high vibration conditions such as start-up, variable frequency speed regulation, or high load, when the vibration amplitude is detected to reach a preset threshold, the external control circuit drives the piezoelectric ceramic component 20 in real time based on the air conditioner's built-in operating status signal to generate an active excitation torque that is opposite in phase and matches the amplitude of the disturbance torque. This torque acts on the stud 10 structure and is transmitted to the compressor base through the annular damping component 40 and the support damping component 30, accurately canceling the radial and tangential vibration components excited by rotor eccentricity, mass imbalance, and installation constraints, thereby achieving active suppression of key vibration modes. Compared to traditional passive solutions that rely solely on fixed-parameter damping elements, this design integrates the piezoelectric ceramic component 20 into the annular groove 11 of the stud 10, forming a closed-loop force transmission system with the annular damping element 40 and the axial damping pad 50. This not only results in a compact and easy-to-assemble structure but also achieves integrated control of vibration sensing, judgment, and response. This design combines the advantages of wide-bandwidth passive vibration absorption with high-precision active cancellation under specific operating conditions, effectively avoiding performance failures and even resonance amplification issues in passive systems at specific frequencies. It significantly reduces the vibration level and structural fatigue risk of the compressor in complex operating environments, thereby improving overall noise performance, service life, and energy efficiency stability.

[0037] See Figure 2 As shown, in one embodiment, the piezoelectric ceramic component 20 is composed of a plurality of piezoelectric ceramic sheets arranged in a circumferential direction.

[0038] Specifically, the piezoelectric ceramic assembly 20 does not use a single ring-shaped piezoelectric ceramic, but rather multiple independent piezoelectric ceramic sheets (usually 2 to 8 sheets, preferably 4 or 6 sheets) are evenly distributed along the circumference of the stud 10 and fitted onto the inner wall of the annular groove 11 in the middle section of the stud 10. Each piezoelectric ceramic sheet is arc-shaped or fan-shaped, and its radius of curvature matches the inner diameter of the groove of the stud 10, ensuring a tight fit without gaps and effectively transmitting radial and tangential mechanical stress.

[0039] Each piezoelectric ceramic sheet is electrically isolated from the others in the circumferential direction; that is, each sheet has an independent lead-out electrode and is connected to a multi-channel drive module in an external control circuit via flexible wires. This segmented layout allows the control system to apply different driving voltages to each piezoelectric ceramic sheet, thereby achieving spatially asymmetrical, directionally controllable active deformation output.

[0040] During assembly, the piezoelectric ceramic sheet is first bonded or clamped into the annular groove 11 of the stud 10. Then, an annular damping element 40 (such as a high-damping rubber ring or composite elastomer) is fitted around its outer periphery. This damping element protects the piezoelectric ceramic sheet from external impacts and also acts as a force transmission medium, converting the local deformation of the piezoelectric ceramic sheet into bending moment control of the entire stud 10 structure. Because the piezoelectric ceramic sheets are distributed circumferentially, when one or more sheets are excited, they can expand or contract locally in a specific direction, causing the stud 10 to bend in a specific orientation, generating a reverse excitation torque in the desired direction.

[0041] The control circuit calculates the spatial direction of the current disturbance bending moment (e.g., biased towards the positive X-axis or negative Y-axis) based on real-time vibration information (including voltage signals induced by each piezoelectric ceramic element and compressor operating status parameters) using algorithms (such as least squares method, modal decomposition, or model-based inverse control). Based on this, it allocates the driving voltage amplitude and polarity to each piezoelectric ceramic element. For example, if the main vibration direction is detected at a certain angle θ, a voltage of opposite polarity can be applied to the piezoelectric ceramic elements located at θ±90°, causing one side to elongate and the other to shorten, thereby generating an active control force to counteract the bending moment in that direction.

[0042] In other words, traditional single-piece or ring-type piezoelectric elements can only produce axisymmetric deformation, making it difficult to effectively suppress asymmetric vibrations in specific directions. However, using a multi-piece piezoelectric ceramic structure distributed along the circumference can accurately identify and cancel radial or tangential disturbance torques in any direction, improving the directional selectivity and control precision of active vibration reduction. Furthermore, compressors often excite multi-mode coupled vibrations during start-up, shutdown, and frequency conversion, with the vibration direction dynamically changing over time. Segmented piezoelectric components can be independently driven through multiple channels, allowing for real-time adjustment of the output force combination of each segment, flexibly matching vibration modes of different frequencies and directions, and avoiding the failure of a single control strategy.

[0043] In one embodiment, the piezoelectric ceramic sheet has a concave curved surface, and the curvature of the curved surface is consistent with the curvature of the inner wall of the annular groove 11.

[0044] Specifically, the stud 10 has an annular groove 11 in its middle section. The inner wall of this groove is part of a cylindrical surface with a defined radius of curvature (i.e., equal to the radius of the stud 10 body at that location). To ensure that the piezoelectric ceramic assembly 20 can fit tightly against the inner wall of the groove and effectively participate in the mechanical response, each piezoelectric ceramic sheet is pre-processed into a curved surface shape that geometrically matches the inner wall of the groove, typically an arc or a fan-shaped ring.

[0045] Specifically, during the manufacturing process, the piezoelectric ceramic sheet undergoes precision molding, cutting, or grinding to ensure that both its inner surface (the side facing the axis of the stud 10) and outer surface have the same radius of curvature as the annular groove 11 of the stud 10. For example, if the diameter of the stud 10 is 20 mm, the inner radius of curvature of the piezoelectric ceramic sheet is approximately 10 mm, and the overall shape is a thin-walled arc-shaped sheet. The arc length is customized according to the required number of circumferentially distributed sheets (e.g., approximately 90° arc length for each of 4 sheets, and approximately 60° for 6 sheets).

[0046] During assembly, each curved piezoelectric ceramic sheet is inserted into the annular groove 11 along the axial direction of the stud 10 and evenly arranged in the circumferential direction. Its inner surface completely fits the bottom surface of the groove, while its outer surface contacts the inner wall of the subsequently fitted annular damping component 40. To enhance the interfacial bonding strength and stress transmission efficiency, a layer of flexible conductive adhesive or high shear strength structural adhesive can be coated between the piezoelectric ceramic sheet and the groove. This ensures the reliability of the electrical connection and avoids performance degradation due to fretting wear.

[0047] Furthermore, due to the inherent brittleness of piezoelectric ceramic materials, forcibly bending and installing flat sheets can easily lead to internal micro-cracks or even breakage, affecting service life and control accuracy. However, using a pre-formed curved structure ensures that the piezoelectric ceramic sheet is in a stress-free bonding state in its natural condition, avoiding residual stress during assembly and ensuring structural integrity and stable electromechanical coupling performance in long-term vibration environments.

[0048] In other words, the curved piezoelectric ceramic sheet conformally fits the inner wall of the annular groove 11 across its entire surface, increasing the effective contact area and avoiding stress concentration caused by point or line contact. This allows the stud 10 to transmit its local strain energy to the piezoelectric ceramic sheet more evenly and efficiently when subjected to vibration bending moment, thereby improving sensing sensitivity. Conversely, during active driving, the deformation of the piezoelectric ceramic sheet can be more fully converted into a reverse bending moment on the stud 10, improving the efficiency of active control force output. Furthermore, piezoelectric ceramics are brittle functional materials with low tensile strength and are extremely sensitive to mechanical stress. If forced to bend to adapt to the curved substrate during assembly or operation, irreversible microcracks are easily generated internally, leading to a decrease in piezoelectric constant, deterioration of insulation performance, or even open circuit failure. By adopting a pre-formed curved structure, the piezoelectric ceramic sheet is always in a state of zero pre-bending or micro-pre-compression, fundamentally avoiding the risk of assembly damage and significantly extending its service life in the harsh vibration environment of the compressor.

[0049] See Figure 1 and Figure 2 As shown, in one embodiment, the upper end of the stud 10 is provided with an external thread 12, and the nut 60 is matched with the external thread 12.

[0050] Specifically, the stud 10, as the core load-bearing and force-transmitting element, is cylindrical in shape, with a standard or custom-made external thread 12 (such as metric threads like M6 or M8, or non-standard threads adapted to the compressor mounting holes) machined on its upper end. This external thread 12 extends a predetermined length (usually 10-20mm) along the axial direction of the stud 10 to ensure sufficient engagement with the nut 60, meeting the requirements for tensile strength, vibration resistance, and anti-loosening.

[0051] Nut 60 can be a standard hexagonal nut, a toothed lock nut, a nylon insert self-locking nut, or a specially designed preload adjusting nut. In actual operation, a preset preload torque can be applied to nut 60 using a torque wrench or angle control method to moderately compress the entire laminated structure (support damping component 30 → piezoelectric ceramic assembly 20 → annular damping component 40 → axial damping pad 50) in the axial direction, eliminating assembly gaps between components and ensuring stable contact pressure between the piezoelectric ceramic plate and the groove of stud 10 and annular damping component 40.

[0052] In other words, through the threaded connection, nut 60 can apply a controllable axial preload to the entire vibration damping assembly. This preload ensures that each damping element (especially the supporting damping element 30 and the axial damping pad 50) is in an effective working compression state, maximizing energy dissipation performance; on the other hand, it ensures that the piezoelectric ceramic sheet is firmly attached to the inner wall of the annular groove 11, preventing micro-displacement or contact failure caused by vibration, and ensuring the stability of sensing and drive signals. Furthermore, threaded connections are a standardized and versatile mechanical connection method, requiring no welding, riveting, or special tooling for assembly. When repairing or replacing the piezoelectric ceramic assembly 20, simply loosening nut 60 allows for disassembly of the upper assembly, simplifying operations and significantly reducing manufacturing and after-sales costs. Simultaneously, by adjusting the tightness of nut 60, the preload can be fine-tuned to adapt to the varying stiffness / damping characteristics required by different compressor models or installation environments.

[0053] In one embodiment, the axial damping pad 50 is made of rubber.

[0054] Specifically, the main function of the axial damping pad 50 is to provide elastic support and damping energy dissipation in the axial direction. This damping pad is made of polymer rubber material, specifically natural rubber (NR), styrene-butadiene rubber (SBR), silicone rubber (VMQ), ethylene propylene diene monomer (EPDM) rubber, or polyurethane rubber (PU), etc., and the selection is based on the compressor operating environment (such as temperature range, oil resistance, aging performance) and vibration reduction requirements.

[0055] Structurally, the axial damping pad 50 is typically machined into an annular shape or a disc shape with a central through hole. Its inner diameter is slightly larger than the outer diameter of the stud 10 to facilitate easy insertion into the stud 10. The outer diameter matches the bottom surface of the annular damping element 40 or the nut 60 to ensure uniform load distribution. The thickness is generally controlled between 2-8mm to ensure sufficient compressive deformation space to absorb impact while avoiding excessive thickness that would lead to insufficient stiffness and affect the overall structural stability.

[0056] In other words, rubber materials possess excellent viscoelasticity. When subjected to axial alternating loads (such as compressor start-up and shutdown impacts, or axial force fluctuations caused by exhaust pulsations), their molecular chains undergo repeated stretching and relaxation, converting mechanical vibration energy into heat energy for dissipation. Compared to metal springs, which only store energy without dissipation, rubber damping pads can reduce the transmission rate of axial vibrations, especially exhibiting a significant suppression effect on mid-to-high frequency vibrations in the 50-500Hz range.

[0057] In one embodiment, the support damping member 30 and the annular damping member 40 are made of nitrile rubber or neoprene rubber.

[0058] Specifically, the support damping element 30 is located at the bottom of the stud 10, directly contacting the compressor mounting base or bracket, bearing the static load of the whole machine and isolating external excitation from the compressor base; the annular damping element 40 is sleeved in the middle section of the stud 10, covering the outer periphery of the piezoelectric ceramic assembly 20, mainly transmitting and dissipating the radial / tangential force generated by the active deformation of the piezoelectric ceramic sheet, and suppressing its local resonance.

[0059] Both types of damping components use nitrile rubber (NBR) or chloroprene rubber (CR) as the main material. Specifically: Nitrile butadiene rubber (NBR): Acrylonitrile content is typically controlled between 28% and 40%, balancing oil resistance and elasticity. Suitable for applications where there is a risk of lubricating oil vapor or refrigerant contact inside the compressor.

[0060] Chloroprene rubber (CR): It has excellent weather resistance, ozone resistance and flame retardancy, and is suitable for high temperature, high humidity or outdoor operating environments (such as heat pump type air conditioner outdoor units).

[0061] Both types of rubber can have their hardness adjusted according to vibration damping requirements (typically Shore A hardness is 50-80), and their dynamic mechanical properties can be optimized by adding compounding agents such as carbon black, antioxidants, and plasticizers.

[0062] See Figure 3 As shown, the present invention also discloses a compressor, including: a compressor body 70 and a compressor vibration damping structure as described above. The compressor body 70 includes a housing 71 and a foot 72. The studs 10 of the compressor vibration damping structure pass through the housing 71 and the foot 72 from bottom to top to achieve a fixed connection.

[0063] Specifically, the compressor body 70 mainly includes a sealed metal housing 71 and a foot 72 (also called a mounting foot or support foot, usually made of cast iron, stamped steel plate or welded structure, used to fix the compressor to the chassis, bracket or base of the outdoor unit of the air conditioner) fixed to the bottom of the housing 71.

[0064] A central through hole is made at the corresponding position on the bottom of the compressor housing 71 (or a pre-reserved hole near the existing process hole / exhaust pipe hole is used), and this hole penetrates the wall thickness of the housing 71; at the same time, a coaxial mounting hole is also provided at the corresponding position on the foot 72. The two holes are manufactured to ensure high coaxiality, forming a continuous vertical channel.

[0065] The electrodes of the piezoelectric ceramic component 20 are connected to the external drive / sensing circuit of the compressor via flexible wires, enabling real-time monitoring of the vibration state at the footplate 72 and the application of a reverse control voltage to achieve active vibration reduction. The entire system can be linked with the air conditioner main control board to achieve intelligent vibration suppression.

[0066] In other words, by applying the compressor vibration reduction structure mentioned above, the technical defects of existing passive vibration reduction technology, such as poor adaptability under multiple operating conditions, narrow vibration reduction frequency band, and potential resonance amplification, can be effectively overcome. This achieves an intelligent control mechanism of "passive-active" coordinated vibration reduction, improving the compressor's vibration suppression capability and operational reliability across the entire operating range. Specifically, when the compressor is in stable operation or low vibration condition, the vibration reduction structure effectively absorbs and dissipates the conventional vibration energy caused by rotor rotation through a multi-stage passive damping system consisting of support damping component 30, annular damping component 40 and axial damping pad 50, maintaining the low-noise and stable operation of the whole machine. However, under non-steady-state high vibration conditions such as start-up, variable frequency speed regulation or high load, when the vibration amplitude is detected to reach a preset threshold, the external control circuit drives the piezoelectric ceramic component 20 in real time based on the air conditioner's built-in operating status signal to generate an active excitation torque that is opposite in phase and matches the amplitude of the disturbance torque. This torque acts on the stud 10 structure and is transmitted to the compressor foot 72 through the annular damping component 40 and support damping component 30, accurately canceling the radial and tangential vibration components excited by rotor eccentricity, mass imbalance and installation constraints, thereby achieving active suppression of key vibration modes. Compared to traditional passive solutions that rely solely on fixed-parameter damping elements, this design integrates the piezoelectric ceramic component 20 into the annular groove 11 of the stud 10, forming a closed-loop force transmission system with the annular damping element 40 and the axial damping pad 50. This not only results in a compact and easy-to-assemble structure but also achieves integrated control of vibration sensing, judgment, and response. This design combines the advantages of wide-bandwidth passive vibration absorption with high-precision active cancellation under specific operating conditions, effectively avoiding performance failures and even resonance amplification issues in passive systems at specific frequencies. It significantly reduces the vibration level and structural fatigue risk of the compressor in complex operating environments, thereby improving overall noise performance, service life, and energy efficiency stability.

[0067] See Figure 3 As shown, in one embodiment, the stud 10 passes through the housing 71, the support damping member 30, the foot 72 and the axial damping pad 50 from bottom to top, and is connected to the nut 60; the upper and lower ends of the support damping member 30 abut against the lower surface of the foot 72 and the inner surface of the housing 71, respectively, and the annular damping member 40 is located inside the foot 72.

[0068] Specifically, the stud 10, as the core force transmission and positioning element, adopts a bottom-up insertion path, and its assembly sequence and relative positional relationship are as follows: The stud 10 first emerges upward from the compressor housing 71 and passes through the following sequentially: The bottom of the housing 71 has a through hole (this hole is located at the bottom of the housing 71, is usually circular, has a diameter slightly larger than the outer diameter of the stud 10, and is equipped with a sealing structure). Support damping element 30 (sleeved on stud 10, located below foot 72); The piezoelectric ceramic component 20 is installed in the annular groove 11 of the stud 10, and then an annular damping component 40 is fitted around the piezoelectric ceramic component 20. Foot 72 (Foot 72 is a metal mounting leg fixed to the bottom of housing 71, and its center is provided with a mounting hole coaxial with the through hole of housing 71). Axial damping pad 50 (placed on the upper surface of the foot 72 and fitted onto the upper end of the stud 10). Finally, screw the nut 60 into the top of the stud 10 to complete the overall pre-tightening.

[0069] The upper end face of the support damping member 30 is tightly fitted to the lower surface of the foot 72, while the lower end face abuts against the inner surface of the housing 71. After the nut 60 is pre-tightened, the entire assembly is compressed, putting the support damping member 30 in an axially compressed state, forming an elastic interlayer between the housing 71 and the foot 72, isolating vibrations from the external support from being transmitted to the housing 71.

[0070] The annular damping element 40 is not located above or below the foot 72, but rather embedded inside the foot 72. Specifically, the foot 72 is manufactured with an annular space (or a step on the inner wall of the through hole) reserved in its thickness direction to accommodate the annular damping element 40. This damping element covers the outer periphery of the piezoelectric ceramic assembly 20, which is nested in the annular groove 11 in the middle section of the stud 10, and is entirely located within the internal region surrounded by the foot 72. This arrangement ensures that the annular damping element 40 is in close contact with the inner wall of the foot 72, effectively transmitting and dissipating radial and tangential vibrations.

[0071] In one embodiment, the foot 72 is provided with a mounting hole, the inner diameter of which matches the outer diameter of the annular damping member 40.

[0072] Specifically, the foot 72 has a through mounting hole that extends vertically through the thickness of the foot 72, with its axis coaxial with the path of the stud 10. This mounting hole is not a simple open hole, but rather has an annular step, groove, or smooth inner cylindrical surface at a specific height on its inner wall, specifically designed to accommodate the annular damping element 40.

[0073] In other words, the matching design between the inner diameter of the mounting hole and the outer diameter of the annular damper 40 solves the problem of easy displacement, rotation, or detachment of traditional free-placed rubber parts. Even under conditions of bumpy transportation or high-frequency vibration, the annular damper 40 can still maintain stable contact with the piezoelectric ceramic assembly 20 and the inner wall of the foot 72, ensuring that the vibration reduction function remains effective.

[0074] See Figure 4 As shown, the present invention also discloses a compressor vibration reduction method, applied to the compressor described above, the vibration reduction method comprising: S110, Read the compressor's status information and the piezoelectric voltage of all piezoelectric ceramic sheets; Specifically, during compressor operation, the control system simultaneously acquires two types of key data. One type is the compressor's own operating status information, including current motor speed, operating frequency, running time, whether it is in the start-up or shutdown phase, ambient temperature, and current load. This information is used to determine whether the compressor's current operating condition is prone to causing severe vibration. The other type is the voltage signal output by the piezoelectric ceramic plates installed inside the mounting base. Because piezoelectric ceramics have the characteristic of "generating electricity under force," when the compressor vibrates due to imbalance of internal moving parts or external disturbances, the mounting base undergoes slight deformation, causing the embedded piezoelectric ceramic plates to be compressed or stretched, thereby generating a voltage across their terminals. This voltage signal is amplified and filtered by a high-impedance signal conditioning circuit and then acquired by the control system in real time, serving as a direct basis for reflecting the intensity and direction of local vibration.

[0075] S120. The total bending moment is calculated based on the state information and piezoelectric voltage. Specifically, the control system inputs the two types of data mentioned above into a pre-established mechanical model. This model comprehensively considers factors such as the specific installation position of the piezoelectric ceramic plates on the mounting base (e.g., distance from the compressor's central axis and distribution angle), the structural stiffness of the mounting base, and the mass distribution of the compressor casing. By analyzing the voltage magnitude and polarity measured by each piezoelectric ceramic plate, the direction and relative strength of the local force at that location can be inferred; combined with the lever arm length from the piezoelectric ceramic plate to the compressor's center of gravity or rotation axis, the contribution of each point to the overall tilting tendency of the compressor can be estimated. Subsequently, the system performs vector synthesis of all these local contributions according to spatial directions, ultimately deriving a physical quantity representing the overall stress tendency of the compressor—the "total bending moment." This total bending moment reflects whether the compressor, under its current operating condition, is being subjected to a resultant torque that causes it to sway, tilt, or twist.

[0076] S130. Determine whether the total bending moment exceeds the preset threshold. Specifically, the system internally stores a pre-set safety limit value, called the "preset threshold." This threshold was determined through extensive experimental testing and simulation analysis, representing the maximum acceptable bending moment level of the compressor during normal operation. If the absolute value of the currently calculated total bending moment is less than or equal to this threshold, it indicates that the vibration is within a controllable range and will not significantly affect structural safety or noise performance. Conversely, if the absolute value of the total bending moment is greater than this threshold, it indicates that the compressor is experiencing strong dynamic disturbances and may have approached or entered the resonance region, posing a risk of increased vibration, increased noise, or even structural fatigue.

[0077] S140. If the total bending moment does not exceed the preset threshold, the compressor performs passive vibration reduction. Specifically, in this scenario, the control system does not apply any drive signal to the piezoelectric ceramic plate, allowing it to continue monitoring the vibration state solely as a sensor. At this point, the compressor relies entirely on rubber-like damping elements within its mechanical structure (such as support dampers, annular dampers, and axial damping pads) to absorb and dissipate vibrational energy. These elastic elements convert mechanical vibration into heat energy through molecular friction and hysteresis within the material, thus achieving "passive vibration reduction" without external energy input. This method consumes extremely low power and is suitable for most stable operating conditions.

[0078] S150. If the total bending moment exceeds the preset threshold, the target reverse bending moment is calculated, and the driving voltage of each piezoelectric ceramic sheet is calculated based on the target reverse bending moment. Specifically, once the vibration is determined to be too strong, the system immediately switches to active control mode. First, it generates a "target reverse bending moment" with a slightly larger amplitude and completely opposite direction to the current total bending moment. The purpose of this reverse bending moment is not only to counteract the original disturbance moment, but also to provide a certain amount of additional damping force to quickly attenuate the vibration that has occurred.

[0079] Next, the system needs to rationally allocate the overall target reverse bending moment to each piezoelectric ceramic element. Since the piezoelectric ceramic elements are located at different positions in space, their influence on the overall bending moment also varies. The control system uses a pre-defined position weighting relationship to decompose the target reverse bending moment into the specific thrust or tension that each piezoelectric ceramic element should generate. Then, based on the physical characteristics of each piezoelectric ceramic element (such as thickness, area, material sensitivity, etc.), the required voltage to generate the desired thrust or tension is further determined. This process is typically completed through table lookup or linear interpolation to ensure efficient and accurate calculations.

[0080] S160: Each piezoelectric ceramic sheet outputs deformation force according to the corresponding driving voltage to counteract vibration.

[0081] Specifically, the control system finally sends the calculated drive voltage commands to the high-voltage drive circuit. This circuit amplifies the low-voltage control signal into a high-voltage signal of several hundred volts and applies it to the corresponding piezoelectric ceramic plates. Under the influence of the electric field, the piezoelectric ceramics undergo micron-level dimensional changes—some elongate, some shorten, depending on the voltage polarity and installation direction. These minute deformations are transmitted through the foot structure, forming a set of coordinated active control forces. These forces, when combined in space, generate a torque that is exactly opposite to the original disturbance bending moment, thereby effectively counteracting the compressor's swaying tendency, reducing vibration amplitude, and decreasing noise transmitted to the external support.

[0082] The entire process is executed in a millisecond-level cycle, forming a closed-loop intelligent vibration reduction system that can both sense changes and actively intervene to achieve high-performance and high-efficiency vibration control.

[0083] In one embodiment, a rectangular coordinate system is established with the geometric center of the annular groove as the origin O: Z-axis: Along the stud axis; X-axis: Located in the horizontal plane, pointing towards the radial reference direction of the compressor; Y-axis: Located in the horizontal plane, orthogonal to the X-axis.

[0084] Where θ is defined i This represents the polar angle of the i-th piezoelectric ceramic sheet relative to the X-axis in the circumferential direction of the annular groove cross-section.

[0085] When θ i =0°: The piezoelectric ceramic plate is located in the +X direction (pointing towards the compressor's center of mass); θ i =90°: The piezoelectric ceramic sheet is located in the +Y direction; θ i =180°: The piezoelectric ceramic sheet is located in the -X direction; θ i =270°: The piezoelectric ceramic sheet is located in the -Y direction.

[0086] Under the influence of compressor rotor imbalance force, electromagnetic imbalance force, and gas pressure pulsation, the compressor feet apply a time-varying lateral excitation force to the stud. This lateral excitation force will form a bending moment vector M at the middle section of the annular groove. e (t): ; Among them, M x The corresponding bending moment about the X-axis, M y The corresponding bending moment about the Y-axis.

[0087] Under the assumption of small deformation elasticity, the axial stress at any point on the cross section of the annular groove is: ; Where r is the radial distance from the center of the piezoelectric ceramic sheet to the neutral axis of the stud; I is the moment of inertia of the middle section of the annular groove; and θ is the polar angle of the section.

[0088] The i-th piezoelectric ceramic sheet is located at polar angle θ i At this location, the axial (Z direction) stress it experiences is: ; The piezoelectric equation for a piezoelectric ceramic sheet is: ; Where g is the piezoelectric constant, Let be the axial stress, and t be the axial thickness of the piezoelectric ceramic sheet. Substituting these values, we can obtain the voltage generated by the bending moment in the i-th piezoelectric ceramic sheet: ; During the bending moment sensing process, the control circuit reads the voltage signal output by each piezoelectric ceramic element, and then uses the above calculation method to deduce the real-time M. x and M y And vector synthesis to obtain M e (t).

[0089] The control circuit obtains the bending moment M on the stud. x and M y Subsequently, the axial elongation or shortening of each piezoelectric ceramic sheet is controlled by utilizing the inverse piezoelectric effect to achieve a target reverse bending moment M. c (t).

[0090] ; The target bending moment is decomposed into each piezoelectric ceramic sheet. The bending moment component that the i-th piezoelectric ceramic sheet needs to bear is: ; Among them, F i The required output force for the i-th piezoelectric ceramic element; the axial stress of the i-th piezoelectric ceramic element. i and strain The calculation method is as follows: Where A is the area of ​​the upper and lower force-bearing surfaces of the piezoelectric ceramic sheet, and E is the elastic modulus.

[0091] According to the inverse piezoelectric effect, we can obtain: ; Among them, U i Let be the voltage to be output by the i-th piezoelectric ceramic sheet. By reverse deduction, the voltage signal to be output by the control circuit can be obtained as follows: ; The control circuit outputs voltage U at time t. i By controlling the piezoelectric ceramic sheet at time t, its deformation can be controlled in real time. The deformation force of the piezoelectric ceramic sheet weakens the instantaneous bending moment on the stud. Since the electrical response of the piezoelectric ceramic sheet is only related to the total stress state acting on it at that moment, the bending moment M(t+1) calculated by the control circuit at time t+1 is not the actual external bending moment and needs to be discarded. c The disturbance of (t), i.e., the external bending moment at time t+1, is: ; The working process at time t+1 is the same as at time t. This method realizes the integrated design of piezoelectric ceramic sheet bending moment sensing and output, which can output compensation torque in real time to offset the bending moment transmitted to the vibration reduction structure by the radial and tangential vibration of the compressor, and realize the adaptive vibration reduction effect of the compressor.

[0092] The aforementioned compressor vibration reduction method, based on an intelligent vibration reduction structure with piezoelectric ceramic components, achieves real-time sensing, dynamic evaluation, and active response to the compressor's vibration state. This effectively solves key problems of traditional passive vibration reduction technologies, such as poor adaptability and limited suppression capabilities under varying operating conditions, thus improving the intelligence level and overall performance of the machine's vibration control. Specifically, this method first reads the compressor's operating status information (such as speed, load, start / stop signals, frequency conversion commands, etc.) and the piezoelectric voltage output by each piezoelectric ceramic element (reflecting the strain or bending moment response caused by the current vibration), and integrates multi-source sensor data to accurately calculate the total bending moment acting on the compressor's mounting base. This total bending moment characterizes the radial and tangential vibration resultant torque caused by factors such as rotor eccentricity, unbalanced mass, and installation constraints, and is a key basis for determining whether an active vibration reduction mechanism needs to be activated. When the total bending moment does not exceed the preset threshold, the system maintains a passive vibration reduction mode, relying on a mechanical damping network composed of support damping components, ring damping components, and axial damping pads to absorb conventional vibration energy, ensuring low power consumption and high reliability of the foundation vibration reduction effect. However, once the total bending moment exceeds the threshold (usually corresponding to non-steady-state high vibration conditions such as start-stop, rapid frequency conversion, or high load), the system immediately activates the active vibration reduction logic: based on the amplitude and direction of the total bending moment, the system calculates the required target offset bending moment in reverse, and further decouples and distributes it to each piezoelectric ceramic sheet, generating the corresponding driving voltage command. Under the action of the driving voltage, each piezoelectric ceramic sheet generates a controllable deformation force, which is transmitted through the stud structure to form a reverse torque that is opposite in phase and matches the amplitude of the disturbance bending moment, thereby achieving effective offsetting of the vibration source. Compared with the existing passive schemes that only rely on fixed parameter damping elements, this method achieves adaptive switching of the vibration reduction strategy under operating conditions through "sensing-judgment-response" closed-loop control: it retains the advantages of simple and maintenance-free passive vibration reduction structure, while introducing high-response speed and high-precision active intervention capability under key high vibration conditions. This method not only effectively suppresses random vibrations over a wide frequency band, but also specifically eliminates resonance peaks in specific modes, avoiding vibration amplification caused by impedance mismatch in traditional passive systems at certain frequencies. Ultimately, overall system noise is reduced, structural fatigue damage is mitigated, and reliability and service life are substantially improved, making it particularly suitable for high-end air conditioning and refrigeration equipment with stringent vibration and noise control requirements.

[0093] The above embodiments are preferred implementations of the present invention. In addition, the present invention can be implemented in other ways. Any obvious substitutions without departing from the concept of the present technical solution are within the protection scope of the present invention.

Claims

1. A compressor vibration damping structure, characterized in that, include: The device comprises a stud, a piezoelectric ceramic assembly, a support damping element, an annular damping element, an axial damping pad, and a nut. The stud has an annular groove in its middle section. The support damping element, piezoelectric ceramic assembly, annular damping element, axial damping pad, and nut are mounted on the stud axially from bottom to top. The piezoelectric ceramic assembly fits into the annular groove. The annular damping element is sleeved on the outer periphery of the piezoelectric ceramic assembly, and the upper and lower ends of the annular damping element abut against the axial damping pad and the support damping element, respectively. The piezoelectric ceramic assembly is electrically connected to an external control circuit.

2. The compressor vibration reduction structure according to claim 1, characterized in that, The piezoelectric ceramic assembly consists of several piezoelectric ceramic sheets arranged in a circumferential direction.

3. The compressor vibration reduction structure according to claim 2, characterized in that, The piezoelectric ceramic sheet has a concave curved surface, and the curvature of the surface is consistent with the curvature of the inner wall of the annular groove.

4. The compressor vibration damping structure according to claim 1, characterized in that, The upper end of the stud is provided with an external thread, and the nut is matched with the external thread.

5. The compressor vibration damping structure according to claim 1, characterized in that, The axial damping pad is made of rubber.

6. The compressor vibration reduction structure according to claim 1, characterized in that, The supporting damping element and the annular damping element are made of nitrile rubber or neoprene rubber.

7. A compressor, characterized in that, include: The compressor body and the compressor vibration damping structure as described in any one of claims 1-6, wherein the compressor body includes a housing and a foot, and the studs of the compressor vibration damping structure pass through the housing and the foot in sequence from bottom to top to achieve a fixed connection.

8. The compressor according to claim 7, characterized in that, The stud passes through the housing, the support damping member, the foot, and the axial damping pad in sequence from bottom to top, and is connected to the nut; the upper and lower ends of the support damping member abut against the lower surface of the foot and the inner surface of the housing, respectively, and the annular damping member is located on the inner side of the foot.

9. The compressor according to claim 8, characterized in that, The foot is provided with a mounting hole, the inner diameter of which matches the outer diameter of the annular damping element.

10. A method for reducing vibration in a compressor, applied to a compressor as described in any one of claims 7-9, characterized in that, The vibration reduction method includes: Read the compressor's status information and the piezoelectric voltage of all piezoelectric ceramic plates; The total bending moment is calculated based on the state information and piezoelectric voltage. Determine whether the total bending moment exceeds a preset threshold; If the total bending moment does not exceed the preset threshold, the compressor will perform passive vibration reduction. If the total bending moment exceeds the preset threshold, the target reverse bending moment is calculated, and the driving voltage of each piezoelectric ceramic sheet is calculated based on the target reverse bending moment. Each piezoelectric ceramic sheet outputs deformation force according to its corresponding driving voltage to counteract vibration.

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