A composite damper device for a compressor

Abstract

This invention relates to the field of refrigeration equipment compressor technology, specifically disclosing a composite vibration damping device for compressors. The device includes an outer constraint unit and an inner energy-absorbing unit, with the inner energy-absorbing unit placed within the outer constraint unit and not connected to it. The inner energy-absorbing unit includes a first support plate, a second support plate, and a torsion assembly. The first and second support plates are arranged vertically, and the torsion assembly is positioned between and connected to both the first and second support plates. This composite vibration damping device for compressors solves the problem that current compressor vibration damping structures struggle to simultaneously meet the contradictory requirements of achieving low stiffness and high vibration isolation during compressor operation, and high stiffness and strong constraint when the compressor is subjected to external impacts.

Description

Technical Field

[0001] This invention relates to the field of refrigeration equipment compressor technology, and more specifically, to a composite vibration damping device for compressors. Background Technology

[0002] The compressor is the core power component of refrigeration equipment such as refrigerators. It will generate vibration during operation. This vibration will not only cause noise, but may also be transmitted to the refrigerator body and cause structural resonance. Therefore, it is necessary to install a low-rigidity and high-vibration-isolation vibration-damping and energy-absorbing structure between the compressor and the body. Secondly, during the packaging and transportation of refrigerators, the compressor needs to withstand complex working conditions such as bumps and tilts. In this environment of high rigidity and strong constraints, if the constraints are insufficient, it is easy to cause large shaking, resulting in failures such as internal pipe rupture and loose parts.

[0003] To address the above issues, current compressors utilize vibration-damping structures with zero or negative Poisson's ratio characteristics. For example, Chinese invention patent application number 202211585863.0 discloses "A Torsional Negative Poisson's Ratio Energy Absorption Device Based on Boundary Curve and Its Design Method," which achieves torsional functionality by setting an arc-shaped rod, rotating block, support column, and disk between the upper and lower rings. However, this method struggles to withstand large torsional impacts. When subjected to significant torsional impacts, the connection between the arc-shaped rod and the disk becomes unstable due to excessive torsion, leading to structural damage. Therefore, it is only suitable for compressors operating in low-stiffness and high-vibration-isolation environments. For example, Chinese invention patent application number 202210089234.2 discloses a vibration reduction structure with zero Poisson bit characteristics, including two opposing panels, a support plate, and reinforcing ribs disposed within the cell formed by the panels and support plate. The reinforcing ribs include a central ring and several connecting rods tangent to the outer diameter of the ring. However, when the compressor is subjected to a large torsional impact, because the support plate and connecting rods are connected, excessive torsion of the reinforcing ribs can cause the connection between the support plate and connecting rods to break, leading to structural damage and making it difficult to achieve a vibration reduction effect. Therefore, it can only be adapted to compressors operating under conditions of low stiffness and high vibration isolation. In summary, current compressor vibration reduction structures cannot simultaneously meet the contradictory requirements of achieving low stiffness and high vibration isolation during compressor operation and high stiffness and strong constraint during compressor transportation. Summary of the Invention

[0004] In order to overcome the shortcomings of the prior art, the present invention provides a composite vibration damping device for compressors, which aims to solve the problems in the prior art.

[0005] The technical solution adopted by the present invention to solve its technical problem is: a composite vibration damping device for a compressor, comprising an outer constraint unit and an inner energy absorption unit, wherein the inner energy absorption unit is placed inside the outer constraint unit and they are not connected to each other; The inner energy-absorbing unit includes a first support plate, a second support plate, and a torsion assembly. The first and second support plates are arranged vertically, and the torsion assembly is disposed between the first and second support plates and connected to the first and second support plates respectively.

[0006] It is worth noting that the torsion component includes multiple wedge surfaces, which are evenly distributed between the first support plate and the second support plate, so that the junction of the torsion component and the first support plate forms a first regular polygon, and the junction of the torsion component and the second support plate forms a second regular polygon. The intersection of the wedge-shaped surface and the first support plate forms a first intersection edge, and the first regular polygon is composed of the first intersection edge; the intersection of the wedge-shaped surface and the second support plate forms a second intersection edge, and the second regular polygon is composed of the second intersection edge.

[0007] Preferably, both the first and second support disks are circular disks, the first regular polygon is a regular polygon inscribed in the first support disk, and the second regular polygon is a regular polygon inscribed in the second support disk. The lengths of the first and second intersecting edges can be constrained by the diameters of the first and second support disks.

[0008] Optionally, the diameter of the first support disk is larger than the diameter of the second support disk. When the inner energy-absorbing unit is subjected to vertical pressure, the first and second support disks compress and move closer together. The spiral structure's wedge-shaped curved surface combination will then twist and deform along the spiral direction, achieving vibration damping and buffering in the compression direction, thereby responding to compression deformation.

[0009] Specifically, the ratio between the diameter of the first support plate, the diameter of the second support plate, the height difference between the first and second support plates, and the length of the side of the wedge surface is a fixed value.

[0010] It is worth noting that the outer constraint unit includes a first support ring and a second support ring arranged vertically. Multiple support ribs are formed between the first and second support rings. The first support ring, the second support ring, and the support ribs together form a cavity for housing the inner energy-absorbing unit. The cooperation of the first support ring, the second support ring, and the support ribs provides horizontal stiffness constraint.

[0011] Specifically, the outer constraint unit further includes a third support ring member, which is disposed between the first support ring member and the second support ring member. The inner diameter of the first support ring member and the inner diameter of the second support ring member are both larger than the inner diameter of the third support ring member, so as to divide the cavity into a first sub-cavity and a second sub-cavity arranged vertically. Both the first sub-cavity and the second sub-cavity are provided with inner layer energy-absorbing units, and the inner layer energy-absorbing units provided in the first sub-cavity and the second sub-cavity are chiral folding types.

[0012] Optionally, the second support disk of the inner energy-absorbing unit is positioned close to the third support ring, and the inner diameter of the third support ring is larger than the diameter of the second support disk. This allows the second support disks of the two inner energy-absorbing units to contact each other. This enables torsional buffering through the two inner energy-absorbing units, further improving the vibration reduction effect.

[0013] Preferably, the plurality of supporting ribs are evenly distributed between the first supporting ring and the third supporting ring, and the two ends of the supporting ribs are respectively connected to the first supporting ring and the third supporting ring. Multiple supporting ribs are evenly distributed between the second and third supporting ring members, and both ends of each supporting rib are connected to the second and third supporting ring members, respectively. This further dissipates residual vibration energy, thereby further improving the vibration reduction effect.

[0014] Specifically, the top surface of the first support plate of the inner energy absorption unit located in the first sub-cavity is provided with a connecting clip to connect with the mounting plate of the compressor.

[0015] The beneficial effects of this invention are as follows: In the composite vibration damping device for the compressor, the synergistic effect of the outer constraint unit and the inner energy-absorbing unit simultaneously meets the different needs of the refrigerator compressor operation and transportation. When the refrigerator is operating normally, the high-frequency vibration generated by the compressor is transmitted to the composite vibration damping device. The inner energy-absorbing unit first undergoes elastic deformation, quickly absorbing the high-frequency vibration energy, thereby reducing the transmission efficiency of vibration to the refrigerator body and achieving vibration reduction and noise reduction. During refrigerator packaging and transportation, when the compressor is subjected to impacts such as bumps and torsion, the outer constraint unit quickly provides high-rigidity constraint, effectively reducing the lateral displacement and overturning amplitude of the compressor. The inner energy-absorbing unit utilizes a torsion assembly located between the first and second support plates. When the first and second support plates are compressed, the torsion assembly undergoes torsional deformation. Since the outer constraint unit and the inner energy-absorbing unit are not interconnected, the inner energy-absorbing unit is not constrained by the outer constraint unit when undergoing torsional deformation, thus absorbing impact energy through large-amplitude deformation and preventing damage to the compressor's internal pipes and components due to rigid collisions. In this way, the contradictory requirements of achieving low stiffness and high vibration isolation during compressor operation and high stiffness and strong constraint during compressor transportation can be met simultaneously. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the composite vibration damping device.

[0017] Figure 2 This is an exploded view of a composite vibration damping device.

[0018] Figure 3 This is a cross-sectional view of the composite vibration damping device.

[0019] Figure 4 This is one of the structural schematic diagrams of the inner layer energy-absorbing unit.

[0020] Figure 5 This is the second schematic diagram of the inner energy-absorbing unit.

[0021] Figure 6 This is the third schematic diagram of the inner energy-absorbing unit.

[0022] Figure 7 for Figure 6 A cross-sectional view of the inner energy-absorbing unit taken along the AA section line.

[0023] Figure 8 for Figure 6 A cross-sectional view of the inner energy-absorbing unit taken along the BB section line.

[0024] Figure 9 This is a schematic diagram of two chiral refractory inner energy-absorbing units.

[0025] Figure 10This is a schematic diagram of the compressor structure after the composite vibration damping device is installed.

[0026] Figure 11 Comparison of vibration reduction VLDs with a fixed vibration frequency of 20Hz for the vibration source.

[0027] Figure 12 Comparison of vibration reduction VLDs with a fixed vibration frequency of 50Hz for the vibration source.

[0028] Figure 13 Comparison of vibration reduction VLDs with a fixed vibration frequency of 70Hz for the vibration source.

[0029] Figure 14 A comparison of axial compressive force-displacement curves for the three structures.

[0030] Figure 15 This is a schematic diagram of the structure in Comparative Example 1.

[0031] Figure 16 This is a schematic diagram of the structure in Comparative Example 2.

[0032] In the diagram: 1 Compressor; 11 Mounting plate; 2 Outer constraint unit; 21 First support ring; 22 Second support ring; 23 Support rib; 24 Cavity; 241 First sub-cavity; 242 Second sub-cavity; 25 Third support ring; 3 Inner energy absorption unit; 31 First support disk; 32 Second support disk; 34 Torsion assembly; 341 Wedge surface; 4 Connecting clip; D1 Diameter of the first support disk; D2 Diameter of the second support disk; x1 First torsion angle; x2 Second torsion angle; x3 Bevel angle; z1 First junction edge; z2 Second junction edge; z3 Side edge of the wedge surface; h Height difference between the first and second support disks; 1A Upper energy absorption ring; 2A Energy absorption disk; 3A Lower energy absorption ring; 4A Energy absorption rotating block; 5A Energy absorption arc rod; 6A Energy absorption support column; 2B Vibration damping panel; 3B Vibration damping support plate; 5B Vibration damping ring; 6B Vibration damping connecting rod. Detailed Implementation

[0033] The specific embodiments of the present invention will be further described below with reference to the accompanying drawings. It should be noted that these descriptions are for the purpose of aiding understanding the present invention, but do not constitute a limitation thereof. Furthermore, the technical features involved in the various embodiments of the present invention described below can be combined with each other as long as they do not conflict with each other.

[0034] Combination Figures 1 to 16The composite vibration damping device for a compressor shown includes an outer constraint unit 2 and an inner energy absorption unit 3. The inner energy absorption unit 3 is placed inside the outer constraint unit 2 and is not connected to it. In this embodiment, the material of the outer constraint unit 2 is photosensitive resin, and the material of the inner energy absorption unit is thermoplastic polyurethane (TPU).

[0035] The inner energy-absorbing unit 3 includes a first support disk 31, a second support disk 32, and a torsion assembly 34. The first support disk 31 and the second support disk 32 are arranged vertically, and the torsion assembly 34 is disposed between the first support disk 31 and the second support disk 32 and is connected to the first support disk 31 and the second support disk 32 respectively.

[0036] In the composite vibration damping device for the compressor, the outer constraint unit 2 and the inner energy absorption unit 3 work together to simultaneously meet the different needs of the refrigerator compressor 1 during operation and transportation. When the refrigerator is working normally, the high-frequency vibration generated by the compressor 1 is transmitted to the composite vibration damping device. The inner energy absorption unit 3 first undergoes elastic deformation, quickly absorbing the high-frequency vibration energy, thereby reducing the transmission efficiency of vibration to the refrigerator body and achieving vibration reduction and noise reduction effects. During refrigerator packaging and transportation, when the compressor 1 is subjected to impacts such as bumps and torsion, the outer constraint unit 2 quickly provides high-rigidity constraint, effectively reducing the lateral displacement and overturning of the compressor 1. The inner energy-absorbing unit 3 utilizes the torsion component 34 located between the first support plate 31 and the second support plate 32. When the first support plate 31 and the second support plate 32 are compressed, the torsion component 34 undergoes torsional deformation. Since the outer constraint unit 2 and the inner energy-absorbing unit 3 are not interconnected, the inner energy-absorbing unit 3 is not constrained by the outer constraint unit 2 when it undergoes torsional deformation. Thus, it absorbs impact energy through large-scale deformation, preventing damage to the internal pipes and components of the compressor 1 due to rigid collisions. In this way, the contradictory requirements of achieving low rigidity and high vibration isolation during compressor 1 operation and high rigidity and strong constraint during compressor 1 transportation can be simultaneously met.

[0037] It is worth noting that, such as Figures 1-5 As shown, the torsion component 34 includes a plurality of wedge surfaces 341, which are evenly distributed between the first support disk 31 and the second support disk 32, so that the junction of the torsion component 34 and the first support disk 31 forms a first regular polygon, and the junction of the torsion component 34 and the second support disk 32 forms a second regular polygon. The intersection of the wedge surface 341 and the first support disk 31 forms a first intersection edge z1, and the first regular polygon is composed of the first intersection edge z1; the intersection of the wedge surface 341 and the second support disk 32 forms a second intersection edge z2, and the second regular polygon is composed of the second intersection edge z2.

[0038] Preferably, both the first support disk 31 and the second support disk 32 are circular disks, the first regular polygon is a regular polygon inscribed in the first support disk 31, and the second regular polygon is a regular polygon inscribed in the second support disk 32.

[0039] In this way, the lengths of the first intersection edge z1 and the second intersection edge z2 can be constrained by the diameter D1 of the first support plate 31 and the diameter D2 of the second support plate 32.

[0040] Optional, such as Figure 4 and Figure 5 As shown, the diameter D1 of the first support disk 31 is larger than the diameter D2 of the second support disk 32.

[0041] In this embodiment, the center of the first regular polygon and the center of the second regular polygon are located on the same vertical axis, and each vertex of the first regular polygon and the second regular polygon is not located on the same vertical line, so that each vertex of the first regular polygon and the second regular polygon is staggered from each other; combined with the different diameters of the first support disk 31 and the second support disk 32, and the inscribed case, the areas of the first regular polygon and the second regular polygon are not equal; in this way, in the vertical direction, a wedge surface 341 can be formed by two adjacent vertices of the first regular polygon and two adjacent vertices of the second regular polygon, and all the wedge surfaces 341 can be combined to form a spiral structure that rotates in a clockwise or counterclockwise direction.

[0042] When the inner energy-absorbing unit 3 is subjected to vertical pressure, the first support disk 31 and the second support disk 32 are compressed and brought together. The combination of the spiral structure's wedge-shaped curved surface 341 will twist and deform along the spiral direction, achieving vibration reduction and buffering in the compression direction, thereby responding to compression deformation.

[0043] Specifically, such as Figures 4-9 As shown, the ratio between the diameter D1 of the first support plate 31, the diameter D2 of the second support plate 32, the height difference h between the first support plate 31 and the second support plate 32, and the length of the side z3 of the wedge surface 341 is a fixed value.

[0044] In this embodiment, the ratio ranges from (25~26):(16~17):(13~14):(13~14), preferably 25.2:16.1:14:13.76. Specifically, the angle between the side z3 of the wedge surface 341 and the second intersection edge z2 is set as the first twist angle x1, the angle between the side z3 of the wedge surface 341 and the first intersection edge z1 is set as the second twist angle x2, and the angle between the side z3 of the wedge surface 341 and the upper or lower surface of the second disk is set as the chamfer angle x3. Through the above preferred ratio, the first twist angle x1 can be constrained to 29.06°, the second twist angle x2 to 159.11°, and the chamfer angle x3 to 41.39°. The above angles are obtained by drawing in a 3D software such as SolidWorks using the preferred ratio and then annotating the angles using the built-in function of the 3D software.

[0045] When other parameters remain unchanged, if the diameter D1 of the first support plate 31 is too small, the torsional arm will be severely insufficient. Under the same axial compression, the torsional angle will be directly compressed by the geometric dimensions, and the rotation will be almost invisible to the naked eye. In addition, due to insufficient space, the connection surface between the first support plate 31 and the wedge surface 341 is too narrow, resulting in extremely low structural stiffness. Radial buckling will occur under pressure, making it unable to bear the static load of the compressor 1. If the diameter D1 of the first support plate 31 is too large, the radial span of the wedge surface 341 will be too large. Under axial compression, radial bulging and buckling will occur in the middle of the wedge surface 341, and all the axial force will be wasted on radial deformation, resulting in a significant decrease in torsional efficiency. Furthermore, the rotational inertia of the spiral structure composed of the wedge surface 341 is too large, resulting in a delayed response under high-frequency micro-vibration and an inability to effectively suppress the micro-vibration of the compressor 1. Moreover, due to the excessive diameter, material waste and increased weight will occur, leading to higher costs.

[0046] When other parameters remain unchanged, if the diameter D2 of the second support plate 32 is too large, it will result in a severe lack of torsional arm. Under the same axial compression, the torsional angle will be directly compressed by the geometric dimensions, and the rotation will be almost invisible to the naked eye. In addition, due to insufficient space, the connection surface between the first support plate 31 and the wedge surface 341 is too narrow, resulting in extremely low structural stiffness. Radial buckling will occur under pressure, making it unable to bear the static load of the compressor 1. Furthermore, the excessive diameter will cause material waste and increased weight, leading to higher costs. If the diameter D2 of the second support plate 32 is too small, the radial span of the wedge surface 341 will be too large. Under axial compression, radial bulging and buckling will occur in the middle of the wedge surface 341, and all the axial force will be wasted on radial deformation, resulting in a significant decrease in torsional efficiency. In addition, the helical structure formed by the wedge surface 341 has an excessive moment of inertia, resulting in a delayed response under high-frequency micro-vibration and an inability to effectively suppress the micro-vibration of the compressor 1.

[0047] When other parameters remain unchanged, if the height difference h between the first support plate 31 and the second support plate 32 is too small, the axial compression stroke will be extremely short. Even if the chamfer angle x3 is reasonable, the first torsion angle x1 and the second torsion angle x2 corresponding to the extremely short compression, such as 1 mm, will approach 0, and no torsion will be visible. In addition, this situation will result in extremely high wedge bending stiffness, requiring a load of hundreds of Newtons to trigger deformation. The micro-vibrations of the compressor 1 during daily operation will not be able to make the structure respond, and the vibration reduction function will be useless. If the height difference h between the first support plate 31 and the second support plate 32 is too large, the slenderness ratio of the inner energy absorption unit 3 will be too large. During axial compression, the entire lateral buckling (tilting) will occur instead of circumferential torsion, thus directly failing. In addition, if the axial stiffness is too low, the static sinking of the compressor 1 will be too large, which will pull on the refrigeration pipes and bring safety hazards.

[0048] When other parameters remain unchanged, if the length of the side z3 of the wedge surface 341 is too small, the wedge surface 341 is almost a straight inclined plane. When axially compressed, only axial compression and radial bulging will occur, with no circumferential torsional component. If the length of the side z3 of the wedge surface 341 is too large, the torsion angle will be too large, and after unloading, there will be problems such as inability to self-reset and reverse jamming.

[0049] It is worth noting that, such as Figure 2 and Figure 3 As shown, the outer constraint unit 2 includes a first support ring 21 and a second support ring 22 arranged vertically. A plurality of support ribs 23 are formed between the first support ring 21 and the second support ring 22. The first support ring 21, the second support ring 22 and the support ribs 23 together form a cavity 24 for placing the inner energy absorption unit 3.

[0050] The cooperation of the first supporting ring 21, the second supporting ring 22 and the supporting rib 23 can provide horizontal stiffness constraint, so that the entire composite vibration damping device will not deform when subjected to horizontal pressure, and also serves to protect the inner energy absorption unit 3 located in the cavity 24 from horizontal pressure.

[0051] Specifically, the outer constraint unit 2 further includes a third support ring 25, which is disposed between the first support ring 21 and the second support ring 22. The inner diameter of the first support ring 21 and the inner diameter of the second support ring 22 are both larger than the inner diameter of the third support ring 25, so as to divide the cavity 24 into a first sub-cavity 241 and a second sub-cavity 242 arranged vertically. The first sub-cavity 241 and the second sub-cavity 242 are each provided with an inner layer energy absorption unit 3, and the inner layer energy absorption units 3 provided in the first sub-cavity 241 and the second sub-cavity 242 are chiral folding types.

[0052] Preferably, the second support disk 32 of the inner energy-absorbing unit 3 is disposed close to the third support ring 25, and the inner diameter of the third support ring 25 is larger than the diameter D2 of the second support disk 32.

[0053] In this embodiment, the purpose of having an inner diameter greater than the diameter D2 of the second support disk 32 is to ensure that the second support disks 32 of the two inner energy-absorbing units 3 can contact each other after the two inner energy-absorbing units 3 are placed in the first sub-cavity 241 and the second sub-cavity 242 respectively.

[0054] During installation, two chiral folding inner energy-absorbing units 3 are placed in the first sub-cavity 241 and the second sub-cavity 242 respectively, and the second support plates 32 of the two inner energy-absorbing units 3 are located within the annular structure of the third support ring 25, so that the second support plates 32 of the two inner energy-absorbing units 3 are in contact. After the composite vibration damping device is placed vertically and installed on the compressor 1, the first sub-cavity 241 and the second sub-cavity 242 limit the two inner energy-absorbing units 3, so that they will not shift during the operation of the compressor 1 or during transportation. After the two second support plates 32 are in contact, when vertical pressure is applied, the two inner energy-absorbing units 3 will be subjected to vertical pressure, so that torsional buffering can be performed through the two inner energy-absorbing units 3, thereby further improving the vibration damping effect.

[0055] Optionally, a plurality of the support ribs 23 are evenly distributed between the first support ring 21 and the third support ring 25, and the two ends of the support ribs 23 are respectively connected to the first support ring 21 and the third support ring 25. Multiple support ribs 23 are evenly distributed between the second support ring 22 and the third support ring 25, and the two ends of the support ribs 23 are respectively connected to the second support ring 22 and the third support ring 25.

[0056] In this embodiment, through the cooperation of the first supporting ring 21, the second supporting ring 22, the third supporting ring 25 and the supporting rib 23, the supporting rib 23 located on the same vertical plane can form a concave structure. When subjected to vertical compression, after the inner energy-absorbing unit 3 absorbs most of the vibration energy through torsional deformation, the concave structure can further dissipate the remaining vibration energy through slight deformation, thereby further improving the vibration reduction effect.

[0057] It is worth noting that, such as Figure 10 As shown, the top surface of the first support plate 31 of the inner energy absorption unit 3 located in the first sub-cavity 241 is provided with a connecting clip 4 so as to connect with the mounting plate 11 of the compressor 1.

[0058] In this embodiment, the mounting plate 11 has an opening, and the connecting clip 4 is installed in the opening of the mounting plate 11. After the first support plate 31 of the inner energy-absorbing unit 3 located in the first sub-cavity 241 is connected to the mounting plate 11 through the connecting clip 4, the compressor 1 sits on the horizontal plane through the composite vibration damping device. The compressor 1 will press down on the composite vibration damping device, thus ensuring the positional constraint of the outer constraint unit 2. Then, the positional constraint of the outer constraint unit 2 ensures the positional constraint of the inner energy-absorbing unit 3 located in the second sub-cavity 242. In this way, as long as the compressor 1 sits on the horizontal plane through the composite vibration damping device, the positional relationship between the compressor 1, the inner energy-absorbing unit 3 and the outer constraint unit 2 will be constrained, and the components will not detach.

[0059] Next, vibration reduction VLD tests were conducted on the composite vibration reduction device used in this scheme, Comparative Example 1 in the prior art, and Comparative Example 2 in the prior art at different test frequencies. The test method was based on the national standard "Test Methods for Static and Dynamic Performance of Vibration and Shock Isolators" (GB / T15168—2013). Among them, such as... Figure 15 As shown, the structure of Comparative Example 1 achieves its torsional function by setting an energy-absorbing arc-shaped rod 5A, an energy-absorbing rotating block 4A, an energy-absorbing support column 6A, and an energy-absorbing disk 2A between the energy-absorbing upper ring 1A and the energy-absorbing lower ring 3A; Figure 16 As shown, the structure of Comparative Example 2 includes two opposing damping panels 2B, a damping support plate 3B, and damping reinforcing ribs disposed within the cell formed by the damping panels and the damping support plate. The damping reinforcing ribs include a central damping ring 5B and several damping connecting rods 6B tangent to the outer diameter of the damping ring 5B.

[0060] Specifically, the load (the protected object, in this application, a compressor) is fixed to the three structures mentioned above, and the three structures are fixed to an electromagnetic vibrator (vibration source). Accelerometers are installed on the vibration source and the protected object, and vibration reduction VLD tests are conducted at the corresponding test frequencies. Vibration Level Difference (VLD) is a term commonly used in vibration engineering, transportation engineering, and other fields to describe the difference in vibration levels between two different locations or states. In vibration isolation system design, the vibration reduction effect of the isolation device can be quantified by calculating the vibration level difference between the vibration source and the protected object before and after isolation. VLD is usually calculated in decibels (dB), and the formula is: ; Indicates the vibration acceleration level of the compressor body; This indicates the vibration acceleration level transmitted to the refrigerator body or bottom plate; This represents the effective value of the compressor body vibration acceleration; This represents the effective value of the vibration acceleration transmitted to the refrigerator body or bottom plate; Indicates the vibration power of the compressor body; This indicates the vibration power transmitted to the refrigerator body or base.

[0061] In a compressor vibration isolation system, the vibration level drop is... , The larger the value, the better the vibration isolation performance and the smaller the vibration transmitted to the housing.

[0062] Refrigerator compressors are mostly reciprocating piston compressors. Vibration primarily originates from the motor's operating frequency, crankshaft rotation, and the reciprocating impact of the piston. The main vibration range is 20-100Hz, with the strongest vibration source being 48-50Hz. (Combined with...) Figures 11-13 The performance of embodiments of this solution in low-stiffness and high-vibration-isolation application scenarios is described. Figures 11-13 In the figure, the vertical axis points downwards as positive. The larger the VLD value (the lower the curve), the better the vibration isolation performance. If the curve is above the 0 mark, then VLD is negative, indicating that the structure not only fails to reduce vibration but also amplifies it. Figure 11 (Vibration source fixed at a vibration frequency of 20Hz). Figure 12 (The vibration source has a fixed vibration frequency of 50Hz) and Figure 13 (With the vibration source fixed at a frequency of 70Hz), the curve of this solution is significantly lower than that of the two comparative examples, demonstrating a clear advantage in low-frequency vibration reduction. Therefore, this embodiment exhibits better vibration reduction performance than Comparative Examples 1 and 2 at several key frequencies (20Hz, 50Hz, and 70Hz). Especially at higher frequency vibrations, Comparative Examples 1 and 2 even amplify the vibration, while this embodiment still shows good vibration reduction. This is because the inner energy-absorbing unit 3 of this embodiment continuously consumes the vertically transmitted vibration energy through compression and torsion during the compression and vibration process, thereby significantly reducing the vibration on the protected side.

[0063] Combination Figure 14 The performance of the embodiments of this solution in high-stiffness and strong-constraint application scenarios is described. The inner energy-absorbing unit 3 of this solution, Comparative Example 1, and Comparative Example 2 were 3D printed using thermoplastic polyurethane (TPU). Compression-unloading experiments were conducted on the three structures using a universal testing machine, with a compression distance of 60% of the overall height of the vibration-damping model. Figure 14In the axial compressive force-displacement curve, the higher the load value (axial compressive force) under the same compressive displacement, the stronger the structure's load-bearing capacity and impact resistance. The load (axial compressive force) that the inner energy-absorbing unit 3 of this scheme can withstand under the same compressive displacement is significantly higher than that of Comparative Example 1 and Comparative Example 2, and the curve plateau segment is smoother, indicating that it not only has higher load-bearing stiffness but also maintains stable energy absorption capacity during large deformation. Therefore, the force that the inner energy-absorbing unit 3 of this scheme can withstand is significantly higher than that of Comparative Example 1 and Comparative Example 2.

[0064] Table 1 shows the statistical analysis of platform stress, sample energy absorption, and specific energy absorption for the three structures as quantitative evaluation indicators. Compared with Comparative Example 1, the platform stress of the inner energy-absorbing unit 3 in this scheme is increased by approximately 652%, and the energy absorption and specific energy absorption are increased by 73% and 582%, respectively. Compared with Comparative Example 2, the platform stress of the inner energy-absorbing unit 3 in this scheme is increased by approximately 3613%, and the energy absorption and specific energy absorption are increased by 3070% and 2319%, respectively. In summary, the inner energy-absorbing unit 3 in this scheme can improve the energy absorption performance of traditional damping and energy-absorbing structures, and significantly improve the impact resistance and buffering energy absorption effect of the structure.

[0065] Table 1 compares the mechanical properties of different vibration damping and energy absorption structures: In Table 1, the platform stress = applied load force / cross-sectional area of ​​the sample, where the applied load force is... Figure 14 The first peak value of the force in the curve corresponding to each sample is given. The samples include the structures of the embodiments of the present invention, the structure of Comparative Example 1, and the structure of Comparative Example 2. The energy absorbed by the sample is the area of ​​the corresponding curve in the comparison graph of axial compressive force-displacement curves. The specific energy absorbed is equal to the energy absorbed by the sample and the mass of the sample.

[0066] The embodiments of the present invention have been described in detail above with reference to the accompanying drawings, but the present invention is not limited to the described embodiments. For those skilled in the art, various changes, modifications, substitutions, and variations can be made to these embodiments without departing from the principles and spirit of the present invention, and these variations still fall within the protection scope of the present invention.

Claims

1. A composite vibration damping device for a compressor, characterized in that, It includes an outer constraint unit and an inner energy absorption unit, wherein the inner energy absorption unit is placed inside the outer constraint unit and they are not connected to each other; The inner energy-absorbing unit includes a first support plate, a second support plate, and a torsion assembly. The first support plate and the second support plate are arranged vertically, and the torsion assembly is disposed between the first support plate and the second support plate and is connected to the first support plate and the second support plate respectively. The torsion assembly includes multiple wedge surfaces, which are evenly distributed between the first support plate and the second support plate, so that the junction of the torsion assembly and the first support plate forms a first regular polygon, and the junction of the torsion assembly and the second support plate forms a second regular polygon. The intersection of the wedge-shaped surface and the first support plate forms a first intersection edge, and the first regular polygon is composed of the first intersection edge; the intersection of the wedge-shaped surface and the second support plate forms a second intersection edge, and the second regular polygon is composed of the second intersection edge.

2. The composite vibration damping device for a compressor according to claim 1, characterized in that: Both the first support disk and the second support disk are circular disks. The first regular polygon is a regular polygon inscribed in the first support disk, and the second regular polygon is a regular polygon inscribed in the second support disk.

3. A composite vibration damping device for a compressor according to claim 2, characterized in that: The diameter of the first support plate is larger than the diameter of the second support plate.

4. A composite vibration damping device for a compressor according to claim 3, characterized in that: The ratio between the diameter of the first support plate, the diameter of the second support plate, the height difference between the first and second support plates, and the length of the side of the wedge surface is a fixed value.

5. A composite vibration damping device for a compressor according to claim 1, characterized in that: The outer constraint unit includes a first support ring and a second support ring arranged vertically. Multiple support ribs are formed between the first support ring and the second support ring. The first support ring, the second support ring, and the support ribs together form a cavity for placing the inner energy absorption unit.

6. A composite vibration damping device for a compressor according to claim 5, characterized in that: The outer constraint unit further includes a third support ring, which is disposed between the first support ring and the second support ring. The inner diameter of the first support ring and the inner diameter of the second support ring are both larger than the inner diameter of the third support ring, so as to divide the cavity into a first sub-cavity and a second sub-cavity arranged vertically. Both the first sub-cavity and the second sub-cavity are provided with inner layer energy-absorbing units, and the inner layer energy-absorbing units provided in the first sub-cavity and the second sub-cavity are chiral folding types.

7. A composite vibration damping device for a compressor according to claim 6, characterized in that: The second support disk of the inner energy-absorbing unit is located close to the third support ring, and the inner diameter of the third support ring is larger than the diameter of the second support disk.

8. A composite vibration damping device for a compressor according to claim 6, characterized in that: The plurality of support ribs are evenly distributed between the first support ring and the third support ring, and the two ends of the support ribs are respectively connected to the first support ring and the third support ring. The multiple supporting ribs are evenly distributed between the second supporting ring and the third supporting ring, and the two ends of the supporting ribs are respectively connected to the second supporting ring and the third supporting ring.

9. A composite vibration damping device for a compressor according to claim 6, characterized in that: The top surface of the first support plate of the inner energy absorption unit located in the first sub-cavity is provided with a connecting clip to connect with the mounting plate of the compressor.

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