Design method of vibration isolation spring for compressor and vibration isolation system for compressor

Abstract

The present invention discloses a design method for a vibration isolation spring for a compressor and a vibration isolation system for a compressor. The design method for a vibration isolation spring for a compressor comprises the following steps: determining F1 based on F2 / F1 being greater than or equal to a preset target value, where F1 is the natural frequency of the vibration isolation system of the compressor vibration isolation spring, and F2 is the operating frequency of the compressor; determining δ0 based on F1 and δ0 being less than or equal to δ, where δ is determined based on T fk and F2, δ0 is the static compression of the compressor-isolation spring isolation system, δ is the target static compression threshold, T fk The target vibration isolation efficiency is determined, and the wire diameter d, the intermediate diameter D, and the number of turns n of the vibration isolation spring are determined. The design method of the vibration isolation spring for the compressor is universal.

Description

Technical Field

[0001] The present invention relates to the technical field of compressor vibration isolation, and in particular to a design method for a vibration isolation spring for a compressor and a vibration isolation system for a compressor. Background Art

[0002] Appliances such as refrigerators and air conditioners have a housing and a compressor mounted on it. When the compressor is operating, it generates vibrations. The compressor has a footplate, and the housing has a baseplate. A vibration isolation element is placed between the compressor footplate and the baseplate, creating a compressor-isolation element vibration isolation system. This vibration isolation system effectively prevents vibrations generated by the compressor from being transmitted to the baseplate, resulting in an appliance with relatively low vibration noise.

[0003] In traditional technology, the vibration isolation element is a rubber foot (without springs). Rubber foot pads (without springs) can generally meet the vibration isolation requirements of household appliances such as refrigerators and air conditioners. However, the vibration isolation efficiency of the compressor-rubber foot system is generally below 70%. When the compressor-rubber foot system is applied to appliances such as car air conditioners, which may vibrate strongly depending on the environment, it cannot effectively reduce vibration noise. In contrast, the vibration isolation efficiency of the compressor-vibration isolation spring system can exceed 70%, reaching 90% or even 95%. However, when traditional technology designs vibration isolation springs for compressors to construct the compressor-vibration isolation spring system, the design method of the vibration isolation spring lacks versatility. Often, a specific design method can only be used for compressors of a certain displacement, weight, and support structure, and cannot be used for compressors of different displacements, weights, and support structures. Summary of the Invention

[0004] The main purpose of the invention is to provide a universal design method for a vibration isolation spring for a compressor.

[0005] To achieve the above-mentioned object, the present invention proposes a design method for a vibration isolation spring for a compressor, comprising the following steps:

[0006] Determine F1 based on the ratio F2 / F1 being greater than or equal to the preset target value, where F1 is the natural frequency of the compressor-vibration isolation spring isolation system, and F2 is the operating frequency of the compressor;

[0007] Determine δ0 based on F1 and δ0 is less than or equal to δ, δ is determined based on T fk Determined by F2, δ0 is the static compression of the compressor-isolation spring isolation system, δ is the target static compression threshold, T fk is the target vibration isolation efficiency; and

[0008] Determine the wire diameter d, median diameter D and number of turns n of the vibration isolation spring.

[0009] In one embodiment, the compressor is a variable frequency compressor, F2 is the minimum value of the compressor operating frequency, and the preset target value is 2.5.

[0010] In one embodiment, when T fk When it is greater than or equal to 90%, δ is calculated as follows:

[0011] δ=26.76-0.534*F2.

[0012] In one embodiment, F1 is calculated as follows:

[0013] F1=(1 / 2π)*(K / M) 1 / 2

[0014] Where K is the spring constant of the isolation spring, and M is the mass of the compressor;

[0015] In the step of determining F1 according to F2 / F1 being greater than or equal to the preset target value, when F2 / F1 is less than the preset target value, K is adjusted until F2 / F1 is greater than or equal to the preset target value.

[0016] In one embodiment, the initial K is determined according to the static stiffness of the rubber foot pads adapted to the compressor.

[0017] In one embodiment, δ0 is calculated as follows:

[0018] δ0=25 / (F1) 2

[0019] In the step of determining δ0 based on F1 and δ0 being less than or equal to δ, when δ0 is greater than δ, K is adjusted until F2 / F1 is greater than or equal to a preset target value and δ0 is less than or equal to δ.

[0020] In one embodiment, the wire diameter d is [1.6 mm, 5.0 mm];

[0021] The median diameter D is calculated as follows:

[0022] D=C*d, where C is the winding ratio of the isolation spring, and C is [8, 20]

[0023] The number of turns n is calculated as follows:

[0024] n=(9800*d) / (K*C 3 ).

[0025] In one embodiment, the wire diameter d is calculated as follows:

[0026] d=(0.0956*M*C / i) 1 / 2

[0027] Where i is the number of mounting holes on the compressor footplate.

[0028] The present invention also provides a vibration isolation system for a compressor, which is used to connect the compressor foot plate and the bottom plate of an electrical appliance, comprising:

[0029] A positioning member, comprising a main body and a first screw portion, wherein one end of the main body is connected to the bottom plate, and the other end is connected to the first screw portion;

[0030] A first auxiliary vibration damping structure has a slot adapted to fit the mounting hole on the compressor footplate, wherein the slot defines a limit plate located at an end of the first auxiliary vibration damping structure;

[0031] a second auxiliary vibration-damping structure, disposed on the main body and in contact with the bottom plate;

[0032] a vibration isolation spring, both ends of which are respectively passed through the first auxiliary vibration damping structure and the second auxiliary vibration damping structure; and

[0033] a first limiting member, threadedly connected to the first screw portion and abutting against an end surface of the first auxiliary vibration-damping structure away from the bottom plate;

[0034] Among them, F2 / F1 is greater than or equal to 2.5, δ0 is less than or equal to δ, and δ is calculated based on T fk and F2, F1 is the natural frequency of the vibration isolation system, F2 is the minimum value of the compressor operating frequency, δ0 is the static compression of the vibration isolation system, δ is the target static compression threshold, T fk is the target vibration isolation efficiency.

[0035] In one embodiment, the first limiting member can contact the end surface of the main body away from the bottom plate;

[0036] The distance between the end surface of the main body away from the bottom plate and the bottom plate is L;

[0037] L is [H1-δ0+a+b-2.0mm, H1-δ0+a+b+6.0mm],

[0038] H1 is the height of the vibration isolation spring, a is the thickness of the limit plate, and b is the thickness of the compressor foot plate.

[0039] In one embodiment, the positioning member further includes a second screw portion, the second screw portion is provided at an end of the main body away from the first screw portion, and the second screw portion is passed through the bottom plate;

[0040] The vibration isolation system for the compressor further includes a second stopper, the second stopper being threadedly connected to the second screw portion so that the second screw portion is fixed to the bottom plate;

[0041] L is the length of the main body.

[0042] In one embodiment, the first limiting member is a nut with a washer, and the second limiting member is a nut with a washer or a lock rivet with an internal thread.

[0043] In one embodiment, the main body includes a rod body and an end cap, the rod body is passed through the base plate, the end cap is located on a side of the base plate away from the compressor foot plate, and the end cap is fixedly connected to the base plate.

[0044] In one embodiment, the outer diameter R1 of the main body is [6.0 mm, 12.0 mm];

[0045] The inner diameter R2 of the first auxiliary vibration damping structure is [R1+2mm, R1+12mm];

[0046] The inner diameter R3 of the second auxiliary vibration damping structure is [R1-1mm, R1+2mm].

[0047] In one embodiment, the inner diameter of the mounting hole on the compressor foot plate is R4;

[0048] The outer diameter R5 of the first auxiliary vibration-damping structure at the slot is [R4-1mm, R4+2mm].

[0049] In the above-mentioned design method of the vibration isolation spring for the compressor, the natural frequency F1 of the vibration isolation system is taken as a variable, that is, the stiffness coefficient K of the vibration isolation spring is taken as a variable, and the boundary conditions of "the natural frequency F1 of the vibration isolation system of the compressor operating frequency F2 / compressor-vibration isolation spring is greater than or equal to the preset target value and the static compression amount δ0 of the vibration isolation system is less than or equal to the target static compression amount threshold δ" are taken as the boundary conditions to design the "stiffness coefficient K and target vibration isolation efficiency T fk Matching vibration isolation spring". And in designing "stiffness coefficient K and target vibration isolation efficiency T fk The process of "matching vibration isolation springs" mainly involves the compressor operating frequency F2, the compressor mass M and the target vibration isolation efficiency T fk Therefore, the design method of the vibration isolation spring for the above compressor is universal and can be used for compressors of different displacements, different weights, and different support structures. BRIEF DESCRIPTION OF THE DRAWINGS

[0050] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the structures shown in these drawings without paying any creative work.

[0051] Figure 1This is a flow chart of a method for designing a vibration isolation spring for a compressor according to one embodiment of the present invention;

[0052] Figure 2 This is a schematic structural diagram of a vibration isolation system for a compressor according to an embodiment of the present invention;

[0053] Figure 3 A schematic structural diagram of a vibration isolation system for a compressor according to another embodiment of the present invention;

[0054] Figure 4 A schematic structural diagram of a vibration isolation system for a compressor according to another embodiment of the present invention;

[0055] Figure 5 for Figure 1 The diagram shows the structure of the first auxiliary vibration reduction structure and the second auxiliary vibration reduction structure of the vibration isolation system for the compressor.

[0056] Description of Figure Numbers:

[0057]

[0058]

[0059] The purpose, features and advantages of the present invention will be further described with reference to the accompanying drawings and in conjunction with the embodiments. DETAILED DESCRIPTION

[0060] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. All other embodiments obtained by ordinary technicians in this field based on the embodiments of the present invention without making any creative efforts shall fall within the scope of protection of the present invention.

[0061] It should be noted that if the embodiments of the present invention involve directional indications (such as up, down, left, right, front, back, etc.), the directional indications are only used to explain the relative position relationship, movement status, etc. between the components under a certain specific posture. If the specific posture changes, the directional indications will also change accordingly.

[0062] In addition, if there are descriptions involving "first", "second", etc. in the embodiments of the present invention, the descriptions of "first", "second", etc. are only for descriptive purposes and cannot be understood as indicating or implying their relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of such features. In addition, if the meaning of "and / or" appearing in the full text is to include three parallel schemes, taking "A and / or B" as an example, it includes scheme A, or scheme B, or a scheme in which A and B are satisfied at the same time. In addition, the technical solutions between the various embodiments can be combined with each other, but it must be based on the ability of ordinary technicians in this field to implement. When the combination of technical solutions is mutually contradictory or cannot be implemented, it should be deemed that such a combination of technical solutions does not exist and is not within the scope of protection required by the present invention.

[0063] The present invention provides a design method for a vibration isolation spring for a compressor, comprising the following steps:

[0064] Step S110 , determining the natural frequency F1 according to whether the compressor operating frequency F2 / the natural frequency F1 of the vibration isolation system of the compressor-vibration isolation spring is greater than or equal to a preset target value.

[0065] The compressor operating frequency F2 can be obtained by consulting the compressor specification sheet (compressor function manual), while the preset target value can be determined empirically. Traditionally, the compressor uses rubber feet for vibration isolation, constructing a compressor-rubber foot vibration isolation system (without springs). The initial value is obtained based on the compressor operating frequency F4 within this isolation system and the natural frequency F3 of the compressor operating frequency F4 / compressor-rubber foot isolation system. Based on this initial value, the preset target value can be determined empirically.

[0066] In the present embodiment, the compressor is a variable frequency compressor. By looking up the compressor specification sheet (compressor function sheet), the range of the compressor operating frequency can be obtained, thereby obtaining the minimum and maximum values ​​of the compressor operating frequency F2. Specifically, in the present embodiment, the natural frequency F1 is determined based on the minimum value of the compressor operating frequency F2 and the natural frequency F1 of the minimum value of the compressor operating frequency F2 / the compressor-vibration isolation spring vibration isolation system being greater than or equal to 2.5. That is, in the present embodiment, the compressor operating frequency F2 is the minimum value of the compressor operating frequency F2, and the preset target value is 2.5. It is understood that in other embodiments, when the compressor operating frequency F2 is the maximum value of the compressor operating frequency F2, the preset target value changes accordingly. The compressor operating frequency F2 adopts the minimum and maximum values, which is more convenient for the design of the vibration isolation spring for the compressor. It is understood that the compressor operating frequency F2 is not limited to the minimum and maximum values ​​of the compressor operating frequency F2.

[0067] The natural frequency F1 of the compressor-vibration isolation spring system is primarily determined by the compressor's mass (including the refrigerant oil) M and the characteristics of the vibration isolation spring (e.g., the spring constant K of the vibration isolation spring). In this embodiment, the natural frequency F1 is calculated as follows:

[0068] F1=(1 / 2π)*(K / M) 1 / 2

[0069] Where K is the stiffness coefficient of the isolation spring, and M is the mass of the compressor.

[0070] It should be noted that in conventional technology, multiple rubber pads are typically placed between the compressor footplate and the appliance's baseplate. Accordingly, in the compressor-isolation spring vibration isolation system of the present application, multiple isolation springs are placed between the compressor footplate and the appliance's baseplate. Specifically, in this embodiment, there are three or four isolation springs.

[0071] It is understandable that in the process of designing a vibration isolation spring for a compressor, it is necessary to determine the initial spring coefficient K0 of the vibration isolation spring in advance. In traditional technology, the compressor uses rubber pads for vibration isolation to construct a vibration isolation system of compressor-rubber pads (excluding springs). In this embodiment, after the compressor is determined, the parameters (material, size, etc.) of the rubber pads that are compatible with the compressor can be found. According to the parameters of the rubber pads, the static stiffness of the rubber pads can be obtained, and the static stiffness is used as the initial spring coefficient K0 of the vibration isolation spring 500. It is understandable that in other embodiments, the initial spring coefficient K0 of the vibration isolation spring can also be determined based on experience.

[0072] The initial F1 can be obtained based on the initial spring constant K0 of the isolation spring.

[0073] When the minimum value of the compressor operating frequency F2 / the initial F1 is greater than or equal to 2.5, the initial F1 is the natural frequency F1 of the compressor-vibration isolation spring isolation system.

[0074] When the minimum value of the compressor operating frequency F2 / the initial F1 is less than 2.5, it is necessary to adjust the stiffness coefficient of the vibration isolation spring, for example, from K0 to K1, from K1 to K2, ... until the minimum value of the compressor operating frequency F2 / the natural frequency F1 of the compressor-vibration isolation spring vibration isolation system is greater than or equal to 2.5. At this time, the F1 determined by the stiffness coefficient is the natural frequency F1 of the compressor-vibration isolation spring vibration isolation system.

[0075] It can be understood that in the process of designing a vibration isolation spring for a compressor, the initial height h0 of the vibration isolation spring can be determined in advance. In some embodiments, the compressor installation height h1 can be obtained by looking up the compressor specification (compressor function book). The appliance height h2 can be obtained by looking up the appliance specification (electrical appliance function book). After obtaining h1 and h2, combined with the technical requirement of the structural design specification that the design installation gap between the compressor and the housing of the appliance is greater than 13mm, it can be seen that h0 = h2-h1-13mm. In traditional technology, the compressor uses rubber foot pads for vibration isolation to construct a compressor-rubber foot pad vibration isolation system (excluding springs). Therefore, in some embodiments, after the compressor is determined, the parameters (material, size, etc.) of the rubber foot pad that is compatible with the compressor can be found. According to the parameters of the rubber foot pad, combined with experience, the initial height h0 of the vibration isolation spring can be determined.

[0076] The spring constant of the vibration isolation spring is related to the material of the spring, the thickness of the spring wire (wire diameter d), the diameter of the spring coil (median diameter D), the number of turns per unit length, and the original length of the spring. Since the initial spring constant K0 and the initial height h0 can be determined in advance, K0 can be adjusted to K1, and K1 can be adjusted to K2, ... until the minimum value of the compressor operating frequency F2 / the natural frequency F1 of the compressor-vibration isolation spring vibration isolation system is greater than or equal to 2.5, the spring constant of the vibration isolation spring can usually be adjusted by adjusting the height of the vibration isolation spring. Therefore, when the natural frequency F1 of the compressor-vibration isolation spring vibration isolation system is determined, the height of the vibration isolation spring is also determined. It should be noted that the adjustment of the height of the vibration isolation spring is limited by the height of the preset installation space and cannot be infinitely small or infinitely large.

[0077] Step S120: determining the static compression δ0 based on the natural frequency F1 of the vibration isolation system and the static compression δ0 of the vibration isolation system being less than or equal to the target static compression threshold δ. The target static compression threshold δ is determined based on the target vibration isolation efficiency T fk Determined by the compressor operating frequency F2.

[0078] In this embodiment, the static compression amount δ0 is calculated as follows:

[0079] δ0=25 / (F1) 2

[0080] Among them, the static compression δ0 of the vibration isolation system needs to be less than or equal to the target static compression threshold δ. When the static compression δ0 of the vibration isolation system is greater than the target static compression threshold δ, F1 needs to be adjusted, that is, the stiffness coefficient K of the vibration isolation spring needs to be adjusted until the compressor operating frequency F2 / the natural frequency F1 of the vibration isolation system of the compressor-vibration isolation spring is greater than or equal to the preset target value, and the static compression δ0 of the vibration isolation system is less than or equal to the target static compression threshold δ. The target static compression threshold δ is determined according to the target vibration isolation efficiency T fk Determined by the compressor operating frequency F2. That is, the natural frequency F1 of the vibration isolation system and the static compression amount δ0 are both equal to the target vibration isolation efficiency T fk Matching. In this way, the target vibration isolation efficiency T fk To design the vibration isolation spring, so as to make the vibration isolation spring and the vibration isolation efficiency T fk Matching makes the vibration isolation system of compressor-vibration isolation spring have a certain vibration isolation efficiency.

[0081] In this embodiment, T fk Greater than or equal to 90%, the target static compression threshold δ is calculated as follows:

[0082] δ=26.76-0.534*F2

[0083] In this way, it is very convenient to determine the target static compression threshold δ.

[0084] It is understood that in other embodiments, when T fk When is changed, the calculation of the target static compression threshold δ will also change accordingly.

[0085] Step S130: Determine the wire diameter d, median diameter D, and number of turns n of the vibration isolation spring.

[0086] In this embodiment, the wire diameter d of the vibration isolation spring is set to [1.6 mm, 5.0 mm]. The wire diameter d of the vibration isolation spring is preferably 2.0 mm, 2.5 mm, 3.0 mm, or 3.5 mm.

[0087] Specifically, in this embodiment, the wire diameter d of the vibration isolation spring is calculated as follows:

[0088] d=(0.0956*M*C / i) 1 / 2

[0089] Where i is the number of mounting holes on the compressor footplate.

[0090] It is understandable that in other embodiments, the wire diameter d of the vibration isolation spring may also be determined based on experience.

[0091] In this embodiment, the median diameter D of the vibration isolation spring is calculated as follows:

[0092] D=C*d, where C is the winding ratio of the vibration isolation spring, and C is [8, 20]. Preferably, C is 10, 12, or 14.

[0093] In this embodiment, the number of coils n of the vibration isolation spring is calculated as follows:

[0094] n=(9800*d) / (K*C 3 ).

[0095] It should be noted that once the natural frequency F1 of the compressor-isolation spring system is determined, the spring constant K and the spring height are also determined. Once the spring height and the number of coils n are determined, the spacing between adjacent coils can be determined.

[0096] In the above-mentioned design method of the vibration isolation spring for the compressor, the natural frequency F1 of the vibration isolation system is taken as a variable, that is, the stiffness coefficient K of the vibration isolation spring is taken as a variable, and the boundary conditions of "the natural frequency F1 of the vibration isolation system of the compressor operating frequency F2 / compressor-vibration isolation spring is greater than or equal to the preset target value and the static compression amount δ0 of the vibration isolation system is less than or equal to the target static compression amount threshold δ" are taken as the boundary conditions to design the "stiffness coefficient K and target vibration isolation efficiency T fk Matching vibration isolation spring". And in designing "stiffness coefficient K and target vibration isolation efficiency T fk The process of "matching vibration isolation springs" mainly involves the compressor operating frequency F2, the compressor mass M and the target vibration isolation efficiency T fk Therefore, the design method of the vibration isolation spring for the above compressor is universal and can be used for compressors of different displacements, different weights, and different support structures.

[0097] The present invention also provides a vibration isolation system for a compressor.

[0098] In the embodiment of the present invention, Figure 2 As shown, the compressor vibration isolation system 10 is used to connect the compressor footplate 20 and the bottom plate 30 of an electrical appliance. Specifically, the electrical appliance comprises a housing and a compressor mounted on the housing, the compressor having the footplate 20, and the housing having the bottom plate 30. The compressor vibration isolation system 10 connects the footplate 20 and the bottom plate 30. When the compressor is operating, it generates vibrations. Connecting the compressor footplate 20 and the bottom plate 30 with the compressor vibration isolation system 10 effectively prevents the vibrations generated by the compressor from being transmitted to the bottom plate 30, thereby achieving an electrical appliance with relatively low vibration noise.

[0099] In some embodiments, the appliance is a refrigerator, in which case the bottom plate 30 may be the bottom plate of the refrigerator housing. In some embodiments, the appliance is a split-type air conditioner, in which case the bottom plate 30 may be the bottom plate of the housing of the air conditioner outdoor unit. In some embodiments, the appliance is a window air conditioner, in which case the bottom plate 30 may be the bottom plate of the housing of the window air conditioner.

[0100] In this embodiment, the vibration isolation system 10 for a compressor includes a positioning member 200 , a first auxiliary vibration reduction structure 300 , a second auxiliary vibration reduction structure 400 , a vibration isolation spring 500 , and a first limit member 600 .

[0101] The positioning member 200 is used to position and assemble the first auxiliary vibration damping structure 300, the second auxiliary vibration damping structure 400, the vibration isolation spring 500, and the first stopper 600. The positioning member 200 includes a main body 210 and a first screw portion 220. One end of the main body 210 is connected to the base plate 30, and the other end is connected to the first screw portion 220.

[0102] The first auxiliary vibration-damping structure 300 has a slot 310 that mates with the mounting hole on the compressor footplate 20. The slot 310 also defines a stopper plate 320 located at the end of the first auxiliary vibration-damping structure 300. The stopper plate 320 prevents the compressor footplate 20 from separating from the first auxiliary vibration-damping structure 300. During assembly, the stopper plate 320 is squeezed and deformed through the mounting hole, thereby securing the first auxiliary vibration-damping structure 300 to the compressor footplate 20.

[0103] The second auxiliary vibration-damping structure 400 is disposed on the main body 210 and contacts the bottom plate 30. In this way, the second auxiliary vibration-damping structure 400 can be stably mounted on the main body 210.

[0104] One end of the isolation spring 500 is passed through the first auxiliary vibration damping structure 300 , and the other end is passed through the second auxiliary vibration damping structure 400 , that is, both ends of the isolation spring 500 are passed through the first auxiliary vibration damping structure 300 and the second auxiliary vibration damping structure 400 respectively.

[0105] The first limiting member 600 is screwed to the first screw portion 220 , and the first limiting member 600 abuts against an end surface of the first auxiliary vibration-damping structure 300 away from the bottom plate 30 .

[0106] Among them, the minimum value of the compressor operating frequency F2 / the natural frequency F1 of the vibration isolation system of the compressor-vibration isolation spring 500 is greater than or equal to 2.5, that is, F2 / F1 is greater than or equal to 2.5, and the static compression amount δ0 of the vibration isolation system of the compressor-vibration isolation spring 500 is less than or equal to the target static compression amount threshold δ. The target static compression amount threshold δ is calculated based on the target vibration isolation efficiency T fk Determined by the minimum value of the compressor operating frequency F2.

[0107] It should be noted that the natural frequency F1 of the compressor-vibration isolation spring 500 vibration isolation system is approximately the same as the natural frequency of the compressor vibration isolation system 10, and the static compression δ0 of the compressor-vibration isolation spring 500 vibration isolation system is approximately the same as the static compression of the compressor vibration isolation system 10. In other words, the natural frequency and static compression of the compressor vibration isolation system 10 are primarily determined by the mass of the compressor itself and the characteristics of the vibration isolation spring 500 (e.g., the spring constant of the vibration isolation spring 500), while the positioning member 200, the first auxiliary vibration damping structure 300, the second auxiliary vibration damping structure 400, and the first stopper 600 have little effect on the natural frequency and static compression of the compressor vibration isolation system 10.

[0108] In the above-mentioned vibration isolation system 10 for a compressor, a corresponding vibration isolation spring 500 can be designed for a specific compressor so that F2 / F1 is greater than or equal to 2.5, and the static compression δ0 of the vibration isolation system of the compressor-vibration isolation spring 500 is less than or equal to the target static compression threshold δ (the target static compression threshold δ is determined based on the target vibration isolation efficiency T fk and the minimum value of the compressor operating frequency F2), so that the vibration isolation spring 500 can be made to be consistent with the target vibration isolation efficiency T fk Matching, and when the vibration isolation spring 500 and the target vibration isolation efficiency are greater than or equal to 80% T fk When matched, the above-mentioned compressor vibration isolation system 10 has a good vibration isolation effect, and when the vibration isolation spring 500 is greater than or equal to the target vibration isolation efficiency T fk When matched, the natural frequency of the compressor can be reduced to below 25 Hz, which greatly avoids the operating frequency range of the compressor, so that the vibration isolation system 10 for the compressor has a better vibration isolation effect.

[0109] In this embodiment, when T fk When it is greater than or equal to 90%, the target static compression threshold δ is calculated as follows:

[0110] δ=26.76-0.534*F2.

[0111] In this embodiment, the first auxiliary vibration damping structure 300 is made of EPDM rubber, and the Shore hardness of the first auxiliary vibration damping structure 300 is 45 to 60. The second auxiliary vibration damping structure 400 is made of EPDM rubber, and the Shore hardness of the second auxiliary vibration damping structure 400 is 45 to 60.

[0112] In this embodiment, when the first limit member 600 contacts the end surface of the first auxiliary vibration damping structure 300 away from the bottom plate 30, the first limit member 600 can contact the end surface of the main body 210 away from the bottom plate 30, that is, the first limit member 600 can simultaneously contact the end surface of the first auxiliary vibration damping structure 300 away from the bottom plate 30 and the end surface of the main body 210 away from the bottom plate 30.

[0113] In this embodiment, the first stopper 600 is a nut with a washer, which can limit the position of the compressor in the direction of the vibration isolation spring installation axis, preventing the compressor from jumping out of the positioning member 200 due to inertial vibration caused by transportation vibration.

[0114] The distance between the end surface of the main body 210 away from the base plate 30 and the base plate 30 is L; L is [H1-δ0+a+b-2.0mm, H1-δ0+a+b+6.0mm], where H1 is the height of the isolation spring 500, a is the thickness of the limit plate 320, and b is the thickness of the compressor foot plate 20. Specifically, in this embodiment, L is preferably H1-δ0+a+b+2.0mm.

[0115] In the above structure, a corresponding vibration isolation spring 500 can be designed for a specific compressor. After the vibration isolation spring 500 is designed, the positioning member 200 can be quickly designed according to H1 and δ0, so that the positioning member 200 can be matched with the vibration isolation spring 500. When L is [H1-δ0+a+b-2.0mm, H1-δ0+a+b+6.0mm], the positioning member 200 can be better matched with the vibration isolation spring 500, so that the vibration reduction performance of the vibration isolation spring 500 can be in a better state.

[0116] In some embodiments, as Figure 3 and Figure 4 As shown, the positioning member 200 also includes a second screw portion 230. The second screw portion 230 is provided at one end of the main body 210 away from the first screw portion 220. The second screw portion 230 is passed through the base plate 30. The vibration isolation system 10 for the compressor also includes a second limiting member 700. The second limiting member 700 is screwed to the second screw portion 230 so that the second screw portion 230 is fixed to the base plate 30. In this case, L is the length of the main body 210. The positioning member 200 of the above structure is very convenient to be fixed to the base plate 30.

[0117] In some embodiments, as Figure 3 As shown, the second limiting member 700 is a nut with a washer. In some embodiments, as Figure 4 As shown in FIG, the second position-limiting member 700 is a lock rivet with an internal thread. Figure 4In the illustrated embodiment, the end cap of the internally threaded rivet is located between the base plate 30 and the main body 210 , and the thickness of the end cap of the internally threaded rivet is negligible relative to the length L of the main body 210 .

[0118] During installation Figure 3 When using the vibration isolation system 10 for the compressor shown, the lower end of the positioning member 200 (the second screw portion 230) is first positioned and locked on the base plate 30 using the second limiting member 700 (with a washer nut); then the second auxiliary vibration damping structure 400 is installed on the main body 210 of the positioning member 200; then the vibration isolation spring 500 is installed on the second auxiliary vibration damping structure 400, and the first auxiliary vibration damping structure 300 is installed in the mounting hole of the compressor foot plate; then, according to the position of the first screw portion 220, the compressor with the first auxiliary vibration damping structure 300 is installed on the vibration isolation spring 500; finally, the upper end (the first screw portion 220) of the positioning member 200 is locked using the first limiting member 600 (with a washer nut).

[0119] Install Figure 4 The steps and installation of the vibration isolation system 10 for the compressor shown Figure 3 The steps of the vibration isolation system 10 for the compressor shown are the same and will not be described in detail here.

[0120] In some embodiments, as Figure 5 As shown, the main body 210 includes a rod 212 and an end cap 214. One end of the rod 212 is connected to the first screw portion 220, and the other end of the rod 212 is inserted into the base plate 30. The end cap 214 is located on the side of the base plate 30 away from the compressor foot plate 20 and is fixedly connected to the base plate 30. Specifically, in this embodiment, the end cap 214 is welded to the base plate 30. In this case, L is the length of the rod 212 minus the thickness of the base plate 30.

[0121] During installation Figure 5 When using the vibration isolation system 10 for the compressor shown, the lower end (end cap 214) of the positioning member 200 is first welded to the base plate 30; then the second auxiliary vibration damping structure 400 is installed on the main body 210 of the positioning member 200; then the vibration isolation spring 500 is installed on the second auxiliary vibration damping structure 400, and the first auxiliary vibration damping structure 300 is installed in the mounting hole of the compressor foot plate; then, according to the position of the first screw portion 220, the compressor with the first auxiliary vibration damping structure 300 is installed on the vibration isolation spring 500; finally, the first limit member 600 (with a washer nut) is used to lock the upper end (first screw portion 220) of the positioning member 200.

[0122] In this embodiment, the outer diameter R1 of the main body 210 is [6.0 mm, 12.0 mm]; the inner diameter R2 of the first auxiliary vibration-damping structure 300 is [R1+2 mm, R1+12 mm]; and the inner diameter R3 of the second auxiliary vibration-damping structure 400 is [R1-1 mm, R1+2 mm]. This ensures that the first and second auxiliary vibration-damping structures 300, 400 are well matched with the main body 210, thereby optimizing the vibration-damping performance of the isolation spring 500.

[0123] Specifically, in this embodiment, the outer diameter R1 of the main body 210 is preferably 6.0 mm, 8.0 mm, or 10.0 mm. The inner diameter R2 of the first auxiliary vibration-damping structure 300 is preferably R1+8 mm. The inner diameter R3 of the second auxiliary vibration-damping structure 400 is preferably R1.

[0124] In this embodiment, the inner diameter of the mounting hole on the compressor footplate 20 is R4; the outer diameter R5 of the first auxiliary vibration damping structure 300 at the slot 310 is [R4-1mm, R4+2mm]. This ensures a good match between the slot 310 of the first auxiliary vibration damping structure 300 and the mounting hole on the compressor footplate 20, thereby facilitating assembly of the compressor footplate 20 and the first auxiliary vibration damping structure 300. Specifically, in this embodiment, the outer diameter R5 of the first auxiliary vibration damping structure 300 at the slot 310 is preferably R4.

[0125] The above descriptions are merely optional embodiments of the present invention and do not limit the patent scope of the present invention. All equivalent structural transformations made using the contents of the present description and drawings under the inventive concept of the present invention, or direct / indirect applications in other related technical fields, are included in the patent protection scope of the present invention.

Claims

1. A design method for a vibration isolation spring for a compressor, characterized in that: The steps include: F1 is determined based on the fact that F2 / F1 is greater than or equal to the preset target value. F1 is the natural frequency of the vibration isolation system of the compressor-vibration isolation spring, and F2 is the operating frequency of the compressor. F1 is calculated as follows: F1=(1 / 2π)*(K / M) 1 / 2 Where K is the spring constant of the isolation spring, and M is the mass of the compressor; Determine δ0 based on F1 and δ0 is less than or equal to δ, δ is determined based on T fk Determined by F2, δ0 is the static compression of the compressor-isolation spring isolation system, δ is the target static compression threshold, T fk is the target vibration isolation efficiency, and δ0 is calculated as follows: δ0=25 / (F1) 2 ;as well as Determine the wire diameter d, median diameter D and number of turns n of the vibration isolation spring.

2. The design method of a vibration isolation spring for a compressor according to claim 1, wherein: The compressor is a variable frequency compressor, F2 is the minimum value of the compressor operating frequency, and the preset target value is 2.

5.

3. The design method of a vibration isolation spring for a compressor according to claim 1, wherein: When T fk When it is greater than or equal to 90%, δ is calculated as follows: δ=26.76-0.534* F2.

4. The design method of a vibration isolation spring for a compressor according to claim 1, wherein: In the step of determining F1 based on F2 / F1 being greater than or equal to the preset target value, when F2 / F1 is less than the preset target value, K is adjusted until F2 / F1 is greater than or equal to the preset target value.

5. The design method of a vibration isolation spring for a compressor according to claim 4, wherein: Determine the initial K based on the static stiffness of the rubber foot pads that fit the compressor.

6. The design method of a vibration isolation spring for a compressor according to claim 4, wherein: In the step of determining δ0 based on F1 and δ0 being less than or equal to δ, when δ0 is greater than δ, K is adjusted until F2 / F1 is greater than or equal to a preset target value and δ0 is less than or equal to δ.

7. The design method of a vibration isolation spring for a compressor according to claim 4, wherein: Wire diameter d is [1.6mm, 5.0mm]; The median diameter D is calculated as follows: D=C*d, where C is the winding ratio of the isolation spring, and C is [8, 20] The number of turns n is calculated as follows: n=(9800*d) / (K*C 3 )。 8. The design method of a vibration isolation spring for a compressor according to claim 7, wherein: The wire diameter d is calculated as follows: d=(0.0956*M*C / i) 1 / 2 Where i is the number of mounting holes on the compressor footplate.

9. A vibration isolation system for a compressor, used to connect the compressor foot plate and the bottom plate of an electrical appliance, characterized in that: include: A positioning member, comprising a main body and a first screw portion, wherein one end of the main body is connected to the bottom plate, and the other end is connected to the first screw portion; A first auxiliary vibration damping structure has a slot adapted to fit the mounting hole on the compressor footplate, the slot defining a limit plate located at an end of the first auxiliary vibration damping structure, the Shore hardness of the first auxiliary vibration damping structure being 45-60; a second auxiliary vibration-damping structure, disposed on the main body and in contact with the bottom plate; a vibration isolation spring, with two ends respectively passing through the first auxiliary vibration damping structure and the second auxiliary vibration damping structure; as well as a first limiting member, threadedly connected to the first screw portion and abutting against an end surface of the first auxiliary vibration-damping structure away from the bottom plate; Among them, F2 / F1 is greater than or equal to 2.5, δ0 is less than or equal to δ, and δ is calculated based on T fk and F2, F1 is the natural frequency of the vibration isolation system, F2 is the minimum value of the compressor operating frequency, δ0 is the static compression of the vibration isolation system, δ is the target static compression threshold, T fk The target vibration isolation efficiency; F1 is calculated as follows: F1=(1 / 2π)*(K / M) 1 / 2 Where K is the spring constant of the isolation spring, and M is the mass of the compressor; δ0 is calculated as follows: δ0=25 / (F1) 2 。 10. The vibration isolation system for a compressor according to claim 9, wherein: The first limiting member can contact the end surface of the main body away from the bottom plate; The distance between the end surface of the main body away from the bottom plate and the bottom plate is L; L is [H1-δ0+a+b-2.0mm, H1-δ0+a+b+6.0mm], H1 is the height of the vibration isolation spring, a is the thickness of the limit plate, and b is the thickness of the compressor foot plate.

11. The vibration isolation system for a compressor according to claim 10, wherein: The positioning member further includes a second screw portion, the second screw portion is provided at an end of the main body away from the first screw portion, and the second screw portion is passed through the bottom plate; The vibration isolation system for the compressor further includes a second stopper, the second stopper being threadedly connected to the second screw portion so that the second screw portion is fixed to the bottom plate; L is the length of the main body.

12. The vibration isolation system for a compressor according to claim 11, wherein: The first limiting member is a nut with a washer, and the second limiting member is a nut with a washer or a lock rivet with an internal thread.

13. The vibration isolation system for a compressor according to claim 10, wherein: The main body includes a rod body and an end cap. The rod body is passed through the base plate. The end cap is located on a side of the base plate away from the compressor foot plate. The end cap is fixedly connected to the base plate.

14. The vibration isolation system for a compressor according to claim 10, wherein: The outer diameter R1 of the main body is [6.0 mm, 12.0 mm]; The inner diameter R2 of the first auxiliary vibration damping structure is [R1+2mm, R1+12mm]; The inner diameter R3 of the second auxiliary vibration damping structure is [R1-1mm, R1+2mm].

15. The vibration isolation system for a compressor according to claim 10, wherein: The inner diameter of the mounting hole on the compressor footplate is R4; The outer diameter R5 of the first auxiliary vibration-damping structure at the slot is [R4-1mm, R4+2mm].

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