A vibration reduction and isolation system based on particle damper and vibration isolator

Abstract

The present invention discloses a vibration reduction and isolation system based on a particle damper and a vibration isolator, which is used to improve the vibration isolation effect of a vibration device and a vibration isolation surface, and includes a device body of the vibration device; a particle damper, which is arranged on the device body, and the particle damper is filled with damping particles to convert the low-frequency vibration of the device body into high-frequency particle motion; a vibration isolator, which is arranged between the device body and the vibration isolation surface, and the damping particles inside the particle damper perform high-frequency particle motion, thereby improving the overall vibration frequency of the system composed of the particle damper and the vibration isolator, increasing the upper excitation frequency of the vibration isolator, and effectively improving the vibration isolation effect of the vibration isolator; at the same time, the particle damper can also absorb a part of the vibration energy, further enhancing the vibration reduction and isolation effect. This design has a better effect than using a particle damper alone for vibration reduction and isolation or using a vibration isolator alone for vibration reduction and isolation.

Description

Technical Field

[0001] The invention relates to the technical field of vibration reduction and isolation, and in particular to a vibration reduction and isolation system based on a particle damper and a vibration isolator. Background Art

[0002] During the operation of various mechanical equipment, vibration is an inevitable phenomenon. Generally speaking, a large part of the vibration generated during the operation of mechanical equipment is harmful, so it is particularly important to reduce and isolate the vibration of mechanical equipment.

[0003] Among the commonly used vibration reduction and isolation methods currently, one is to use damping energy-absorbing elements installed on mechanical equipment. The damping energy-absorbing elements used in this method often occupy a large space and mass, and the use effect is poor; the other is to perform vibration reduction and isolation by installing a vibration isolator between the mechanical equipment and the vibration isolation surface, but this method has the disadvantages of low natural frequency and excessive linear displacement.

[0004] Therefore, a new vibration reduction and isolation solution is urgently needed to solve the above problems. Summary of the invention

[0005] In order to solve the above technical problems, the present invention provides a vibration reduction and isolation system based on a particle damper and a vibration isolator, which is used to improve the vibration isolation effect of a vibration device and a vibration isolation surface, comprising an equipment body of the vibration device; a particle damper, which is arranged on the equipment body and is filled with damping particles to convert the low-frequency vibration of the equipment body into high-frequency particle motion; and a vibration isolator, which is arranged between the equipment body and the vibration isolation surface.

[0006] The particle damper and vibration isolator are combined to treat the vibration reduction and isolation system based on the particle damper and vibration isolator. The damping particles inside the particle damper perform high-frequency particle motion, which increases the overall vibration frequency of the system composed of the particle damper and vibration isolator, increases the upper excitation frequency of the vibration isolator, and can effectively improve the vibration isolation effect of the vibration isolator; at the same time, the particle damper can also absorb part of the vibration energy, further enhancing the vibration reduction and isolation effect. This design can achieve better results than using a particle damper alone for vibration reduction or using a vibration isolator alone for vibration reduction.

[0007] Optionally, it also includes a mounting structure, which is arranged between the equipment body and the vibration isolator or between the vibration isolator and the vibration isolation surface; the vibration equipment is a pump, a machine tool, a power equipment or a motor.

[0008] Optionally, the particle damper is arranged at the first 10 non-rigid modal positions of the mounting structure, the first 10 non-rigid modal positions of the device body, a position with greater vibration of the device body and / or a critical vibration transmission path.

[0009] Optionally, the particle number density a of the damping particles is 0.1-0.99, the particle size d of the damping particles is 0.01-10 mm, and different gradations are adopted; the damping particles are made of metal, alloy or non-metallic material with a restitution coefficient e of 0.1-0.9; the shell material of the particle damper is metal or non-metal, the shape of the shell is a cylinder, a polygonal prism, a flexible bag, a polygonal pyramid, a truncated cone, a flange, a clamp or an irregular shape, and the wall thickness of the shell is 0.01-20 mm.

[0010] Optionally, the mass n of the particle damper is 0.01% to 1000% of the total mass m of the device body and the particle damper.

[0011] Optionally, the upper excitation frequency f of the isolator after the particle damper is installed i Satisfies the following formula:

[0012]

[0013] Where:

[0014] f i is the upper excitation frequency of the isolator after the particle damper is installed;

[0015] is the average collision frequency;

[0016] b is a constant, and its value range is 0<b≤10 9 ;

[0017] π is the ratio of a circle to a circle;

[0018] A j is the vibration amplitude at the installation position of the particle damper;

[0019] d is the particle size of the damping particles;

[0020] a is the particle number density of the damping particles;

[0021] f j It is the upper excitation frequency of the vibration isolator when the vibration reduction and isolation system based on the particle damper and the vibration isolator is not provided with the particle damper.

[0022] Optionally, f i ≤f2, where f2 is the standing wave frequency of the vibration isolator 3; and Wherein, f0 is the natural frequency of the vibration isolator.

[0023] Optionally, the particle damper follows Δ*U i Maximum principle design, where △ is the upper excitation frequency f after installing the particle damper i The reduction in vibration transmissibility caused by the vibration, U i is the energy consumption of the particle damper, △ and U i Satisfies the following formula:

[0024]

[0025] Where:

[0026] m is the mass of the device body;

[0027] n is the mass of the particle damper;

[0028] ξ is the system damping ratio of the system consisting of the device body and the particle damper;

[0029] g j is the modal participation factor of the particle damper;

[0030] is the average collision frequency;

[0031] f0 is the natural frequency of the vibration isolator;

[0032]

[0033] Where:

[0034] h is the particle size correlation coefficient, and its value range is 0<h<10 5 ;

[0035] e is the particle recovery coefficient;

[0036] A j is the vibration amplitude at the installation position of the particle damper;

[0037] π is the ratio of a circle to a circle;

[0038] m is the mass of the device body;

[0039] g j is the modal participation factor of the particle damper installation position;

[0040] f i The upper excitation frequency of the vibration isolator when the particle damper is installed in the vibration reduction and isolation system based on the particle damper and the vibration isolator.

[0041] Optionally, under the premise of ensuring that the system damping ratio ξ of the system composed of the device body and the particle damper remains unchanged, 0<ξ<1 should also be satisfied, wherein the system damping ratio ξ satisfies the following formula:

[0042]

[0043] Where:

[0044] C0 is the critical damping of the system consisting of the device body and the particle damper;

[0045] C is the damping of the vibration isolator;

[0046] m is the mass of the device body;

[0047] n is the mass of the particle damper;

[0048] k is the system stiffness.

[0049] Optionally, the vibration isolation rate T of the integrated vibration reduction and isolation system is:

[0050]

[0051] Where:

[0052] Δ is the upper excitation frequency f after installing the particle damper i The reduction in vibration transmissibility of the induced vibration;

[0053] π is the ratio of a circle to a circle;

[0054] m is the mass of the device body;

[0055] ξ x is the damping ratio of the isolator;

[0056] a i It is the vibration acceleration at different frequencies when the equipment does not adopt integrated vibration reduction and isolation measures;

[0057] f0 is the natural frequency of the vibration isolator;

[0058] U i is the energy consumption of the particle damper;

[0059] f i The upper excitation frequency of the vibration isolator when the particle damper is installed in the vibration reduction and isolation system based on the particle damper and the vibration isolator. BRIEF DESCRIPTION OF THE DRAWINGS

[0060] Figure 1 It is a structural schematic diagram of the principle of the vibration reduction and isolation system based on the particle damper and the vibration isolator;

[0061] Figure 2 It is a structural schematic diagram of the vibration reduction and isolation system based on the particle damper and the vibration isolator in the first embodiment;

[0062] Figure 3 for Figure 2 A front view of

[0063] Figure 4 for Figure 2 A cross-sectional view of

[0064] Figure 5 for Figure 4 A partial enlarged schematic diagram of the cross section where the first particle damper is located;

[0065] Figure 6 for Figure 4 A partial enlarged schematic diagram of the cross section where the second particle damper is located;

[0066] Figure 7 for Figure 4 A partial enlarged schematic diagram of the cross section where the third particle damper is located;

[0067] Figure 8 It is a structural schematic diagram of a vibration reduction and isolation system based on a particle damper and a vibration isolator in Example 2;

[0068] Fig. 9 for Figure 8 A cross-sectional view of

[0069] Fig.10 for Fig. 9 A partial enlarged schematic diagram of the cross section where the fourth particle damper is located;

[0070] Fig.11 for Fig. 9 A partial enlarged schematic diagram of the cross-section where the fifth particle damper is located.

[0071] Fig.12 for Figure 2 The comparison diagram of the vibration reduction effect before and after of the vibration reduction and isolation system based on particle damper and vibration isolator is shown;

[0072] Fig.13 for Figure 8 The figure shows a comparison of the vibration reduction effects before and after of the vibration reduction and isolation system based on particle dampers and vibration isolators.

[0073] Figure 1-13 In the figure, the reference numerals are described as follows:

[0074] 1 equipment body, 2 particle damper, 21 damping particles, 3 vibration isolator, 4 vibration isolation surface;

[0075] 5 water pump body, 51 first base, 61 first particle damper, 62 second particle damper, 63 third particle damper, 7 first vibration isolator;

[0076] 8 diesel engine body, 81 second base, 91 fourth particle damper, 92 fifth particle damper, 10 second vibration isolator. DETAILED DESCRIPTION

[0077] In order to enable those skilled in the art to better understand the technical solution of the present invention, the present invention is further described in detail below in conjunction with the accompanying drawings and specific embodiments.

[0078] Without loss of generality, this embodiment is based on Figure 1 The principle diagram shown in the figure details the integrated particle vibration reduction and isolation solution, in which the vibration generated during the operation of the vibration equipment needs to be effectively processed to effectively reduce the impact of the vibration on the vibration isolation surface. Here, the "vibration isolation surface" refers to the plane that directly bears the vibration of the vibration equipment after being isolated by the vibration isolator, which is generally the ground, but can also be other bearing structures such as walls and desktops. Of course, the above-mentioned vibration isolation surface is not limited to a plane, but can also be a concave or convex surface.

[0079] It should be understood that the functional composition of the vibration equipment with different working principles to be subjected to vibration reduction and isolation treatment does not constitute a substantial limitation to the technical solution requested for protection in this application. For example, the vibration equipment can be various types of pumps such as centrifugal pumps, plunger pumps, turbine pumps, and worm pumps; the vibration equipment can be various types of motors such as linear motors, stepper motors, and servos; the vibration equipment can be various types of power equipment such as diesel engines, gasoline engines, and dual-fuel engines; the vibration equipment can be various types of machine tools such as punching machines, drilling machines, milling machines, and grinders.

[0080] Of course, there is no limitation on the specific working mode of the vibration device, and the working times can be one-time or multiple times, and the excitation mode can be vibration or impact. Figure 1 The figure shows a schematic structural diagram of the principle of a vibration reduction and isolation system based on a particle damper and a vibration isolator. The vibration reduction and isolation system based on a particle damper and a vibration isolator is used to improve the vibration isolation effect of a vibration device and a vibration isolation surface 4, and includes: an equipment body 1 of the above-mentioned vibration device; a particle damper 2, which is arranged on the equipment body 1, and the particle damper 2 is filled with damping particles 21 to convert the low-frequency vibration of the equipment body 1 into high-frequency particle motion; and a vibration isolator 3, which is arranged between the equipment body 1 and the vibration isolation surface 4.

[0081] The particle damper 2 and the vibration isolator 3 are combined to perform vibration reduction and isolation on the vibration reduction and isolation system based on the particle damper and the vibration isolator. The damping particles 21 inside the particle damper 2 perform high-frequency particle motion, which increases the overall vibration frequency of the system composed of the particle damper 2 and the vibration isolator 3, thereby increasing the upper excitation frequency of the vibration isolator 3, and increasing the ratio of the upper excitation frequency of the vibration isolator 3 to the natural frequency of the vibration isolator 3, thereby effectively improving the vibration isolation effect of the vibration isolator 3; at the same time, the particle damper 2 can also absorb part of the vibration energy, further enhancing the vibration reduction and isolation effect. This design can achieve better results than using the particle damper 2 alone for vibration reduction and isolation or using the vibration isolator 3 alone for vibration reduction and isolation.

[0082] The particle number density a of the damping particles 21 filled in the particle damper 2 is 0.1-0.99, the particle size d of the damping particles 21 is 0.01-10 mm, and different gradations are adopted; the damping particles 21 are made of metal, alloy or non-metal material with a restitution coefficient e of 0.1-0.9.

[0083] Different types of damping particles have different properties and should be selected according to specific circumstances. At the same time, there is no restriction on the types of damping particles 21 inside the particle damper 2, that is, a plurality of damping particles 21 can exist in one particle damper 2 at the same time.

[0084] The shell material of the particle damper 2 is metal or non-metal, and the shell has an outer shape of a cylinder, a polygonal prism, a flexible bag, a polygonal pyramid, a truncated cone, a flange, a clamp or an irregular shape, and the wall thickness of the shell is 0.01-20 mm.

[0085] The selection of the above-mentioned shell depends on the specific situation, for example, it can be determined according to the shape and size of the installation position of the particle damper 2 on the device body 1; it can also be determined according to the size and weight of the particle damper 2. Of course, if conditions permit, it is also possible not to set a shell and directly fill the damping particles 21 in the internal gap of the device body 1.

[0086] The mass n of the particle damper 2 is 0.01% to 1000% of the total mass m of the device body 1 and the particle damper 2 .

[0087] When the particle damper 2 is used alone, the mass p of the mounting structure of the equipment body 1 is often taken into account in determining its mass. The mass of the particle damper 2 is often selected as 0.01% to 1000% of (m+p). When the particle damper 2 is used in combination with the vibration isolator 3, only the mass of the vibration reduction and isolation system based on the particle damper and the vibration isolator at the upper part of the vibration isolator 3 needs to be considered, that is, the mass of the particle damper 2 can be selected as 0.01% to 1000% of m, so that the technician can choose a particle damper 2 with a smaller mass n, thereby making the selection of the particle damper 2 more flexible and diverse.

[0088] The upper excitation frequency f of the isolator 3 after the particle damper is installed i Satisfies the following formula:

[0089]

[0090] Where:

[0091] f i is the upper excitation frequency of the isolator 3 after the particle damper is installed;

[0092] b is a constant, and its value range is 0<b≤10 9 ;

[0093] π is the ratio of a circle to a circle;

[0094] A j is the vibration amplitude at the installation position of particle damper 2;

[0095] d is the particle size of the damping particles 21;

[0096] a is the particle number density of the damping particles 21;

[0097] f j It is the upper excitation frequency of the vibration isolator 3 when the particle damper 2 is not provided in the above-mentioned vibration reduction and isolation system based on the particle damper and the vibration isolator.

[0098] As a preference, f i ≤f2, the vibration reduction and isolation effect is optimal, where f2 is the standing wave frequency of the vibration isolator 3. Furthermore, the natural frequency f0 of the vibration isolator 3 is equal to the upper excitation frequency f i Satisfies the following formula:

[0099]

[0100] Where:

[0101] f0 is the natural frequency of the vibration isolator 3;

[0102] f i is the upper excitation frequency of the vibration isolator 3.

[0103] This formula is an effective vibration isolation formula. The vibration isolation of the vibration isolator 3 is effective only when the upper excitation frequency satisfies this formula. Otherwise, the vibration isolation is invalid, that is, the vibration transmitted to the vibration isolation surface 4 through the vibration isolator 3 is not weakened. Therefore, technicians should pay attention to this problem when setting up a vibration reduction and isolation system based on a particle damper and a vibration isolator, and ensure that the upper excitation frequency f of the vibration isolator 3 after the particle damper is installed is equal to i The relationship with the natural frequency f0 satisfies Test data show that the total vibration level can be reduced by about 50dB after adopting the integrated vibration reduction and isolation design.

[0104] It can be understood that the upper excitation frequency f of the vibration isolator 3 i is the overall vibration frequency of the system consisting of the device body 1 and the particle damper 2. The particle damper 2 reduces the original vibration frequency f of the device body 1 to j Transformed into the overall vibration frequency f of the system consisting of the device body 1 and the particle damper 2 i , thereby increasing the upper excitation frequency of the vibration isolator 3 from f when only the device body 1 is set j Transformed to a higher f i , thereby increasing the ratio of the upper excitation frequency of the vibration isolator 3 to the natural frequency of the vibration isolator 3 , and enhancing the vibration isolation effect of the vibration isolator 3 .

[0105] In actual application, technicians can change the upper excitation frequency f of the vibration isolator 3 by adjusting the particle size d and particle number density a of the damping particles 21. i , then you can satisfy Under the premise of making the upper excitation frequency f i As large as possible, thereby enhancing the vibration isolation effect of the vibration isolator 3. In order to obtain the best vibration reduction and isolation effect, the particle damper 2 is arranged at the first 10 non-rigid modal positions of the mounting structure, the first 10 non-rigid modal positions of the equipment body 1, the position with larger vibration of the equipment body 1 and / or the key vibration transmission path to ensure good vibration reduction and isolation.

[0106] The particle damper 2 is designed according to the principle of maximum energy consumption and maximum reduction of vibration transmissibility, that is, △*U i Maximum, where △ is the upper excitation frequency f after installing the particle damper i The reduction in vibration transmissibility caused by the vibration, U i is the energy consumption of the particle damper, △ and U i Satisfies the following formula:

[0107]

[0108] Where:

[0109] m is the mass of the device body;

[0110] n is the mass of the particle damper;

[0111] ξ is the system damping ratio of the system consisting of the device body and the particle damper;

[0112] g j is the modal participation factor of the particle damper;

[0113] is the average collision frequency;

[0114] f0 is the natural frequency of the vibration isolator;

[0115]

[0116] Where:

[0117] h is the particle size correlation coefficient, and its value range is 0<h<10 5 ;

[0118] e is the particle recovery coefficient;

[0119] A j is the vibration amplitude at the installation position of the particle damper;

[0120] π is the ratio of a circle to a circle;

[0121] m is the mass of the device body;

[0122] g j is the modal participation factor of the particle damper installation position;

[0123] f i The upper excitation frequency of the vibration isolator when the particle damper is installed in the vibration isolation system based on the particle damper and the vibration isolator

[0124] When designing the particle damper 2, not only the upper excitation frequency f of the isolator 3 should be considered i , the energy efficiency of particle damper 2 must also be taken into account. The above product (△*U i ) can be simplified to the problem of selecting the maximum value of a certain function formula, and then some parameters of the particle damper 2 can be determined and the design of the particle damper 2 can be improved.

[0125] Of course, this is only one design method of the particle damper 2. The particle damper 2 may not be designed according to this idea, and its specific form and parameters may be determined according to actual conditions.

[0126] It should be noted that the damping design of the particle damper 2 (expressed by energy consumption and not involved in the vibration isolation rate calculation) is related to the stiffness of the vibration isolator 3, which is specifically reflected in the absolute value of vibration. When the vibration isolation rate of the vibration isolator is constant, the smaller the upper vibration is, the smaller the vibration after vibration isolation is. Under the premise of ensuring that the system damping ratio ξ of the system composed of the equipment body 1 and the particle damper 2 remains unchanged, it should also satisfy 0<ξ<1, where the system damping ratio ξ satisfies the following formula:

[0127]

[0128] Where:

[0129] C0 is the critical damping of the system consisting of the device body 1 and the particle damper 2;

[0130] C is the damping of the vibration isolator 3;

[0131] m is the mass of the device body;

[0132] n is the mass of the particle damper;

[0133] k is the system stiffness.

[0134] Selecting a vibration isolator 3 with a higher C value can improve the damping of the system, thereby ensuring that the vibration of the system in the resonance zone before vibration isolation is within a controllable range. However, selecting a vibration isolator 3 with a higher C value will cause ξ to become larger and the vibration isolation effect to become worse. After installing the particle damper, the critical damping C0 of the system increases. Therefore, the vibration isolator 3 can be selected based on the actual conditions of the equipment body 1 and the particle damper 2.

[0135] The vibration isolation rate T of the integrated vibration reduction and isolation system using this solution is:

[0136]

[0137] Where:

[0138] Δ is the upper excitation frequency f after installing the particle damper i The reduction in vibration transmissibility of the induced vibration;

[0139] π is the ratio of a circle to a circle;

[0140] m is the mass of the device body;

[0141] ξ x is the damping ratio of the isolator;

[0142] a i It is the vibration acceleration at different frequencies when the equipment does not adopt integrated vibration reduction and isolation measures;

[0143] f0 is the natural frequency of the vibration isolator;

[0144] Ui is the energy consumption of the particle damper;

[0145] f i The upper excitation frequency of the vibration isolator when the particle damper is installed in the vibration reduction and isolation system based on the particle damper and the vibration isolator.

[0146] It should be noted that the above conclusion is universal, that is, it is also applicable to other vibration reduction and isolation systems based on particle dampers and vibration isolators that meet the conditions of the present invention.

[0147] Embodiment 1:

[0148] like Figure 2 As shown, it is a structural schematic diagram of a specific embodiment of a vibration reduction and isolation system based on a particle damper and a vibration isolator provided by the present invention. The mechanical equipment is a water pump, and its equipment body is a water pump body 5. Three particle dampers are arranged on the water pump body 5, namely: a first particle damper 61, a second particle damper 62 and a third particle damper 63. A first vibration isolator 7 is arranged between the water pump body 5 and the ground (not shown in the figure).

[0149] The integrated vibration reduction and isolation system further comprises a mounting structure, which is arranged between the water pump body 5 and the first vibration isolator 7 .

[0150] The above-mentioned mounting structure in this specific embodiment is the first base 51. Of course, the specific form of the above-mentioned mounting structure is not limited here. The above-mentioned mounting structure can be a variety of structural forms such as a base, a support frame, etc.; at the same time, the above-mentioned mounting structure can also be arranged between the first vibration isolator 7 and the ground (not shown in the figure).

[0151] It should be pointed out that when designing a vibration reduction and isolation system based on a particle damper and a vibration isolator, if the above-mentioned mounting structure is arranged on the upper part of the first vibration isolator 7, the overall mass of the above-mentioned mounting structure and the water pump body 5 will be used as the mass for calculating the upper excitation of the vibration isolator.

[0152] like Figure 3 and Figure 4 As shown, Figure 3 is a front view of the water pump body 5, Figure 4 for Figure 3 A cross-sectional view of the pump body 5 shows the general positions of the plurality of particle dampers disposed on the pump body 5; Figure 5 , Figure 6 and Figure 7 As shown, they are respectively partial enlarged schematic diagrams of the cross-sections at the locations of the various particle dampers.

[0153] like Figure 5, which is a partially enlarged schematic diagram of the cross section of the location of the first particle damper 61, the first particle damper 61 is arranged on the pump body of the water pump body 5; Figure 6 , which is a partially enlarged schematic diagram of the cross section of the location of the second particle damper 62, and the second particle damper 62 is arranged in the above-mentioned base; Figure 7 , which is a partially enlarged schematic diagram of the cross section of the location of the third particle damper 63 . The third particle damper 63 is arranged on the motor of the water pump body 5 , and this location is the vibration source location of the water pump body 5 .

[0154] It should be noted that the particle damper is preferably disposed at a location of the water pump body 5 where vibration is greater and / or on a key vibration transmission path.

[0155] The purpose of arranging the particle dampers at these positions is to enable the two functions of the particle dampers, namely, increasing the vibration frequency and absorbing the vibration energy, to be fully exerted, thereby optimizing the functions of the particle dampers. The determination of the positions with larger vibrations and the key vibration transmission paths requires a modal analysis of the water pump body 5, and the modal analysis method is a well-known analysis method, so it will not be repeated here.

[0156] Of course, the above conclusions about the location of the particle damper are not limited to this embodiment, but are also applicable to other vibration reduction and isolation systems based on particle dampers and vibration isolators that meet the conditions of the present invention.

[0157] like Fig.12 As shown in FIG. 1 , it is a comparison diagram of the vibration reduction effect of the water pump provided in this embodiment. The four curves in the figure respectively represent the vibration reduction effect curves when rigid installation (i.e., no vibration reduction and isolation treatment is performed), only particle dampers are set, only vibration isolators are set, and particle dampers and vibration isolators are integrated. It can be seen from the figure that in the range of relatively high vibration frequency of the water pump body 5, the integrated design of the vibration isolator and the particle damper has a better vibration reduction and isolation effect than the other three vibration reduction and isolation setting methods.

[0158] Embodiment 2:

[0159] like Figure 8 and Fig. 9 As shown, Figure 8 A schematic structural diagram of a specific implementation of a vibration reduction and isolation system based on a particle damper and a vibration isolator provided by the present invention. Fig. 9 for Figure 8 The cross-sectional view of the mechanical device is a diesel engine, and the device body is a diesel engine body 8. Two particle dampers are arranged on the diesel engine body 8, namely: a fourth particle damper 91 and a fifth particle damper 92. The diesel engine body 8 is arranged on a second base 81, and a second vibration isolator 10 is arranged between the second base 81 and the ground (not shown in the figure).

[0160] like Fig.10 As shown, it is a partial enlarged schematic diagram of the cross section of the fourth particle damper 91, and the fourth damper 91 is arranged on the pipeline of the diesel engine body 8; Fig.11 , which is a partially enlarged schematic diagram of the cross section of the location of the fifth particle damper 92. The fifth particle damper 92 is arranged on the second base 81 of the diesel engine body 8, and this position is a key position for vibration transmission.

[0161] like Fig.13 As shown in FIG. 1 , it is a comparison diagram of the vibration reduction effect of the diesel engine provided in this embodiment. The four curves in the figure respectively represent the vibration reduction effect curves when rigid installation (i.e., no vibration reduction and isolation treatment is performed), only particle dampers are set, only vibration isolators are set, and particle dampers and vibration isolators are integrated. It can be seen from the figure that in the range of relatively high vibration frequency of the diesel engine body 8, the integrated design of the vibration isolator and the particle damper has a better vibration reduction and isolation effect than the other three vibration reduction and isolation setting methods.

[0162] The above are only preferred embodiments of the present invention. It should be pointed out that, for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the principles of the present invention. These improvements and modifications should also be regarded as the scope of protection of the present invention.

Claims

1. A vibration reduction and isolation system based on a particle damper and a vibration isolator, used to improve the vibration isolation effect of a vibration device and a vibration isolation surface, characterized in that: include: A device body of the vibration device; A particle damper is arranged on the device body, and the particle damper is filled with damping particles to convert the low-frequency vibration of the device body into high-frequency particle motion; A vibration isolator, arranged between the equipment body and the vibration isolation surface; The upper excitation frequency f of the isolator after the particle damper is installed is i Satisfies the following formula: Where: f i is the upper excitation frequency of the isolator after the particle damper is installed; is the average collision frequency; b is a constant, and its value range is 0 <b≤10 9 ; π is the ratio of a circle to a circle; A j is the vibration amplitude at the installation position of the particle damper; d is the particle size of the damping particles; a is the particle number density of the damping particles; f j The upper excitation frequency of the vibration isolator when the vibration reduction and isolation system based on the particle damper and the vibration isolator is not provided with the particle damper; f i ≤f2, where f2 is the standing wave frequency of the isolator; and Wherein, f0 is the natural frequency of the vibration isolator; The particle damper is arranged at the first 10 non-rigid modal positions of the mounting structure, the first 10 non-rigid modal positions of the device body, the position of the device body with greater vibration and / or the key vibration transmission path; The particle damper follows △*U i Maximum principle design, where △ is the upper excitation frequency f after installing the particle damper i The reduction in vibration transmissibility caused by the vibration, U i is the energy consumption of the particle damper, △ and U i Satisfies the following formula: Where: m is the mass of the device body; n is the mass of the particle damper; ξ is the system damping ratio of the system consisting of the device body and the particle damper; g j is the modal participation factor of the particle damper; is the average collision frequency; f0 is the natural frequency of the vibration isolator; Where: h is the particle size correlation coefficient, ranging from 0 <h<10 5 ; e is the particle recovery coefficient; A j is the vibration amplitude at the installation position of the particle damper; π is the ratio of a circle to a circle; m is the mass of the device body; g j is the modal participation factor of the particle damper installation position; f i The upper excitation frequency of the vibration isolator when the particle damper is installed in the vibration reduction and isolation system based on the particle damper and the vibration isolator.

2. The vibration reduction and isolation system based on a particle damper and a vibration isolator according to claim 1, characterized in that: It also includes a mounting structure, which is arranged between the equipment body and the vibration isolator or between the vibration isolator and the vibration isolation surface; the vibration equipment is a pump, a machine tool, a power equipment or a motor.

3. The vibration reduction and isolation system based on a particle damper and a vibration isolator according to claim 1, characterized in that: The particle number density a of the damping particles is 0.1 to 0.99, the particle size d of the damping particles is 0.01 to 10 mm, and different gradations are adopted; the damping particles are made of metal, alloy or non-metal material with a recovery coefficient e of 0.1 to 0.9; the shell material of the particle damper is metal or non-metal, and the wall thickness of the shell is 0.01 to 20 mm.

4. The vibration reduction and isolation system based on a particle damper and a vibration isolator according to claim 3, characterized in that: The mass n of the particle damper is 0.01% to 1000% of the total mass m of the device body and the particle damper.

5. The vibration reduction and isolation system based on a particle damper and a vibration isolator according to claim 1, characterized in that: Under the premise of ensuring that the system damping ratio ξ of the system composed of the device body and the particle damper remains unchanged, 0<ξ<1 should also be satisfied, wherein the system damping ratio ξ satisfies the following formula: Where: C0 is the critical damping of the system consisting of the device body and the particle damper; C is the damping of the vibration isolator; m is the mass of the device body; n is the mass of the particle damper; k is the system stiffness.

6. The vibration reduction and isolation system based on a particle damper and a vibration isolator according to claim 5, characterized in that: The vibration isolation rate T of the integrated vibration reduction and isolation system is: Where: △ is the upper excitation frequency f after installing the particle damper i The reduction in vibration transmissibility of the induced vibration; π is the ratio of a circle to a circle; m is the mass of the device body; ξ x is the damping ratio of the isolator; a i It is the vibration acceleration at different frequencies when the equipment does not adopt integrated vibration reduction and isolation measures; f0 is the natural frequency of the vibration isolator; U i is the energy consumption of the particle damper; f i The upper excitation frequency of the vibration isolator when the particle damper is installed in the vibration reduction and isolation system based on the particle damper and the vibration isolator.

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