【摘要】：為了解決傳統(tǒng)的被動(dòng)式的隔振方法在控制船用柴油機(jī)振動(dòng)時(shí)性能上的缺陷,滿足人們對(duì)船舶振動(dòng)越來越高的要求,本文設(shè)計(jì)研制了一款新型的主被動(dòng)復(fù)合隔振器。本文將其設(shè)計(jì)在傳統(tǒng)的被動(dòng)式的雙層被動(dòng)隔振系統(tǒng)基礎(chǔ)之上,增加一個(gè)次級(jí)力源裝置對(duì)系統(tǒng)中間質(zhì)量輸出激振力,通過適當(dāng)?shù)目刂扑惴▽?duì)次級(jí)激振力進(jìn)行控制,對(duì)被控的振動(dòng)系統(tǒng)輸入外部能量,減小系統(tǒng)力的傳遞率,以達(dá)到振動(dòng)控制的預(yù)定目標(biāo)。主被動(dòng)復(fù)合隔振器主要由上、下兩層隔振裝置,作為中間質(zhì)量的中間平臺(tái),以及安裝在中間平臺(tái)上的四臺(tái)慣性式電磁作動(dòng)器與功率放大器等設(shè)備零件組成。本文的研究工作圍繞著主被動(dòng)復(fù)合隔振器中慣性式電磁作動(dòng)器設(shè)計(jì)和主被動(dòng)復(fù)合隔振器整體結(jié)構(gòu)設(shè)計(jì)展開,深入分析隔振原理,設(shè)計(jì)出各部分的零件圖,經(jīng)過加工生產(chǎn)出各個(gè)部分的零件,并最終裝配成樣機(jī)。論文的主要工作包括:1、從隔振的基本原理出發(fā),重點(diǎn)探討兩層隔振系統(tǒng)和雙層主動(dòng)控制隔振的系統(tǒng)特性,為主被動(dòng)復(fù)合隔振器的設(shè)計(jì)提供必要的理論依據(jù)。2、完成了慣性式電磁作動(dòng)器磁路的設(shè)計(jì),選用釹鐵硼稀土永磁材料作為作動(dòng)器磁路中的永磁體,選用10#鋼作為軟磁材料。并使用Ansoft電磁場(chǎng)有限元分析軟件詳細(xì)地分析了軛鐵厚度、導(dǎo)磁磁缸厚度和導(dǎo)磁磁缸長(zhǎng)度對(duì)設(shè)計(jì)的釹鐵硼永久磁鐵磁路特性的影響。對(duì)慣性式電磁作動(dòng)器彈簧,風(fēng)扇的重要組成部件進(jìn)行了計(jì)算。依據(jù)仿真與計(jì)算的結(jié)果,利用AutoCAD軟件對(duì)慣性式電磁作動(dòng)器的各個(gè)零件進(jìn)行了詳細(xì)的設(shè)計(jì)工作,并用Pro/e建模軟件建立了慣性式電磁作動(dòng)器的二維效果模型。在各個(gè)零件加工完成之后,對(duì)慣性式電磁作動(dòng)器進(jìn)行了了組裝工作,并對(duì)其性能進(jìn)行了詳細(xì)的測(cè)試工作。測(cè)試結(jié)果表明四臺(tái)慣性式電磁作動(dòng)器的性能良好,完全可以作為振動(dòng)主動(dòng)控制系統(tǒng)的次級(jí)激振力。3、確定了肖氏硬度為60～70HS的丁腈橡膠(NBR)作為上下兩層隔振橡膠的材料,并根據(jù)主被動(dòng)復(fù)合隔振器的尺寸,對(duì)上下兩層的隔振橡膠組件進(jìn)行了了設(shè)計(jì),并計(jì)算出橡膠組件在承載5噸靜載力的情況下的變形量,通過理論計(jì)算并對(duì)比Ansys的計(jì)算結(jié)果,表明本文的設(shè)計(jì)的隔振橡膠組件的變形量完全在允許的范圍內(nèi)。最后完成了主被動(dòng)復(fù)合隔振器其他部件的設(shè)計(jì),并根據(jù)設(shè)汁圖紙建立了三維立體模型,各個(gè)零件加工完成之后,并對(duì)主被動(dòng)復(fù)合隔振器進(jìn)行了組裝,為振動(dòng)主動(dòng)控制試驗(yàn)做好了充分的前期準(zhǔn)備。
[Abstract]:In order to solve the defects of the traditional passive vibration isolation method in controlling the vibration of marine diesel engine and meet the higher and higher requirements of ship vibration, a new type of active and passive composite isolator is designed and developed in this paper. In this paper, it is designed on the basis of the traditional passive double-layer passive vibration isolation system, and a secondary force source device is added to output the excitation force to the intermediate mass of the system, and the secondary excitation force is controlled by the appropriate control algorithm. The external energy is input to the controlled vibration system to reduce the transmission rate of the system force in order to achieve the predetermined goal of vibration control. The active and passive composite isolator is mainly composed of upper and lower two layers of vibration isolator, which is used as the intermediate platform of intermediate mass, as well as four inertial electromagnetic actuators and power amplifiers installed on the intermediate platform. The research work of this paper revolves around the design of inertial electromagnetic actuator and the overall structure design of active and passive composite isolator in active and passive composite isolator. The principle of vibration isolation is deeply analyzed and the part drawings of each part are designed. After processing and production of each part of the parts, and finally assembled into a prototype. The main work of this paper is as follows: 1. Based on the basic principle of vibration isolation, this paper focuses on the characteristics of two-layer vibration isolation system and double-layer active control vibration isolation system, and provides the necessary theoretical basis for the design of passive composite isolator. 2, The design of magnetic circuit of inertia electromagnetic actuator is completed. ND-Fe-B rare earth permanent magnet material is selected as permanent magnet in actuator magnetic circuit and 10 # steel is selected as soft magnetic material. The effects of yoke iron thickness, magnetic cylinder thickness and magnetic cylinder length on the magnetic circuit characteristics of the designed ND-Fe-B permanent magnet are analyzed in detail by using Ansoft electromagnetic field finite element analysis software. The important components of inertia electromagnetic actuator spring and fan are calculated. According to the results of simulation and calculation, the parts of inertial electromagnetic actuator are designed in detail by using AutoCAD software, and the two-dimensional effect model of inertial electromagnetic actuator is established by Pro/e modeling software. After the machining of each part, the inertial electromagnetic actuator is assembled, and its performance is tested in detail. The test results show that the four inertial electromagnetic actuators have good performance and can be used as the secondary excitation force of the active vibration control system. 3, The nitrile rubber (NBR) with Shaw hardness of 60~70HS was determined as the material of the upper and lower two layers of vibration isolation rubber, and according to the size of the active and passive composite isolator, the vibration isolation rubber assembly of the upper and lower layers was designed. The deformation of the rubber assembly under the condition of bearing 5 tons of static load is calculated. Through theoretical calculation and comparison of the calculation results of Ansys, it is shown that the deformation of the vibration isolation rubber assembly designed in this paper is completely within the allowable range. Finally, the design of other components of the active and passive composite isolator is completed, and the three-dimensional model is established according to the juice setting drawings. After the processing of each part, the active and passive composite isolator is assembled. Adequate preparation has been made for the active vibration control test.
【學(xué)位授予單位】：哈爾濱工程大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2014
【分類號(hào)】：TB535.1;U664.121

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本文編號(hào)：2477383