液體動(dòng)壓滑動(dòng)軸承實(shí)驗(yàn)臺(tái)設(shè)計(jì)【含CAD高清圖紙和說明書】

【溫馨提示】 dwg后綴的文件為CAD圖，可編輯，無水印，高清圖，，壓縮包內(nèi)文檔可直接點(diǎn)開預(yù)覽，需要原稿請(qǐng)自助充值下載，請(qǐng)見壓縮包內(nèi)的文件，所見才能所得，下載可得到【資源目錄】下的所有文件哦--有疑問可咨詢QQ:1304139763 或 414951605

浙江理工大學(xué)本科畢業(yè)設(shè)計(jì)（論文）任務(wù)書 丁建峰 同學(xué)（專業(yè) / 班級(jí)： 機(jī)械設(shè)計(jì)制造及其自動(dòng)化09（4）班 ） 現(xiàn)下達(dá)畢業(yè)設(shè)計(jì)（論文）課題任務(wù)書，望能保質(zhì)保量地認(rèn)真按時(shí)完成。 課題名稱 液體動(dòng)壓滑動(dòng)軸承試驗(yàn)臺(tái) 主要任務(wù)與 目標(biāo) 滑動(dòng)軸承是用來支撐軸及其它回轉(zhuǎn)零件的一種重要部件，因其本身具有一些獨(dú)特的優(yōu)點(diǎn)：軸頸軸瓦間所特有的潤(rùn)滑油膜具有緩沖吸振作用，使用壽命長(zhǎng)，結(jié)構(gòu)緊湊，回轉(zhuǎn)速度高等，這些優(yōu)點(diǎn)使它在某些場(chǎng)合占有重要地位。因此滑動(dòng)軸承在金屬切削機(jī)床、內(nèi)燃機(jī)、鐵路機(jī)及車輛、軋鋼機(jī)、雷達(dá)、衛(wèi)星通信地面站及天文望遠(yuǎn)鏡等方面的應(yīng)用十分廣泛 。為了幫助大學(xué)學(xué)生更加深入、細(xì)致地了解和研究滑動(dòng)軸承，各種滑動(dòng)軸承實(shí)驗(yàn)臺(tái)應(yīng)運(yùn)而生，但在實(shí)驗(yàn)的效率、效果方面都還有不足。 主要任務(wù)： 本課題重點(diǎn)完成實(shí)驗(yàn)臺(tái)傳動(dòng)電機(jī)及調(diào)速方法選擇、相應(yīng)傳感器的選擇，其主要內(nèi)容有： 1、了解液體動(dòng)壓滑動(dòng)軸承實(shí)驗(yàn)臺(tái)研制研究目的。理解液體動(dòng)壓滑動(dòng)軸承結(jié)構(gòu)及 其特點(diǎn)。確定完整實(shí)驗(yàn)系統(tǒng)總體方案。 2、相關(guān)測(cè)試用傳感器型號(hào)、電機(jī)選定。 3、進(jìn)行油溫測(cè)試，對(duì)油膜進(jìn)行加熱，測(cè)得油溫與壓力的關(guān)系 （這是以前所不具有的，是本試驗(yàn)臺(tái)最大的創(chuàng)新） 4、對(duì)油膜形成過程進(jìn)行三維仿真。 目標(biāo)：設(shè)計(jì)一個(gè)試驗(yàn)臺(tái)，了解到溫度變化與油膜壓力、粘度的關(guān)系。 主要內(nèi)容與基本要求 （這個(gè)是別人做好的試驗(yàn)臺(tái)，我拿過來做參考）。 1、電 機(jī) 2、皮 帶 3、摩擦力傳感器 4、壓力傳感器：測(cè)量軸承表面油膜壓力，共7個(gè)F1~ F7， 5、軸 瓦 6、加載傳感器：測(cè)量外加載荷值 7、主 軸 9、油 槽 10、底 座 11、面 板 12、調(diào)速旋鈕：控制電機(jī)轉(zhuǎn)速 試驗(yàn)臺(tái)啟動(dòng)后，由電機(jī)1通過皮帶帶動(dòng)主軸7在油槽9中轉(zhuǎn)動(dòng)，在油膜粘力作用下通過摩擦力傳感器3測(cè)出主軸旋轉(zhuǎn)時(shí)受到的摩擦力矩；當(dāng)潤(rùn)滑油充滿整個(gè)軸瓦內(nèi)壁后軸瓦上的7個(gè)壓力傳感器可分別測(cè)出分布在其上的油膜壓力值；待穩(wěn)定工作后由溫度傳感器t1測(cè)出入油口的油溫，t2測(cè)出出油口的油溫。 主要參 考資料 及文獻(xiàn) 閱讀任務(wù) [1] 張直明，謝友柏.滑動(dòng)軸承的流體動(dòng)力潤(rùn)滑理論[M].北京:高等教育出版社，1986 [2] 西北工業(yè)大學(xué)機(jī)械原理及機(jī)械零件教研組.機(jī)械設(shè)計(jì).人民教育出版社，1979,1 [3] 許尚賢.液體靜壓和動(dòng)靜壓滑動(dòng)軸承設(shè)計(jì).東南大學(xué)出版社，1989 [4] Sun Meili, Zhang Zhiming. http://www.51lunwen.com/benkekaiti/ Experimental Study of the Film Distribution of Statically and Dynamically Loaded Cylinder Journal Bearing [ J ]. Journal of Shanghai University: Natural Science Edition, 1997, 3 (5) : 500 - 507 [5] 劉詩(shī)海.教學(xué)儀器的現(xiàn)狀與發(fā)展.教學(xué)儀器與實(shí)驗(yàn),2003 ,(5):25 [6] 楊可楨，程光蘊(yùn)，李仲生.機(jī)械設(shè)計(jì)基礎(chǔ)[M]. 北京:高等教育出版社，1986，253-265 [7] wang wen, ZhangZhiming.Calculation of journal dynamic locus aided by database of non一stationary oil film force of single bush segment [C].Asia-Pacific Vibration Conference'93, Japan, 1993,365-369 [8] 費(fèi)業(yè)泰.論文代寫誤差理淪與數(shù)據(jù)處理.北京:機(jī)械工業(yè)出版社，2000，5 [9]濮良貴，紀(jì)名剛.機(jī)械設(shè)計(jì)（第八版）[M].北京：高等教育出版社，2012：22. [10]孫恒，陳作模，葛文杰.機(jī)械原理（第七版）[M].北京：高等教育出版社，2006：77. 外文 翻譯任務(wù) 原文1：Research on the reliability of sliding bearing support in a swash-plate type axial piston water hydraulic pump 譯文1：研究的可靠性,滑動(dòng)軸承支撐斜盤式軸向柱塞泵型水液壓 原文2：Application of computational fluid dynamic to model the hydraulic performance of subsurface flow wetlands 譯文2：應(yīng)用計(jì)算流體動(dòng)力學(xué)模型來模擬地下水流水力性能的濕地 閱讀了10000字以上的外文，并且翻譯了5000字英譯漢。 計(jì)劃進(jìn)度： 起止時(shí)間 內(nèi)容 負(fù)責(zé)人 2012.9.20 分管院領(lǐng)導(dǎo)作畢業(yè)設(shè)計(jì)動(dòng)員（教師） 分管院長(zhǎng) 2012.9.20-2012.10.08 畢業(yè)設(shè)計(jì)相關(guān)文件及規(guī)定學(xué)習(xí)、優(yōu)秀畢業(yè)設(shè)計(jì)（論文）交流；確定教師所帶人數(shù)、完成選題表、所級(jí)題目審核 各系系主任 2012.10.09-2012.10.15 教學(xué)委員會(huì)題目審核、按專業(yè)畢業(yè)設(shè)計(jì)動(dòng)員（學(xué)生） 分管院長(zhǎng)、學(xué)生線 2012.10.16-2012.10.22 學(xué)生選題 各系系主任、各班班長(zhǎng) 2012.10.23-2012.10.29 各所根據(jù)學(xué)生選題情況進(jìn)行平衡調(diào)整，確定指導(dǎo)教師及各課題學(xué)生，上交畢業(yè)設(shè)計(jì)（論文）信息表。 各系系主任 2012.10.30-2012.11.06 教師填寫畢業(yè)設(shè)計(jì)任務(wù)書、確定外文閱讀與翻譯資料，并下達(dá)畢業(yè)設(shè)計(jì)任務(wù) 指導(dǎo)教師 2012.11.07-2012.12.27 學(xué)生畢業(yè)設(shè)計(jì)調(diào)研，完成開題報(bào)告、文獻(xiàn)綜述、外文資料閱讀、翻譯任務(wù) 指導(dǎo)教師 2012.12.28-2013.01.03 學(xué)生提交開題報(bào)告、文獻(xiàn)綜述及外文翻譯初稿，指導(dǎo)教師審閱，提出修改意見 指導(dǎo)教師 2013.01.04-2013.01.11 各系進(jìn)行開題報(bào)告答辯 各系系主任 2013.01.12-2013.02.11 指導(dǎo)教師布置具體設(shè)計(jì)任務(wù)，利用假期完成 指導(dǎo)教師 2013.02.12-2013.02.19 本周開始，指導(dǎo)教師應(yīng)對(duì)所指導(dǎo)的每位學(xué)生進(jìn)行考核登記 畢業(yè)設(shè)計(jì)前期檢查：任務(wù)書、綜述報(bào)告、開題報(bào)告、外文翻譯 院教學(xué)委員會(huì)、院督導(dǎo)組 2013.02.20-2013.04.04 按畢業(yè)設(shè)計(jì)任務(wù)書要求進(jìn)行畢業(yè)設(shè)計(jì) 指導(dǎo)教師 2013.04.05-2013.04.11 畢業(yè)設(shè)計(jì)中期檢查：教師指導(dǎo)情況、學(xué)生完成情況、表格與記錄的填寫情況 院教學(xué)委員會(huì)、院督導(dǎo)組 2013.04.12-2013.05.09 學(xué)生完成課題設(shè)計(jì)，提交畢業(yè)設(shè)計(jì)（論文） 指導(dǎo)教師 2013.05.10-2013.05.15 指導(dǎo)教師完成所指導(dǎo)學(xué)生的畢業(yè)設(shè)計(jì)（論文）的審閱，寫出評(píng)語，評(píng)出成績(jī)；評(píng)議小組分組審閱，寫出評(píng)語，評(píng)定成績(jī) 指導(dǎo)教師、各系評(píng)議組 2013.05.20-2013.05.22 學(xué)院分組進(jìn)行答辯，由答辯小組給出評(píng)語及成績(jī) 答辯小組 2013.05.27-2013.05.28 二次答辯 答辯小組 2013.05.30-2013.05.31 進(jìn)行成績(jī)綜合評(píng)定，上報(bào)學(xué)生畢業(yè)設(shè)計(jì)（論文）成績(jī) 教學(xué)委員會(huì) 實(shí)習(xí)地點(diǎn) 指導(dǎo)教師 簽 名 年 月 日 系 意 見 系主任簽名： 年 月 日 學(xué)院 蓋章 主管院長(zhǎng)簽名： 年 月 日 外文翻譯 畢業(yè)設(shè)計(jì)題目：液體動(dòng)壓滑動(dòng)軸承試驗(yàn)臺(tái) 原文1：Research on the reliability of sliding bearing support in a swash-plate type axial piston water hydraulic pump 譯文1：研究的可靠性,滑動(dòng)軸承支撐斜盤式軸向柱塞泵型水液壓 原文2：Application of computational fluid dynamic to model the hydraulic performance of subsurface flow wetlands 譯文2：應(yīng)用計(jì)算流體動(dòng)力學(xué)模型來模擬地下水流水力性能的濕地 Research on the reliability of sliding bearing support in a swash-plate type axial piston water hydraulic pump Yin F.L., Nie S.L. College of Mechanical Engineering and Applied ElectronicsTechnology Ruan J. Logistics department of the 92962th army People's Liberation Army of China Beijing University of Technology Beijing 100124, China yinfanglong89@163.com Ruan J. Logistics department of the 92962th army People's Liberation Army of China Beijing University of Technology Beijing 100124, China yinfanglong89@163.com Guangzhou 510700, China hlrj84@163.com Abstract—In this paper, two kinds of different sliding bearing support structure including a traditional cross-shaft and a semi-shaft are designed for a water hydraulic pump.The characteristics of the two sliding bearings in each structure are calculated. By comparison, it is found that the working conditions of the two sliding bearings, especially the pv value, in the semi-shaft support structure are near to be identical in the cross-shaft one, which will be helpful to prolong their service life. Based on the Stress-strength interference theory, a reliability calculation model of the friction pair between the shaft and sliding bearings is proposed. The analysis results indicate that the semi-shaft sliding bearing support is beneficial to largely raise the inherent reliability of the water hydraulic pump as well as the service life of the pump. Keywords—water hydraulic pump; sliding bearing; pv value;Reliability Ⅰ.Introduction Water hydraulic system is operated with raw water(pure tap water) substituting for mineral oil. Such systems are becoming more and more popular, especially in the fields of steel and glass production, nuclear power generation, coal and gold mining, food and medicine processing, ocean exploration, and underwater robotics.Compared with conventional mineral oil, raw water that acts as hydraulic fluid has several inherent advantages,including low operating cost, sound environmental compatibility, non-flammability, and low pollution potential to products [1-2]. Water hydraulic axial piston pump (WHAP) is one of key power components in water hydraulic systems. There are several challenging issues associated with the pump,such as conflicts between lubrication and wear, and between sealing and leakage. Especially, shaft and bearings form key friction pairs, which will result in significant influences on the pump’s performance.Generally, the hydrodynamic sliding bearing is extensively used for supporting the water hydraulic pump’s shaft. Therefore, in order to improve the pump’s efficiency and reliability, it is crucial to study the force distribution of sliding bearings thoroughly. According to hydrodynamic lubrication theory, the critical points,which satisfies the wear resistance for sliding bearing and shaft of WHAP includes: (1) An optimal load distributed strategy should be used to determine optimal dimensions for achieving the even distributing of the load. (2) Several suitable materials should be selected to meet the water lubrication working conditions and to ensure a long life with lower friction losses [3]. The concepts of both stress and strength relating to reliability design are generalized. In this paper, thereliability of sliding bearing support will be investigated using Stress-strength interference model to calculate the reliability value of the sliding bearings, which will include the effect of the flow fluctuation in WHAP. II. Description of sliding bearing support Figure (a) shows a schematic of a typical cross-shaft supporting structure. The cylinder block is supported on the shaft. Two sliding bearings are located on the cylinder’s left and right ends to support the shaft. Figure (b) shows a schematic of a novel design, where a semi-shaft supporting structure is employed. The front sliding bearing is used to support the input shaft (spline shaft). And the rear sliding bearing inside the cylinder is used to support the cylinder block. In the semi-shaft support structure, the spline shaft and cylinder are interference fit, and they are combined by a spline.During pump running, the motor drives input shaft rotating, bringing along the rotation of the cylinder.Because of the presence of the angle of swash plate, the whirling motion of the cylinder is translated into straight reciprocating motion of the pistons. When the cylinder rotated a period, the pistons reciprocate a round-trip to complete a process of suction and discharge of the pump. (a) cross-shaft support (b) semi-shaft support Fig. 1 Schematic diagram of sliding bearing support III. Theoretical analyses A. Load characteristics of the bearings.As shown in Figure 1, the reaction component force that act on a single slipper along X-axis and Z-axis can be respectively described as follows: In terms of the axial piston pump, the hydraulic pressure in each piston hole can be represented as: Then the radial resultant force is located in point O (as shown in Figure 1), and the radial resultant force can be expressed as: Furthermore, with the radial force equilibrium along the X-axis of the supporting structure, we have: The torque equilibrium along the X-axis can be written as: Through solving Eqs. (4) – (6), the supporting force of the front and rear bearings can be obtained, respectively: B. PV value of the bearings For the valve plate distribution of axial piston pump,the number of pistons within the discharge pressure area (Zg) during one operating period is variably along with the reciprocating motion of the pistons. Ignoring the influence of the pressure pulsation in the pre-loading and pre-unloading areas, and the cylinder weight, affected by the alternative vibration of the number of piston in the discharge pressure area, the sliding bearing is subjected to periodic unstable loads. Water is characterized by very low dynamical viscosity, which is regarded as poor lubricating properties affecting the performance of sliding and rolling contacts [4]. Here it appears that it is impossible to obtain an acceptable film thickness in water lubricated sliding bearings. Consequently, in practical work, the sliding bearings in WHAP are usually working under the condition of an incomplete liquid lubrication. Especially, at the points of turn on / off, the direct contacts between the matching pairs of the shaft and sliding bearings may take place. Moreover, since it is necessary for the sliding bearings the surface hardness should be as high as possible in order to sustain contacting pressure, and thus, the abrasion between the shaft and bearings would be as low as possible in order to improve the sliding bearings’ reliability. It is essential to select several suitable materials and matching pair. The siding bearings in this paper are made of WR525, which is a thermoplastic composite consisting of carbon fiber in a PEEK matrix. Due to its unique thermal expansion properties, WR525 is ideal for use as impeller wear rings, bushings and case wear rings.WR525 allows the pump user to increase pump efficiency by running tighter wear ring clearances, while decreasing potential pump damage when pumps are cavitated or experience down-line bearing failures. WR525 bearings are specified as standard material on all HGM/HGM-RO boiler feed pumps. As it is known, the critical pv value is a very important parameter for polymers or their composites in tribological applications, and has been widely used in investigation of ploymers’ sliding wear behaviors. Besides, pv limits are affected by variations in temperature, speed,loading,lubrication and surface finish. Exceeding pv limits will result in accelerated wear and premature bearing failure, where p is the intensity of pressure applied to a bearing surface and v is the relative velocity [5]. Furthermore, the pv value is proportional to bearing’s wear, friction power loss and friction heat [6]. Wear, friction power loss and temperature conditions are the three key index of the service life of the bearings. Therefore, the pv value can be used to preliminarily evaluate the sliding bearings’working life in a WHAP. Generally speaking, in order to guarantee the boundary lubricated bearing running reliably, it is necessary to meet the following three conditions [7]: Bearing’s average working specific pressure is: Substituting Eqs. (7) and (8) into Eq. (10), average working specific pressure of the front bearing can be obtained as: And average working specific pressure of the rear bearing can be represented as: Radial circumferential velocity of the shaft is: The friction specific work rate of sliding bearing can be expressed as Substituting Eqs. (11) – (13) into Eq. (14), the friction specific work rate of the front bearing can be obtained as follows: And the friction specific work rate of the rear bearing is calculated as follows: Based on the structure parameters of the WHAP, taking the peak number of pistons in the discharge pressure area (Zg), the working conditions of the bearings under the two different structures are calculated in Table1. C. Scale factor Actually, analyzing Eqs. (10), (11), (14) and (15), it is found that the dz, B andinfluence the match of the two bearings’ working conditions. Define the bearings’linear velocity ratio asaverage specific work rate ratio asThen we have: The three parameters mentioned above can be calculated (as shown in Table 2). D. Reliability model and evaluation In terms of a WHAP, design of the sliding bearing is an important part for raising its reliability. In this paper, the pv value is defined as the stress between the sliding bearing friction pair-Y, and it is a random variable. The allowable pv value [pv] can be defined as the strength-X. Generally speaking, the contact stress p between the friction pair and the relative linear velocity v are mutually independent random variables, and they are all distributed normally, so the product pv is also distributed normally.Thus, according to the formula when the stress and strength are all distributed normally, the reliability coefficientcan be determined by means of the equation: In fact, the pv or allowable pv value can be expressed by the two random variables Pd and ： K is constant coefficient. Pd is the working pressure of the pump and ω is the relative angular velocity. Based on probability theory, the average value and the standard deviation can be obtained, respectively: Through solving Eqs. (22) and (23), we have: The rated pressure of the WHAP can be allowed for fluctuating within ±5%. According to the definition of mean value and the principle of3σ , we have: The allowable pv value [pv] of WR 525 is 8.89MPam/s, and its standard deviation [ pv] s is 0.315.Substituting Eqs. (24) – (28) and their corresponding data into Eq. (20), the reliability coefficient R u of the two kinds of structure can be calculated respectively. Hence, the corresponding reliability R for each structure can be obtained, as listed in Table 3. IV. Discussion In terms of the WHAP, the failure of any sliding bearing could destroy the pump’s supporting and balance to cause severe noise and vibration. It also could lead to the invalidation of the flow distribution and make the volumetric efficiency decrease sharply. Thus, service life of WHAP is determined by the bearing which has the severe working condition. Table 1 presents the calculated results of the key parameters in two different sliding bearings distribution structure. It indicates that the working conditions of the sliding bearings in each distribution structure are different.Firstly, the center distance L2 in the semi-shaft structure is smaller than the cross-shaft one. This means that the rear bearing in the semi-shaft structure is closer to the center point of the resultant force, and the distance between the front and bearing is also smaller. Thus it is favorable to balance the torque of F1 and F2 so that making the sliding bearings work smoothly. Secondly, the loads on the sliding bearings in each structure are different. In the cross-shaft structure, the loads on the front bearing are much larger than on the rear one. However, in the semi-shaft structure, the loads on the front bearing reduced, while the loads on the rear bearing increased, so as to make the bearings’ supported load condition in the front and rear location closely and their loads distributed evenly. Additionally, the front bearing’s average working specific pressure (pz) and its pv value in the cross-shaft structure, are much larger than the rear one. However, in the semi-shaft structure, the front bearing’s pz and pv value reduced slightly, for which the rear bearing increases a little. Comparing the results listed in Table 2, it can be seen that thevalue of the semi-shaft structure are smaller than which are in the cross-shaft structure. Moreover, these values are close to 1. It is revealed that in the semi-shaft structure, the working conditions of the two sliding bearings are near to be identical. From Table 3, the reliability value of the siding bearings support in the semi-shaft structure are higher. It is indicated that the sliding bearings of the semi-shaft have longer service life than those in the cross-shaft.Consequently, it can be concluded that the distribution of sliding bearings in the semi-shaft structure is beneficial to make the bearings’ working conditions equilibrium and to improve the reliability of the pump. V. Conclusion In this research, two sliding bearings of the WHAP which have the same size work in the same water medium in same time. So the change law of loads on the bearings similar. Besides, they are made of the same material: WR525. Hence, the life of the two sliding bearing support structure depends on the bearing which has higher working conditions especially the pv value. So it is important to design a rational structure arrangement to make the two bearings’ working conditions as equal as possible. Consequently, for the sake of raising the sliding bearing’s life in the WHAP, the scale factorsmust be close to 1. Additionally, the degree of reliability is a main indicator for the reliability of the sliding bearing support structure. So the reliability value of the sliding bearing support structure should be as large as possible for improving the WHAP’s reliability. By comparing the working conditions of the sliding bearings in each structure, it is found that the pv value of the two sliding bearings in the semi-shaft structure are closer than in the cross-shaft one. And the scale factorof the semi-shaft structure are closer to 1, compared to the cross-shaft one. Additionally, the reliability value of the sliding bearings in the semi-shaft structure is higher than which in the cross-shaft one.Obviously, all the comparisons mentioned above show that the arrangement of sliding bearings in the semi-shaft structure does a better job in achieve the purpose of distributing the load averagely and raising the service life of the sliding bearings in the water hydraulic piston pump as well as improving the reliability of WHAP. ACKNOWLEDGMENT This research was funded by Natural Science Foundations of China (№s 50675074 and 51075007), NCET of State Education Ministry (№ NCET-07-0330), and PHR (IHLB) 20090203. REFERENCES Nomenclature The author;Yin F.L. Nie S.L. Ruan J. Nationality:China Source:The 2011 International Conference on Fluid Power and Mechatronics, Beijing, August 16-17, 2011, 282-286. 研究的可靠性,滑動(dòng)軸承支撐斜盤式軸向柱塞泵型水液壓 Yin F.L., Nie S.L. 大學(xué)的機(jī)械工程和應(yīng)用ElectronicsTechnology Ruan J. 中國(guó) 北京 北京科技大學(xué) 中國(guó)人民解放軍 物流部門的92962部隊(duì) 100124 Yinfanglong89@163.com 中國(guó) 廣州 hlrj84@163.com 510700 文摘-在本文中,兩種不同的滑動(dòng)軸承支撐結(jié)構(gòu)包括一個(gè)傳統(tǒng)的十字軸和半軸,被設(shè)計(jì)為--水液壓泵?；瑒?dòng)軸承在每個(gè)結(jié)構(gòu)計(jì)算。相比之下,特別是兩個(gè)根據(jù)應(yīng)力-強(qiáng)度干涉理論,一個(gè)可靠性計(jì)算模型之間的摩擦副軸和提出了滑動(dòng)軸承。分析結(jié)果表明,半軸滑動(dòng)軸承的支持是有益的,很大程度上提高固有可靠性的水液壓泵以及泵的使用壽命。 滑動(dòng)軸承pv值,在半軸支撐結(jié)構(gòu)都是相同的附近的十字軸,這將有助于延長(zhǎng)其使用壽命。 關(guān)鍵詞—水液壓泵;滑動(dòng)軸承;pv值;可靠性 Ⅰ介紹 水液壓系統(tǒng)的原始水(純自來水)取代了礦物油。這種系統(tǒng)正變得越來越流行,尤其是在田野的鋼鐵和玻璃生產(chǎn)、核電、煤炭、黃金礦業(yè)、食品和醫(yī)藥處理、海洋探險(xiǎn),水下機(jī)器人。與傳統(tǒng)的礦物油,原水,充當(dāng)液壓流體有幾個(gè)固有優(yōu)勢(shì),包括更低的運(yùn)營(yíng)成本、合理的環(huán)境兼容性、耐燃性、低污染潛力產(chǎn)品[1-2]。 水液壓軸向柱塞泵(重?fù)?是一個(gè)關(guān)鍵的動(dòng)力組件在水液壓系統(tǒng)。有幾個(gè)挑戰(zhàn)性問題相關(guān)的泵,如沖突之間,潤(rùn)滑和穿密封和泄漏。特別是,軸和軸承形式主要摩擦副,這將導(dǎo)致顯著影響泵性能。通常,水動(dòng)力滑動(dòng)軸承是廣泛用于支持水液壓泵的軸。因此,為了提高泵的效率和可靠性,這是至關(guān)重要的,研究了滑動(dòng)軸承力分布的徹底。根據(jù)流體動(dòng)力潤(rùn)滑理論,關(guān)鍵的點(diǎn),這滿足了耐磨性的滑動(dòng)軸承和軸的重?fù)舭?(1)一個(gè)最佳負(fù)載分布策略應(yīng)該用于確定最優(yōu)尺寸對(duì)實(shí)現(xiàn)甚至分發(fā)的負(fù)載。(2)幾個(gè)應(yīng)該選擇合適的材料,以滿足水潤(rùn)滑的工作條件,確保一個(gè)長(zhǎng)壽命和低摩擦損失[3]。 二者的概念的應(yīng)力和強(qiáng)度可靠性設(shè)計(jì)有關(guān)的推廣。在本文中,可信度的滑動(dòng)軸承的支持將被采用了應(yīng)力-強(qiáng)度干涉模型來計(jì)算可靠性價(jià)值的滑動(dòng)軸承,這將包括流動(dòng)的影響波動(dòng)。 Ⅱ描述的滑動(dòng)軸承的支持 圖(a)展示了一個(gè)示意性的一個(gè)典型的十字軸支承結(jié)構(gòu)。缸體的軸上的支持。兩個(gè)滑動(dòng)軸承位于汽缸的左和右端支持軸。圖(b)顯示了一個(gè)新穎的設(shè)計(jì)原理,在那里一個(gè)半軸支承結(jié)構(gòu)采用。前面的滑動(dòng)軸承是用來支持輸入軸(花鍵軸)。和后方滑動(dòng)軸承在氣缸內(nèi)用于支持缸體。在半軸支撐結(jié)構(gòu)、花鍵軸和圓柱干涉配合,他們結(jié)合的花鍵。在泵運(yùn)行時(shí),馬達(dá)驅(qū)動(dòng)器輸入軸旋轉(zhuǎn),帶上的旋轉(zhuǎn)圓筒。因?yàn)榇嬖诘姆啦ò宓慕嵌?旋轉(zhuǎn)運(yùn)動(dòng)的缸是翻譯成直線往復(fù)運(yùn)動(dòng)的活塞。當(dāng)缸旋轉(zhuǎn)一個(gè)時(shí)期,活塞往復(fù)運(yùn)動(dòng)的往返來完成一個(gè)過程的入口及出口的泵。 （a） 十字軸的支持 （b）半軸的支持 圖1示意圖的滑動(dòng)軸承的支持 Ⅲ理論分析 a的負(fù)荷特性軸承。如圖1所示,反應(yīng)分力,作用于一個(gè)滑塊沿著x軸和z軸可以分別描述如下: 在術(shù)語的軸向柱塞泵、液壓在每個(gè)活塞孔可以表示為: 然后徑向合力位于點(diǎn)O(如圖1),和徑向合力可以表述為: 此外,由于徑向力平衡沿著x軸的支承結(jié)構(gòu),我們有: 沿著x軸的扭矩平衡可以寫成: 通過求解方程式。(4)-(6),支持力量的前后軸承可以分別獲得: B PV值的軸承 對(duì)于閥板分布的軸向柱塞泵,活塞的數(shù)量在放電壓力區(qū)(Zg)在一個(gè)操作周期是不定地隨著活塞的往復(fù)運(yùn)動(dòng)。忽略壓力脈動(dòng)的影響在預(yù)加載和pre卸貨區(qū),汽缸重量,受替代振動(dòng)的數(shù)量活塞在放電壓力區(qū),滑動(dòng)軸承受到周期性不穩(wěn)定的負(fù)載。水具有非常低的動(dòng)力粘度,它被認(rèn)為是貧窮的潤(rùn)滑性能影響性能的滑動(dòng)和滾動(dòng)接觸[4]。這里似乎是不可能獲得一個(gè)可接受的膜厚度在水潤(rùn)滑滑動(dòng)軸承。因此,在實(shí)際工作,滑動(dòng)軸承在打敗通常工作條件下的一個(gè)不完整的液體潤(rùn)滑。特別是,在點(diǎn)開/關(guān),直接接觸摩擦副之間的滑動(dòng)軸承的軸和可能發(fā)生。此外,因?yàn)樗潜匾幕瑒?dòng)軸承表面硬度應(yīng)該盡可能高的為了維持接觸壓力,因此,磨損的軸和軸承之間會(huì)盡可能低為了提高滑動(dòng)軸承的可靠性。 它是必要的選擇幾個(gè)合適的材料和匹配的一對(duì)。外墻軸承在本文是由WR525,這是一種熱塑性復(fù)合構(gòu)成的碳纖維在PEEK矩陣。由于其獨(dú)特的熱膨脹性能,非常適合用作WR525葉輪磨損環(huán)、襯套和案例穿環(huán)。WR525允許泵用戶增加泵效率進(jìn)行更嚴(yán)格的穿環(huán)間隙,同時(shí)減少潛在的泵損壞當(dāng)泵cavitated或經(jīng)驗(yàn)的下線軸承故障。WR525軸承被指定為標(biāo)準(zhǔn)物質(zhì)在所有HGM / HGM-RO鍋爐給水泵。 眾所周知,關(guān)鍵的pv值是一個(gè)非常重要的參數(shù)對(duì)聚合物或他們的復(fù)合材料在摩擦學(xué)的應(yīng)用程序,并已廣泛應(yīng)用于調(diào)查ploymers“滑動(dòng)磨損行為。此外,pv極限溫度變化的影響、速度、加載,潤(rùn)滑和表面光潔度。超過光伏限制將導(dǎo)致加速磨損和過早軸承故障,p是壓力強(qiáng)度應(yīng)用于軸承表面,v是相對(duì)速度[5]。此外,pv值成正比軸承的磨損、摩擦功率損耗和摩擦熱[6]。穿,摩擦功率損耗和溫度條件下的三個(gè)關(guān)鍵指標(biāo)的軸承的使用壽命。因此,pv值可用于初步評(píng)估滑動(dòng)軸承的工作生活在一個(gè)重?fù)?。一般來說,為了保證邊界潤(rùn)滑軸承運(yùn)行可靠,必須滿足以下三個(gè)條件[7]: 軸承的平均工作特定壓力是: 取代方程式。(7)和(8)到Eq。(10),平均單位壓力的工作前軸承可以得到: 和平均單位壓力的工作后軸承可以表示為: 徑向圓周速度的軸是: 具體工作率的摩擦滑動(dòng)軸承可以表達(dá)為 取代方程式。(11)-(13)到Eq。(14),摩擦具體工作率的前軸承可以得到如下: 和摩擦率的具體工作后軸承是計(jì)算方式如下: 基于結(jié)構(gòu)參數(shù)的重?fù)?采取的峰值活塞在放電壓力區(qū)(Zg),工作條件下的軸承的兩個(gè)不同的結(jié)構(gòu)計(jì)算中。 C 比例因子 實(shí)際上,分析方程式。(10),(11),(14)和(15),它是發(fā)現(xiàn)dz,B 和比賽的兩個(gè)軸承工作條件。定義軸承'linear速度比特定工作率比我們有: 上面提到的三個(gè)參數(shù)可以計(jì)算(如表2所示)。 D 可靠性模型和評(píng)價(jià) 從一個(gè)重?fù)?滑動(dòng)軸承的設(shè)計(jì)是一個(gè)重要的部分為提高其可靠性。摘要pv值定義為應(yīng)力之間的滑動(dòng)軸承摩擦副y,它是一個(gè)隨機(jī)變量。允許的pv值(pv)可以被定義為強(qiáng)度x。一般來說,接觸應(yīng)力p之間的摩擦副和相對(duì)線速度v是相互獨(dú)立的隨機(jī)變量,并且他們都是正態(tài)分布,所以產(chǎn)品pv也正態(tài)分布。因此,根據(jù)公式當(dāng)壓力和強(qiáng)度都是分布式通?？煽啃韵禂?shù)可以確定通過方程: 事實(shí)上,pv或容許pv值可以表示為兩個(gè)隨機(jī)變量Pd和: K是常數(shù)系數(shù)。Pd是工作壓力的泵和角速度ω是相對(duì)的?；诟怕世碚?平均值和標(biāo)準(zhǔn)偏差分別可以得到: 通過求解方程式。(22)和(23日),我們有: 額定壓力的重?fù)艨梢员辉试S在±5%的波動(dòng)。根據(jù)定義的平均值和of3σ原則,我們有: 允許的pv值(pv)的525年是8.89 mpam WR / s,其標(biāo)準(zhǔn)偏差(pv)年代是0.315。取代方程式。(24)-(28)和相應(yīng)的數(shù)據(jù)轉(zhuǎn)換成Eq。(20),可靠性系數(shù)R u的兩種結(jié)構(gòu)可以分別計(jì)算。因此,相應(yīng)的可靠性R可以得到每一個(gè)結(jié)構(gòu),如表3所示。 Ⅳ討論 在術(shù)語的重?fù)?任何一個(gè)失敗的滑動(dòng)軸承可以摧毀泵的支持和平衡造成嚴(yán)重的噪音和振動(dòng)。它還可能導(dǎo)致的失效流分布和使容積效率大幅下降。因此,使用壽命的重?fù)羰怯奢S承具有嚴(yán)重的工作條件。 表1給出了計(jì)算結(jié)果的關(guān)鍵參數(shù)在兩個(gè)不同的滑動(dòng)軸承分布結(jié)構(gòu)。它表明,滑動(dòng)軸承的工作條件在每個(gè)分布結(jié)構(gòu)是不同的。首先,該中心距離L2在半軸結(jié)構(gòu)是小于十字軸一。這意味著后軸承在半軸結(jié)構(gòu)接近中心點(diǎn)的合力,之間的距離也變小前和軸承。因此它有利于平衡扭矩的F1和F2,以便使滑動(dòng)軸承工作順利。其次,對(duì)滑動(dòng)軸承載荷在每個(gè)結(jié)構(gòu)是不同的。在十字軸結(jié)構(gòu)、負(fù)載前軸承是遠(yuǎn)遠(yuǎn)大于背面的一個(gè)。然而,在半軸結(jié)構(gòu)