22絞肉機的設計,22,絞肉機,設計 故障的分析、尺寸的決定以及凸輪的分析和應用前言介紹：作為一名設計工程師有必要知道零件如何發(fā)生和為什么會發(fā)生故障，以便通過進行最低限度的維修以保證機器的可靠性。有時一次零件的故障或者失效可能是很嚴重的一件事情，比如，當一輛汽車正在高速行駛的時候，突然汽車的輪胎發(fā)生爆炸等。另一方面，一個零件發(fā)生故障也可能只是一件微不足道的小事，只是給你造成了一點小麻煩。一個例子是在一個汽車冷卻系統(tǒng)里的暖氣裝置軟管的松動。后者發(fā)生的這次故障造成的結果通常只不過是一些暖氣裝置里冷卻劑的損失，是一種很容易被發(fā)現并且被改正的情況。能夠被零件進行吸收的載荷是相當重要的。一般說來，與靜載重相比較，有兩個相反方向的動載荷將會引起更大的問題，因此，疲勞強度必須被考慮。另一個關鍵是材料是可延展性的還是脆性的。例如，脆的材料被認為在存在疲勞的地方是不能夠被使用的。很多人錯誤的把一個零件發(fā)生故障或者失效理解成這樣就意味著一個零件遭到了實際的物理破損。無論如何，一名設計工程師必須從一個更廣泛的范圍來考慮和理解變形是究竟如何發(fā)生的。一種具有延展性的材料，在破裂之前必將發(fā)生很大程度的變形。發(fā)生了過度的變形，但并沒有產生裂縫，也可能會引起一臺機器出毛病，因為發(fā)生畸變的零件會干擾下一個零件的移動。因此，每當它不能夠再履行它要求達到的性能的時候，一個零件就都算是被毀壞了（即使它的表面沒有被損毀）。有時故障可能是由于兩個兩個相互搭配的零件之間的不正常的磨擦或者異常的振動引起的。故障也可能是由一種叫蠕變的現象引起的，這種現象是指金屬在高溫下時一種材料的塑性流動。此外，一個零件的實際形狀可能會引起故障的發(fā)生。例如，應力的集中可能就是由于輪廓的突然變化引起的，這一點也需要被考慮到。當有用兩個相反方向的動載荷，材料不具有很好的可延展性時，對應力考慮的評估就特別重要。 一般說來，設計工程師必須考慮故障可能發(fā)生的全部方式，包括如下一些方面：——壓力——變形——磨損——腐蝕——振動——環(huán)境破壞——固定設備松動在選擇零件的大小與形狀的時候，也必須考慮到一些可能會產生外部負載影響的空間因素，例如幾何學間斷性，為了達到要求的外形輪廓及使用相關的連接件，也會產生相應的殘余應力。凸輪是被應用的最廣泛的機械結構之一。凸輪是一種僅僅有兩個組件構成的設備。主動件本身就是凸輪，而輸出件被稱為從動件。通過使用凸輪，一個簡單的輸入動作可以被修改成幾乎可以想像得到的任何輸出運動。常見的一些關于凸輪應用的例子有：——凸輪軸和汽車發(fā)動機工程的裝配——專用機床——自動電唱機——印刷機——自動的洗衣機——自動的洗碗機高速凸輪(凸輪超過 1000 rpm 的速度)的輪廓必須從數學意義上來定義。無論如何，大多數凸輪以低速(少于 500 rpm)運行而中速的凸輪可以通過一個大比例的圖形表示出來。一般說來，凸輪的速度和輸出負載越大，凸輪的輪廓在被床上被加工時就一定要更加精密。材料的設計屬性當他們與抗拉的試驗有關時，材料的下列設計特性被定義如下。靜強度：一個零件的強度是指零件在不會失去它被要求的能力的前提下能夠承受的最大應力。因此靜強度可以被認為是大約等于比例極限，從理論上來說，我們可以認為在這種情況下，材料沒有發(fā)生塑性變形和物理破壞。剛度：剛度是指材料抵抗變形的一種屬性。這條斜的模數線以及彈性模數是一種衡量材料的剛度的一種方法。彈性：彈性是指零件能夠吸收能量但并沒有發(fā)生永久變形的一種材料的屬性。吸收的能量的多少可以通過下面彈性區(qū)域內的應力圖表來描述出來。韌性：韌性和彈性是兩種相似的特性。無論如何，韌性是一種可以吸收能量并且不會發(fā)生破裂的能力。因此可以通過應力圖里面的總面積來描述韌性，就像用圖 2.8 b 描繪的那樣。顯而易見，脆性材料的韌性和彈性非常低，并且大約相等。脆性：一種脆性的材料就是指在任何可以被看出來的塑性變形之前就發(fā)生破裂的材料。脆性的材料一般被認為不適合用來做機床的零部件，因為當遇到由軸肩，孔，槽，或者鍵槽等幾何應力集中源引起的高的應力時，脆性材料是無法來產生局部屈服的現象以適應高的應力環(huán)境的。延展性：一種延展性材料會在破裂之前表現出很大程度上的塑性變形現象。延展性是通過可延展的零件在發(fā)生破裂前后的面積和長度的百分比來測量的。一個在發(fā)生破裂的零件，其伸長量如果為 5%，則認為該伸長量就是可延展性和脆性材料分界線。可鍛性：可鍛性從根本上來說是指材料的一種在承受擠壓或壓縮是可以發(fā)生塑性變形的能力，同時，它也是一種在金屬被滾壓成鋼板時所需金屬的重要性能。硬度：一種材料的硬度是指它抵抗擠壓或者拉伸它的能力。一般說來，材料越硬，它的脆性也越大，因此，彈性越小。同樣，一種材料的極限強度粗略與它的硬度成正比。機械加工性能（或切削性）：機械加工性能是指材料的一種容易被加工的性能。通常，材料越硬，越難以加工。壓應力和剪應力除抗拉的試驗之外，還有其它一些可以提供有用信息的靜載荷的實驗類型。壓縮測試：大多數可延展材料大約有相同特性，當它們處于受壓狀態(tài)的緊張狀態(tài)時。極限強度，無論如何，不能夠被用于評價壓力狀態(tài)。當一件具有可延展性的樣品受壓發(fā)生塑性變形時，材料的其它部分會凸出來，但是在這種緊張的狀態(tài)下，材料通常不會發(fā)生物理上的破裂。因此，一種可延展的材料通常是由于變形受壓而損壞的，并不是壓力的原因。 剪應力測試：軸，螺釘，鉚釘和焊接件被用這樣一種方式定位以致于生產了剪應力。一張抗拉試驗的試驗圖紙就可以說明問題。當壓力大到可以使材料發(fā)生永久變形或發(fā)生破壞時，這時的壓力就被定義為極限剪切強度。極限剪切強度，無論如何，不等于處于緊張狀態(tài)的極限強度。例如，以鋼的材料為例，最后的剪切強度是處于緊張狀態(tài)大約極限強度的 75%。當在機器零部件里遇到剪應力時，這個差別就一定要考慮到了。動力載荷不會在各種不同的形式的力之間不停發(fā)生變化的作用力被叫作靜載荷或者穩(wěn)定載荷。此外，我們通常也把很少發(fā)生變化的作用力叫作靜載荷。在拉伸實驗中，被分次、逐漸的加載的作用力也被叫作靜載荷。另一方面，在大小和方向上經常發(fā)生變化的力則被稱為動載荷。動載荷可以被再細分為以下的 3 種類型。變載荷：所謂變載荷，就是說載荷的大小在變，但是方向不變的載荷。比如說，變載荷會產生忽大忽小的張應力，但不會產生壓應力。周期性載荷：像這樣的話，如果大小和方向同時改變，則就是說這種載荷會反復周期性的產生變化的拉應力和壓應力，這種現象往往就伴隨著應力在方向和大小上的周期性變化。沖擊載荷：這類載荷是由于沖擊作用產生的。一個例子就是一臺升降機墜落到位于通道底部的一套彈簧裝置上，這套裝置產生的力會比升降機本身的重量大上好幾倍。當汽車的一個輪胎碰撞到道路上的一個突起或者路上的一個洞時，相同的沖擊荷載的類型也會在汽車的減震器彈簧上發(fā)生。疲勞失效－疲勞極限線圖正如圖 2.10a 所示，如果材料的某處經常會產生大量的周期性作用力，那么在材料的表面就很可能會出現裂縫。裂縫最初是在應力超過它極限壓力的地方開始出現的，而通常這往往是有微小的表面缺陷的地方，例如有一處材料出現瑕疵或者一道極小的劃痕。當循環(huán)的次數增加時，最初的裂縫開始在軸的周圍的逐漸產生許多類似的裂縫。所以說，第一道裂縫的意義就是指應力集中的地方，它會加速其它裂縫的產生。一旦整個的外圍斗出現了裂縫，裂縫就會開始向軸的中心轉移。最后，當剩下的固體的內部地區(qū)變得足夠小，且當壓力超過極限強度時，軸就會突然發(fā)生斷裂。對斷面的檢查可以發(fā)現一種非常有趣的圖案，如圖 2.13 中所示。外部的一個環(huán)形部分相對光滑一些，因為原來表面上相互交錯的裂縫之間不斷地發(fā)生磨擦導致了這種現象的產生。無論如何，中心部分是粗糙的，表明中心是突然發(fā)生了斷裂，類似于脆性材料斷裂時的現象。這就表明了一個有趣的事實。當正在使用的機器零件由于靜載荷的原因出現問題時，由于材料具有的延展性，他們通常會發(fā)生一定程度的變形。盡管許多地由于靜壓力導致的零件故障可以通過頻繁的做實際的觀察并且替換全部發(fā)生變形的零件來避免。不管怎樣，疲勞失效有助于起到警告的作用。汽車中發(fā)生故障的零件中的 90%的原因都是因為疲勞的作用。一種材料的疲勞強度是指在壓力的反復作用下的抵抗產生裂縫的能力。持久極限是用來評價一種材料的疲勞強度的一個重要參數。進一步說明就是，持久極限就是指在無限循環(huán)的作用力下不引起失效的壓力值。讓我們回頭來看在圖 2.9 所示的疲勞試驗機器的。試驗是這樣被進行的：一件小的重物被插入，電動機被啟動。在試樣的失效過程中，由計算寄存器記錄下循環(huán)的次數 N，并且彎曲壓力的相應最大量由第 2.5 方程式計算。然后用一個新的樣品替換掉被毀壞的樣品，并且將另一個重物插入以增加負荷量。壓力的新的數值再次被計算，并且相同的程序再次被重復進行，直到零件的失效只需要一個完整周期時為止。然后根據壓力值和所需的循環(huán)的次數來繪制一個圖。正如圖表 2.14a 所示圖形，該圖被稱為持久極限曲線或者 S-N 曲線。由于這需要的前提是要進行無限次的循環(huán)，所以我們可以以 100 萬個循環(huán)用來作循環(huán)參考單位。因此，持久極限可以從圖表 2.14a 那里看到，該材料是在承受了 100萬個循環(huán)后而沒有發(fā)生失效的。 用圖 2.14 描繪的關系對于鋼的材料來說更為典型，因為當 N 接近非常大的數字時，曲線就會變得水平。因此持久極限等于曲線接近一條水平的切線時的壓力水平。由于包含了大量的循環(huán)，在繪圖時，N 通常會被按照對數標度來畫，如圖 2.14 b 中所示。當采用這樣的方法做時，水平的直線就可以更容易發(fā)現材料的持久極限值。對于鋼的材料來說，持久極限值大約等于極限強度的 50%。無論如何，已經加工完成的表面如果不是一樣的光滑，持久極限的值就會被降低。例如，對于鋼材料的零件來說，63 微英寸（ μin ）的機械加工的表面，零件的持久極限占理論的持久極限的百分比降低到了大約 40%。而對于粗糙的表面來說 （300μin ，甚至更多），百分比可能降低到 25%左右的水平。最常見的疲勞損壞的類型通常是由于彎曲應力所引起的。其次就是扭應力導致的失效，而由于軸向負載引起的疲勞失效卻極少發(fā)生。彈性材料通常使用從零到最大值之間變化的剪應力值來做實驗，以此來模擬材料實際的受力方式。就一些有色金屬而論，當循環(huán)的次數變得非常大時，疲勞曲線不會隨著循環(huán)次數的增大而變得水平。，而疲勞曲線的繼續(xù)變小，表明不管作用力有多么的小，多次的應力反復作用都會引起零件的失效。這樣的一種材料據說沒有持久極限。對于大多數有色金屬來說，它們都有一個持久極限，數值大小大約是極限強度的 25%。溫度對屈服強度和彈性模數的影響一般說來，當在說明一種擁有特殊的屬性的材料時，如彈性模數和屈服強度，表示這些性能在室溫環(huán)境下就可以存在。在低的或者較高的溫度下，材料的特性可能會有很大的不同。例如，很多金屬在低溫時會變得更脆。此外，當溫度升高時，材料的彈性模數和屈服強度都會變差。圖 2.23 顯示了低碳鋼的屈服強度在從室溫升高到 1000oC 過程中被降低了大約 70%。當溫度升高時，圖 2.24 顯示了低碳鋼在彈性模數 E 方面的削減。正如從圖上可以看見的那樣，彈性模數在從室溫升高到 1000oC 過程中大約降低了 30%。從這張圖表中，我們也能看到在室溫下承受了一定載荷而不會發(fā)生變形的零件卻可能在高溫時承受相同載荷時發(fā)生永久變形。蠕變： 一種塑性變形的現象由于溫度效應的影響，金屬中產生了一種被稱為蠕變的現象，一個承受了一定的載荷的零件的塑性變形是按照一個時間函數來逐漸增加的。蠕變現象在室溫的條件下也是存在的，但它發(fā)生的過程是如此之慢，以致于很少變得像在預期壽命中溫度被升高到 300oC 或更多時那樣顯著，逐漸增加的塑性變形可能在一段短的時期內變得很明顯。材料的抗蠕變強度是指材料抵抗蠕變的屬性，并且抗蠕變強度的數據可以通過處理長期的蠕變試驗(模擬實際零件的操作條件)來獲得。在試驗的過程中，給定的材料在規(guī)定的溫度下的塑性應變被被進行了實時監(jiān)控。由于蠕變是一種塑性變形現象，發(fā)生了蠕變的零件的尺寸可能就會被永久的改變。因此，如果一個零件是在很強的強度下運轉的話，那么設計工程師必須精確地預言將在機器的使用壽命期間可能發(fā)生的蠕變的次數。否則，與此伴隨的或者相關的問題就可能發(fā)生。在高溫下，當螺栓被用來緊固零件時，蠕變就可能變成一個必須解決的問題。處在壓力狀態(tài)下的螺釘，蠕變是按照一個時間函數來發(fā)生的。因為變形是塑性的，夾緊力的損失將可能導致螺紋連接件的意外松動。像這種特殊的現象，通常被稱為松弛，我們可以通過進行適當的蠕變強度時測試來確定是不是發(fā)生了蠕變。 圖 2.25 顯示了三種承受了恒定的張緊力的低碳鋼零件的典型的蠕變曲線。從中，我們可以注意到在高溫條件下，蠕變發(fā)生的速度逐漸加速，直到零件失效。從圖表里的時間軸上(x 軸)，我們可以描述在 10 年的時間里，這種產品的預期壽命?？偨Y機器設計者必須理解進行抗拉的靜止強度的測試目的。這種試驗可以確定被在設計方程式過程中使用的許多金屬的機械特性。像彈性模數，比例極限，屈服強度，彈性，以及延展性等等可以根據抗拉試驗來決定它們的特性。動載荷是指那些，在大小和方向上發(fā)生變化并且可能需要對機器零件在抵抗失效能力上的研究。由于應力的反復作用，允許使用的安全應力是基于材料的持久極限而不是基于屈服強度或者是極限強度。壓力集中在機器零件改變尺寸的位置發(fā)生，例如在一塊平的金屬板上的一個孔或者一塊平板、一個溝槽、一個圓軸上的皮帶在寬度方向上的突然變化。尤其是在一塊平板上或一塊條板上有一個孔的情況下，當孔的大小減少時，最大應力的值相對于平均應力變得大得多。減少的壓力集中影響的方法通常就是使在形狀上的變化更有規(guī)律性。被設計出來的機械零件被用于在低于屈服強度或者極限強度的一些允許的環(huán)境下使用。這種方法可以用來照顧到在加工期間像材料屬性的變化和殘余應力的產生這樣的未知因素， 以及用來做近似而不是精確計算的方程式。根據屈服強度或者極限強度來確定安全系數以決定安全應力的大小。溫度能影響金屬的機械特性。溫度的增加可能會引起金屬的熱脹和蠕變，并且還可能降低它的屈服強度和它的彈性模數。如果大多數金屬不被允許在溫度發(fā)生變化時發(fā)生膨脹或者收縮，那么壓力就會被當做載荷來看待。這現象在依靠干涉配合來進行零件裝配時是有益的。一個轂或者孔的內徑比與它相配的軸或者圓柱的直徑小一點。先將轂加熱后，由于熱脹冷縮，此時可以輕松的將軸插入其中。當它冷卻以后，同樣由于熱脹冷縮，它的內孔直徑會變小，從而對插入其中的軸產生了很大的摩擦力，有效的防止了軸的松動。計算機輔助制造構造的類型盤形凸輪. 這類凸輪是最受歡迎的類型之一，因為這種凸輪的設計和制造是比較簡單和容易的。如圖 6.1 所示的盤形凸輪?？梢宰⒁獾綇膭蛹苿拥搅伺c凸輪的旋轉軸垂直的位置。所有的凸輪都按照兩個不同的實體在運轉時不會互相碰撞的基本原理來運行。因此，隨著凸輪的旋轉（在這種情況下，一般是逆時針轉），從動件要么向上移動要么就接受適當的約束。我們應該把注意力集中于防止從動件發(fā)生粘接和使從動件的運動滿足生產的要求。當從動件向下移動時，彈簧需要使從動件的棍子和凸輪的輪廓保持。棍子是被用來減少齒輪接觸表面的磨擦力的。對于凸輪的每次旋轉來說，從動件通過對凸輪底部死點的沖擊使其移動到頂端。 圖 6.2 所示的是一個帶有一個尖頂從動件的盤形凸輪。復雜的動作可以通過這類從動件產生，因為一個點能夠精確地跟隨著凸輪輪廓的任何突然變化。無論如何，這種設計局限于負荷是非常小的應用里；否則兩個實體的接觸點將會被磨損掉，從而導致一系列的問題出現。盤形凸輪的兩個另外的變量分別是旋轉的從動件和從動件的偏移量，如圖 6.3所示。當需要的是旋轉的運動時，一個旋轉的從動件就會被使用。關于從動件的偏移量，我們需要注意從動件的偏移量的大小是取決于像壓力角和凸輪外輪廓等參數的，這兩個參數稍后將會被介紹。沒有偏移量的從動件被稱作同軸心的從動件。傳遞動力的凸輪：如圖 6.4 所描繪的被用來傳遞動力的凸輪。當凸輪朝著水平的方向傳遞運動時，從動件會產生上下滑動。從這里我們可以看出，一個旋轉的從動件和一個滑動的從動件都可以被使用。這種類型的動作通常會被用在一些生產用于凸輪上的產品的專用機床上。這種設計上的變化在旋轉和傳輸動力的三維的凸輪上體現了出來。例如，一塊手工制造的步槍原料被放在一臺專用車床上。這塊原料的形狀是要求能夠實現以各凸輪所要達到的功能。當它旋轉并傳輸動力時，從動件就可以控制用來把一塊木材加工成生產步槍原料的機床。 主動凸輪：在上述的凸輪設計中，凸輪和從動件之間在往返運動中保持接觸是通過彈簧力的作用來保證的。無論如何，處于高速運轉中的凸輪，用來保持凸輪和從動件之間的接觸的彈簧力可能會變得很大，這是由于凸輪在高速運動中的加速度會產生額外的動作用力，接觸的位置可能會發(fā)生變形。在這種情況下，接觸面可能產生過大的壓力，這樣將會導致零件過早的被磨損。主動凸輪是不需要彈簧的，因為從動件被迫在兩個方向上與凸輪接觸。這樣的主動凸輪可以分為 4 類：圓柱形的凸輪，開槽的盤形凸輪(也叫表面凸輪)，分型板凸輪，以及共軛凸輪。圓柱形凸輪：如圖 6.5 所示，圓柱形凸輪可以使從動件實現不斷的往復運動。圖 6.6 所示的是一個旋轉的從動件的應用實例。通過凸輪上槽溝的設計，我們可以實現使用幾個凸輪軸來完成從動件的圓周分布。開槽的盤形凸輪：在圖 6.8 上，我們可以看到一個帶有旋轉的從動件的分型板凸輪，但是這樣的設計也可以被用于傳遞動力的從動件上面。凸輪 E 和 F 一起繞著凸輪軸 B 旋轉。凸輪 E 始終保持與滾筒 C 接觸，而凸輪 F 則一直和滾筒D 保持著接觸。滾筒 C 和滾筒 D 都被安裝在一根直角杠桿上，而這個直角杠桿是繞著點 A 擺動的從動件。當凸輪 F 提供個滾筒 D 的需要的動作時，凸輪 E則被用于給滾筒 C 提供需要的動作。共軛凸輪．這種類型的凸輪，正如圖表 6.9 描述的那樣，由一個被安裝在凸輪軸偏心處的圓凸輪組成。從動件每次的擺度等于兩倍的凸輪的偏心矩 e。這樣的凸輪會生產簡諧振運動而沒有保留時間。下面更進一步的討論一下第 6.8 部分。計算機輔助制造的專有名詞在我們涉及凸輪的設計之前，我們很有必要知道各種各樣被用于鑒別凸輪的重要的設計參數?？匆幌孪聢D 6.11 中的術語。如果你把凸輪想像成是不動的，而從動件是繞著凸輪轉動的，那么，你將更容易理解對凸輪的描述。軌跡點：是指尖頂從動件的終點或者輥子中心或者輥子之類的從動件的終點。凸輪輪廓：凸輪的實際形狀?；鶊A：是指能夠畫出來的且與凸輪的輪廓線相切的最小的圓。它的中心也就是凸輪軸的中心。凸輪軸里的最小的半徑就是基圓的半徑。嚙合曲線：假定凸輪是固定不動的，從動件繞著凸輪旋轉的，那么，軌跡點的路徑就是嚙合曲線。優(yōu)圓：優(yōu)圓是指與嚙合曲線相切，且它的中心也在分配軸的中心的圓。壓力角：壓力角是指從動件的運動方向與節(jié)圓上輥子的中心所在的點之間的角度。凸輪外形：與凸輪輪廓相同。BDC：是 Bottom Dead Center 的縮寫，是指從動件離凸輪中心最近的位置。行程：是指從動件在 BDC 和 TDC 之間走過的路程的長度。高度上的行程：是指從動件從 BDC 轉到 TDC 的時高度的變化值。返程：是指從動件從 TDC 轉到 BDC 時所需時間。輪廓平行線：是指當凸輪在轉動時，從動件可以和凸輪的中心保持恒定的距離不變的軌跡。我們可以通過圖 6.12 獲得對壓力角的意義有一個更清楚、更深刻的理解。在這里，F T 是影響輥子的一個合力。在任何一個接觸點的地方，它一定是與表面垂直的。F T 的方向顯而易見不與從動件運動的方向平行。相反，它時通過壓力角α 來表明從動件的運動的方向的。因此，力 FT 可以被分解為水平方向的力 FH 和垂直方向的力 FV 兩部分。垂直分量是向上驅動從動件的那個力，因此，忽略了摩擦力，就等于從動件所受的力。水平方向的力沒有座有用功，但是它仍然是不可或缺的。事實上，它試圖使從動件能夠沿著它的方向走。這樣就可能會損壞從動件或者使從動件被卡死。很明顯，我們希望壓力角能夠盡可能的減小測向力的大小。一個實際的經驗法則是設計凸輪輪廓時，應使壓力角的度數不超過 30o 。壓力角的大小，一般說來，取決于從動件的以下四個參數： ——基圓的大小?！獜膭蛹鄬χ鲃蛹膱A心的偏移量的大小?！獫L筒直徑的大小?！馆嗇喞矫?取決于使用的從動件運動的從動件行程和類型)。如果凸輪的要求沒有改變，那么前面提到的一些參數就不能被改變。例如空間的限制。在我們已經學習過了如何設計凸輪之后，我們將學到減小壓力角的各種各樣的方法。湘潭大學興湘學院畢業(yè)論文（設計）任務書論文（設計）題目： 絞肉機的設計 學號：2006183822 姓名：李昌席 專業(yè)：機械設計制造及其自動化 指導教師： 系主任： 一、主要內容及基本要求 原料:肉類 生產動力: 螺旋供料器的轉速 n＝326r/min 要求:繪制總裝備圖 A01 張,其他元件圖周拆合為 1.5A0 圖 說明書 1 份 10000 字以上 全部激光打印 翻譯資料 1 份 3000 字符 光盤 2 張 二、重點研究的問題絞肉機的結構，工作原理以及完成對中等復雜程度機械的計算、結構設計等工作. 三、進度安排序號 各階段完成的內容 完成時間1 熟悉題目 調研 收集材料 第 1-2 周 2 方案設計 論證 第 3-4 周3 總體設計 機械設計計算 第 5-7 周4 繪制裝備圖 元件圖 第 8-11 周5 撰寫說明書 翻譯資料 第 12-13 周6 修改圖紙 打圖 第 14 周四、應收集的資料及主要參考文獻1 吳宗澤主編．機械設計實用手冊[M]．第一版．北京：化學工業(yè)出版社．1999 2 濮良貴、紀名剛主編．機械設計[M]．第七版．北京：高等教育出版社．2001 3 張裕中主編．食品加工技術裝備[M]．第一版．北京：中國輕工業(yè)出版社．2000 4 無錫輕工業(yè)學院、天津輕工業(yè)學院編．食品工廠機械與設備[M]．第二版．北京：輕工業(yè)出版社．1985 5 胡繼強主編．食品機械與設備[M]．第一版．北京：中國輕工業(yè)出版社．1999 6 李興國主編．食品機械學（下冊）V．第一版．四川：四川教育出版社．1992 7 中國農業(yè)機械化科學研究院編．實用機械設計手冊（下）[M]．北京：中國農業(yè)機械出版社．1985 8 成大先主編．機械設計手冊（第 4 卷）[M]．第四版．北京：化學工業(yè)出版社．2002 9 毛謙德、李振清主編．袖珍機械設計師手冊[M]．第二版．北京：機械工業(yè)出版社．2002 10 馬曉湘、鐘均祥主編．畫法幾何及機械制圖[M]．第二版．華南理工大學出版社1992 11 張萬昌主編．熱加工工業(yè)基礎 V．第一版．北京:高等教育出版社．1997 Failure Analysis， Dimensional Determination And Analysis， Applications Of Cams INTRODUCTION It is absolutely essential that a design engineer know how and why parts fail so that reliable machines that require minimum maintenance can be designed． Sometimes a failure can be serious， such as when a tire blows out on an automobile traveling at high speed． On the other hand， a failure may be no more than a nuisance． An example is the loosening of the radiator hose in an automobile cooling system． The consequence of this latter failure is usually the loss of some radiator coolant， a condition that is readily detected and corrected． The type of load a part absorbs is just as significant as the magnitude． Generally speaking， dynamic loads with direction reversals cause greater difficulty than static loads， and therefore， fatigue strength must be considered． Another concern is whether the material is ductile or brittle． For example， brittle materials are considered to be unacceptable where fatigue is involved． Many people mistakingly interpret the word failure to mean the actual breakage of a part． However， a design engineer must consider a broader understanding of what appreciable deformation occurs． A ductile material， however will deform a large amount prior to rupture． Excessive deformation， without fracture，may cause a machine to fail because the deformed part interferes with a moving second part． Therefore，a part fails(even if it has not physically broken)whenever it no longer fulfills its required function． Sometimes failure may be due to abnormal friction or vibration between two mating parts． Failure also may bedue to a phenomenon called creep， which is the plastic flow of a material under load at elevated temperatures． In addition， the actual shape of a part may be responsible for failure． For example， stress concentrations due to sudden changes in contour must be taken into account． Evaluation of stress considerations is especially important when there are dynamic loads with direction reversals and the material is not very ductile． In general， the design engineer must consider all possible modes of failure， which include the following． —— Stress —— Deformation —— Wear —— Corrosion —— Vibration —— Environmental damage —— Loosening of fastening devices The part sizes and shapes selected also must take into account many dimensional factors that produce external load effects， such as geometric discontinuities， residual stresses due to forming of desired contours，and the application of interference fit joints． Cams are among the most versatile mechanisms available． A cam is a simple two-member device． The input member is the cam itself， while the output member is called the follower． Through the use of cams，a simple input motion can be modified into almost any conceivable output motion that is desired． Some of the common applications of cams are —— Camshaft and distributor shaft of automotive engine —— Production machine tools —— Automatic record players —— Printing machines —— Automatic washing machines —— Automatic dishwashers The contour of high-speed cams (cam speed in excess of 1000 rpm) must be determined mathematically． However， the vast majority of cams operate at low speeds(less than 500 rpm) or medium-speed cams can be determined graphically using a large-scale layout． In general， the greater the cam speed and output load， the greater must be the precision with which the cam contour is machined． DESIGN PROPERTIES OF MATERIALS The following design properties of materials are defined as they relate to the tensile test． Figure 2.7 Static Strength． The strength of a part is the maximum stress that the part can sustain without losing its ability to perform its required function． Thus the static strength may be considered to be approximately equal to the proportional limit， since no plastic deformation takes place and no damage theoretically is done to the material． Stiffness． Stiffness is the deformation-resisting property of a material． The slope of the modulus line and， hence， the modulus of elasticity are measures of the stiffness of a material． Resilience． Resilience is the property of a material that permits it to absorb energy without permanent deformation． The amount of energy absorbed is represented by the area underneath the stress-strain diagram within the elastic region． Toughness． Resilience and toughness are similar properties． However， toughness is the ability to absorbenergy without rupture． Thus toughness is represented by the total area underneath the stress-strain diagram， as depicted in Figure 2． 8b． Obviously， the toughness and resilience of brittle materials are very low and are approximately equal． Brittleness． A brittle material is one that ruptures before any appreciable plastic deformation takes place． Brittle materials are generally considered undesirable for machine components because they are unable to yield locally at locations of high stress because of geometric stress raisers such as shoulders， holes， notches， or keyways． Ductility． A ductility material exhibits a large amount of plastic deformation prior to rupture． Ductility is measured by the percent of area and percent elongation of a part loaded to rupture． A 5%elongation at rupture is considered to be the dividing line between ductile and brittle materials． Malleability． Malleability is essentially a measure of the compressive ductility of a material and， as such， is an important characteristic of metals that are to be rolled into sheets． Figure 2.8 Hardness． The hardness of a material is its ability to resist indentation or scratching． Generally speaking， the harder a material， the more brittle it is and， hence， the less resilient． Also， the ultimate strengthof a material is roughly proportional to its hardness． Machinability． Machinability is a measure of the relative ease with which a material can be machined． In general， the harder the material， the more difficult it is to machine． COMPRESSION AND SHEAR STATIC STRENGTH In addition to the tensile tests， there are other types of static load testing that provide valuable information． Compression Testing． Most ductile materials have approximately the same properties in compression as in tension． The ultimate strength， however， can not be evaluated for compression． As a ductile specimen flows plastically in compression， the material bulges out， but there is no physical rupture as is the case in tension． Therefore， a ductile material fails in compression as a result of deformation， not stress． Shear Testing． Shafts， bolts， rivets， and welds are located in such a way that shear stresses are produced． A plot of the tensile test． The ultimate shearing strength is defined as the stress at which failure occurs． The ultimate strength in shear， however， does not equal the ultimate strength in tension． For example， in the case of steel， the ultimate shear strength is approximately 75% of the ultimate strength in tension． This difference must be taken into account when shear stresses are encountered in machine components． DYNAMIC LOADS An applied force that does not vary in any manner is called a static or steady load． It is also common practice to consider applied forces that seldom vary to be static loads． The force that is gradually appliedduring a tensile test is therefore a static load． On the other hand， forces that vary frequently in magnitude and direction are called dynamic loads． Dynamic loads can be subdivided to the following three categories． Varying Load． With varying loads， the magnitude changes， but the direction does not． For example， the load may produce high and low tensile stresses but no compressive stresses． Reversing Load． In this case， both the magnitude and direction change． These load reversals produce alternately varying tensile and compressive stresses that are commonly referred to as stress reversals． Shock Load． This type of load is due to impact． One example is an elevator dropping on a nest of springs at the bottom of a chute． The resulting maximum spring force can be many times greater than the weight of the elevator， The same type of shock load occurs in automobile springs when a tire hits a bump or hole in the road． FATIGUE FAILURE-THE ENDURANCE LIMIT DIAGRAM The test specimen in Figure 2.10a．， after a given number of stress reversals will experience a crack at the outer surface where the stress is greatest． The initial crack starts where the stress exceeds the strength of the grain on which it acts． This is usually where there is a small surface defect， such as a material flaw or a tiny scratch． As the number of cycles increases， the initial crack begins to propagate into a continuous series of cracks all around the periphery of the shaft． The conception of the initial crack is itself a stress concentration that accelerates the crack propagation phenomenon． Once the entire periphery becomes cracked， the cracks start to move toward the center of the shaft． Finally， when the remaining solid inner area becomes small enough， the stress exceeds the ultimate strength and the shaft suddenly breaks． Inspection of the break reveals a very interesting pattern， as shown in Figure 2.13． The outer annular area is relatively smooth because mating cracked surfaces had rubbed against each other． However， the center portion is rough， indicating a sudden rupture similar to that experienced with the fracture of brittlematerials． This brings out an interesting fact． When actual machine parts fail as a result of static loads， they normally deform appreciably because of the ductility of the material． Figure 2.13 Thus many static failures can be avoided by making frequent visual observations and replacing all deformed parts． However， fatigue failures give to warning． Fatigue fail mated that over 90% of broken automobile parts have failed through fatigue． The fatigue strength of a material is its ability to resist the propagation of cracks under stress reversals． Endurance limit is a parameter used to measure the fatigue strength of a material． By definition， the endurance limit is the stress value below which an infinite number of cycles will not cause failure． Let us return our attention to the fatigue testing machine in Figure 2.9． The test is run as follows： A small weight is inserted and the motor is turned on． At failure of the test specimen， the counter registers the number of cycles N， and the corresponding maximum bending stress is calculated from Equation 2.5． The broken specimen is then replaced by an identical one， and an additional weight is inserted to increase the load． A new value of stress is calculated， and the procedure is repeated until failure requires only one complete cycle． A plot is then made of stress versus number of cycles to failure． Figure 2.14a shows the plot， which is called the endurance limit or S-N curve． Since it would take forever to achievean infinite number of cycles， 1 million cycles is used as a reference． Hence the endurance limit can befound from Figure 2.14a by noting that it is the stress level below which the material can sustain 1 million cycles without failure． The relationship depicted in Figure 2.14 is typical for steel， because the curve becomes horizontal as N approaches a very large number． Thus the endurance limit equals the stress level where the curve approaches a horizontal tangent． Owing to the large number of cycles involved， N is usually plotted on a logarithmic scale， as shown in Figure 2.14b． When this is done， the endurance limit value can be readily detected by the horizontal straight line． For steel， the endurance limit equals approximately 50% of the ultimate strength． However， if the surface finish is not of polished equality， the value of the endurance limit will be lower． For example， for steel parts with a machined surface finish of 63 microinches ( μin． )，the percentage drops to about 40%． For rough surfaces (300μin． or greater)， the percentage may be as low as 25%． The most common type of fatigue is that due to bending． The next most frequent is torsion failure， whereas fatigue due to axial loads occurs very seldom． Spring materials are usually tested by applying variable shear stresses that alternate from zero to a maximum value， simulating the actual stress patterns． In the case of some nonferrous metals， the fatigue curve does not level off as the number of cycles becomes very large． This continuing toward zero stress means that a large number of stress reversals will cause failure regardless of how small the value of stress is． Such a material is said to have no endurance limit． For most nonferrous metals having an endurance limit， the value is about 25% of the ultimate strength． EFFECTS OF TEMPERATURE ON YIELD STRENGTH AND MODULUS OF ELASTICITY Generally speaking， when stating that a material possesses specified values of properties such as modulus of elasticity and yield strength， it is implied that these values exist at room temperature． At low or elevated temperatures， the properties of materials may be drastically different． For example， many metals aremore brittle at low temperatures． In addition， the modulus of elasticity and yield strength deteriorate as the temperature increases． Figure 2.23 shows that the yield strength for mild steel is reduced by about 70% in going from room temperature to 1000oF． Figure 2.24 shows the reduction in the modulus of elasticity E for mild steel as the temperature increases． As can be seen from the graph， a 30% reduction in modulus of elasticity occurs in going from room temperature to 1000oF． In this figure， we also can see that a part loaded below the proportional limit at room temperature can be permanently deformed under the same load at elevated temperatures． Figure 2.24 CREEP: A PLASTIC PHENOMENON Temperature effects bring us to a phenomenon called creep， which is the increasing plastic deformation of a part under constant load as a function of time． Creep also occurs at room temperature， but the process is so slow that it rarely becomes significant during the expected life of the temperature is raised to 300oC or more， the increasing plastic deformation can become significant within a relatively short period of time． The creep strength of a material is its ability to resist creep， and creep strength data can be obtained by conducting long-time creep tests simulating actual part operating conditions． During the test， theplastic strain is monitored for given material at specified temperatures． Since creep is a plastic deformation phenomenon， the dimensions of a part experiencing creep are permanently altered． Thus， if a part operates with tight clearances， the design engineer must accurately predict the amount of creep that will occur during the life of the machine． Otherwise， problems such binding or interference can occur． Creep also can be a problem in the case where bolts are used to clamp tow parts together at elevated temperatures． The bolts， under tension， will creep as a function of time． Since the deformation is plastic，loss of clamping force will result in an undesirable loosening of the bolted joint． The extent of this particular phenomenon， called relaxation， can be determined by running appropriate creep strength tests． Figure 2.25 shows typical creep curves for three samples of a mild steel part under a constant tensile load． Notice that for the high-temperature case the creep tends to accelerate until the part fails． The time line in the graph (the x-axis) may represent a period of 10 years， the anticipated life of the product． Figure 2.25 SUMMARY The machine designer must understand the purpose of the static tensile strength test． This test determines a number of mechanical properties of metals that are used in design equations． Such terms as modulus of elasticity， proportional limit， yield strength， ultimate strength， resilience， and ductility define properties that can be determined from the tensile test． Dynamic loads are those which vary in magnitude and direction and may require an investigation of the machine part’s resistance to failure． Stress reversals may require that the allowable design stress be basedon the endurance limit of the material rather than on the yield strength or ultimate strength． Stress concentration occurs at locations where a machine part changes size， such as a hole in a flat plateor a sudden change in width of a flat plate or a groove or fillet on a circular shaft． Note that for the case of a hole in a flat or bar， the value of the maximum stress becomes much larger in relation to the average stress as the size of the hole decreases． Methods of reducing the effect of stress concentration usually involve making the shape change more gradual． Machine parts are designed to operate at some allowable stress below the yield strength or ultimate strength． This approach is used to take care of such unknown factors as material property variations and residual stresses produced during manufacture and the fact that the equations used may be approximate ratherthat exact． The factor of safety is applied to the yield strength or the ultimate strength to determine the allowable stress． Temperature can affect the mechanical properties of metals． Increases in temperature may cause a metal to expand and creep and may reduce its yield strength and its modulus of elasticity． If most metals are not allowed to expand or contract with a change in temperature， then stresses are set up that may be added to the stresses from the load． This phenomenon is useful in assembling parts by means of interferencefits． A hub or ring has an inside diameter slightly smaller than the mating shaft or post． The hub is then heated so that it expands enough to slip over the shaft． When it cools， it exerts a pressure on the shaft resulting in a strong frictional force that prevents loosening． TYPES OF CAM CONFIGURATIONS Plate Cams． This type of cam is the most popular type because it is easy to design and manufacture． Figure 6． 1 shows a plate cam． Notice that the follower moves perpendicular to the axis of rotation of the camshaft． All cams operate on the principle that no two objects can occupy the same space at the same time． Thus， as the cam rotates ( in this case， counterclockwise )， the follower must either move upward or bind inside the guide． We will focus our attention on the prevention of binding and attainment of the desired output follower motion． The spring is required to maintain contact between the roller of the follower and the cam contour when the follower is moving downward． The roller is used to reduce friction and hence wear at the contact surface． For each revolution of the cam， the follower moves through two strokes-bottom dead center to top dead center (BDC to TDC) and TDC to BDC． Figure 6.2 illustrates a plate cam with a pointed follower． Complex motions can be produced with this type of follower because the point can follow precisely any sudden changes in cam contour． However， this design is limited to applications in which the loads are very light； otherwise the contact point of both members will wear prematurely， with subsequent failure． Two additional variations of the plate cam are the pivoted follower and the offset sliding follower， whichare illustrated in Figure 6.3． A pivoted follower is used when rotary output motion is desired． Referringto the offset follower， note that the amount of offset used depends on such parameters as pressure angle and cam profile flatness， which will be covered later． A follower that has no offset is called an in-line follower． Figure 6.3 Translation Cams． Figure 6.4 depicts a translation cam． The follower slides up and down as the cam translates motion in the horizontal direction． Note that a pivoted follower can be used as well as a sliding-type follower． This type of action is used