外文翻譯--雙曲柄環(huán)板式針擺行星傳動裝置的傳動效率分析

1、<p>　　中文3330字，2170單詞,10100英文字符</p><p>　　EFFICIENCY ANALYSIS OF DOUBLE CRANK RING-PLATE-TYPE PIN-CYCLOIDAL GEAR PLANETARY DRIVE</p><p><b>　　LiXin</b></p><p>　　Depart

2、ment of Mechanical Engineering，</p><p>　　University of Maryland．</p><p>　　Maryland U SA</p><p>　　He Weidong</p><p>　　Department of Mechanical Engineering，</p>

3、<p>　　Dalian Railway Institute，</p><p>　　Dalian 116028．China</p><p>　　Linda SchmidI</p><p>　　Department of Mechanical Engineenng，</p><p>　　University of Maryland，&

4、lt;/p><p>　　Maryland，U．S .A</p><p><b>　　Li Lixing</b></p><p>　　Department of Mechanical Engineedng．</p><p>　　Dalian Railway tnstitute，</p><p>　　Da

5、lian 116028．China</p><p>　　Abstract：From the general formula for calculating the efficiency ofplanatary gear trains，the efficiency oft the double crank ring-plate-type pin-eycloidal gear planetary driveis de

6、rived To prove the theory,all experimental study has been conducted Thetested value ofthe efficiency of a sample set of the new—type drive in the experiment agrees with the calculated one It shows that the new—type drive

7、 is of not merely high beating capaeity,but also quite high efficiency.</p><p>　　Key words：Double crank ring—plate—type Pin—cycloidal gear planetary drive Mesh efficiency.</p><p>　　0 INTRODUCTl

8、0N</p><p>　　It iS known that the traditional cycloidal—pin wbeel planetary drive of K-H—V type which is of multi-tooth mesh and has hardened tooth flank of gears has a series of essenfial advantages such as

9、small volume,1ight weight．wide range of transmission ratio，high efficiency，and utliformo perating aswell .On the other hand，the pin-cycloidal K-H-V type planetary drive has a nataral weak point that the arm bearing，which

10、 supports the cycloidal gear on the arm is placed insidetbe cycloidal gear,thereforet</p><p>　　To overcome the shortcoming ofthe traditional cycloidel-pin wheeI planetary gear train,we developed some designs

11、 of the double crank ring-plate-type pin—cycloidal gear planetary drive．The new-type drive keeps all the advantages described above．</p><p>　　Since the arm bearing iS placed outside the cycloidal gear,the si

12、zeof the bearing IS llO iongar res塒cted to any extent．The bearingcapacity ofthewhole driveiSthel'eforcmuch enlarged．Moreover,tlle drive does not need the special output unit as the traditionalone does，so that the rig

13、idity of the 011tput shaft becomes muchhigher．1t is shown that the concerned drive will surely provideindustries with such a Flew kind ofdrives Which are ofsmall vo1-ume，light weight，wide range of ltansmission ratio，hig&

14、lt;/p><p>　　Since the structure of the new-type drive is quite differentfrom the ffaditional one，it is necessary for u,s to make sure thathe efficiency ofthe new driveis high．Inthispaper,we present a theoretica

15、l and experimental study on the efficiency analysis of he new-type drive．</p><p>　　1 KINEMATICPIUNCIPLE</p><p>　　The kinematic diagram of the double crank ring-plate-type pin-cycloidal gear plan

16、etary drive is shown in Fig．1．The pin gear is mounted On the coupler BC of a four-barparallelogram linkage ABCD．</p><p>　　The center oft he pin gear is at the middle ofthe coupler．And the center of the eyc

17、loidal geat,which meshes with the pin gear,is at the middle ofthe fixed Iink AD．The center distance (eccentricity) is always equal to the length，of the crank and parallel to them．As a motor drives crank 1 to rotate．the c

18、oupler does a pure translation．The point on the coupler,or on the pin gear,moves along a circle ofradius equal to f．The center point 0f the pin gear moves along the circle of radius l with its c</p><p><

19、b>　　Where: </b></p><p>　　-----Angular velocity of the driving crank l</p><p>　　----Angular velocity of the cycloidal gear or the output shaft</p><p>　　----Number of teeth

20、of the cycloidal gear</p><p>　　----Number of the pins</p><p>　　For static balance of the mechanism．two ring．plates with phase difiefence may be used．To keep dynamic balance．We may use another ax

21、ially 8ymmeUicaI pair offing-plates．Moreover, to ensul'e that the driven crank of the four-bar parallelogram link． age stably passes the dead point，we rise a synchronous belt drive as shown in Fig．2 or an ordinary ge

22、ar train of thing gears kine．matieally connecting the two cranks’shaIts．In the case where two motors，which have the same dynamic performance．drive the re</p><p>　　2 GENERAL FORMULA FOR CALCULATING EFFICIENCY

23、 OF PLANIHIARY GEAR TRAINS</p><p>　　Almost all kinds of planetary gear~ains can be considered in general to be 8 basic mechanism eomisting ofthree members a．B and c as shownin Fig．4．We define base the fixed

24、member,and c as the arm of the gear train．The formula for determining the etficiency of basic mechanism is therefore general for planetary gear trains.</p><p>　　Fig．2 Kinematic diagram ofdouble crank ring-pl

25、ate-type pin-cycloidal</p><p>　　gear planetary drive with synchronous belt drive</p><p>　　l .Output shaft 2．Cycloidal gear 3．Ring-plate with pin gear</p><p>　　3’．Ring-plalc with pin

26、 gear of 180。phase difference from 3</p><p>　　4 .Input shaft(shaft of the driving crank)5．Driring pulley</p><p>　　6．Synchronous belt 7.Driven pulley 8．Driven crank</p><p>　　Fig.3

27、 Double crank four ring-plate-type pin-cycloidal</p><p>　　Gear planetary drive driven by two motor</p><p>　　1.Output shaft 2.Cycloidal gear 3.Ring-plate with pin gear outside</p><p&

28、gt;　　3/.Ring-plate with pin gear inside of 180. Phase difference from 3</p><p>　　4.Input shaft (driving crank shaft) 5.Input shaft (driving crank shaft)</p><p>　　There are four cases we need to

29、discuss.</p><p>　　(1)Member bis fixed,and if member a is active,the efficiency of the train is</p><p>　　If member ia is passive,the efficiency of the train is</p><p>　　Where ----Re

30、spective powers on members a and b with b being fixed</p><p>　　The above two equations can be expresses into a uniform one</p><p>　　Where ----Respective torques on members a and c</p>

31、<p>　　-----Respective rotation velocities of members a and c with respect to b</p><p>　　--------Transmission ratio of members c and a with respect to b</p><p>　　In the case where a is cativ

32、e ,p=+1,otherwise p=-1.</p><p>　　(2)Member c is imaginarily fixed，and If member a is active，the efficiency ofthe train is</p><p>　　If member is passive，the efficiency ofthe train is</p>

33、<p>　　where ——Respective powers on members a and b with c beingfixed</p><p>　　The two equations can also be expressed into another uniform one</p><p>　　where Ma，Mb——Respec“"torqu

34、es oiltoember a and b</p><p>　　——RespectiVe rotation velocities of members a and bwith respectto c</p><p>　　——Tansmission ratio ofmembers b and a with respect to c</p><p>　　In the

35、case where a is active,q=+1,otherwise q=-1.</p><p>　　Beside,it slao holds among members a,b and c that </p><p>　　Combining Eqs.(2),(3) and (4) yields </p><p>　　AS p=1 and p=1/p,we

36、 then have</p><p>　　Eq(5)is the general expression for the rel~ionship between and Where is the efficiency ofthe planetary gear Tain with the fixed member b，andis the efficiency of nle imaginary gear train

37、 (relative to member c)where all the axes ale fixed．</p><p>　　Now we need to put our attention to a．rlother problem．As we Clmnge the fixed member from b to c．how to know wherther the condition of action of

38、member a changes，changes from active to Passive or viee versa It earlbe done as follows</p><p>　　Define ，the transmission ratio of members c and B with respectto a .We then change the form as</p><

39、;p>　　If >0，then and have the same signs，the action condition ofmember a does not change Otherwise<0，and it changes</p><p>　　As the fixcd member changes from b to c．There are four cases for dctcrt

40、mning the signs ofp and q in Eq．(5)in accordance willl the action condition of member a．The result is shown in Table l.</p><p>　　3 EFFIClENCY oF THE DOUBLE CRANK RING-PLATE—TYPE PIN．CYCL0lDAL GEAR PLANETARY

41、 REDUCER</p><p>　　The double cFank ring-plate-type pin-eycloidal gear planetary driveis a K-H-VplanetarygeartrainwithVbeingfixed(Fig．5)</p><p>　　Fig 5 Kinematic diagramofdoublecrank ring-plate-t

42、ype</p><p>　　pincycloidal gear planetary drive</p><p>　　Using the general Eq．(5)and substituting a with b，b with V and c with H．We have</p><p>　　Where is the mesh efficiency of a

43、pair of pin and cyeloidal gears taking into account the friction losses in their internal mesh</p><p>　　where ——Number of the pins</p><p>　　——Nunlber of teeth ofthe cycloidal gear</p>&l

44、t;p>　　And p=1，q=1 for member b being passive．Thus the mesh efficiency of ring-plate-type pin-cycloidal gear planetary drive iS 0btained</p><p><b>　　(6)</b></p><p>　　Taking into a

45、ccount the energy lossas in bearings，synchronous belt drive，and in splashing about the lubricant oil，the total efficiency of the whole reducer of double crank ring-plate-type pin-cycloidal gear planetary drive with the s

46、ynchronous belt drive is as foflows</p><p><b>　　(7)</b></p><p>　　Where ----Emciellcy of the bearings</p><p>　　——EfIicllncy due to the losses in lubricant oil</p>

47、;<p><b>　　splashing</b></p><p>　　——Emciency ofthe synchronous belt drive</p><p>　　4 CALCULAllON EXAMPLE</p><p>　　Basic parameters of the sample set of the coflc

48、emed drive</p><p>　　Diameter ofthe circle where pin centers locate：150mm</p><p>　　Eccentdc distance：3 5mm</p><p>　　Radius of the pin bushing：7mm</p><p>　　Radius of the

49、pin：5mm</p><p>　　Transmission ratio：14</p><p>　　Number of the pins，z。=15</p><p>　　Numberofthe cycloldal gear：zb=14</p><p>　　Rated power：6 kW</p><p>　　Rated

50、 torque：720N·m</p><p>　　The mesh efficiency of he ring-platc-type pin-cycloidal gear planctary driveis calculated using Eq.(6)</p><p>　　Where </p><p>　　and we assgn the v

51、alue of =0.997 (The relative morion between the cycloidal gear andthe pmis a pure rolling wtmfine lubricating，and beth the surfaces are well harden.The eftficiency is thercfurc rather high and is usually equal to 0 997～

52、0 998).</p><p>　　We also assign =0 985 (nIe efficiency of rolling bearings is usually equal to 0. 98～0 99)．l (No lubricant oil，but grease is used)，=0 993 (Energy losses in synchronous drive is small Since it

53、 is in action on]y at the dead center ofthefour-bar parall e- lcgram linkage when there is no torque transmitted between the two cranks)</p><p>　　Finally we obtain the total efficiency ofthe reducer.</p&

54、gt;<p>　　5 EXPERIⅧNTAtL STUDY</p><p>　　We have successfully developed a sample set of the double crank ring-plate—type pin—eycloidal gear planetary reducer(See the photo in Fig 6) and tested it in an

55、 experimental study The experimental equipment is shown in Fig .7</p><p>　　Fig.6 Photo of the sample</p><p>　　The input and output shafts were respectively connected to a torque-veloeity senso

56、r and also to a mechauieal efficiency—meter． The input shaft was also connected to a speed．a(chǎn)dlustable direct eta-rent motor．The 0utptit shaft was connected to a magenet power loader．We loaded the reducer in each steps in

57、 experiment .The loads at each step were respectively 25％．50% ,75%,, J00％, 125,‰,150％,175％，200％ of 360 N·m．which is the rned torque of a high performance tradirional cycloidal—pin wheel planetary r</p><p

58、>　　To prove that the load-carrying capacity ofthe new．type reducer call reach two times of that of a high—performanee tradition． al cyeloida]一pin wheel planetary reducer with the same 1engffi of the diameter ofthe cir

59、clewherethe pin centersl~ate．Wele tthe reducer being te．szed keep on operating fof 4 h at the maximum load(torque：720 N’m，power：6 kW) It showed that in this fight period of testing,the efficiency kept in the range of 93％

60、～94％ Wluch is higher than the traditional one,and the teraperature</p><p>　　6 CONCLUSIONS</p><p>　　(1) The formula for cslcufating血e efficienw 0ft he double crank ring plate—type pin-cyeloidal g

61、ear planetary drive from thegeneral expression for planetary gear trains ls derived It showss That the emciency valuel is relatedt ot the lransmission ratio</p><p>　　(2) Expenmental study has been conducted

62、oil me drive The result shows that the tested value of the totaJ efficiency is a llittle Bit higher than that of the calculated one.</p><p>　　(3)T he new-type drive keeps all the advantages ofthe trndi- tion

63、al cycloidal-pin wheel planetary drive .Moreover,its bearing capacity reaches two times as large as the traditional one witth the same lenmh 0f the diameter of the circle where the pin centes locate .At the same time，the

64、 rigidity of the shaft is much higher, and the efficiency is higlh as well The new·-ype drive is highly alive and worthy to study further.</p><p><b>　　外文翻譯（譯文）</b></p><p>　　雙曲柄環(huán)

65、板式針擺行星傳動裝置的傳動效率分析</p><p>　　李欣(馬里蘭大學，美國) </p><p>　　何衛(wèi)東(大連鐵道學院機械工程系，大連，116028)</p><p>　　Linda Schmidt (馬里蘭大學，美國)</p><p>　　李力行(大連鐵道學院機械工程系，大連，116028)</p><p>　

66、　摘要：由行星齒輪傳動裝置的傳動效率的一般公式，可以推算出雙曲柄環(huán)板式針擺行星傳動裝置的傳動效率的公式。為了證明這個理論，作者進行了試驗性的研究。從實驗中得出的這種新型的傳動裝置的傳動效率值與所估計的一致。這表明新型傳動裝置不僅承載能力高，而且傳動效率相當高。</p><p>　　關鍵字：雙曲柄環(huán)板式　針擺行星傳動裝置　嚙合效率</p><p><b>　　前言</b>

67、;</p><p>　　傳統(tǒng)的K-H-V型擺線針輪行星傳動裝置，齒面硬，嚙合齒數(shù)多，具有一系列的優(yōu)點，例如，體積小，重量輕，傳動比范圍大，傳動效率高，傳動平穩(wěn)等。另一方面，K-H-V型針擺行星傳動裝置具有一個本質(zhì)的弱點，就是轉臂軸承置于擺線輪內(nèi)部，尺寸受到限制。正因為如此，承載能力也不能很好的發(fā)揮。</p><p>　　為了克服傳統(tǒng)的擺針輪行星傳動裝置的弱點，我們研制了新型的雙曲柄環(huán)板式針

68、擺行星傳動裝置。新型傳動裝置保留了上述的所有優(yōu)點。因為轉臂軸承置于擺線輪外，尺寸便不再受到任何限制。這樣整個裝置的承載能力就提高了。而且，這種裝置不再像傳統(tǒng)裝置一樣需要特殊的輸出元件，這樣輸出軸的剛度就更大了。這表明雙曲柄環(huán)板式針擺行星傳動裝置將為國民經(jīng)濟的各個工業(yè)部門提供一種體積小、重量輕、傳動比范圍大、傳動效率高、傳動平穩(wěn)、輸出軸剛度大、結構緊湊和傳動能力高的新型裝置。</p><p>　　因為新型傳動裝置與

69、傳統(tǒng)裝置不同，因此我們有必要證實新型傳動裝置的傳動效率進行研究。在這一論文中，我們將通過理論與實驗的研究對這種新型傳動裝置的傳動效率進行分析。</p><p><b>　　工作原理　</b></p><p>　　雙曲柄環(huán)板式針擺行星傳動裝置的機構簡圖如圖1所示。在平行四桿機構ABCD的連桿BC上裝有針輪，針輪的中心位于連桿BC的中點。與針輪相嚙合的擺線輪的中心位于固定

70、連桿AD的中點。針輪與擺線輪的中心距（不正圓）的大小等于主、從動曲柄的長度ｌ。連桿隨著傳動裝置的轉動而轉動。位于連桿或針輪上的一點，在以ｌ為半徑的圓上運動。針輪的中點在以為圓心，以ｌ為半徑的圓上運動。由于針輪的嚙合上具有擺線輪，所以前者將使后者繞著固定軸旋轉。</p><p>　　圖１. 雙曲柄環(huán)板式針擺行星傳動裝置的傳動機構簡圖</p><p>　　傳動比公式為 （1）

71、</p><p>　　這里，是傳動軸１的角速度；</p><p>　　是擺線輪或輸出軸的角速度；</p><p><b>　　是擺線輪的齒數(shù)；</b></p><p><b>　　是針數(shù)。</b></p><p>　　為了使構造達到靜力平衡，兩環(huán)板成180；要達到動力平衡，我

72、們采用另外一對對稱的環(huán)板。為確保平行四桿結構中的傳動軸平穩(wěn)的經(jīng)過終點，我們采用齒形帶（如圖2）普通齒輪結構（將三個齒輪與兩個曲柄連接）。在這種情況下，具有同等動力的發(fā)動機，驅動著各個曲柄（如圖3）。當然，我們也不必控制這種構造范圍的大小。</p><p>　　由一般公式推算雙曲柄環(huán)板式針擺行星傳動裝置的傳動效率公式</p><p>　　大多數(shù)的行星傳動裝置都可以看作是由a、b、c三部分組成

73、的基本構造（如圖4）。我們設b固定，c為轉臂軸承。用語計算基本構造的一般公式也適用于雙曲柄環(huán)板式針擺行星傳動裝置。</p><p>　　圖2.具有齒形帶的雙曲柄環(huán)板式針擺行星傳動裝置的傳動簡圖</p><p>　　輸出軸2.擺線輪3.帶針輪的環(huán)板3.與3成的帶針輪的環(huán)板4.輸入軸（驅動曲柄的傳動軸）5.主動齒形帶輪6.齒形帶7.從動齒形帶輪8.從動曲柄</p><p&g

74、t;　　圖3.由兩個發(fā)動機驅動的雙曲柄環(huán)板式針擺行星傳動裝置</p><p>　　輸出軸2.擺線輪3.帶針輪的環(huán)板3.與3成的帶針輪的環(huán)板4.輸入軸（驅動曲柄的傳動軸）5. 輸入軸（驅動曲柄的傳動軸）</p><p>　　圖4.構造的三個組成部分</p><p>　　我們來討論以下四種情形：</p><p><b>　?。?）b固定

75、，</b></p><p>　　如果a是主動輪，雙曲柄環(huán)板式針擺行星傳動裝置的傳動效率為</p><p>　　如果a是從動輪，雙曲柄環(huán)板式針擺行星傳動裝置的傳動效率為</p><p>　　這里，，分別為在b固定的前提下，a，b的功率。</p><p>　　以上兩個等式可以化為一個通式</p><p><

76、;b>　?。?）</b></p><p>　　這里，，分別為a，c的轉矩；，分別為與b相關a，c的轉速；為與b相關c，a的傳動比。</p><p>　　這種情況下，a為主動輪時，p=+1，否則，p=－1。</p><p><b>　?。?）c固定，</b></p><p>　　如果a是主動輪，雙曲柄環(huán)板

77、式針擺行星傳動裝置的傳動效率為</p><p>　　如果a是從動輪，雙曲柄環(huán)板式針擺行星傳動裝置的傳動效率為</p><p>　　這里，，分別為在c固定的前提下，a，b的功率。</p><p>　　以上兩個等式可以化為一個通式</p><p><b>　?。?）</b></p><p>　　這里，

78、，分別為a，b的轉矩；，分別為與c相關a，b的轉速；為與c相關b，a的傳動比。</p><p>　　這種情況下，a為主動輪時，q=+1，否則，q=－1。</p><p>　　除此之外，a，b，c 還有以下關系</p><p><b>　?。?）</b></p><p>　　結合（2），（3），（4）可以得到</p&

79、gt;<p>　　當p=±1，p=1/p時，我們可以得到</p><p><b>　?。?）</b></p><p>　　等式（5）是表示，之間關系的通式。這里是在b固定的前提下，行星傳動裝置的傳動效率；為與c相關，假設所有軸固定的前提下，行星傳動裝置的傳動效率。</p><p>　　現(xiàn)在我們要解決另外一個問題。隨著我們

80、從固定b到固定c，a是怎樣變化的，從主動輪到從動輪，還是從從動輪到主動輪。我們可以采用如下做法：</p><p>　　設與a相關，c，b的傳動比我們可以將形式化為</p><p>　　如果>0, 則和同號，a的情況不變化；< 0, a發(fā)生變化。</p><p>　　隨著從固定b到固定c，等式（5）中的p，q符號有以下四種變化，而a 的情況也會隨之改變。結

81、果如表1所示。</p><p>　　表1.等式（5）中p，q的符號變化</p><p>　　四、雙曲柄環(huán)板式針擺行星傳動裝置減速器的效率</p><p>　　雙曲柄環(huán)板式針擺行星傳動裝置是固定V的K-H-V型的行星傳動裝置。（如圖5）</p><p>　　圖5. 雙曲柄環(huán)板式針擺行星傳動裝置的傳動簡圖</p><p>

82、<b>　　H（輸入）</b></p><p>　　V 固定 b（擺線輪，輸出）</p><p>　　等式（5）中，如果a=b，b=V，c=H，可以得到</p><p>　　這里，是在不考慮嚙合內(nèi)部摩擦力的情況下，一對針輪、擺線輪的嚙合效率 </p><p>　　這里，是針數(shù)，是擺線輪的齒數(shù)。&l

83、t;/p><p>　　因為b是從動輪，p=1，q=1。因此可以得出雙曲柄環(huán)板式針擺行星傳動裝置的嚙合效率為</p><p><b>　?。?）</b></p><p>　　考慮到減速器中潤滑油的損耗，這種帶有齒形帶的雙曲柄環(huán)板式針擺行星傳動裝置的減速器的效率為</p><p><b>　?。?）</b>

84、</p><p>　　這里，是軸承的傳動效率；</p><p>　　潤滑油分濺后的效率；</p><p>　　是齒形帶的傳動效率。</p><p><b>　　五、計算示例</b></p><p>　　實驗所用傳動裝置的基本參數(shù)：</p><p>　　針輪中心所在圓的直徑：

85、150mm</p><p><b>　　偏心距：3.5mm</b></p><p><b>　　針束的半徑：7mm</b></p><p><b>　　針的半徑：5mm</b></p><p><b>　　傳動比：14</b></p><

86、;p><b>　　針數(shù)：=15</b></p><p><b>　　擺線輪數(shù)：=14</b></p><p><b>　　功率：6KW</b></p><p><b>　　轉矩：720Nm</b></p><p>　　雙曲柄環(huán)板式針擺行星傳動裝置的嚙

87、合效率可以利用等式（6）得出</p><p><b>　　這里，</b></p><p>　　我們設=0.997（擺線輪與針的相對運動齒面非常硬，沒有摩擦力，所以傳動效率非常高，通常為0.997~~0.998）；我們設=0.985（滾動軸承效率通常為0.98~~0.99），=1（用潤滑脂替代潤滑油），=0.993（齒形帶能量損耗小，因為只有達到平行四桿機構終點時才會損

88、耗能量，而此時兩曲柄的轉矩為零）。</p><p>　　最后我們得到減速器的效率為：</p><p><b>　　六、實驗研究</b></p><p>　　我們已經(jīng)成功研制了雙曲柄環(huán)板式針擺行星傳動裝置的減速器（如圖6），并且進行了實驗性的研究。試驗裝置如圖7.所示。</p><p><b>　　圖6.研制樣機

89、照片</b></p><p>　　圖7.減速器試驗裝置</p><p>　　減速器的輸入軸和輸出軸分別裝有一臺轉矩轉速傳感器，并與機械效率儀聯(lián)接。輸入軸與直流電動機相連，輸出軸與磁粉加載器相連。進行加載試驗時，采用分級加載。載荷級分別為同樣針齒中心圓直徑的高性能通用擺線針輪行星減速器額定載荷360Nm的25％，50％，75％，100％，125％，150％，175％，200％。每

90、級載荷分別加載１h，并每隔30min紀錄一次轉速、轉矩、效率、噪聲和振動等數(shù)據(jù)，每級載荷測一次溫升，試驗結果見表２所示。</p><p>　　表2 雙曲柄環(huán)板式針擺行星減速器試驗結果</p><p>　　圖8 為減速器的傳動效率與輸出轉矩的關系曲線。從圖8可以看出，該減速器的傳動效率隨著轉矩的增大而增大，開始時增加較快，隨著轉矩的不斷增大而趨向平緩。</p><p&g

91、t;　　圖8 傳動效率與轉矩的關系</p><p>　　為了證明該新型雙曲柄環(huán)板式針擺行星減速器的額定功率與轉矩確能較同樣針齒中心圓直徑的通用高性能擺線針輪行星減速器提高一倍，我們又讓該新型環(huán)板式針擺行星減速器，在最大載荷下（功率為6kW, 轉矩為720NM）下，連續(xù)運轉4h，其傳動效率穩(wěn)定在93%~94%之間，高于同樣針齒中心圓直徑的高性能擺線針輪行星減速器，且齒面熱平衡溫度僅為75。</p>&

92、lt;p>　　實驗結果表明：我們所研制的雙曲柄環(huán)板式針擺行星減速器傳遞的轉矩，可比同樣針齒中心圓直徑的通用高性能擺線針輪行星減速器的額定功率提高一倍。同時，其傳動效率可達到93.8%。</p><p><b>　　七、結論</b></p><p>　?。?） 由計算行星傳動裝置的傳動效率的統(tǒng)一公式得出計算雙曲柄環(huán)板式針擺行星傳動裝置的公式，這表明傳動效率與傳動比