外文翻譯--客車變速器疲勞壽命試驗(yàn)臺機(jī)械結(jié)構(gòu)設(shè)計(jì)(原文）

1、International Journal of Computer Communication and Information System ( IJCCIS) – Vol2. No1. ISSN: 0976–1349 July – Dec 2010Design and Development of Torque Testing Rig for a GearboxAmruta Lomate1, Suhas Mohite2, an

2、d Rahul Shinde31Mechanical Department, Bharati Vidhyapeeth, College of Engineering, Pune, MaharashtraAmu2384@yahoo.co.in2Mechanical department, Govt. College of Engineering, Karad, Maharashtra3Executive director, Cyclo T

3、ransmission Ltd. Satara, Maharashtramohitess@yahoo.com, cyclobox@rediffmail.com Abstract - Gearbox is an indispensae element of power transmission drives of most mechanical systems. Therefore, it is very es

4、sential to assure the performance of gear drives before they are put to use to ensure the trouble free functioning of systems. While testing performance of the gearbox, it is importance to check the torq

5、ue carrying capacity at rated speeds. This work presents the design and development of a torque testing rig for 0.5-10 kN-m capacity carried out for a gearbox having multi-plate brake system. While calibratio

6、n of torque testing rig experimentally measured data is compared with the theoretical calculations and a good agreement between experimental and theoretical calculations is observed. Index terms –Gear box, design

7、, torque, calibrationI. INTRODUCTIONGearbox is an indispensable element of power transmission drives of most mechanical systems such as vehicles, machinery and cranes, etc. The main function of the ind

8、ustrial gear drive is to reliably transmit torque and rotary motion between prime mover and driven piece of equipment, at acceptable level of noise, vibration and temperature. When one or more of the prece

9、ding operating characteristics exceeds allowable limits, it can lead to failure of the gearbox. Manufacturing companies or customers have to bear big cost and time for the failure of gear drive system during operatio

10、n. Therefore, it is very essential for the manufacturer to assure the quality of gear drives before they are put to use to ensure trouble free functioning of systems. While testing the performance of gearbox, it is im

11、portance to check the torque carrying capacity at different speeds. At present, Cyclo transmission ltd. does not have any torque testing facility. So to measure the torque; company has to rely on theoretical

12、calculations according to ISO (International Organization for Standardization) and AGMA (American Gear Manufacturers Association) standards to specify torque ratings. Therefore, it is very necessary for them to h

13、ave a test rig for gearboxes to assure quality of the gearbox. Torque testing rig is an essential facility that every gear manufacturing company must have. To fulfil above needs of the torque testing rig, a literature

14、 survey was undertaken with the view to finalize its features and specification. Different types of torque testing rig available in market are studied. From above literature it is found out that each method has

15、some advantages and disadvantages. For torque testing back to back, digi-torque and multi-plate brake systems are studied “Ref. [1-3]” For back to back arrangement two similar gear boxes are required, w

16、hich may not be available in some of the cases. In digi-torque method the flywheel was used to apply the torque, which is not suitable for high torque measurement. Both these methods are not suitable for this

17、application. Multi-plate brake torque testing system (torque applying) is suitable because it can provide wide range of torque (from 500 N-m to 10 KN-m) at different speeds. The brake plates are partially wetted t

18、o avoid wear and control the temperature of brake plates. For actuating multi-plate brake system, actuators are needed. While studying different brake actuators [4]., it was found that hydraulic actuator is sui

19、table for applying the pressure for multi plate brake system, because it provides fast response along with smooth engagement by controlling the rate of pressure built-up with a pressure control valve. By referri

20、ng to the literature in the point of torque measurement, it was found out that canister type load cell can provide high torque measurement because this load cell is suitable for high torque or load range and also eli

21、minates the need of prior checking [5]. Finally it is decided to design and develop a hydraulically actuated multiplate brake torque testing rig for different gearbox, maximum torque of 10 kNm at rated speed.II. METH

22、ODOLOGYThe proposed system has multi plate brake assembly as a main and core component. The assembly is mounted in between the bracket and fixed on and around the shaft. Figure 1 Outline of the proposed gearbox test rig

23、12International Journal of Computer Communication and Information System ( IJCCIS) – Vol2. No1. ISSN: 0976–1349 July – Dec 2010box. The analytical and the experimental readings are compared.Figure 4 Schematic arrang

24、ement of the test rig for calibrationThese results are given for different pressure values ranging from 2 bars to 20 bars. The calibrated measurement units (load cell, digital display and pressure gauge) ar

25、e used. For finding theoretical value following equation is referred. hi Ot P d D d D Z M × + × ? × × × =16) ( ) ( 2 12 2 π µ(3) Where, Ph is hydraulic pressure, D is outer diameter of pis

26、ton and d is inner diameter of piston. The test rig can also be tested for duty cycle test of some of the gear boxes.V. RESULTS AND DISCUSSIONThe testing has been done on different types of gearboxes, different types o

27、f testing is done the results are discussed below. Calibration of the test rig carried out by comparing experimental result with theoretical values. The test results of a few models are done, one is discussed below.1

28、. Gear box Model number 4010-4,[11]. Specifications: Input power- 10H.P.,Output speed- 5.75 r.p.m, Output torque- 10.5 Nm.Testing was carried out for 10 minutes at different constant pressure values and readings were ob

29、served after every 2 minutes to allow for the system to get stabilized. 020004000600080001000012000Torque, Nm2 3 5 8 10 12 15 16 18 19 20Pressure, BarExperimental Torque, NmAnalytical Torque, NmFigure 5 Comparison of a

30、nalytical and experimental torque valuesTable I.Comparison of analytical and experimental torque valuesSr. No. PressureExperimenta l TorqueAnalytical TorqueAbsolute error % Error1 2 1044 1002 42 4.122 3 1545 1503 42

31、2.793 5 2550 2505 45 1.794 8 4052 4008 44 1.095 10 5050 5010 40 0.796 12 6055 6012 43 0.717 15 7559 7515 44 0.598 16 8061 8016 45 0.569 18 9067 9018 49 0.5410 19 9568 9519 49 0.5111 20 10069 10020 49 0.49It is observed t

32、hat the experimental readings for torque are higher than analytical values by an absolute margin of 40-50 Nm for the entire torque range. In terms of the percentage this accounts for approximately 5 to 0.5%. F

33、urther, higher error (5%) is observed at lower torque (and lower pressure) whereas, lower error (0.5%) is observed at higher torque values. The reasons for this error could be attributed to various causes that ar

34、e not considered in theoretical calculations. The possible causes are mentioned below. a) In analytical calculation, friction in the bearings, oil seals and other moving parts is not considered.b) The tested gear

35、boxes have a lower operating speed (5-10 rpm) at such speeds the stick-slip phenomenon in between the brake plates is more significant, this could be one of the sources of the error.c) Inertia of the system.d) When t

36、he hydraulic pressure increases the friction in the various parts increases.e) Errors in load cell readings.f) Errors in display unit.g) The error in the pressure gauge also the pressure indicator is analogue display s

37、o the manual mistake may be occurred.The obtained results were compared to the theoretically calculated and a good agreement between the experimentally obtained and theoretically calculated results were seen.