WO2014079130A1 - Method for obtaining traction curve of hydraulic transmission locomotive - Google Patents
Method for obtaining traction curve of hydraulic transmission locomotive Download PDFInfo
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- WO2014079130A1 WO2014079130A1 PCT/CN2012/087810 CN2012087810W WO2014079130A1 WO 2014079130 A1 WO2014079130 A1 WO 2014079130A1 CN 2012087810 W CN2012087810 W CN 2012087810W WO 2014079130 A1 WO2014079130 A1 WO 2014079130A1
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M17/00—Testing of vehicles
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- the power system is first designed according to the operating conditions of the locomotive. Then, according to the power system, the auxiliary system is selected, the running part and the steel structure are designed, and the whole vehicle design is finally completed.
- the calculation of the expected traction curve is indispensable, which can represent the traction performance of the locomotive, and the traction performance is the most basic characteristic parameter of the locomotive.
- the transmission relationship of the power system is shown in Figure 1.
- the engine 1 as the power source usually has a main output shaft and a secondary output shaft.
- the auxiliary output shaft is connected to an auxiliary device 2 such as a fan.
- the main output shaft is connected to the input end of the hydraulic transmission box 10, hydraulic
- the output end of the transmission case 10 is connected to the wheel axle 6 of the machine.
- the hydraulic transmission case 10 has an input end gear pair 3, a torque converter 4 and an output end gear pair 5, and the torque converter 4 has a pump wheel 41, a guide wheel 42 and a turbine 43 therein.
- the main output shaft is connected to the pump impeller 41 of the torque converter 4 through the input end gear pair 3.
- the pump impeller 41 drives the liquid in the torque converter to flow, and then the turbine 43 of the torque converter 4 is rotated by the guide wheel 42.
- the turbine 43 passes through the output end.
- the gear pair 5 outputs power to the wheel axle 6, wherein the guide wheel 42 is fixed inside the torque converter 4.
- the expected traction curve is generally based on the technical parameters of the engine and hydraulic transmission box and the characteristic parameters of the locomotive itself, as shown in Figure 2, the specific steps are as follows:
- Ml according to the engine performance curve, obtain the net power and engine torque after the engine is deducted from the auxiliary power, and obtain the external characteristic curve of the engine, that is, the relationship between the rotational speed and the torque and power; M2, according to the torque converter in the hydraulic transmission case The dimensionless parameter of the pump wheel is obtained by the pump wheel at each speed ratio; M3, obtaining a common input characteristic point of the engine and the hydraulic transmission box according to the external characteristic curve of the engine and the parabolic curve of the pump wheel load;
- both the manual calculation and the program calculation require a common parameter, that is, the dimensionless parameter of the torque converter.
- the manufacturer does not provide a torque converter for confidentiality.
- the dimensionless parameters and dimensional parameters bring difficulties to the calculation of the traction curve. If the dimensionless parameters of the torque converter are not available, there is no way to obtain the expected traction curve of the hydraulic transmission locomotive, so the power system cannot be performed. Configuration. SUMMARY OF THE INVENTION
- the present invention provides a method for obtaining a traction curve of a hydraulic transmission locomotive, which is used to overcome the deficiencies in the prior art, simplify the steps, and automate the process.
- the invention provides a method for obtaining a traction curve of a hydraulic transmission locomotive, the method comprising the following steps:
- step 5 If the engine output torque M c exceeds the maximum input torque of the hydraulic transmission box and / or the net output power N c of the engine exceeds the maximum input power of the hydraulic transmission box, reselect the engine and repeat steps 2) and 3 above) ; if the engine output torque M c does not exceed the hydraulic transmission box The maximum input torque and the engine net output power N c does not exceed the maximum input power of the hydraulic transmission box, then proceed to step 5);
- n b is obtained according to the transmission and a torque converter impeller speed than the turbine rotation speed n t ⁇ , the torque T M obtained turbine torque ratio k in accordance with the pump impeller of the torque converter and torque M b, n t according to the turbine speed and the turbine torque M t obtain turbine power N t ;
- FIG. 1 is a schematic diagram of a transmission relationship of a power system
- FIG. 3 is a flowchart provided by an embodiment of the present invention.
- FIG. 4 is a schematic diagram of comparison between an expected traction curve and an expected traction curve in the prior art according to an embodiment of the present invention.
- DETAILED DESCRIPTION OF THE INVENTION As shown in FIG. 3, an embodiment of the present invention provides a method for obtaining a traction curve of a hydraulic transmission locomotive, the method comprising the following steps:
- torque converter speed ratio, efficiency ⁇ , torsion ratio k and torque coefficient equivalent parameter C are constant
- torque coefficient equivalent Parameter C is the series of values obtained from the test
- step 54 If the engine output torque M c exceeds the maximum input torque of the hydraulic transmission box and/or the net output power N c of the engine exceeds the maximum input power of the hydraulic transmission box, reselect the engine and repeat steps 2) and 3) If the engine output torque M c does not exceed the maximum input torque of the hydraulic transmission box and the engine net output power N c does not exceed the maximum input power of the hydraulic transmission box, proceed to step 5);
- M t obtains turbine power N t ;
- the method for obtaining the traction curve of the hydraulic transmission locomotive replaces the dimensionless parameter of the torque converter with the test data, obtains the axle traction force and the locomotive speed through simple calculation, and finally obtains the expected traction curve, and the technical solution provided by the invention is relatively
- the process is simple, and each step utilizes existing determined parameters or test data, avoiding the use of unobtained torque converter dimensionless parameters.
- ( ⁇ is a constant.
- the present invention is applicable to the torque converter parameters of the hydraulic transmission device is unknown, especially the case where the torque coefficient cannot be measured. It can be seen from the above calculation formula that the technical solution provided by the embodiment is convenient and quick to calculate. Ordinary office software can be quickly calculated without the need to program a computer program.
- the expected traction curve 30 obtained by the technical solution is approximately the same as the expected traction curve 20 obtained by using the prior art, and the technical solution of the present invention is to calculate the expected traction by using a pure algebra method.
- the curve can be adjusted according to the actual situation, and the calculation procedure of the tedious expected traction curve in the prior art is solved by a simple method, and the accuracy is sufficient. You can meet the engineering needs, simplifying the calculation process.
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Abstract
A method for obtaining a traction curve of a hydraulic transmission locomotive. The method comprises: obtaining, by using a test, a speed ratio, an efficiency, a torque ratio and a torque coefficient equivalent parameter of a torque converter; calculating net output power of an engine; calculating output torque of the engine, and verifying whether the output torque of the engine exceeds a maximum input torque of a hydraulic transmission box and whether the net output power of the engine exceeds a maximum input power of the hydraulic transmission box; calculating a rotating speed of a pump wheel; obtaining a force moment of the pump wheel according to the rotating speed of the pump wheel and the torque coefficient equivalent parameter of the torque converter; calculating a rotating speed of a turbine and a force moment of the turbine, and calculating power of the turbine; and calculating an axle traction and a locomotive speed, and obtaining an expected traction curve according to the axle traction and the locomotive speed. Dimensionless parameters of the torque converter is replaced by test data, the axle traction and the locomotive speed are obtained by using simple calculation, and the expected traction curve is finally obtained. Compared with the prior art, the process of the technical solution is simple, thereby avoiding that the expected traction curve is obtained by using the dimensionless parameters of the torque converter.
Description
液力传动机车牵引曲线的获得方法 本申请要求于 2012年 11月 22日提交中国专利局、 申请号为 201210479054.1、 发明名称为 "液力传动机车牵引曲线的获得方法" 的中国专利申请的优先权， 其全 部内容通过引用结合在本申请中。 技术领域 本发明涉及液力传动技术， 尤其涉及一种液力传动机车牵引曲线的获 得方法。 背景技术 Method for obtaining traction curve of hydraulic transmission locomotive This application claims priority to Chinese patent application filed on November 22, 2012 by the Chinese Patent Office, Application No. 201210479054.1, entitled "Method for Obtaining Traction Curve of Hydraulic Transmission Locomotive" The entire contents of which are incorporated herein by reference. TECHNICAL FIELD The present invention relates to hydraulic transmission technology, and more particularly to a method for obtaining a traction curve of a hydraulic transmission locomotive. Background technique
在液力传动机车设计过程中， 首先要根据机车运用条件， 设计动力系 统， 然后根据动力***， 选配辅助***， 设计走行部及钢结构， 最终完成 整车设计。 在设计动力***过程中， 预期牵引曲线的计算必不可少， 它可 以表示机车的牵引性能， 而牵引性能是机车最基本的特征参数。 In the design process of the hydraulic transmission locomotive, the power system is first designed according to the operating conditions of the locomotive. Then, according to the power system, the auxiliary system is selected, the running part and the steel structure are designed, and the whole vehicle design is finally completed. In the process of designing the power system, the calculation of the expected traction curve is indispensable, which can represent the traction performance of the locomotive, and the traction performance is the most basic characteristic parameter of the locomotive.
动力***的传动关系如图 1所示， 发动机 1作为动力源通常有主输出 轴和辅输出轴， 辅输出轴连接风机等辅助设备 2 , 主输出轴连接液力传动 箱 10输入端， 液力传动箱 10输出端连接机车轮轴 6, 液力传动箱 10内部 具有输入端齿轮副 3、 变矩器 4及输出端齿轮副 5 , 变矩器 4内部具有泵 轮 41、 导轮 42及涡轮 43 , 主输出轴通过输入端齿轮副 3连接变矩器 4的 泵轮 41，泵轮 41带动变矩器内液体流动再通过导轮 42带动变矩器 4的涡 轮 43转动， 涡轮 43通过输出端齿轮副 5将动力输出给机车轮轴 6, 其中 导轮 42固定在变矩器 4内部。 The transmission relationship of the power system is shown in Figure 1. The engine 1 as the power source usually has a main output shaft and a secondary output shaft. The auxiliary output shaft is connected to an auxiliary device 2 such as a fan. The main output shaft is connected to the input end of the hydraulic transmission box 10, hydraulic The output end of the transmission case 10 is connected to the wheel axle 6 of the machine. The hydraulic transmission case 10 has an input end gear pair 3, a torque converter 4 and an output end gear pair 5, and the torque converter 4 has a pump wheel 41, a guide wheel 42 and a turbine 43 therein. The main output shaft is connected to the pump impeller 41 of the torque converter 4 through the input end gear pair 3. The pump impeller 41 drives the liquid in the torque converter to flow, and then the turbine 43 of the torque converter 4 is rotated by the guide wheel 42. The turbine 43 passes through the output end. The gear pair 5 outputs power to the wheel axle 6, wherein the guide wheel 42 is fixed inside the torque converter 4.
目前， 预期牵引曲线一般根据发动机机及液力传动箱的技术参数和机 车本身特征参数的进行， 如图 2所示， 具体步骤如下： At present, the expected traction curve is generally based on the technical parameters of the engine and hydraulic transmission box and the characteristic parameters of the locomotive itself, as shown in Figure 2, the specific steps are as follows:
Ml、 根据发动机性能曲线， 得到发动机扣除辅助功率后的净功率和 发动机扭矩，并求出发动机的外特性曲线即转速与扭矩、功率的关系曲线； M2、 根据液力传动箱中的变矩器的无因次参数， 得到泵轮在各转速 比下的泵轮负荷抛物曲线；
M3、 根据发动机的外特性曲线和泵轮负荷抛物曲线获得发动机与液 力传动箱的共同输入特性点； Ml, according to the engine performance curve, obtain the net power and engine torque after the engine is deducted from the auxiliary power, and obtain the external characteristic curve of the engine, that is, the relationship between the rotational speed and the torque and power; M2, according to the torque converter in the hydraulic transmission case The dimensionless parameter of the pump wheel is obtained by the pump wheel at each speed ratio; M3, obtaining a common input characteristic point of the engine and the hydraulic transmission box according to the external characteristic curve of the engine and the parabolic curve of the pump wheel load;
M4、 根据共同输入特性点， 获得液力传动装置涡轮输出特性曲线； M4, obtaining a turbine output characteristic curve of the hydraulic transmission device according to the common input characteristic point;
M5、 根据输出特性曲线， 结合机车参数， 如车轴车轮箱档位、 速比、 效率及车轮直径等,获得预期牵引曲线。 M5, according to the output characteristic curve, combined with the locomotive parameters, such as axle wheel box gear position, speed ratio, efficiency and wheel diameter, etc., to obtain the expected traction curve.
釆用手工实现以上过程， 计算烦瑣， 工作量大， 效率低； 利用计算机 程序实现以上过程， 速度快， 但是应用不太灵活， 必须要输入程序所定义 的参数， 有些参数因液力传动装置的变矩器无因次参数难以获得而无法确 定， 导致程序计算无法进行。 实现Using the above process manually, the calculation is cumbersome, the workload is large, and the efficiency is low. The computer program is used to realize the above process, the speed is fast, but the application is not flexible, the parameters defined by the program must be input, and some parameters are due to the hydraulic transmission device. The torque converter's dimensionless parameters are difficult to obtain and cannot be determined, resulting in program calculations being impossible.
从现有技术的以上步骤可以看出， 无论手工计算还是程序计算均需要 共同的参数即变矩器的无因次参数， 针对某些液力传动装置， 制造商为了 保密， 不提供变矩器的无因次参数及尺寸参数， 给牵引曲线的计算带来了 困难， 如果变矩器的无因次参数无法获得， 均没有办法获得液力传动机车 预期牵引曲线， 因此也就无法进行动力***的配置。 发明内容 本发明提供一种液力传动机车牵引曲线的获得方法， 用于克服现有技 术中的缺陷， 简化步骤， 实现过程自动化。 It can be seen from the above steps of the prior art that both the manual calculation and the program calculation require a common parameter, that is, the dimensionless parameter of the torque converter. For some hydraulic transmission devices, the manufacturer does not provide a torque converter for confidentiality. The dimensionless parameters and dimensional parameters bring difficulties to the calculation of the traction curve. If the dimensionless parameters of the torque converter are not available, there is no way to obtain the expected traction curve of the hydraulic transmission locomotive, so the power system cannot be performed. Configuration. SUMMARY OF THE INVENTION The present invention provides a method for obtaining a traction curve of a hydraulic transmission locomotive, which is used to overcome the deficiencies in the prior art, simplify the steps, and automate the process.
本发明提供一种液力传动机车牵引曲线的获得方法， 该方法包括以下 步骤： The invention provides a method for obtaining a traction curve of a hydraulic transmission locomotive, the method comprising the following steps:
1 ) 利用试验获得变矩器转速比 ii、 效率 η、 变扭比 k及扭矩系数当 量参数 C; 1) Using the test to obtain the torque converter speed ratio ii, the efficiency η, the torsion ratio k and the torque coefficient quantity parameter C;
2 )根据发动机额定功率 Ne和辅助设备消耗的功率 Nf获得发动机的净 输出功率 Nc; 2) obtaining the net output power N c of the engine according to the engine rated power N e and the power consumed by the auxiliary device N f ;
3 )根据发动机净输出功率 Nc和发动机额定转速 nc获得发动机输出力 矩 Mc, 并核实发动机输出力矩 Mc是否超出液力传动箱最大输入力矩， 发 动机净输出功率 Nc是否超出液力传动箱最大输入功率； 3) Obtain the engine output torque M c according to the engine net output power N c and the engine rated speed n c , and verify whether the engine output torque M c exceeds the maximum input torque of the hydraulic transmission box, and whether the net output power N c of the engine exceeds the hydraulic transmission Maximum input power of the box;
4 ) 如果发动机输出力矩 Mc超出液力传动箱最大输入力矩和 /或发动 机净输出功率 Nc超出液力传动箱最大输入功率， 则重新选定发动机， 并 重复上述步骤 2 )和步骤 3 )； 如果发动机输出力矩 Mc未超出液力传动箱
最大输入力矩且发动机净输出功率 Nc也未超出液力传动箱最大输入功率， 则进行步骤 5 ) ； 4) If the engine output torque M c exceeds the maximum input torque of the hydraulic transmission box and / or the net output power N c of the engine exceeds the maximum input power of the hydraulic transmission box, reselect the engine and repeat steps 2) and 3 above) ; if the engine output torque M c does not exceed the hydraulic transmission box The maximum input torque and the engine net output power N c does not exceed the maximum input power of the hydraulic transmission box, then proceed to step 5);
5 )根据发动机的额定转速 nc和输入端齿轮副的传动比 i2获得泵轮转 速 nb; 5) obtaining the pump wheel speed n b according to the rated speed n c of the engine and the gear ratio i 2 of the input gear pair ;
6 )根据泵轮转速 nb和变矩器扭矩系数当量参数 C获得泵轮力矩 Mb;6) obtaining the pump wheel torque M b according to the pump wheel speed n b and the torque converter torque coefficient equivalent parameter C;
7 )根据泵轮转速 nb及变矩器传动比 ^获得涡轮转速 nt, 根据泵轮力 矩 Mb及变矩器变扭比 k获得涡轮力矩 Mt, 根据涡轮转速 nt和涡轮力矩 Mt获得涡轮功率 Nt; 7) n b is obtained according to the transmission and a torque converter impeller speed than the turbine rotation speed n t ^, the torque T M obtained turbine torque ratio k in accordance with the pump impeller of the torque converter and torque M b, n t according to the turbine speed and the turbine torque M t obtain turbine power N t ;
8 )根据涡轮功率 Nt、 涡轮转速 nt、 输出齿轮副的传动比 i3、 变矩器 效率 η和车轮直径 r获得轮轴牵引力 F, 根据涡轮功率 Nt、 输出齿轮副的 传动比 i3和车轮直径 r获得机车速度 V, 根据轮轴牵引力 F的值和机车速 度 V的值获得预期牵引曲线。 8) Obtaining the axle traction force F according to the turbine power N t , the turbine speed n t , the gear ratio i 3 of the output gear pair, the torque converter efficiency η and the wheel diameter r, according to the turbine power N t , the gear ratio i 3 of the output gear pair The locomotive speed V is obtained with the wheel diameter r, and the expected traction curve is obtained based on the value of the axle traction force F and the value of the locomotive speed V.
本发明提供的液力传动机车牵引曲线的获得方法， 用试验数据代替变 矩器无因次参数， 通过简单的计算获得轮轴牵引力和机车速度， 最终得到 预期牵引曲线， 本发明提供的技术方案相对现有技术， 过程简洁， 且每个 步骤均利用现有确定的参数或试验数据， 避开了利用无法得到的变矩器无 因次参数获取预期牵引曲线。 附图说明 图 1为动力***的传动关系示意图； The method for obtaining the traction curve of the hydraulic transmission locomotive provided by the invention replaces the dimensionless parameter of the torque converter with the test data, obtains the axle traction force and the locomotive speed through simple calculation, and finally obtains the expected traction curve, and the technical solution provided by the invention is relatively In the prior art, the process is simple, and each step utilizes the existing determined parameters or test data, avoiding the use of the unobtained torque converter dimensionless parameter to obtain the expected traction curve. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a schematic diagram of a transmission relationship of a power system;
图 2为现有技术的流程图； 2 is a flow chart of the prior art;
图 3为本发明实施例提供的流程图 FIG. 3 is a flowchart provided by an embodiment of the present invention.
图 4为本发明实施例提供的预期牵引曲线与现有技术中预期牵引曲线 对比示意图。 具体实施方式 如图 3所示， 本发明实施例提供一种液力传动机车牵引曲线的获得方 法， 该方法包括以下步骤： FIG. 4 is a schematic diagram of comparison between an expected traction curve and an expected traction curve in the prior art according to an embodiment of the present invention. DETAILED DESCRIPTION OF THE INVENTION As shown in FIG. 3, an embodiment of the present invention provides a method for obtaining a traction curve of a hydraulic transmission locomotive, the method comprising the following steps:
Sl、 通过试验获得变矩器转速比 、 效率 η、 变扭比 k及扭矩系数当 量参数 C; 变矩器转速比 、 效率 η、 变扭比 k均为常数， 扭矩系数当量
参数 C是根据试验获得的 ―系列值； Sl, through the test to obtain the torque converter speed ratio, efficiency η, torsion ratio k and torque coefficient equivalent parameter C; torque converter speed ratio, efficiency η, variable twist ratio k are constant, torque coefficient equivalent Parameter C is the series of values obtained from the test;
S2、 根据发动机额定功率 Ne和辅助设备消耗的功率 Nf获得发动机的 净输出功率 Nc; S2, obtaining a net output power N c of the engine according to the engine rated power Ne and the power consumed by the auxiliary device N f ;
S3、 根据发动机净输出功率 Nc和发动机额定转速 nc获得发动机输出 力矩 Mc, 并核实发动机输出力矩 Mc是否超出液力传动箱最大输入力矩， 发动机净输出功率 Nc是否超出液力传动箱最大输入功率； S3. Obtain an engine output torque M c according to the engine net output power N c and the engine rated speed n c , and verify whether the engine output torque M c exceeds the maximum input torque of the hydraulic transmission box, and whether the net output power N c of the engine exceeds the hydraulic transmission Maximum input power of the box;
54、 如果发动机输出力矩 Mc超出液力传动箱最大输入力矩和 /或发动 机净输出功率 Nc超出液力传动箱最大输入功率， 则重新选定发动机， 并 重复上述步骤 2 )和步骤 3 )； 如果发动机输出力矩 Mc未超出液力传动箱 最大输入力矩且发动机净输出功率 Nc也未超出液力传动箱最大输入功率， 则进行步骤 5 ) ； 54. If the engine output torque M c exceeds the maximum input torque of the hydraulic transmission box and/or the net output power N c of the engine exceeds the maximum input power of the hydraulic transmission box, reselect the engine and repeat steps 2) and 3) If the engine output torque M c does not exceed the maximum input torque of the hydraulic transmission box and the engine net output power N c does not exceed the maximum input power of the hydraulic transmission box, proceed to step 5);
55、根据发动机的额定转速 nc和输入端齿轮副的传动比 i2获得泵轮转 速 nb; 55, according to the rated speed n c of the engine and the gear ratio i 2 of the input gear pair to obtain the pump wheel speed n b ;
56、根据泵轮转速 nb和变矩器扭矩系数当量参数 C获得泵轮力矩 Mb; S7、根据泵轮转速 nb及变矩器传动比 ^获得涡轮转速 nt,根据泵轮力 矩 Mb及变矩器变扭比 k获得涡轮力矩 Mt, 根据涡轮转速 nt和涡轮力矩56. Obtain the pump wheel torque M b according to the pump wheel speed n b and the torque converter torque coefficient equivalent parameter C; S7, obtain the turbine speed n t according to the pump wheel speed n b and the torque converter transmission ratio, according to the pump wheel torque M b and the torque converter torque ratio k obtain the turbine torque M t , according to the turbine speed n t and the turbine torque
Mt获得涡轮功率 Nt; M t obtains turbine power N t ;
S8、 根据涡轮功率 Nt、 涡轮转速 nt、 输出齿轮副的传动比 i3、 变矩器 效率 η和车轮直径 r获得轮轴牵引力 F, 根据涡轮功率 Nt、 输出齿轮副的 传动比 i3和车轮直径 r获得机车速度 V, 根据轮轴牵引力 F的值和机车速 度 V的值获得预期牵引曲线。 S8, obtaining the axle traction force F according to the turbine power N t , the turbine speed n t , the gear ratio i 3 of the output gear pair, the torque converter efficiency η and the wheel diameter r , according to the turbine power N t , the gear ratio i 3 of the output gear pair The locomotive speed V is obtained with the wheel diameter r, and the expected traction curve is obtained based on the value of the axle traction force F and the value of the locomotive speed V.
本发明提供的液力传动机车牵引曲线的获得方法， 用试验数据代替变 矩器无因次参数， 通过简单的计算获得轮轴牵引力和机车速度， 最终得到 预期牵引曲线， 本发明提供的技术方案相对现有技术， 过程简洁， 且每个 步骤均利用现有确定的参数或试验数据， 避开了利用无法得到的变矩器无 因次参数。 The method for obtaining the traction curve of the hydraulic transmission locomotive provided by the invention replaces the dimensionless parameter of the torque converter with the test data, obtains the axle traction force and the locomotive speed through simple calculation, and finally obtains the expected traction curve, and the technical solution provided by the invention is relatively In the prior art, the process is simple, and each step utilizes existing determined parameters or test data, avoiding the use of unobtained torque converter dimensionless parameters.
作为上述实施例的具体实现方式， 步骤 S2中若发动机辅助设备消耗 的功率为 Nf, 则发动机净输出功率满足 Λ^ = Λ^ - Λ^。步骤 S5中泵轮转速满 足 = Λ。 步骤 S6中泵轮力矩满足 ^ = 0¾2。 As a specific implementation of the above embodiment, if the power consumed by the engine auxiliary device is N f in step S2, the net output power of the engine satisfies Λ^ = Λ^ - Λ^. The pump wheel speed in step S5 satisfies = Λ . The pump wheel torque in step S6 satisfies ^ = 03⁄4 2 .
步骤 S3中发动机输出力矩满足 =^。 步骤 S7中涡轮转速满足
nt = i,nb； 涡轮力矩满足 Μ, = Μέ ; 涡轮功率满足 N, = ςΜΛ。 步骤 S8中轮轴 牵引力满足 F = ^ 机车速度满足 = 2 τπ·3Λ^。 其中（^为常数。 本发明适用于液力传动装置的变矩器参数未知， 尤其是扭矩系数无法 测量的情况。 由上述计算公式可以看出， 本实施例提供的技术方案计算方 便快捷，借助普通的办公软件就可快速计算， 无须编制计算机程序； 其次， 无须知道液力变矩器的扭矩系数， 只须得到扭矩系数当量参数 C的值。 其 中 C = 9.8 i 5 , μ为变矩器中液体介质的密度， λ为变矩器的扭矩系数， d 为变矩器的循环圓直径； 因 λ无法获得， 本实施例中通过试验获得扭矩系 数当量参数 C来代替液力变矩器的扭矩系数。 The engine output torque in step S3 satisfies =^. The turbine speed is satisfied in step S7 n t = i, n b ; The turbine torque satisfies Μ, = Μ έ ; the turbine power satisfies N, = ςΜ Λ . In step S8, the axle traction force satisfies F = ^, and the locomotive speed satisfies = 2 τπ· 3 Λ^. Wherein (^ is a constant. The present invention is applicable to the torque converter parameters of the hydraulic transmission device is unknown, especially the case where the torque coefficient cannot be measured. It can be seen from the above calculation formula that the technical solution provided by the embodiment is convenient and quick to calculate. Ordinary office software can be quickly calculated without the need to program a computer program. Secondly, it is not necessary to know the torque coefficient of the torque converter, only the torque coefficient equivalent parameter C is required. Where C = 9.8 i 5 , μ is the torque converter The density of the medium medium, λ is the torque coefficient of the torque converter, d is the diameter of the circular circle of the torque converter; because λ cannot be obtained, the torque coefficient equivalent parameter C is obtained by the test in the present embodiment instead of the torque converter. Torque factor.
获得扭矩系数当量参数 C的步骤为： The steps to obtain the torque coefficient equivalent parameter C are:
11 )将变矩器安装在试验台上； 11) Mount the torque converter on the test bench;
12 )向变矩器上施加阻力矩 Μ， ， 使试验台输出恒定功率， 测试变矩 器输出转速 η; 12) Applying a resistive torque 变 to the torque converter, so that the test bench outputs a constant power, and testing the torque converter output speed η;
13 ) 由 C = ^获得扭矩系数当量参数( 。 13) Obtain the torque coefficient equivalent parameter from C = ^ ( .
n n
上述试验过程中通过向变矩器上施加一系列的阻力矩 M， ，测试得出 变矩器对应的一系列输出转速 η , 从而获得对应的一系列扭矩系数当量参 数 C ,再通过 S6由 ^ = (¾2获得一系列泵轮力矩，通过步骤 S7由 = 获 得一系列涡轮转速； 由 = kMb获得一系列涡轮力矩； 由 N, = CxMtnt获得一 系列涡轮功率； 通过步骤 S8由 F = ^ ^获得一系列轮轴牵引力； 由 V = 2m N 得一系、列机车速度，从而根据一系列的轮轴牵引力 F和一系列 与轮轴牵引力 F对应的机车速度 V值能够获得预期牵引曲线。 如图 4所示，本技术方案得出的预期牵引曲线 30与利用现有技术得出的预 期牵引曲线 20相比近似相同， 且本发明的技术方案是利用纯代数的方法计算 预期牵引曲线， 可以根据实际情况， 对快速计算公式进行调整， 用简便的方 法解决了现有技术中繁瑣的预期牵引曲线计算步骤， 并有足够的精度， 能满 足工程需要， 简化了计算流程。 During the above test, a series of resistance torques M are applied to the torque converter, and a series of output rotational speeds η corresponding to the torque converter are obtained, thereby obtaining a corresponding series of torque coefficient equivalent parameters C, and then passing S6 by ^ = (3⁄4 2 obtains a series of pump wheel torques, obtains a series of turbine speeds by = in step S7; obtains a series of turbine torques from = kM b ; obtains a series of turbine powers from N, = C x M t n t ; S8 obtains a series of axle traction by F = ^ ^; a series of locomotive speeds is obtained from V = 2m N, so that the expected traction can be obtained according to a series of axle traction force F and a series of locomotive speed V values corresponding to the axle traction force F. As shown in FIG. 4, the expected traction curve 30 obtained by the technical solution is approximately the same as the expected traction curve 20 obtained by using the prior art, and the technical solution of the present invention is to calculate the expected traction by using a pure algebra method. The curve can be adjusted according to the actual situation, and the calculation procedure of the tedious expected traction curve in the prior art is solved by a simple method, and the accuracy is sufficient. You can meet the engineering needs, simplifying the calculation process.
最后应说明的是： 以上各实施例仅用以说明本发明的技术方案， 而非
对其限制； 尽管参照前述各实施例对本发明进行了详细的说明， 本领域的 普通技术人员应当理解： 其依然可以对前述各实施例所记载的技术方案进 行修改， 或者对其中部分或者全部技术特征进行等同替换； 而这些修改或 者替换， 并不使相应技术方案的本质脱离本发明各实施例技术方案的范
Finally, it should be noted that the above embodiments are only used to illustrate the technical solution of the present invention, and The invention is described in detail with reference to the foregoing embodiments, and those skilled in the art should understand that the technical solutions described in the foregoing embodiments may be modified, or some or all of the technologies may be modified. The features are equivalently replaced; and these modifications or substitutions do not deviate from the essence of the technical solutions of the embodiments of the present invention.
Claims
1、 一种液力传动机车牵引曲线的获得方法， 其特征在于， 该方法包 括以下步骤： 1. A method for obtaining the traction curve of a hydraulic transmission locomotive, characterized in that the method includes the following steps:
1 ) 通过试验获得变矩器转速比 ii、 效率 η、 变扭比 k及扭矩系数当 量参数 C; 1) Obtain the torque converter speed ratio ii, efficiency η, torque ratio k and torque coefficient equivalent parameter C through experiments;
2 )根据发动机额定功率 Ne和辅助设备消耗的功率 Nf获得发动机的净 输出功率 Nc; 2) Obtain the net output power N c of the engine based on the engine rated power Ne and the power consumed by the auxiliary equipment N f ;
3 )根据发动机净输出功率 Nc和发动机额定转速 nc获得发动机输出力 矩 Mc, 并核实发动机输出力矩 Mc是否超出液力传动箱最大输入力矩， 发 动机净输出功率 Nc是否超出液力传动箱最大输入功率； 3) Obtain the engine output torque Mc according to the engine net output power N c and the engine rated speed n c , and verify whether the engine output torque Mc exceeds the maximum input torque of the hydraulic transmission box, and whether the engine net output power N c exceeds the hydraulic transmission Maximum input power of the box;
4 ) 如果发动机输出力矩 Mc超出液力传动箱最大输入力矩和 /或发动 机净输出功率 Nc超出液力传动箱最大输入功率， 则重新选定发动机， 并 重复上述步骤 2 )和步骤 3 )； 如果发动机输出力矩 Mc未超出液力传动箱 最大输入力矩且发动机净输出功率 Nc也未超出液力传动箱最大输入功率， 则进行步骤 5 ) ； 4) If the engine output torque Mc exceeds the maximum input torque of the hydraulic transmission box and/or the engine net output power Nc exceeds the maximum input power of the hydraulic transmission box, reselect the engine and repeat the above steps 2) and 3). ; If the engine output torque Mc does not exceed the maximum input torque of the hydraulic transmission box and the engine net output power N c does not exceed the maximum input power of the hydraulic transmission box, proceed to step 5);
5 )根据发动机的额定转速 nc和输入端齿轮副的传动比 i2获得泵轮转 速 nb; 5) Obtain the pump wheel speed n b according to the rated speed n c of the engine and the transmission ratio i 2 of the input gear pair;
6 )根据泵轮转速 nb和变矩器扭矩系数当量参数 C获得泵轮力矩 Mb; 6) Obtain the pump wheel torque M b according to the pump wheel speed n b and the torque converter torque coefficient equivalent parameter C;
7 )根据泵轮转速 nb及变矩器传动比 ^获得涡轮转速 nt, 根据泵轮力 矩 Mb及变矩器变扭比 k获得涡轮力矩 Mt, 根据涡轮转速 nt和涡轮力矩7) The turbine speed n t is obtained according to the pump wheel speed n b and the torque converter transmission ratio ^. The turbine torque M t is obtained according to the pump wheel torque M b and the torque converter torque ratio k. The turbine speed n t and the turbine torque are obtained.
Mt获得涡轮功率 Nt; M t obtains turbine power N t ;
8 )根据涡轮功率 Nt、 涡轮转速 nt、 输出齿轮副的传动比 i3、 变矩器 效率 η和车轮直径 r获得轮轴牵引力 F; 根据涡轮功率 Nt、 输出齿轮副的 传动比 i3和车轮直径 r获得机车速度 V； 根据轮轴牵引力 F的值与机车速 度 V的值获得预期牵引曲线。 8) Obtain the axle traction force F according to the turbine power N t , turbine speed nt , the transmission ratio i 3 of the output gear pair, the torque converter efficiency eta and the wheel diameter r ; according to the turbine power N t , the transmission ratio i 3 of the output gear pair and wheel diameter r to obtain the locomotive speed V; obtain the expected traction curve based on the values of the axle traction force F and the locomotive speed V.
2、 根据权利要求 1所述的液力传动机车牵引曲线的获得方法， 其特 征在于， 获得扭矩系数当量参数 C的步骤为： 2. The method for obtaining the traction curve of a hydraulic transmission locomotive according to claim 1, characterized in that the step of obtaining the torque coefficient equivalent parameter C is:
11 )将变矩器安装在试验台上； 11) Install the torque converter on the test bench;
12 )向变矩器上施加阻力矩 Μ， ， 使试验台输出恒定功率， 测试变矩
器输出转速 n; 12) Apply resistance torque M, to the torque converter to make the test bench output constant power and test the torque conversion The output speed of the device is n;
13 ) 由 = ^获得扭矩系数当量参数 C。 13) Obtain the torque coefficient equivalent parameter C from = ^.
n n
3、 根据权利要求 1或 2所述的液力传动机车牵引曲线的获得方法， 其特征在于， 步骤 2) 中若发动机辅助设备消耗的功率为 Nf, 则发动机净 输出功率满足 N£ = - 。 3. The method for obtaining the traction curve of a hydraulic transmission locomotive according to claim 1 or 2, characterized in that, in step 2), if the power consumed by the engine auxiliary equipment is N f , then the engine net output power satisfies N £ = - .
4、 根据权利要求 1或 2所述的液力传动机车牵引曲线的获得方法， 其特征在于， 步骤 5) 中泵轮转速满足 = 2 。 4. The method for obtaining the traction curve of a hydraulic transmission locomotive according to claim 1 or 2, characterized in that, in step 5), the pump wheel speed satisfies = 2 .
5、 根据权利要求 1或 2所述的液力传动机车牵引曲线的获得方法， 其特征在于， 步骤 6) 中泵轮力矩满足 6=0¾2。 5. The method for obtaining the traction curve of a hydraulic transmission locomotive according to claim 1 or 2, characterized in that, in step 6), the pump wheel torque satisfies 6 =0¾ 2 .
6、 根据权利要求 1或 2所述的液力传动机车牵引曲线的获得方法， 其特征在于， 步骤 3) 中发动机输出力矩满足 其中（^为常数。 6. The method for obtaining the traction curve of a hydraulic transmission locomotive according to claim 1 or 2, characterized in that the engine output torque in step 3) satisfies where (^ is a constant.
7、 根据权利要求 1或 2所述的液力传动机车牵引曲线的获得方法， 其特征在于， 步骤 7) 中涡轮转速满足 涡轮力矩满足 M^tM 涡 轮功率满足 N^ M 其中（^为常数。 7. The method for obtaining the traction curve of a hydraulic transmission locomotive according to claim 1 or 2, characterized in that, in step 7), the turbine speed satisfies the turbine torque satisfying M^tM and the turbine power satisfies N^M where (^ is a constant.
8、 根据权利要求 1或 2所述的液力传动机车牵引曲线的获得方法， 其特征在于，步骤 8 )中轮轴牵引力满足 F = &^；机车速度满足 = lm Nt , r 8. The method for obtaining the traction curve of a hydraulic transmission locomotive according to claim 1 or 2, characterized in that in step 8), the axle traction force satisfies F = &^; the locomotive speed satisfies = lm N t , r
其中（^为常数。
Among them (^ is a constant.
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| CN201210479054.1A CN102980779B (en) | 2012-11-22 | 2012-11-22 | The preparation method of hydrodynamic drive locomotive traction curve |
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| CN107676186B (en) * | 2017-09-27 | 2020-07-07 | 广州汽车集团股份有限公司 | Engine torque control method |
| CN109489877B (en) * | 2018-12-12 | 2021-04-20 | 中国北方车辆研究所 | Method for testing power flow of transmission link of comprehensive transmission device of road test vehicle |
| CN112484988A (en) * | 2020-11-24 | 2021-03-12 | 重庆红宇精密工业集团有限公司 | Method for testing constant speed ratio performance of hydraulic torque converter |
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