CN103776630B - Metal band type stepless speed variator slip rate testboard - Google Patents
Metal band type stepless speed variator slip rate testboard Download PDFInfo
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- CN103776630B CN103776630B CN201410053227.2A CN201410053227A CN103776630B CN 103776630 B CN103776630 B CN 103776630B CN 201410053227 A CN201410053227 A CN 201410053227A CN 103776630 B CN103776630 B CN 103776630B
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- oil cylinder
- drivewheel
- cvt
- driven pulley
- oil
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Abstract
The invention discloses a kind of metal band type stepless speed variator slip rate testboard, including mechanical driving part, hydraulic part and observing and controlling part. The invention has the beneficial effects as follows: when CVT drivewheel oil cylinder is fixing, it is possible to be accurately performed the test of CVT slip rate. And clamping force is controlled, carry out the test of slip rate when different clamping force, draw and the optimal slip ratio corresponding to the highest transmission efficiency of CVT. The present invention is significant to realizing the control research of CVT optimal slip ratio.
Description
Technical field
The present invention relates to the testboard of a kind of automobile metal belt buncher (CVT) slip rate test, be mainly used in the test of automobile CVT slip rate, development and through engineering approaches for sliding optimal control policy are provided fundamental basis.
Background technology
The major reason that CVT transmission efficiency is on the low side is that metal tape clamping force is excessive, with ensure metal tape under any operating mode non-slip, and excessive clamping force not only makes CVT transmission efficiency reduce, and adds the energy consumption of hydraulic control system. There are some researches show, reduce metal tape clamping force, make metal tape produce certain sliding with belt wheel, it is possible to improve CVT transmission efficiency. But, excessive sliding not only can cause the rapid decline of transmission efficiency, and can have a strong impact on the life-span of CVT. Therefore, CVT there will necessarily be an optimal slip ratio in running, makes the transmission efficiency of CVT reach maximum. The test of optimal slip ratio all had very important significance for the transmission efficiency of metal belt-type CVT, life-span.
Slip rate ε=ig/ is, it is by the speed ratio i of CVTsWith gear ratio igTogether decide on. And gear ratio is subject to slave cylinder pressure and the joint effect of actuating cylinder pressure, time any one changes when principal and subordinate wheel oil cylinder working-pressure, inherently cause the change of another one, thus causing the change of gear ratio. The definition of optimal slip ratio: when CVT operates in a certain gear ratio, the slip rate corresponding to the highest transmission efficiency of CVT in this condition, it is the optimal slip ratio under this gear ratio. Domestic vehicles buncher testboard is in the method for testing of slip rate, it does not have a kind of testboard when gear ratio is certain, metal belt-type CVT slip rate can tested. Obtaining the optimal slip ratio under gear ratio one stable condition it is necessary to put forth effort to solve in CVT running, gear ratio is subject to this relation of the joint effect of slave cylinder pressure and actuating cylinder pressure.
Summary of the invention
It is an object of the invention to provide a kind of slip rate to CVT and carry out the testboard of accurately test, can solve the problem that in CVT slip rate testing experiment, gear ratio is subject to drivewheel oil cylinder and driven pulley this problem of oil cylinder joint effect, provides technical foundation for sliding optimum control.
The technical scheme is that, a kind of metal band type stepless speed variator slip rate testboard, including mechanical driving part, hydraulic part and observing and controlling part, described mechanical driving part includes stand, equipped with drive motor on stand, loading motor, equipped with input torque rotary speed sensor on the output shaft of drive motor, the axle head at the output shaft of input torque rotary speed sensor couples CVT input shaft shaft coupling;Equipped with outfan torque rotary speed sensor on the output shaft of loading motor, the axle head at the output shaft of outfan torque rotary speed sensor couples CVT outfan shaft coupling; Described hydraulic part includes hydraulic pump drive motor, is connected to hydraulic pump at the hydraulic pump drive motor first line of a couplet, and the oil-out of hydraulic pump connects the P mouth of electromagnetic proportion relief valve, driven pulley oil cylinder and fuel inlet ball check valve respectively; Another termination drivewheel oil cylinder of fuel inlet ball check valve, the pipeline between fuel inlet ball check valve and drivewheel oil cylinder is connected to oil return ball valve; Described observing and controlling part includes monitoring and control unit and sensor-based system, and described monitoring and control unit includes part of detecting and control part, and part of detecting includes data collecting card, communication serial ports, display; Described control part includes control knob, control knob connects logic input. interface, logic input. interface connects control logic circuit and electromagnetic proportion relief valve, control logic circuit connects drive motor converter, loading motor converter respectively, drive motor converter connects drive motor, and loading motor converter connects loading motor; Described sensor-based system is connected with data collecting card, includes input torque speed probe, drivewheel laser range finder, driven pulley laser range finder, drivewheel oil cylinder working-pressure sensor, driven pulley oil cylinder working-pressure sensor, output shaft torque, speed probe; Drivewheel laser range finder is contained in by drivewheel oil cylinder, driven pulley laser range finder is contained in by driven pulley oil cylinder, drivewheel oil cylinder working-pressure sensor is contained in fuel inlet ball check valve with on the indirectly pipeline of drivewheel oil cylinder, and driven pulley oil cylinder working-pressure sensor is contained on the pipeline between the P mouth of electromagnetic proportion relief valve and driven pulley oil cylinder.
The invention has the beneficial effects as follows: when CVT drivewheel oil cylinder is fixing, it is possible to be accurately performed the test of CVT slip rate. And the clamping force of CVT is controlled, carry out the test of slip rate when different clamping force, draw and the slip rate corresponding to the highest transmission efficiency of CVT. The present invention is significant to realizing the control research of CVT optimal slip ratio.
Accompanying drawing explanation
Fig. 1 is mechanical driving part structure chart of the present invention;
Fig. 2 is hydraulic part hydraulic schematic diagram of the present invention;
Fig. 3 is observing and controlling partial block diagram of the present invention.
Detailed description of the invention
As shown in Figure 1, Figure 2, Figure 3 shows, a kind of metal band type stepless speed variator slip rate testboard, including mechanical driving part, hydraulic part and observing and controlling part, it is characterized in that: described mechanical driving part includes stand 15, equipped with drive motor 1 on stand 15, loading motor 14, equipped with input torque rotary speed sensor 2 on the output shaft of drive motor 1, the output shaft of input torque rotary speed sensor 2 is coupled with the power shaft 4 of CVT5 by CVT input shaft shaft coupling 3; Equipped with outfan torque rotary speed sensor 13 on the output shaft of loading motor 14, the output shaft of outfan torque rotary speed sensor 13 is coupled with the power shaft 11 of CVT5 by CVT outfan shaft coupling 12; Described hydraulic part includes hydraulic pump drive motor 16, and coupling at hydraulic pump drive motor 16 has hydraulic pump 17, the oil-out of hydraulic pump 17 to connect the P mouth of electromagnetic proportion relief valve 18, driven pulley oil cylinder 10, fuel inlet ball check valve 19 respectively; Another termination drivewheel oil cylinder 7 of fuel inlet ball check valve 19, the pipeline between fuel inlet ball check valve 19 and drivewheel oil cylinder 7 is connected to oil return ball valve 20; Described observing and controlling part includes monitoring and control unit and sensor-based system, and described monitoring and control unit includes part of detecting and control part, and part of detecting includes data collecting card, communication serial ports, display;Described control part includes control knob, control knob connects logic input. interface, logic input. interface connects control logic circuit and electromagnetic proportion relief valve 18, control logic circuit connects drive motor converter, loading motor converter respectively, drive motor converter connects drive motor 1, and loading motor converter connects loading motor 14; Described sensor-based system is connected with data collecting card, includes input torque speed probe 2, drivewheel laser range finder 9, driven pulley laser range finder 8, drivewheel oil cylinder working-pressure sensor 21, driven pulley oil cylinder working-pressure sensor 22, output shaft torque, speed probe 13; It is other that drivewheel laser range finder 9 is contained in drivewheel oil cylinder 7, it is other that driven pulley laser range finder 8 is contained in driven pulley oil cylinder 10, drivewheel oil cylinder working-pressure sensor 21 is contained in fuel inlet ball check valve 19 with on the indirectly pipeline of drivewheel oil cylinder 7, and driven pulley oil cylinder working-pressure sensor 22 is contained on the pipeline between the P mouth of electromagnetic proportion relief valve 18 and driven pulley oil cylinder 10.
Comprising the following steps that of test.
Testboard is after full speed is than zero load running-in in situation:
1. control hydraulic pump 17 output flow 25L/min by hydraulic pump drive motor 16.
2. manual unlocking fuel inlet ball check valve 19, close oil return ball valve 20, now fluid flows into drivewheel oil cylinder 7 through fuel inlet ball check valve 19, change the gear ratio of CVT5, when gear ratio reaches desired value 1.2, this desired value is measured by drivewheel laser range finder 9 and driven pulley laser range finder 8 and is obtained, and closes fuel inlet ball check valve 19. Owing to fuel inlet ball check valve 19 is Non-follow control, it is possible that fluid enters the situation that drivewheel oil cylinder 7 is too much, now can opening oil return ball valve 20, fluid flows into fuel tank T from drivewheel oil cylinder 7 through oil return ball valve 20, when gear ratio is close to desired value, close oil return ball valve 20. Finally regulating the gear ratio obtained is 1.18.
3. control electromagnetic proportion relief valve 18 by control station, regulate driven pulley cylinder oil extremely safe oil pressure 1.5Mpa.
4. drive motor 1 is carried out rotating speed control by converter, makes the stabilization of speed of drive motor 1 at 1000r/min.
5. loading motor 14 is carried out direct torque by converter, and the torque making loading motor 14 is stable at 40N/min.
6. after regulating, regulate oil pressure to maximum oil pressure 2Mpa by electromagnetic proportion relief valve 18, begin through monitoring and control unit and carry out data record, draw CVT5 slip rate now and efficiency.
7. keeping the gear ratio of CVT5, torque, rotating speed is constant, reduces oil pressure successively by electromagnetic proportion relief valve 18, namely reduces the clamping force of CVT, from 2Mpa to 1.9, and 1.8 ..., until substantially reducing occurs in CVT5 efficiency. Then oil pressure extremely safe oil pressure is raised.
8., in the slip rate of many groups CVT5 recorded with the data of efficiency, finding out most effective one group is 91.2%, and now the oil pressure of CVT5 driven pulley 10 is 0.5Mpa, and corresponding slip rate 1.2% is the optimal slip ratio under this operating mode.
9. regulate gear ratio, torque, rotating speed, carry out next group experiment.
Through organizing experiment, CVT5 optimal slip ratio under different operating modes can be drawn more.
Slip rate ε=the ig/iS of CVT5, is the speed ratio by CVT5 and gear ratio is determined. Speed ratio is=ωp/ ωs=Np/ ns, the input speed N that input torque rotary speed sensor measurement obtains can be passed throughpThe output speed n obtained with outfan torque rotary speed sensor measurementsDraw. Gear ratio ig=Rs/ Rp, the axial displacement corresponding with the principal and subordinate wheel radius of gyration can be measured by laser range finder and draw, thus obtaining the slip rate of CVT5.
The efficiency eta of CVT is defined as: η=(loading motor torque × loading motor rotating speed)/(drive motor torque × drive motor rotating speed).
Claims (1)
1. a metal band type stepless speed variator slip rate testboard, including mechanical driving part, hydraulic part and observing and controlling part, it is characterized in that: described mechanical driving part includes stand (15), equipped with drive motor (1) on stand (15), loading motor (14), equipped with input torque rotary speed sensor (2) on the output shaft of drive motor (1), the output shaft of input torque rotary speed sensor (2) is coupled with the power shaft (4) of CVT (5) by CVT input shaft shaft coupling (3); Equipped with outfan torque rotary speed sensor (13) on the output shaft of loading motor (14), the output shaft of outfan torque rotary speed sensor (13) is coupled with the output shaft (11) of CVT (5) by CVT outfan shaft coupling (12); Described hydraulic part includes hydraulic pump drive motor (16), being connected to hydraulic pump (17) at hydraulic pump drive motor (16) first line of a couplet, the oil-out of hydraulic pump (17) connects the P mouth of electromagnetic proportion relief valve (18), driven pulley oil cylinder (10) and fuel inlet ball check valve (19) respectively; Another termination drivewheel oil cylinder (7) of fuel inlet ball check valve (19), the pipeline between fuel inlet ball check valve (19) and drivewheel oil cylinder (7) is connected to oil return ball valve (20); Described observing and controlling part includes monitoring and control unit and sensor-based system, and described monitoring and control unit includes part of detecting and control part, and part of detecting includes data collecting card, communication serial ports, display; Described control part includes control knob, control knob connects logic input. interface, logic input. interface connects control logic circuit and electromagnetic proportion relief valve (18), control logic circuit connects drive motor converter, loading motor converter respectively, drive motor converter connects drive motor (1), and loading motor converter connects loading motor (14); Described sensor-based system is connected with data collecting card, include input torque speed probe (2), drivewheel laser range finder (9), driven pulley laser range finder (8), drivewheel oil cylinder working-pressure sensor (21), driven pulley oil cylinder working-pressure sensor (22), output shaft torque, speed probe (13); It is other that drivewheel laser range finder (9) is contained in drivewheel oil cylinder (7), it is other that driven pulley laser range finder (8) is contained in driven pulley oil cylinder (10), drivewheel oil cylinder working-pressure sensor (21) is contained in fuel inlet ball check valve (19) with on the indirectly pipeline of drivewheel oil cylinder (7), and driven pulley oil cylinder working-pressure sensor (22) is contained on the pipeline between the P mouth of electromagnetic proportion relief valve (18) and driven pulley oil cylinder (10);
Manual unlocking fuel inlet ball check valve (19), close oil return ball valve (20), now fluid flows into drivewheel oil cylinder (7) through fuel inlet ball check valve (19), change the gear ratio of CVT (5), when gear ratio reaches desired value, described desired value is measured by drivewheel laser range finder (9) and driven pulley laser range finder (8) and is obtained, and closes fuel inlet ball check valve (19); Owing to fuel inlet ball check valve (19) is Non-follow control, it is possible that fluid enters the situation that drivewheel oil cylinder (7) is too much, now can open oil return ball valve (20), fluid flows into fuel tank T from drivewheel oil cylinder (7) through oil return ball valve (20), when gear ratio is close to desired value, close oil return ball valve (20);
The gear ratio of maintenance CVT (5), torque, rotating speed is constant, reduces oil pressure successively by electromagnetic proportion relief valve (18), until substantially reducing occurs in CVT (5) efficiency, then raises oil pressure extremely safe oil pressure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410053227.2A CN103776630B (en) | 2014-02-13 | 2014-02-13 | Metal band type stepless speed variator slip rate testboard |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410053227.2A CN103776630B (en) | 2014-02-13 | 2014-02-13 | Metal band type stepless speed variator slip rate testboard |
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| Publication Number | Publication Date |
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| CN103776630A CN103776630A (en) | 2014-05-07 |
| CN103776630B true CN103776630B (en) | 2016-06-15 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201410053227.2A Expired - Fee Related CN103776630B (en) | 2014-02-13 | 2014-02-13 | Metal band type stepless speed variator slip rate testboard |
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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN106594269B (en) * | 2016-12-30 | 2018-05-22 | 湘潭大学 | Buncher metal belt transmission reliability compensates control device and control method |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2658451Y (en) * | 2003-11-21 | 2004-11-24 | 周云山 | Digital electrohydraulic control system for metal belt type stepless speed changer |
| CN102353535A (en) * | 2011-07-01 | 2012-02-15 | 重庆大学 | Low-power-consumption hardware-in-loop test platform and method for stepless speed changer of vehicle |
| CN202994466U (en) * | 2012-12-28 | 2013-06-12 | 四川诚邦测控技术有限公司 | CVT test system |
| CN103162958A (en) * | 2013-02-06 | 2013-06-19 | 河南科技大学 | Vehicle hydraulic machinery stepless transmission test bench and test system |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5037954B2 (en) * | 2007-01-15 | 2012-10-03 | ヤマハ発動機株式会社 | Belt type continuously variable transmission and vehicle |
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2014
- 2014-02-13 CN CN201410053227.2A patent/CN103776630B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2658451Y (en) * | 2003-11-21 | 2004-11-24 | 周云山 | Digital electrohydraulic control system for metal belt type stepless speed changer |
| CN102353535A (en) * | 2011-07-01 | 2012-02-15 | 重庆大学 | Low-power-consumption hardware-in-loop test platform and method for stepless speed changer of vehicle |
| CN202994466U (en) * | 2012-12-28 | 2013-06-12 | 四川诚邦测控技术有限公司 | CVT test system |
| CN103162958A (en) * | 2013-02-06 | 2013-06-19 | 河南科技大学 | Vehicle hydraulic machinery stepless transmission test bench and test system |
Non-Patent Citations (2)
| Title |
|---|
| 基于滑移率控制的金属带式无级变速器夹紧力研究;曹成龙 等;《中国机械工程》;20121210;第23卷(第23期);正文第47-55页，图4-2~4-10，表4-5 * |
| 金属带式CVT变速机理试验研究;梁晓龙;《万方学位论文库》;20131107;第2895-2897页，图5 * |
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