CN102840974B - Non-torque testing device for side loads of mechanical clutches - Google Patents
Non-torque testing device for side loads of mechanical clutches Download PDFInfo
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- CN102840974B CN102840974B CN201110174319.2A CN201110174319A CN102840974B CN 102840974 B CN102840974 B CN 102840974B CN 201110174319 A CN201110174319 A CN 201110174319A CN 102840974 B CN102840974 B CN 102840974B
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Abstract
The invention aims to provide a non-torque testing device for side loads of mechanical clutches. The energy consumption of the testing device is reduced, thus the investment and test costs of the testing device are lowered. A power output shaft of a motor is connected with a flywheel connecting disc, a pressure adjusting device comprises an oil cylinder and a pressure-loaded shaft sleeve with a bearing, the bearing of the pressure-loaded shaft sleeve is arranged in a bearing bush, a power output component of the oil cylinder exerts pressure on the bearing bush, a height-adjustable supporting device is arranged between the flywheel connecting disc and the pressure adjusting device, a bearing pedestal on the inner side of the middle part of the flywheel connecting disc is matched with one end part of a main shaft of a bearing-supported mechanical clutch, the disc edge of the flywheel connecting disc is fixedly connected with the rotating part of the mechanical clutch, the height-adjustable supporting device is pressed against a bearing on the power output side of the main shaft of the mechanical clutch, the pressure-loaded shaft sleeve of the pressure adjusting device is used for being sleeved on the power output end part of the main shaft of the mechanical clutch, and the power output shaft of the motor and the main shaft of the mechanical clutch are coaxially arranged.
Description
Technical field
The present invention relates to mechanical clutch side and carry test unit.
Background technology
When the online transmission of mechanical clutch, it is transmitting torque only.Mechanical clutch is by gear, and when belt transmits power, it be non-online transmission, and now clutch spindle is cantilevered installation, not only bears moment of torsion, is called unbalance loading and exist perpendicular to pulling force or the thrust of the output shaft of cantilever simultaneously.The size of this pulling force or thrust is multiplied by the distance of point of force application to clutch shaft bearing, is called the unbalance loading ability of clutch coupling PTO, and it is this product Specifeca tion speeification.
In the time of production-type test, can on large-scale synthesis testing table, carry out unbalance loading aptitude tests, because mechanical clutch peak power can be 1000-2000KW, its testing table need be invested ten million yuan, and test run once needs to turn round 16 hours, more than energy consumes 30,000 degree.Because mechanical clutch model is many, outgoing control needs frequent test, its investment and testing expenses, and energy consumption is a large problem.
Summary of the invention
The object of the present invention is to provide a kind of mechanical clutch side to carry without torsional moment test device, its Energy Intensity Reduction, therefore investment and testing expenses reduce.
Carry without torsional moment test device for realizing the mechanical clutch side of described object, be characterized in, comprise firm banking, be supported on the simulated engine shell on firm banking, be supported on the motor on simulated engine shell, be supported on rotationally the flywheel terminal pad on simulated engine shell, be supported on the height adjustable support on firm banking and be supported on the pressure adjustment assembly on firm banking, the power output shaft of motor connects flywheel terminal pad, pressure adjustment assembly comprises oil cylinder and the pressure-bearing axle sleeve with bearing, the bearing of pressure-bearing axle sleeve is arranged in a bearing holder (housing, cover), the power output of oil cylinder is exerted pressure on this bearing holder (housing, cover), height adjustable support is between flywheel terminal pad and pressure adjustment assembly, the inner side, middle part of flywheel terminal pad forms bearing seat, this bearing seat is for an end of fitted bearing supported mechanical formula clutch spindle, the web of flywheel terminal pad is fixedly connected with the rotating part of mechanical clutch, height adjustable support is used for the bearing of the power outgoing side that withstands mechanical clutch main shaft, thereby flywheel terminal pad and the height adjustable support mechanical clutch main shaft of support rotating jointly, the backup rolls cover of pressure adjustment assembly is for being enclosed within the clutch end portion of mechanical clutch main shaft, the power output shaft of motor, mechanical clutch main shaft coaxial line.
Described mechanical clutch side is carried without torsional moment test device, and its further feature is that height adjustable support is lifting jack.
Motor drives flywheel terminal pad, the rotating part of flywheel terminal pad driving mechanical formula clutch coupling, make the bearing of mechanical clutch main shaft on flywheel terminal pad, under the common support of the bearing that height adjustable support withstands, rotate, the pressure that pressure adjustment assembly imposes on pressure-bearing axle sleeve becomes the unbalance loading of mechanical clutch main shaft, thereby described mechanical clutch side is carried the unbalance loading performance that can be used for test mechanical formula clutch coupling without torsional moment test device, and the power that motor drives is designed to only meet the energy that the friction of clutch spindle bearing element consumes, therefore Energy Intensity Reduction, therefore investment and testing expenses reduce.Aforementioned techniques scheme is mainly that moment of torsion and unbalance loading are separated, by dingus low energy consumption device independent test clutch coupling unbalance loading ability.Adapt to very convenient to the adjustment of different model product.Avoided by conventional gears, belt, chain transmission etc. goes to produce unbalance loading, also silk ribbon attached to an official seal or a medal solution the contradiction of loading and high-speed rotation.
Brief description of the drawings
Fig. 1 is that mechanical clutch side is carried the front view without torsional moment test device.
Fig. 2 is the unbalance loading ability test schematic diagram of the product of the new research and development on the test unit shown in Fig. 1.
In figure:
Embodiment
As depicted in figs. 1 and 2, mechanical clutch side is carried without torsional moment test device and is comprised firm banking 1, is supported on simulated engine shell 11 on firm banking 1, is supported on motor 4 on simulated engine shell 11, is supported on rotationally flywheel terminal pad 8 on simulated engine shell 11, is supported on the height adjustable support 22 on firm banking 1 and is supported on the pressure adjustment assembly on firm banking 1.
The outside of flywheel terminal pad 8 is connected by simulated engine shell 11 rotationally by bearing 2, the middle inside of flywheel terminal pad 8 forms bearing seat 81, and the edge of flywheel terminal pad 8 is for for example, being connected with the pivotable parts (active gear ring) of mechanical clutch.Motor 4 is arranged on simulated engine shell 11 by motor terminal pad 7, and its power output shaft connects flywheel terminal pad 8, and driving device formula clutch coupling is gear ring initiatively, and then rotating part with dynamic clutch rotates.Motor 4 is high speed oil motor, and its power can be designed to only meet the energy that the friction of clutch spindle bearing element consumes, and is about 10KW, and speed can be adjusted to 2400rpm.The mechanical clutch side of different model is carried without torsional moment test device and is changed different simulated engine shells 11 and flywheel terminal pad 8.
Pressure adjustment assembly comprises the oil cylinder 15 that supported by support 16 and the pressure-bearing axle sleeve 25 with bearing 20, and the bearing 20 of pressure-bearing axle sleeve 25 is arranged in bearing holder (housing, cover) 19, and the power output 18 of oil cylinder 15 is exerted pressure on bearing holder (housing, cover) 25.Bearing holder (housing, cover) 19 is for being enclosed within the main shaft of mechanical clutch.Power output 18 is for example vee-block.
Height adjustable support 22 is between flywheel terminal pad 8 and pressure adjustment assembly.Height Adjustable bracing or strutting arrangement 22 is for example lifting jack.
The inner side, middle part of flywheel terminal pad 8 forms bearing seat 81, and this bearing seat 81 is for an end of fitted bearing supported mechanical formula clutch spindle.
As shown in Figure 2, the side that tested mechanical clutch 26 is arranged on is as shown in Figure 1 carried without on torsional moment test device, particularly, the shell 263 of mechanical clutch is fixedly connected with simulation of engine bell housing 12 (end face is all designed to SAE (American Association of Engineers's standard) interface), the shell 263 of mechanical clutch is supported on main shaft 261 by bearing 83, the left end of the main shaft 261 of mechanical clutch 28 is arranged on by bearing 82 in the bearing seat 81 of inner side, middle part of flywheel terminal pad 8, the bearing 83 of the power outgoing side of the main shaft 261 of mechanical clutch 26 is withstood by Height Adjustable bracing or strutting arrangement 22.The pressure-bearing axle sleeve 25 of pressure adjustment assembly is enclosed within the outside of the power efferent of main shaft 261.Pressure-bearing axle sleeve 25 can regulate to the distance (being made as variable X) of clutch coupling 83.
The edge of flywheel terminal pad 8 is fixedly connected with by bolt 23 with mechanical clutch 26, and when motor 4 flywheel driven terminal pads 8 rotate, band dynamic clutch 26 rotates, and then clutch output shaft 261 drives pressure-bearing cover 25 to rotate.
With oil cylinder 15 to rotation pressure-bearing axle sleeve 25 execute clutch coupling unbalance loading pressure (being made as variable P) by technical manual.
Unbalance loading pressure P is multiplied by offset distance X=unbalance loading ability.Unbalance loading is applied on clutch bearing on the main shaft 261 of rotation.Rotating speed in accordance with regulations, unbalance loading, the technical manuals such as time get final product the temperature rise of gaging clutch bearing, abrasion condition.
Embodiment as shown in Figure 1 separates moment of torsion and unbalance loading, by dingus low energy consumption device independent test clutch coupling unbalance loading ability.Adapt to very convenient to the adjustment of different model product.Avoided by conventional gears, belt, chain transmission etc. goes to produce unbalance loading, also silk ribbon attached to an official seal or a medal solution the contradiction of loading and high-speed rotation.
Claims (5)
1. mechanical clutch side is carried without torsional moment test device, it is characterized in that, comprise firm banking, be supported on the simulated engine shell on firm banking, be supported on the motor on simulated engine shell, be supported on rotationally the flywheel terminal pad on simulated engine shell, be supported on the height adjustable support on firm banking and be supported on the pressure adjustment assembly on firm banking, the power output shaft of motor connects flywheel terminal pad, pressure adjustment assembly comprises oil cylinder and the pressure-bearing axle sleeve with bearing, the bearing of pressure-bearing axle sleeve is arranged in a bearing holder (housing, cover), the power output of oil cylinder is exerted pressure on this bearing holder (housing, cover), height adjustable support is between flywheel terminal pad and pressure adjustment assembly, the inner side, middle part of flywheel terminal pad forms bearing seat, this bearing seat is for an end of fitted bearing supported mechanical formula clutch spindle, the web of flywheel terminal pad is fixedly connected with the rotating part of mechanical clutch, height adjustable support is used for the bearing of the power outgoing side that withstands mechanical clutch main shaft, thereby flywheel terminal pad and the height adjustable support mechanical clutch main shaft of support rotating jointly, the pressure-bearing axle sleeve of pressure adjustment assembly is enclosed within the clutch end portion of mechanical clutch main shaft, the power output shaft of motor, mechanical clutch main shaft coaxial line.
2. mechanical clutch side as claimed in claim 1 is carried without torsional moment test device, it is characterized in that, height adjustable support is lifting jack.
3. mechanical clutch side as claimed in claim 1 is carried without torsional moment test device, it is characterized in that, the pressure-bearing axle sleeve of pressure adjustment assembly is enclosed within the clutch end portion of mechanical clutch main shaft movably to adjust the desired unbalance loading arm of force of test.
4. mechanical clutch side as claimed in claim 1 is carried without torsional moment test device, it is characterized in that, motor is high speed oil motor, and its power can be designed to only meet the energy that the friction of clutch spindle bearing element consumes.
5. mechanical clutch side as claimed in claim 1 is carried without torsional moment test device, it is characterized in that, the simulation of engine bell housing end face of simulated engine shell is designed to American Association of Engineers's standard interface.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110174319.2A CN102840974B (en) | 2011-06-24 | 2011-06-24 | Non-torque testing device for side loads of mechanical clutches |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110174319.2A CN102840974B (en) | 2011-06-24 | 2011-06-24 | Non-torque testing device for side loads of mechanical clutches |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102840974A CN102840974A (en) | 2012-12-26 |
| CN102840974B true CN102840974B (en) | 2014-10-22 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110174319.2A Active CN102840974B (en) | 2011-06-24 | 2011-06-24 | Non-torque testing device for side loads of mechanical clutches |
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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| KR101593837B1 (en) * | 2014-11-12 | 2016-02-12 | 두산중공업 주식회사 | Performance of the test object test device |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| PL291901A1 (en) * | 1990-10-03 | 1992-06-01 | Fiat Auto Spa | Apparatus for coupling a system of intertial masses with a shaft in particular at brake and clutch testing stands |
| CN2648428Y (en) * | 2003-09-23 | 2004-10-13 | 洛阳轴研科技股份有限公司 | Clutch separating bearing analog testing machine for car |
| CN2663962Y (en) * | 2003-12-06 | 2004-12-15 | 重庆大渡口区利德工业制造有限公司 | Combination property detecting instrument housing of automatic clutch |
| CN101561352A (en) * | 2009-04-29 | 2009-10-21 | 邵春平 | Automobile clutch comprehensive performance test bed |
| CN101660970A (en) * | 2009-09-24 | 2010-03-03 | 浙江天马轴承股份有限公司 | Large bearing testing machine |
| CN102062696A (en) * | 2010-12-17 | 2011-05-18 | 湖北三环离合器有限公司 | Multifunctional simulation test bed for auto clutch |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0552703A (en) * | 1991-08-28 | 1993-03-02 | Aisin Chem Co Ltd | Method and apparatus for testing lockup clutch |
-
2011
- 2011-06-24 CN CN201110174319.2A patent/CN102840974B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| PL291901A1 (en) * | 1990-10-03 | 1992-06-01 | Fiat Auto Spa | Apparatus for coupling a system of intertial masses with a shaft in particular at brake and clutch testing stands |
| CN2648428Y (en) * | 2003-09-23 | 2004-10-13 | 洛阳轴研科技股份有限公司 | Clutch separating bearing analog testing machine for car |
| CN2663962Y (en) * | 2003-12-06 | 2004-12-15 | 重庆大渡口区利德工业制造有限公司 | Combination property detecting instrument housing of automatic clutch |
| CN101561352A (en) * | 2009-04-29 | 2009-10-21 | 邵春平 | Automobile clutch comprehensive performance test bed |
| CN101660970A (en) * | 2009-09-24 | 2010-03-03 | 浙江天马轴承股份有限公司 | Large bearing testing machine |
| CN102062696A (en) * | 2010-12-17 | 2011-05-18 | 湖北三环离合器有限公司 | Multifunctional simulation test bed for auto clutch |
Non-Patent Citations (1)
| Title |
|---|
| JP特開平5-52703A 1993.03.02 |
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| CN102840974A (en) | 2012-12-26 |
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