CN102840974A - 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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- CN102840974A CN102840974A CN2011101743192A CN201110174319A CN102840974A CN 102840974 A CN102840974 A CN 102840974A CN 2011101743192 A CN2011101743192 A CN 2011101743192A CN 201110174319 A CN201110174319 A CN 201110174319A CN 102840974 A CN102840974 A CN 102840974A
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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 the mechanical clutch side and carry test unit.
Background technology
During the online transmission of mechanical clutch, it only transmits moment of torsion.Mechanical clutch is through gear, and belt is during with transmission of power, and it be non-online transmission, and this moment, clutch spindle was the cantilevered installation, not only bore moment of torsion, and exists pulling force or thrust perpendicular to the output shaft of cantilever to be called unbalance loading simultaneously.The size of this pulling force or thrust multiply by the distance of point of force application to the clutch shaft bearing, is called the unbalance loading ability of clutch coupling PTO, and it is this product Specifeca tion speeification.
When production-type test, can on the large-scale synthesis testing table, carry out the unbalance loading aptitude tests; Because the mechanical clutch peak power can be 1000-2000KW; Its testing table need be invested ten million yuan, and test run once need turn round 16 hours, more than energy consumption 30,000 degree.Because the mechanical clutch model is many, outgoing control needs frequent test, its investment and testing expenses, and energy consumption is a big problem.
Summary of the invention
The object of the present invention is to provide a kind of mechanical clutch side to carry no torsional moment test device, its energy consumption reduces, and therefore investment and testing expenses reduce.
For the mechanical clutch side that realizes said purpose is carried no torsional moment test device; Be characterized in; Comprise firm banking, be supported on simulated engine shell on the firm banking, be supported on motor on the simulated engine shell, be supported on flywheel terminal pad on the simulated engine shell rotationally, be supported on the adjustable height bracing or strutting arrangement on the firm banking and be supported on the pressure adjustment assembly on the firm banking; The PTO of motor connects the flywheel terminal pad; Pressure adjustment assembly comprises the pressure-bearing axle sleeve that oil cylinder and tape spool hold, and the Bearing Installation of pressure-bearing axle sleeve is in a bearing holder (housing, cover), and the power output of oil cylinder is exerted pressure on this bearing holder (housing, cover); The adjustable height bracing or strutting arrangement is between flywheel terminal pad and pressure adjustment assembly; The inboard bearing seat that forms in the middle part of flywheel terminal pad, this bearing seat is used for an end of fitted bearing supported mechanical formula clutch spindle, and the web of flywheel terminal pad is fixedly connected the rotating part of mechanical clutch; The adjustable height bracing or strutting arrangement is used to withstand the bearing of the power outgoing side of mechanical clutch main shaft; But thereby the mechanical clutch main shaft that flywheel terminal pad and adjustable height bracing or strutting arrangement together support are rotated, the backup rolls cover of pressure adjustment assembly is used to be enclosed within the clutch end portion of mechanical clutch main shaft, the PTO of motor, mechanical clutch main shaft coaxial line.
Described mechanical clutch side is carried no torsional moment test device, and its further characteristics are that the adjustable height bracing or strutting arrangement is a lifting jack.
Motor driven flywheel terminal pad; The flywheel terminal pad drives the rotating part of mechanical clutch; Make the mechanical clutch main shaft under the together support of the bearing that the bearing on the flywheel terminal pad, adjustable height bracing or strutting arrangement withstand, rotate; The pressure that pressure adjustment assembly imposes on the 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 no torsional moment test device can be used for test mechanical formula clutch coupling, and the power of motor driven is designed to only to satisfy the energy that the friction of clutch spindle bearing element consumes and gets final product; Therefore energy consumption reduces, and therefore investment and testing expenses reduce.The aforementioned techniques scheme mainly is that moment of torsion and unbalance loading are separated, with dingus low energy consumption device independent test clutch coupling unbalance loading ability.Adjustment adapts to very convenient to the different model product.Avoided using conventional gears, belt, chain transmission etc. go to produce unbalance loading, and also silk ribbon attached to an official seal or a medal has been separated the contradiction of loading and high speed rotating.
Description of drawings
Fig. 1 is the front view that the mechanical clutch side is carried no torsional moment test device.
Fig. 2 is the unbalance loading ability test schematic diagram of the product of the new research and development on test unit shown in Figure 1.
Among the figure:
Embodiment
As depicted in figs. 1 and 2, the mechanical clutch side is carried no torsional moment test device and is comprised firm banking 1, is supported on simulated engine shell 11 on the firm banking 1, is supported on motor 4 on the simulated engine shell 11, is supported on flywheel terminal pad 8 on the simulated engine shell 11 rotationally, is supported on the adjustable height bracing or strutting arrangement 22 on the firm banking 1 and is supported on the pressure adjustment assembly on the firm banking 1.
The outside of flywheel terminal pad 8 is connected by simulated engine shell 11 through bearing 2 rotationally; The middle inside of flywheel terminal pad 8 forms bearing seat 81, and the edge of flywheel terminal pad 8 is used for being connected with the pivotable parts (for example active gear ring) of mechanical clutch.Motor 4 is installed on the simulated engine shell 11 through motor terminal pad 7, and its PTO connects flywheel terminal pad 8, and driving device formula clutch coupling is gear ring initiatively, and then drives the rotating part rotation of clutch coupling.Motor 4 is the high speed oil motor, and its power can be designed to only to satisfy the energy that the friction of clutch spindle bearing element consumes and get final product, and is about 10KW, and adjustable-speed is to 2400rpm.The mechanical clutch side of different model is carried different simulated engine shell 11 and the flywheel terminal pads 8 of no torsional moment test device replacing.
Pressure adjustment assembly comprises that the oil cylinder 15 that is supported by support 16 holds 20 pressure-bearing axle sleeve 25 with tape spool, and the bearing 20 of pressure-bearing axle sleeve 25 is installed in the 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 used to be enclosed within the main shaft of mechanical clutch.Power output 18 for example is a vee-block.
Adjustable height bracing or strutting arrangement 22 is between flywheel terminal pad 8 and pressure adjustment assembly.Height Adjustable bracing or strutting arrangement 22 for example is a lifting jack.
The inboard bearing seat 81 that forms in the middle part of flywheel terminal pad 8, this bearing seat 81 is used for an end of fitted bearing supported mechanical formula clutch spindle.
As shown in Figure 2; To be installed in side as shown in Figure 1 by examination mechanical clutch 26 carries on the no torsional moment test device; Particularly; The shell 263 of mechanical clutch is fixedly connected with simulation of engine bell housing 12 (end face all is designed to SAE (AAE's standard) interface); The shell 263 of mechanical clutch is supported on the main shaft 261 by bearing 83, and the left end of the main shaft 261 of mechanical clutch 28 is installed in the inboard bearing seat 81 in the middle part of flywheel terminal pad 8 through bearing 82, and 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 be regulated to the distance (being made as variable X) of clutch coupling 83.
The edge of flywheel terminal pad 8 is fixedly connected through bolt 23 with mechanical clutch 26, when motor 4 drives 8 rotations of flywheel terminal pad, drive clutch coupling 26 and rotate, and then clutch output shaft 261 drives 25 rotations of pressure-bearing cover.
Pressure-bearing axle sleeve 25 with 15 pairs of rotations of oil cylinder is executed clutch coupling unbalance loading pressure (being made as variable P) by technical manual.
The unbalance loading pressure P is multiplied by offset distance X=unbalance loading ability.Unbalance loading affacts on the clutch bearing on the main shaft 261 of rotation.By the rotating speed of regulation, unbalance loading, 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, with dingus low energy consumption device independent test clutch coupling unbalance loading ability.Adjustment adapts to very convenient to the different model product.Avoided using conventional gears, belt, chain transmission etc. go to produce unbalance loading, and also silk ribbon attached to an official seal or a medal has been separated the contradiction of loading and high speed rotating.
Claims (5)
1. the mechanical clutch side is carried no torsional moment test device; It is characterized in that; Comprise firm banking, be supported on simulated engine shell on the firm banking, be supported on motor on the simulated engine shell, be supported on flywheel terminal pad on the simulated engine shell rotationally, be supported on the adjustable height bracing or strutting arrangement on the firm banking and be supported on the pressure adjustment assembly on the firm banking; The PTO of motor connects the flywheel terminal pad; Pressure adjustment assembly comprises the pressure-bearing axle sleeve that oil cylinder and tape spool hold, and the Bearing Installation of pressure-bearing axle sleeve is in a bearing holder (housing, cover), and the power output of oil cylinder is exerted pressure on this bearing holder (housing, cover); The adjustable height bracing or strutting arrangement is between flywheel terminal pad and pressure adjustment assembly; The inboard bearing seat that forms in the middle part of flywheel terminal pad, this bearing seat is used for an end of fitted bearing supported mechanical formula clutch spindle, and the web of flywheel terminal pad is fixedly connected the rotating part of mechanical clutch; The adjustable height bracing or strutting arrangement is used to withstand the bearing of the power outgoing side of mechanical clutch main shaft; But thereby the mechanical clutch main shaft that flywheel terminal pad and adjustable height bracing or strutting arrangement together support are rotated, the backup rolls cover of pressure adjustment assembly is enclosed within the clutch end portion of mechanical clutch main shaft, the PTO of motor, mechanical clutch main shaft coaxial line.
2. mechanical clutch side as claimed in claim 1 is carried no torsional moment test device, it is characterized in that, the adjustable height bracing or strutting arrangement is a lifting jack.
3. mechanical clutch side as claimed in claim 1 is carried no 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 with the desired unbalance loading arm of force of adjustment test.
4. mechanical clutch side as claimed in claim 1 is carried no torsional moment test device, it is characterized in that, motor is the high speed oil motor, and its power can be designed to only to satisfy the energy that the friction of clutch spindle bearing element consumes and get final product.
5. mechanical clutch side as claimed in claim 1 is carried no torsional moment test device, it is characterized in that, simulation of engine bell housing end face is designed to AAE'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 true CN102840974A (en) | 2012-12-26 |
| CN102840974B 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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| CN (1) | CN102840974B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101593837B1 (en) * | 2014-11-12 | 2016-02-12 | 두산중공업 주식회사 | Performance of the test object test device |
Citations (7)
| 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 |
| JPH0552703A (en) * | 1991-08-28 | 1993-03-02 | Aisin Chem Co Ltd | Method and apparatus for testing lockup clutch |
| 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 |
-
2011
- 2011-06-24 CN CN201110174319.2A patent/CN102840974B/en active Active
Patent Citations (7)
| 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 |
| JPH0552703A (en) * | 1991-08-28 | 1993-03-02 | Aisin Chem Co Ltd | Method and apparatus for testing lockup clutch |
| 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 |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101593837B1 (en) * | 2014-11-12 | 2016-02-12 | 두산중공업 주식회사 | Performance of the test object test device |
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| CN102840974B (en) | 2014-10-22 |
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