CN104748899B - A kind of wheel edge drive structure and its torque real-time detection method - Google Patents
A kind of wheel edge drive structure and its torque real-time detection method Download PDFInfo
- Publication number
- CN104748899B CN104748899B CN201510129001.0A CN201510129001A CN104748899B CN 104748899 B CN104748899 B CN 104748899B CN 201510129001 A CN201510129001 A CN 201510129001A CN 104748899 B CN104748899 B CN 104748899B
- Authority
- CN
- China
- Prior art keywords
- gear
- force
- torque
- gear shaft
- subject
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Landscapes
- Force Measurement Appropriate To Specific Purposes (AREA)
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
Abstract
Torque live signal is had very important significance to electric automobile systems stabilisation and drive system control, and the torque of Direct wheel drives motor now is converted and obtained indirectly using energy transformation approach mostly, and precision is poor.The present invention proposes a kind of Direct wheel drives torque real-time detection method, by by torque detection means reasonable Arrangement on hub reduction gear, on the premise of ensureing that basic transmission is required, the torque of detectable decelerator transmission, and export as electronic signals, so as to the optimal control for drive system, it is low that this method is used for the real-time accuracy of detection height of torque, good stability, highly versatile, cost.
Description
Technical field
The invention belongs to electric automobile drive/transmission system field, and in particular to a kind of wheel edge drive structure and its torque are real
When detection method.
Background technology
Torque is the basic load form of various drive shaft in construction machineries, with the ability to work of dynamic power machine, energy resource consumption,
The elements such as efficiency, running life and security performance are closely connected, Torque test to drive bearing by dynamic loading monitoring and control,
Diagnosis, selection of prime mover capacity of the Intensity Design, failure of each parts of transmission system etc. all have great importance.
Current torque sensing approach mainly includes balance force method, energy transformation approach and TRANSFER METHOD.Balance force method torque measurement
Device is also referred to as dynamometer, is typically made up of whirler, balanced support and equilibrant force measuring mechanism, according to installed in balanced support
On kinds of machine, Electric Dynamometer, hydraulic dynamometer etc. can be divided into.Balanced support has rolling bearing, double rolling-supporting type, sector
Supporting, hydraulic support and air pressure supporting etc..Balance force method directly surveys moment of torsion from body, in the absence of from revolving part to static element
Moment of torsion problem of transmission, but it is suitable only for detecting the moment of torsion under at the uniform velocity working condition, it is impossible to measure dynamic torque.Energy conversion method is
According to law of conservation of energy, the mechanical energy of rotating machinery is measured by measuring the energy such as electric energy, heat energy parameter of other forms,
And then obtain the energy coefficient relevant with moment of torsion（Such as electric energy coefficient）Method to determine tested torque, measurement error compares
Greatly, it is general only to have more application in terms of motor and liquid machine torque measurement.TRANSFER METHOD uses non-contact measurement mostly, uses
It is convenient, it is simple in construction, but non-contact measurement is due to the influence of the factors such as temperature, algorithm and the collection difficulty of coherent signal,
Precision also needs further raising.
The Vehicle Stability System and power-driven system of electric automobile are required for using dtc signal, the acquisition of dtc signal
Optimal control to drive system has great significance.The acquisition of electric automobile dtc signal be typically according to electric moter voltage,
Electric current and tach signal, motor instantaneous torque is estimated according to energy transformation approach indirectly, and this method is special by motor real work
The influence of property, precision is poor.
The content of the invention
The present invention is directed to propose a kind of wheel edge drive structure and its torque real-time detection method.By on hub reduction gear
Reasonable Arrangement torque detection means, on the premise of ensureing that basic transmission is required, hub reduction gear input shaft can be detected in real time
Torque, and export as electronic signals, so that the optimal control for drive system, this method is detected in real time for torque
Precision height, good stability, highly versatile, cost are low.
To achieve the above object of the invention, the technical scheme of offer of the invention is：
A kind of wheel edge drive structure, including reducer shell, intermediate gear shaft, first order driven gear, the second level are driven
Gear, sleeve, force snesor, bearing support；One end of the intermediate gear shaft is supported in the decelerator by bearing inner race
Housing, the other end of the intermediate gear shaft is supported in the endoporus of the sleeve by bearing inner race；The sleeve has screwed hole,
Coupled according to certain angle by force snesor with reducer shell.
Intermediate gear shaft and second level driving gear Integral design into gear shaft structure, first order driven gear with it is middle
Gear shaft is supported in reducer shell by key connecting, intermediate gear shaft right-hand member by bearing inner race, and left end passes through bearing support
Inner ring is supported in the endoporus of sleeve；Second level driven gear is connected with output shaft by key, and output shaft two ends pass through bearing inner race
It is supported in reducer shell.
There is stud at described force snesor two ends, can be screwed into respectively in sleeve and the corresponding screwed hole of reducer shell,
Force snesor can bear pulling force and pressure simultaneously, when it is acted on by power, it will have voltage signal output.
Described sleeve is half-sectional cylindrical structure, and its semi-section is fitted with reducer shell.
When hub reduction gear normal work, the support reaction that bearing support will be acted on by intermediate gear shaft can be analyzed to X
Direction and Y-direction, the angle of bearing support reaction and Y-direction component is, during placement sensor, the axis direction and Y of sensor
The angle in direction is also, i.e., the support force effect of bearing support is only acted on by intermediate gear shaft support reaction and sleeve, place
In balance between two forces state, so as to ensure the normal transmission of gear.Derived by calculatingFor certain value.
According to intermediate gear shaft stress and equalising torque relation, the stress at intermediate gear shaft left end bearing support can be obtained：
In formula--- the power parallel with gear radial load that intermediate gear shaft left end bearing support is subject to
--- the power circumferentially parallel with gear that intermediate gear shaft left end bearing support is subject to
--- gear compound graduation radius of circle
--- the peripheral force that gear is subject to
--- the radial load that gear is subject to
--- the axial force that gear is subject to
--- intermediate gear shaft or so bearing widthwise central distance
--- first order driven gear facewidth center to intermediate gear shaft right-hand member bearing width centre distance
--- second level driving gear facewidth center to intermediate gear shaft right-hand member bearing width centre distance
The radial load that Fr2---- first order driven gears are subject to
The radial load that Fr3---- second level driving gear is subject to
The axial force that Fa2---- first order driven gears are subject to
The axial force that Fa3---- second level driving gear is subject to
The peripheral force that Ft2---- first order driven gears are subject to
The peripheral force that Ft3---- second level driving gear is subject to
R2---- first order driven gear reference radius
R3---- second level driving gear reference radius
In the present invention, the axial force that intermediate gear shaft is subject to all is born by intermediate gear shaft right-hand member bearing, center tooth
Wheel shaft left end bearing is not subject to axial force.Intermediate gear shaft left end shaft affords the active force from intermediate gear shaft will be by sleeve
Support dynamic balance, it can thus be concluded that to the stressing conditions of left end bearing support, as shown in Figure 5.
According to the relation of active force and reaction force, bearing support can be obtained by the support reaction from intermediate gear shaft,
It can be analyzed to the component of X and Y both directions、,WithAngle be.Bearing support is also by the branch of sleeve simultaneously
Support force, force snesor two ends are separately mounted in the screwed hole of sleeve and reducer shell, because sensor axis direction and Y
The angle in direction is also, therefore bearing support is in balance between two forces state.Test force is sleeve to bearing support in force snesor
Support force, can be obtained by bearing support stress balance：
Wherein,--- the input gear axle number of teeth
--- the first order driven gear number of teeth
--- input gear axle reference radius
--- intermediate gear shaft reference radius
--- input gear shaft torque
It can be obtained after conversion：
From formula 6, proportionality coefficientIt is only relevant with hub reduction gear arrangement form and gear parameter, work as hub reduction gear
After design is determined, proportionality coefficientFor definite value.That is hub reduction gear input torqueThe power being subject to force snesorBetween be
Linear ratio relation, therefore can be converted by the signal of force snesor when hub reduction gear works and obtain the real-time of hub reduction gear
Torque.
Compared with prior art, it is of the invention to be advantageous in that：
1. the torque sensing approach is applied to the Torque test of most of decelerator, simple in construction, convenient test, with very
Good versatility；
2. the torque sensing approach is by direct equalizer bearing support reaction, on the premise of ensureing that decelerator is normally driven,
The real-time detection to decelerator torque can be achieved, measurement accuracy is high；
3. the torque sensing approach is conducive to improving drive system of electric automobile effect applied to hub reduction gear Torque test
Rate.
Brief description of the drawings
Fig. 1 has the hub reduction gear general assembly sketch of torque real-time detection function；
Fig. 2 torque detection means assemble partial view；
Fig. 3 torque detection means test lead left views；
Fig. 4 hub reduction gear intermediate gear shaft force analysis sketches；
Fig. 5 shaft strengths analyze sketch.
Label declaration in figure：
1 --- reducer shell；2 --- input gear axle；
3 --- first order driven gear；4 --- intermediate gear shaft；
5 --- second level driven gear；6 --- output shaft；
7 --- torque detection means；
7001 --- bearing support；7002 --- sleeve；7003 --- force snesor.
Embodiment
Below in conjunction with accompanying drawing, the invention will be further described.
This Direct wheel drives torque real-time detection method is described by taking two-stage expansion hub reduction gear as an example by the present invention.
There is the hub reduction gear assembly of torque real-time detection function mainly to include reducer shell 1, input gear axle 2, the first order for this
The parts such as driven gear 3, intermediate gear shaft 4, second level driven gear 5, output shaft 6, torque detection means 7, Torque test machine
Structure is again comprising parts carry bearing 7001, sleeve 7002, force snesor 7003 etc..
As shown in figure 1, the two ends of input gear axle 2 are supported in reducer shell 1 by bearing inner race.First order driven tooth
Wheel 3 is connected with intermediate gear shaft 4 by key, and the right-hand member of intermediate gear shaft 4 is supported in reducer shell 1 by bearing inner race, such as Fig. 3
Installation site of the torque detection means 7 on reducer shell 1 is shown, as shown in Fig. 2 the left end of intermediate gear shaft 4 passes through branch
Hold the inner ring of bearing 7001 and be supported in reducer shell 1 and sleeve 7002.There is stud at the two ends of force snesor 7, and set can be screwed into respectively
In cylinder 7002 and the corresponding screwed hole of reducer shell 1, sleeve 7002 is half-sectional cylindrical structure, its semi-section and reducing gearbox
Body 1 is fitted.Second level driven gear 5 is connected with output shaft 6 by key, and the two ends of output shaft 6 are supported in deceleration by bearing inner race
Device housing 1.
As shown in figure 5, when hub reduction gear normal work, bearing support 7001 will be acted on by intermediate gear shaft 4
Support reaction, can be analyzed to X-direction and Y-direction, and the angle of bearing support reaction and Y-direction component is, arrange force snesor 7003
When, the axis direction of force snesor 7003 and the angle of Y-direction are also, i.e., bearing support 7001 is only by intermediate gear shaft 4
The support reaction of effect is acted on the support force of sleeve 7002, in balance between two forces state.
When hub reduction gear normal work, 2 turns of the power that force snesor 7003 is surveyed and hub reduction gear input gear axle
It is linear ratio relation between square, therefore when hub reduction gear works, can be converted and be taken turns by the signal of force snesor 7003
The real-time torque of side reducer.
As shown in Figure 4, Figure 5.According to intermediate gear shaft stress and equalising torque relation, the supporting of intermediate gear shaft left end can be obtained
Stress at bearing：
In formula--- the power parallel with gear radial load that intermediate gear shaft left end bearing support is subject to
--- the power circumferentially parallel with gear that intermediate gear shaft left end bearing support is subject to
--- gear compound graduation radius of circle
--- the peripheral force that gear is subject to
--- the radial load that gear is subject to
--- the axial force that gear is subject to
--- intermediate gear shaft or so bearing widthwise central distance
--- first order driven gear facewidth center to intermediate gear shaft right-hand member bearing width centre distance
--- first order driven gear facewidth center to intermediate gear shaft right-hand member bearing width centre distance
In the present invention, the axial force that intermediate gear shaft is subject to all is born by intermediate gear shaft right-hand member bearing, center tooth
Wheel shaft left end bearing is not subject to axial force.Intermediate gear shaft left end shaft affords the active force from intermediate gear shaft will be by sleeve
Support dynamic balance, it can thus be concluded that to the stressing conditions of left end bearing support, as shown in Figure 5.
According to the relation of active force and reaction force, bearing support can be obtained by the support reaction from intermediate gear shaft,
It can be analyzed to the component of X and Y both directions、,WithAngle be.Bearing support is also by the branch of sleeve simultaneously
Support force, force snesor two ends are separately mounted in the screwed hole of sleeve and reducer shell, because sensor axis direction and Y
The angle in direction is also, therefore bearing support is in balance between two forces state.Test force is sleeve to bearing support in force snesor
Support force, can be obtained by bearing support stress balance：
It can be obtained after conversion：
From formula 6, proportionality coefficientIt is only relevant with hub reduction gear arrangement form and gear parameter, work as hub reduction gear
After design is determined, proportionality coefficientFor definite value.That is hub reduction gear input torqueThe power being subject to force snesorBetween be
Linear ratio relation, therefore can be converted by the signal of force snesor when hub reduction gear works and obtain the real-time of hub reduction gear
Torque.
The invention provides a kind of Direct wheel drives torque real-time detection method, this torque sensing approach slows down for most of
Device is all suitable for, and in particular to core type decelerator and expansion decelerator, single reduction gear and multi-stage speed reducer, Spur Gear Driving
Decelerator, Helical gear Transmission decelerator and Bevel Gear Transmission decelerator etc..Only this set torque detection means need to be arranged in transmission
On the bearing support of axle one end, it is possible to which reducer input shaft torque is detected in real time.The present invention using gear reduction unit as
The Direct wheel drives torque real-time detection method is described example, is applied equally to by improving the mechanism torque sensing approach
Other kinds of transmission system, also within protection scope of the present invention.
Claims (3)
1. a kind of wheel edge drive structure, it is characterised in that：Including reducer shell, intermediate gear shaft, first order driven gear,
Two grades of driven gears, sleeve, force snesor, bearing supports；One end of the intermediate gear shaft is supported by bearing support inner ring
In the reducer shell, the other end of the intermediate gear shaft is supported in the endoporus of the sleeve by bearing support inner ring；
The sleeve has screwed hole, is coupled according to certain angle by force snesor with reducer shell；
The intermediate gear shaft and second level driving gear Integral design into gear shaft structure, first order driven gear with it is middle
Gear shaft is supported in reducer shell by key connecting, intermediate gear shaft right-hand member by bearing inner race, and left end passes through bearing support
Inner ring is supported in the endoporus of sleeve；Second level driven gear is connected with output shaft by key, and output shaft two ends pass through bearing inner race
It is supported in reducer shell.
2. a kind of wheel edge drive structure according to claim 1, it is characterised in that：There is spiral shell at described force snesor two ends
Post, can be screwed into sleeve and the corresponding screwed hole of reducer shell, force snesor can bear pulling force and pressure simultaneously, when it respectively
When being acted on by power, it will have voltage signal output；
Described sleeve is half-sectional cylindrical structure, and its semi-section is fitted with reducer shell.
3. a kind of a kind of torque real-time detection method of wheel edge drive structure as described in any claim 1 to 2, its feature exists
In：When decelerator normal work, the support reaction and the support force of sleeve that bearing support is only acted on by intermediate gear shaft are acted on,
In balance between two forces state, so as to ensure the normal transmission of gear；Power that force snesor is subject to and reducer input shaft torque it
Between be linear ratio relation, the power that force snesor is subject to exports as electronic signals, after testing, calculate after can obtain decelerator
Real-time torque：
According to intermediate gear shaft stress and equalising torque relation, the stress at intermediate gear shaft left end bearing support can be obtained：
Wherein,--- the power parallel with gear radial load that intermediate gear shaft left end bearing support is subject to
--- the power circumferentially parallel with gear that intermediate gear shaft left end bearing support is subject to
--- gear compound graduation radius of circle
--- the peripheral force that gear is subject to
--- the radial load that gear is subject to
--- the axial force that gear is subject to
--- intermediate gear shaft or so bearing widthwise central distance
--- first order driven gear facewidth center to intermediate gear shaft right-hand member bearing width centre distance
--- second level driving gear facewidth center to intermediate gear shaft right-hand member bearing width centre distance
The radial load that Fr2---- first order driven gears are subject to
The radial load that Fr3---- second level driving gear is subject to
The axial force that Fa2---- first order driven gears are subject to
The axial force that Fa3---- second level driving gear is subject to
The peripheral force that Ft2---- first order driven gears are subject to
The peripheral force that Ft3---- second level driving gear is subject to
R2---- first order driven gear reference radius
R3---- second level driving gear reference radius
Again, according to the relation of active force and reaction force, bearing support can be obtained by the support reaction from intermediate gear shaft, its
It can be analyzed to the component of X and Y both directions、,WithAngle be；Bearing support is also supported by sleeve simultaneously
Power, force snesor two ends are separately mounted in the screwed hole of sleeve and reducer shell, because sensor axis direction and Y side
To angle be also, therefore bearing support is in balance between two forces state；Test force is sleeve to bearing support branch in force snesor
Support force, can be obtained by bearing support stress balance：
Wherein
--- the input gear axle number of teeth
--- the first order driven gear number of teeth
--- input gear axle reference radius
--- intermediate gear shaft reference radius
--- input gear shaft torque
It can be obtained after conversion：
From formula 6, proportionality coefficientIt is only relevant with hub reduction gear arrangement form and gear parameter, when hub reduction gear is set
After meter is determined, proportionality coefficientFor definite value.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510129001.0A CN104748899B (en) | 2015-03-20 | 2015-03-20 | A kind of wheel edge drive structure and its torque real-time detection method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510129001.0A CN104748899B (en) | 2015-03-20 | 2015-03-20 | A kind of wheel edge drive structure and its torque real-time detection method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104748899A CN104748899A (en) | 2015-07-01 |
| CN104748899B true CN104748899B (en) | 2017-08-25 |
Family
ID=53588919
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510129001.0A Active CN104748899B (en) | 2015-03-20 | 2015-03-20 | A kind of wheel edge drive structure and its torque real-time detection method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104748899B (en) |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101183034A (en) * | 2007-12-04 | 2008-05-21 | 奇瑞汽车有限公司 | Electric machine torque measurement method |
| CN201201674Y (en) * | 2008-04-01 | 2009-03-04 | 铨阳能源科技股份有限公司 | Torque force detector of electric bicycle |
| CN201568531U (en) * | 2009-12-24 | 2010-09-01 | 盐城中马汽车零部件有限公司 | Speed reducer assembly for electric car |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10102650A1 (en) * | 2001-01-20 | 2002-08-01 | Bosch Gmbh Robert | Measuring arrangement in a wheel bearing of a motor vehicle for the detection of physical quantities |
| NL1023681C2 (en) * | 2003-06-17 | 2004-12-20 | Spinpower B V | Transmission system for bicycle, has tension difference measuring device with supporting arm and sensor forming a unit to measure the resultant of the transverse forces exerted to the transverse force sensor by the chain parts |
-
2015
- 2015-03-20 CN CN201510129001.0A patent/CN104748899B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101183034A (en) * | 2007-12-04 | 2008-05-21 | 奇瑞汽车有限公司 | Electric machine torque measurement method |
| CN201201674Y (en) * | 2008-04-01 | 2009-03-04 | 铨阳能源科技股份有限公司 | Torque force detector of electric bicycle |
| CN201568531U (en) * | 2009-12-24 | 2010-09-01 | 盐城中马汽车零部件有限公司 | Speed reducer assembly for electric car |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104748899A (en) | 2015-07-01 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103616180B (en) | Bearing radial dynamic load fault simulation diagnostic test platform | |
| CN204964204U (en) | Portable auto steering characteristic testing arrangement | |
| CN102901594A (en) | Device for testing friction moment of pairing rolling bearing | |
| CN207946221U (en) | The fatigue life of RV speed reducers and torsional moment test device | |
| CN102252840B (en) | Tester of fault diagnosis of rotating machinery with closed power | |
| CN106568597A (en) | High precision measurement method for roller gear tooth surface comprehensive meshing rigidity | |
| CN104806733B (en) | A kind of Torque test structures and methods based on shaft strength | |
| CN102928224A (en) | Method for detecting bearing fault of wind generating set | |
| CN110542556A (en) | Tilting pad sliding bearing test box, test bench and test method | |
| CN203798563U (en) | Assembly structure of test system for journal bearing | |
| CN204228409U (en) | RV speed reduction unit drive characteristic test macro | |
| CN202522369U (en) | Engineering vehicle torque sensor calibration device | |
| CN204572932U (en) | Have torque real-time detection function to core type wheel reductor structure | |
| CN109357745A (en) | A kind of automobile driving axle twisting vibration test macro and method | |
| CN104748899B (en) | A kind of wheel edge drive structure and its torque real-time detection method | |
| CN201945843U (en) | Torque loading controller | |
| CN205538211U (en) | Forerunner automobile machinery gearbox transmission error test bench | |
| CN207095858U (en) | A kind of bearing test device for motor | |
| CN103630278B (en) | A kind of current vortex retarder torque measuring method | |
| CN204572931U (en) | A kind of wheel reductor structure with torque real-time detection function | |
| CN202188931U (en) | On-line monitoring system of ship shaft power | |
| CN201575907U (en) | Detection and analyzing device for thin-walled bearings of swash plates of helicopters | |
| CN203069303U (en) | Testing machine for detecting bearing torque | |
| CN204359538U (en) | A kind of high capacity waggon fault detection system | |
| CN103048072A (en) | Bearing torque detection testing machine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |