CN107463753B - Structure for improving noise of EPSc driving unit and inclination angle calculation method - Google Patents
Structure for improving noise of EPSc driving unit and inclination angle calculation method Download PDFInfo
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- CN107463753B CN107463753B CN201710701185.2A CN201710701185A CN107463753B CN 107463753 B CN107463753 B CN 107463753B CN 201710701185 A CN201710701185 A CN 201710701185A CN 107463753 B CN107463753 B CN 107463753B
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- 238000004364 calculation method Methods 0.000 title claims abstract description 9
- 238000004519 manufacturing process Methods 0.000 claims abstract description 12
- 238000004458 analytical method Methods 0.000 claims description 9
- 238000000034 method Methods 0.000 claims description 7
- 239000002184 metal Substances 0.000 claims description 5
- 239000004033 plastic Substances 0.000 claims description 4
- 230000001186 cumulative effect Effects 0.000 claims description 2
- 229910052755 nonmetal Inorganic materials 0.000 abstract description 2
- 238000009825 accumulation Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D15/00—Steering not otherwise provided for
- B62D15/02—Steering position indicators ; Steering position determination; Steering aids
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/10—Noise analysis or noise optimisation
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- Mechanical Engineering (AREA)
- Power Steering Mechanism (AREA)
Abstract
The invention relates to the technical field of automobile part production and manufacturing, in particular to a structure for improving EPSc driving unit noise and an inclination angle calculation method, wherein a 15-degree wedge mechanism is matched with a rubber spring with certain rigidity, so that the complaint of mechanical noise generated by a fit clearance between a sensing unit and a servo shell can be solved, the product quality is improved, after-sales claims are reduced, good economy is achieved, and meanwhile, the wedge mechanism is made of non-metal parts, so that the manufacturing convenience and the part cost are lower.
Description
Technical Field
The invention relates to the technical field of automobile part production and manufacturing, in particular to a structure for improving noise of an EPSc driving unit and an inclination angle calculation method.
Background
At present, the EPSc steering column receives a plurality of noise complaints and claims of customers, and experimental analysis confirms that most of mechanical noise is from the fit clearance between the wedge-shaped supporting disc of the sensing unit and the servo shell, and the sensing unit supporting disc and the servo shell are metal parts, so that the sensing unit supporting disc and the servo shell can emit great noise in the collision process, and the service life and the comfort degree of the whole EPSc are greatly influenced.
It is necessary to design a structure and tilt angle calculation method for improving noise of the EPSc driving unit.
Disclosure of Invention
The invention breaks through the difficult problems in the prior art, and designs a structure for improving the noise of an EPSc driving unit and an inclination angle calculating method.
In order to achieve the above purpose, the invention designs a structure for improving noise of an EPSc driving unit, which comprises a sensing unit cover, an input shaft, a shell, a worm wheel and an output shaft, and is characterized in that: the lower extreme of input shaft and the top of output shaft cooperate and form steering spindle subassembly, the cover is equipped with sensing unit assembly, wedge supporting disk, worm wheel, casing and sensing unit lid on the steering spindle subassembly, and sensing unit assembly, wedge supporting disk, worm wheel all are located inside the casing, and sensing unit lid is at the casing top, and sensing unit assembly is located wedge supporting disk top, and the worm wheel is located wedge supporting disk below, inserts in the space between wedge supporting disk and the casing and is equipped with the wedge compensation ring, installs rubber spring additional on the wedge compensation ring.
The inclination angle of the wedge-shaped compensation ring is 15 DEG + -1.3 deg.
The invention also designs a calculation method for improving the structure inclination angle of the noise of the EPSc driving unit, which is characterized in that: the calculation is carried out according to the following method:
because EPSc mechanism requires the axial to be unable from lock, consequently when not placing the rubber spring, according to the atress analysis can know, the horizontal direction atress is:
F N2 *COSβ=F N1 -F f2 *SINβ （1）；
the friction force formula comprises:
F f1 =F N1 *U1 （a）；
F f2 =F N2 *U2 （b）；
bringing two formulas (a) and (b) into formula (1) to obtain:
F N2 *COSβ=F N1 - F N2 * U2×sinβ; namely F N1 = F N2 *（COSβ+U2*SINβ） （2）；
The vertical stress is as follows:
upward force: f (F) N2 *SINβ （c）；
Downward force: f (F) N1 *U1+COSβ*F N2 *U2 （d）；
Bringing (2) into (c) (d) makes it possible to:
the upward force is: f (F) N2 *SINβ；
The downward force is: f (F) N2 *（U1*COSβ+U2*COSβ+U1U2*SINβ）；
When U1, U2 are constant, let k3=sinβ, k4=u1×cos β+u2×cos β+u1u2×sinβ, and K3 and K4 intersect at β=13.5 to obtain conclusion 1: the self-locking phenomenon of the mechanism is prevented, and the inclined angle of the wedge-shaped compensation ring is set to be larger than 13.5 degrees.
After the rubber spring is placed, according to stress analysis, the stress balance can be obtained: f (F) N2 *COSβ=F N1 +F f2 *SINβ（1’）；
F1=F f1 +F f2 *COSβ+F N2 *SINβ （2’）；
The friction formula can be known:
F f1 =F N1 *U1 （a’）；
F f2 =F N2 *U2 （b’）；
substituting (a ') (b') into (1 ') (2') can obtain:
F N1 =F N2 *( COSβ-U2*SINβ) （3’）；
F1=F N2 *[(COSβ-U2*SINβ)*U1+COSβ*U2+SINβ)] （4’）；
(COS beta-U2 SINbeta) U1+COS beta) U2+SINbeta in the formula (4')]Let K1, f1=f N2 *K1；
For wedge-shaped support discs, it is subjected to a downward resultant force F2 from the wedge-shaped compensating ring, equal in value to F N2 And F is equal to f2 I.e.:
F2=F N2 *SINβ+F f1 *COSβ=F N2 (SINβ+U2*COSβ)；
let SIN beta+u2 COS beta be K2, f2=f N2 * K2, and F N2 =f1/K1, so finally it is available: f2 =f1×k2/K1, according to the coefficient of friction between metal and plasticThe table can be set to u1=u2=0.12, since the axial maximum working load of the bearings on the wedge-shaped support disc is 4000N, i.e. the resultant force F2 to which the wedge-shaped support disc is subjected needs to be less than 4000N, to get conclusion 2: the smaller the tilt angle β, the smaller the F2.
Combining conclusion 1 and conclusion 2, and setting the inclination angle of the wedge-shaped compensation ring to 15 degrees+/-theta in consideration of the range of beta angle values which can be obtained by manufacturing capability.
The θ is the manufacturing and cumulative error, and a specific value is 1.3 °.
Compared with the prior art, the invention can solve the complaint of mechanical noise generated by the fit clearance between the sensing unit and the servo shell by matching the wedge mechanism with the rubber spring with certain rigidity by 15 degrees, improves the product quality, reduces after-sales claims, has good economical efficiency, and meanwhile, the wedge mechanism is made of non-metal parts, so the manufacturing convenience and the part cost are lower.
Drawings
Fig. 1 is a schematic structural view of the present invention.
FIG. 2 is a diagram showing the force analysis of a wedge-shaped compensation ring in a state without a rubber spring.
FIG. 3 is a graph of K value versus beta angle for conclusion 1.
FIG. 4 is a force analysis chart of a wedge-shaped compensation ring according to the present invention.
Fig. 5 is a graph of K versus β angle for conclusion 2.
Referring to fig. 1,1 is a rubber spring, 2 is a wedge-shaped compensation ring, 3 is a wedge-shaped supporting disk, 4 is an input shaft, 5 is a sensing unit cover, 6 is a shell, 7 is a worm wheel, and 8 is an output shaft.
Detailed Description
The invention will be further described with reference to the accompanying drawings.
Referring to fig. 1, the invention designs a structure for improving noise of an EPSc driving unit, which comprises a sensing unit cover, an input shaft, a shell, a worm wheel and an output shaft, and is characterized in that: the lower extreme of input shaft 4 cooperatees with the top of output shaft 8 and forms steering spindle subassembly, the cover is equipped with sensing unit assembly, wedge supporting disk 3, worm wheel 7, casing 6 and sensing unit lid 5 on the steering spindle subassembly, the sensing unit assembly, wedge supporting disk 3, worm wheel 7 all are located casing 6 inside, sensing unit lid 5 is at casing 6 top, the sensing unit assembly is located wedge supporting disk 3 top, worm wheel 7 is located wedge supporting disk 3 below, insert in the space between wedge supporting disk 3 and the casing 6 and be equipped with wedge compensating ring 2, the last rubber spring 1 that is equipped with of wedge compensating ring 2.
The inclination angle of the wedge-shaped compensation ring 2 in the present invention is 15 deg. + -1.3 deg..
A calculation method for improving the structure inclination angle of EPSc driving unit noise is carried out according to the following method:
let beta be the inclination angle of the wedge-shaped compensation ring, F N1 For supporting the compensating ring by the shell, F N2 U1 and U2 are friction coefficients of metal and plastic and F are the pressure of the wedge-shaped supporting disc to the compensating ring f1 F for friction of the housing against the compensating ring f2 The friction force of the wedge-shaped supporting disc to the compensating ring is adopted.
Because the EPSc mechanism requires no axial self-locking, when the rubber spring is not placed, the stress analysis according to fig. 2 indicates that the horizontal stress is:
F N2 *COSβ=F N1 -F f2 *SINβ （1）；
the friction force formula comprises:
F f1 =F N1 *U1 （a）；
F f2 =F N2 *U2 （b）；
bringing two formulas (a) and (b) into formula (1) to obtain:
F N2 *COSβ=F N1 - F N2 * U2×sinβ; namely F N1 = F N2 *（COSβ+U2*SINβ） （2）；
The vertical stress is as follows:
upward force: f (F) N2 *SINβ （c）；
Downward force: f (F) N1 *U1+COSβ*F N2 *U2 （d）；
Bringing (2) into (c) (d) makes it possible to:
the upward force is: f (F) N2 *SINβ；
The downward force is: f (F) N2 *（U1*COSβ+U2*COSβ+U1U2*SINβ）；
When U1, U2 are constant, let k3=sinβ, k4=u1×cos β+u2×cos β+u1u2×sinβ, K3 and K4 intersect at β=13.5, as shown in fig. 3, to obtain conclusion 1: the self-locking phenomenon of the mechanism is prevented, and the inclined angle of the wedge-shaped compensation ring is set to be larger than 13.5 degrees.
After the rubber spring is placed in the invention, according to the stress analysis of fig. 4, the stress balance can be obtained: f (F) N2 *COSβ=F N1 +F f2 *SIN β （1’）；
F1=F f1 +F f2 *COSβ+F N2 *SINβ （2’）；
The friction formula can be known:
F f1 =F N1 *U1 （a’）；
F f2 =F N2 *U2 （b’）；
substituting (a ') (b') into (1 ') (2') can obtain:
F N1 =F N2 *( COSβ-U2*SINβ) （3’）；
F1=F N2 *[(COSβ-U2*SINβ)*U1+COSβ*U2+SINβ)] （4’）；
(COS beta-U2 SINbeta) U1+COS beta) U2+SINbeta in the formula (4')]Let K1, f1=f N2 *K1；
For wedge-shaped support discs, it is subjected to a downward resultant force F2 from the wedge-shaped compensating ring, equal in value to F N2 And F is equal to f2 I.e.:
F2=F N2 *SINβ+F f1 *COSβ=F N2 (SINβ+U2*COSβ)；
let SIN beta+u2 COS beta be K2, f2=f N2 * K2, and F N2 =f1/K1, so finally it is available: f2 =f1×k2/K1, according to metalThe friction coefficient table with plastic can be set with u1=u2=0.12, since the axial maximum working load of the bearing on the wedge-shaped supporting disc is determined by the structural design of the bearing, the axial working condition calculated by the supplier to be the maximum bearable is 4000N, that is, the resultant force F2 born by the wedge-shaped supporting disc needs to be less than 4000N, so as to obtain fig. 5, and the conclusion 2 is obtained according to fig. 5: the smaller the tilt angle β, the smaller the F2;
according to conclusion 1, the angle β is required to be greater than 13.5 °, and based on conclusion 2, the smaller the value the better, and considering the accumulation of parts and manufacturing errors, the angle β is taken to be 15 ° ± θ, where θ is the manufacturing and accumulation error, typically ranging from 1.3 °.
In the implementation, the sensing unit cover compresses the rubber spring to deform the rubber spring to provide axial pretightening force to limit the axial displacement of the wedge-shaped supporting disc, and meanwhile, the axial free gap of the bearing can be eliminated; the wedge-shaped compensation ring is arranged below the rubber spring, and the axial force provided by the rubber spring is inserted between the wedge-shaped support disc and the shell to eliminate the gap between the wedge-shaped support disc and the shell so as to achieve the purpose of limiting the radial movement of the wedge-shaped support disc; according to the invention, even when the gap is increased due to abrasion of the part, the wedge-shaped compensation ring can downwards move under the action of the axial force provided by the rubber spring to compensate the generated gap, so that the risk of noise generated by the sample after fatigue is eliminated.
In the concrete assembly, as shown in fig. 1, the input shaft 4 and the output shaft 8 are pressed into a steering shaft small assembly, and then the worm wheel 7 and the wedge-shaped supporting disc 3 of the patent are pressed into the steering shaft small assembly in sequence to complete the assembly of the sensing unit assembly. The sensor unit and the shell are still in clearance fit in terms of assembly, after the sensor unit assembly is placed in the shell 6, the wedge-shaped compensation ring 2 is inserted into the gap between the wedge-shaped support disc and the shell, and the rubber spring 1 is additionally arranged on the wedge-shaped compensation ring.
Because the height of the rubber spring is slightly higher than the plane of the shell in the state, the rubber spring generates axial force due to extrusion deformation after the sensing unit cover 5 is connected with the shell through the bolt, and the wedge-shaped compensation ring is pressed to axially limit the displacement of the wedge-shaped support disc and simultaneously eliminate the fit clearance between the wedge-shaped support disc and the shell, so that the aim of eliminating noise is achieved.
Claims (4)
1. The utility model provides an improve structure of EPSc drive unit noise, includes sensing unit lid, input shaft, casing, worm wheel, output shaft, its characterized in that: the lower extreme of input shaft (4) cooperatees with the top of output shaft (8) and forms steering spindle little assembly, the cover is equipped with sensing unit assembly on steering spindle little assembly, wedge supporting disk (3), worm wheel (7), casing (6) and sensing unit lid (5), the sensor unit assembly, wedge supporting disk (3), worm wheel (7) all are located inside casing (6), sensing unit lid (5) lid is at casing (6) top, the sensor unit assembly is located wedge supporting disk (3) top, worm wheel (7) are located wedge supporting disk (3) below, insert in the space between wedge supporting disk (3) and casing (6) and have wedge compensating ring (2), install rubber spring (1) additional on wedge compensating ring (2).
2. The structure for improving noise of an EPSc drive unit according to claim 1, wherein: the inclination angle of the wedge-shaped compensation ring (2) is 15 DEG + -1.3 deg.
3. A method of calculating the tilt angle of an EPSc drive unit noise-improving structure according to claim 1, wherein: the calculation is carried out according to the following method:
because EPSc mechanism requires the axial to be unable from lock, consequently when not placing the rubber spring, according to the atress analysis can know, the horizontal direction atress is:
F N2 *COSβ=F N1 -F f2 *SINβ （1）；
the friction force formula comprises:
F f1 =F N1 *U1 （a）；
F f2 =F N2 *U2 （b）；
bringing two formulas (a) and (b) into formula (1) to obtain:
F N2 *COSβ=F N1 - F N2 * U2×sinβ; namely F N1 = F N2 *（COSβ+U2*SINβ） （2）；
The vertical stress is as follows:
upward force: f (F) N2 *SINβ （c）；
Downward force: f (F) N1 *U1+COSβ*F N2 *U2 （d）；
Bringing (2) into (c) (d) makes it possible to:
the upward force is: f (F) N2 *SINβ；
The downward force is: f (F) N2 *（U1*COSβ+U2*COSβ+U1U2*SINβ）；
When U1, U2 are constant, let k3=sinβ, k4=u1×cos β+u2×cos β+u1u2×sinβ, and K3 and K4 intersect at β=14 to obtain conclusion 1: the self-locking phenomenon of the mechanism is prevented, and the inclination angle of the wedge-shaped compensation ring is set to be larger than 13.5 degrees;
after the rubber spring is placed, according to stress analysis, the stress balance can be obtained: f (F) N2 *COSβ=F N1 +F f2 *SIN β （1’）；
F1=F f1 +F f2 *COSβ+F N2 *SINβ （2’）；
The friction formula can be known:
F f1 =F N1 *U1 （a’）；
F f2 =F N2 *U2 （b’）；
substituting (a ') (b') into (1 ') (2') can obtain:
F N1 =F N2 *( COSβ-U2*SINβ) （3’）；
F1=F N2 *[(COSβ-U2*SINβ)*U1+COSβ*U2+SINβ)] （4’）；
(COS beta-U2 SINbeta) U1+COS beta) U2+SINbeta in the formula (4')]Let K1, f1=f N2 *K1；
For wedge-shaped support discs, it is subjected to a downward resultant force F2 from the wedge-shaped compensating ring, equal in value to F N2 And F is equal to f2 I.e.:
F2=F N2 *SINβ+F f1 *COSβ=F N2 (SINβ+U2*COSβ)；
let SIN beta+u2 COS beta be K2, f2=f N2 * K2, and F N2 =f1/K1, so finally it is available: f2 = F1 * k2/K1, according to the friction coefficient table of metal and plastic, can set u1=u2=0.12, since the axial maximum working load of the bearing on the wedge-shaped supporting disc is 4000N, i.e. the resultant force F2 to which the wedge-shaped supporting disc is subjected needs to be less than 4000N, so as to obtain conclusion 2: the smaller the tilt angle β, the smaller the F2;
combining the conclusion 1 and the conclusion 2, and setting the inclination angle of the wedge-shaped compensation ring to be 15 degrees+/-theta in consideration of the range of beta angle values which can be obtained by the manufacturing capability;
beta is the inclination angle of the wedge-shaped compensation ring, F N1 For supporting the compensating ring by the shell, F N2 U1 and U2 are friction coefficients of metal and plastic and F are the pressure of the wedge-shaped supporting disc to the compensating ring f1 F for friction of the housing against the compensating ring f2 The friction force of the wedge-shaped supporting disc to the compensating ring is adopted.
4. A method of calculating the tilt angle of an EPSc drive unit noise-improving structure according to claim 3, wherein: the θ is the manufacturing and cumulative error, and a specific value is 1.3 °.
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| CN201710701185.2A CN107463753B (en) | 2017-08-16 | 2017-08-16 | Structure for improving noise of EPSc driving unit and inclination angle calculation method |
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Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20070018336A (en) * | 2005-08-09 | 2007-02-14 | 주식회사 만도 | Electric Power Steering System Equipped with Clearance Compensator for Use in Worm Gear |
| KR20080061529A (en) * | 2006-12-28 | 2008-07-03 | 남양공업주식회사 | Compensational apparatus of free apartness of worm shaft for electric power steering system |
| DE102008054441A1 (en) * | 2008-12-10 | 2010-06-17 | Zf Lenksysteme Gmbh | Bearing i.e. pivot bearing, for shaft in e.g. pinion steering gear of steering system, has pivot ring, where screw with axially formed wedge-shape is inserted into recess so that ring is radially fixed in housing in clearance-free manner |
| CN102616269A (en) * | 2011-01-25 | 2012-08-01 | 福特全球技术公司 | Toothed-rack steering gear, and servo steering system equipped with the same |
| CN202593606U (en) * | 2012-05-25 | 2012-12-12 | 武汉捷隆汽车电动转向系统有限公司 | Removal and fixation structure for worm axial clearance |
| CN202833955U (en) * | 2012-07-13 | 2013-03-27 | 上海采埃孚转向系统有限公司 | Pressing piece device capable of automatically compensating gear rack meshing gap |
| CN203784261U (en) * | 2014-02-08 | 2014-08-20 | 上海汽车集团股份有限公司 | Worm and gear interval regulation mechanism and worm and gear mechanism |
| CN203796896U (en) * | 2014-05-06 | 2014-08-27 | 荆州恒隆汽车技术(检测)中心 | Backlash compensation structure for EPS assembly |
| WO2016038927A1 (en) * | 2014-09-08 | 2016-03-17 | 日本精工株式会社 | Electrically driven power steering device |
| CN207216615U (en) * | 2017-08-16 | 2018-04-10 | 博世华域转向系统有限公司 | A kind of structure of improvement EPSc driver element noises |
-
2017
- 2017-08-16 CN CN201710701185.2A patent/CN107463753B/en active Active
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20070018336A (en) * | 2005-08-09 | 2007-02-14 | 주식회사 만도 | Electric Power Steering System Equipped with Clearance Compensator for Use in Worm Gear |
| KR20080061529A (en) * | 2006-12-28 | 2008-07-03 | 남양공업주식회사 | Compensational apparatus of free apartness of worm shaft for electric power steering system |
| DE102008054441A1 (en) * | 2008-12-10 | 2010-06-17 | Zf Lenksysteme Gmbh | Bearing i.e. pivot bearing, for shaft in e.g. pinion steering gear of steering system, has pivot ring, where screw with axially formed wedge-shape is inserted into recess so that ring is radially fixed in housing in clearance-free manner |
| CN102616269A (en) * | 2011-01-25 | 2012-08-01 | 福特全球技术公司 | Toothed-rack steering gear, and servo steering system equipped with the same |
| CN202593606U (en) * | 2012-05-25 | 2012-12-12 | 武汉捷隆汽车电动转向系统有限公司 | Removal and fixation structure for worm axial clearance |
| CN202833955U (en) * | 2012-07-13 | 2013-03-27 | 上海采埃孚转向系统有限公司 | Pressing piece device capable of automatically compensating gear rack meshing gap |
| CN203784261U (en) * | 2014-02-08 | 2014-08-20 | 上海汽车集团股份有限公司 | Worm and gear interval regulation mechanism and worm and gear mechanism |
| CN203796896U (en) * | 2014-05-06 | 2014-08-27 | 荆州恒隆汽车技术(检测)中心 | Backlash compensation structure for EPS assembly |
| WO2016038927A1 (en) * | 2014-09-08 | 2016-03-17 | 日本精工株式会社 | Electrically driven power steering device |
| CN207216615U (en) * | 2017-08-16 | 2018-04-10 | 博世华域转向系统有限公司 | A kind of structure of improvement EPSc driver element noises |
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| CN107463753A (en) | 2017-12-12 |
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