CN101698416A - Alignment assistance and ultimate damping type steering gear - Google Patents
Alignment assistance and ultimate damping type steering gear Download PDFInfo
- Publication number
- CN101698416A CN101698416A CN200910207442A CN200910207442A CN101698416A CN 101698416 A CN101698416 A CN 101698416A CN 200910207442 A CN200910207442 A CN 200910207442A CN 200910207442 A CN200910207442 A CN 200910207442A CN 101698416 A CN101698416 A CN 101698416A
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- rack
- tooth bar
- spring
- steering
- deflector
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- 238000013016 damping Methods 0.000 title claims abstract description 15
- 241000269799 Perca fluviatilis Species 0.000 claims description 20
- 239000000463 material Substances 0.000 claims description 4
- 239000002184 metal Substances 0.000 abstract description 5
- 229910052751 metal Inorganic materials 0.000 abstract description 5
- 239000000872 buffer Substances 0.000 abstract 1
- 230000003111 delayed effect Effects 0.000 abstract 1
- 239000000428 dust Substances 0.000 abstract 1
- 238000013461 design Methods 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000011217 control strategy Methods 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 150000002739 metals Chemical class 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000012827 research and development Methods 0.000 description 1
- 230000000452 restraining effect Effects 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
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Abstract
The invention discloses an aligning assistance and ultimate damping type steering gear, comprising a rack, a stop block, a rack lining, a steering gear shell, an inner bulb assembly and a rack dust cover, wherein the rack is arranged in the shell; part of the rack extends out of the shell; the stop block and threads of an inner screwed hole at the front end of the shell are in connecting fit; the rack lining is adjacent to the stop block, and is in interference fit with the inner hole of the shell; the rack lining is in air tightness fit with the rack; and the front end of the inner bulb assembly is connected with threads of the inner hole of the rack. The steering gear also comprises a spring seat and a coil spring, wherein the spring seat is arranged in the shell in press fit; the spring seat is in clearance fit with the rack; and the coil spring is positioned between an inner bulb seat of the inner bulb assembly and the spring seat. The structure of the steering gear can improve the aligning force when the full-vehicle steering is aligned on the one hand so as to avoid incomplete steering alignment and delayed aligning response caused by increased axial force of the rack, and improves the hand feel on a steering ultimate position, buffers on the steering ultimate position, and eliminates the metal impact noise made by the ultimate position on the other hand.
Description
Technical field
The present invention relates to automobile steering system, be specifically related to a kind of automobile auxiliary return and just reaching the tooth bar deflector of ultimate damping noise elimination mechanism.
Background technology
At present, all there is new model constantly to release on the annual market, for same automobile design originating firm, the chassis of some same level vehicles all is general basically, have only and do an amount of the adjustment on some parameter on other system or chassis, a lot of therebetween new cars all can run into configuration, axle load, wheelbase or driving engine etc. owing to car load in research and development change causes car load a certain performance change more or less wherein.
Test figures shows the returnability that influences car load that deflecting roller location parameter, axle load, steering swivel system configuration all can be bigger, because designed, verified, changed the restriction of external conditionss such as cost, do at car load under the situation of little change, return performance can be in certain scope internal loss.If be divided into two kinds of configurations of servo steering system and mechanical steering system, in the car load design, just must take into account the parameter that two kinds of configurations design deflector, commonality is poor.
In the rack-and-gear hydraulic power-assist steering system, because its time timing turns to flowing of liquid, the damping of system is strengthened, also there be the characteristic of steering reversal performance than non helping hand system difference in the friction aggravation.
In electric boosting steering system,, can make return performance obtain certain compensation by motor control strategy.But because the high request of deflector unfailing performance makes that the friction force control of kinematic pair requires to improve between internal mechanism.
Because the number of total coils that each vehicle bearing circle rotates is all different,, produce noise simultaneously, influence the traveling comfort of car load so in operating process, the metal of tooth bar when end position can occur and impact.For manual steering gear, can influence the service life of deflector when serious especially.
The rack and pinion steering gear structure of prior art shown in Figure 1 comprises tooth bar 11, limiting stopper 12, rack bush 13, steering gear housing 14, interior bulb assembly 15, rack boot 16.This deflector comes transfer torque by rack-and-pinion exactly, the forward transmission is that the driver will belong to the moment of torsion of steering handwheel and import from miniature gears by transmission, through the engagement of rack-and-gear, be converted into the output that moves axially of tooth bar, play the function of transfer torque; It is when reverse drive, and promptly car load returns timing, then drives pinion rotation by the tooth bar input; This deflector is to realize by the friction force of each kinematic pair to the damping of steering swivel system influence, for example the force of sliding friction of engagement resistance, tooth bar and the rack bush between force of sliding friction, miniature gears and the tooth bar between tooth bar and rack support seat etc.In a single day these structures just determine not malleable, and gap adjustment range is very limited, and conformability is difficult to control in addition.So, we can say that the prior art rack and pinion steering gear does not possess to turn to substantially to assist back positive function that the metal strike note of end position is same inevitable simultaneously.
Summary of the invention
At the deficiencies in the prior art, the invention provides a kind of assisting back and just reach the deflector of ultimate damping formula, this deflector possesses aligning force when increasing the car load steering reversal, steering system damping is carried out the function of timely adjustment.
The invention discloses a kind of assisting back and just reach the deflector of ultimate damping formula, comprise tooth bar, limiting stopper, rack bush, steering gear housing, interior bulb assembly and rack boot, tooth bar is loaded in the housing, the part tooth bar stretches out housing, limiting stopper is threaded with housing front end internal thread hole and cooperates, rack bush and limiting stopper adjacent and with housing endoporus interference fit, rack bush cooperates with the tooth bar air-tightness, interior bulb assembly front end is connected with the tooth bar inner hole thread, it is characterized in that, also comprise spring perch and coil spring, the spring perch interference presses fit in the housing, spring perch and tooth bar free-running fit, coil spring is between the interior ball cap and spring perch of interior bulb assembly.Form a seal chamber between interior ball cap and the helical spring seat, carry out gas exchange in the cavity of the left and right sides by the through hole on the tooth bar.
Further, described spring perch has spring mounting groove and rack stroke confined planes, and the internal ball cap of rack stroke confined planes carries out spacing, the movement travel of control tooth bar.Has tiny ripple on the rack stroke confined planes, to reduce the area of contact of rack stroke confined planes and interior ball cap.Described spring perch is a plastic material.
Adopt said structure, the aligning force in the time of can increasing the car load steering reversal on the one hand remedies because the steering assembly tooth bar displacing force that the increase of tooth bar axial force causes; Improved the feel of steering lock position on the other hand, cushioned, can eliminate the metal bump sound that sends of end position in the steering lock position.
Description of drawings
Fig. 1: existing rack and pinion steering gear right side structural representation;
Fig. 2: the structural representation at intermediate rod place, deflector of the present invention right side;
Fig. 3: structure principle chart of the present invention;
Fig. 4: spring perch topology view.
Among the figure: 1,11-tooth bar;
2,12-limiting stopper;
3,13-rack bush;
4,14-steering gear housing;
5, bulb assembly in the 15-;
6,16-rack boot;
The 7-spring perch;
The 8-coil spring;
The 9-through hole;
The 10-seal chamber;
17-spring mounting groove;
18-rack stroke confined planes.
The specific embodiment
Below in conjunction with accompanying drawing the present invention is specifically described.
Deflector is in the intermediate rod place of left and right sides symmetrical configuration, Fig. 2 shows the structure at intermediate rod place, deflector right side, and deflector specifically comprises tooth bar 1, limiting stopper 2, rack bush 3, steering gear housing 4, interior bulb assembly 5, rack boot 6, spring perch 7 and coil spring 8.Tooth bar 1 is loaded in the housing 4, the part tooth bar stretches out housing, limiting stopper 2 is threaded with housing 4 front end internal thread holes and cooperates, rack bush 3 and limiting stopper 2 adjacent and with housing 4 endoporus interference fit, rack bush 4 cooperates with tooth bar 1 air-tightness, and interior bulb assembly 5 front ends are connected with tooth bar 1 inner hole thread.Spring perch 7 interference press fit in the housing 4, spring perch 7 and tooth bar 1 free-running fit, and coil spring 8 is between the interior ball cap and spring perch 7 of interior bulb assembly 5.About deflector two interior ball caps and about two helical spring seats 7 be respectively installed with left and right coil spring 8, like this about two seal chambers 10 of formation, the gas exchange of being undertaken in the cavity of the left and right sides by the through hole on the tooth bar 9.
Do not have corner when input, the tooth bar balance position that mediates at steering handwheel, referring to Fig. 3, the suffered left and right sides of piston this moment spring force equates, realizes balance; When steering wheel angle is imported, the deflector miniature gears is by the engagement of rack-and-gear, tooth bar is produced to be moved axially accordingly, in a single day depart from balance position with tooth bar bonded assembly piston like this, about spring will produce the application force that does not wait, suppose that piston moves X, then the spring force that is subjected to of piston is: (along rack shaft to)
F＝F1-Fr＝k*(ΔX+x)-k*(ΔX+x)＝2kx
Wherein F1 represents left spring power, and Fr represents right spring force, and k represents elasticity modulus.In case promptly piston departs from balance position xmm, spring will produce the aligning force of 2kx, and aligning force can impel tooth bar to get back to the intermediate equilibria position after finishing turning to, and utilize this characteristic can realize that deflector assists return function.Simultaneously, when the car load wheel flutter is subjected to ground-surface impact suddenly or lateral forces, little the moving about tooth bar can produce, the present invention is because the effect of the left and right sides spring of above-mentioned increase can be played the good restraining effect for the little displacement of tooth bar that occurs.
Among the present invention, the spring perch structure is optimized, specifically as shown in Figure 4.
Spring perch has spring mounting groove 17 and rack stroke confined planes 18, on the one hand in 18 pairs of the rack stroke confined planes ball cap 5 carry out spacing, thereby the movement travel of control tooth bar 11 is satisfied car load and is turned to requirement; On the other hand, have tiny ripple on the rack stroke confined planes 18, can structurally reduce the area of contact with interior ball cap 5, the shock damping action of spring to system arranged simultaneously; Further use plastic material alternative metals material, can effectively avoid tooth bar to impact the metallic noise that produces, improved the traveling comfort of driving at end position.
Helical spring design is a critical parts of the present invention, its may command aligning torque size, and stored energy when realizing turning to is returned timing and is released energy.
Claims (5)
1. assist back and just reach the deflector of ultimate damping formula for one kind, comprise tooth bar (1), limiting stopper (2), rack bush (3), steering gear housing (4), interior bulb assembly (5) and rack boot (6), tooth bar (1) is loaded in the housing (4), the part tooth bar stretches out housing, limiting stopper (2) is threaded with housing (4) front end internal thread hole and cooperates, rack bush (3) adjacent with limiting stopper (2) and with housing (4) endoporus interference fit, the same tooth bar of rack bush (4) (1) air-tightness cooperates, interior bulb assembly (5) front end is connected with tooth bar (1) inner hole thread, it is characterized in that, also comprise spring perch (7) and coil spring (8), spring perch (7) interference presses fit in the housing (4), spring perch (7) and tooth bar (1) free-running fit, coil spring (8) is positioned between the ball cap and spring perch (7) of bulb assembly (5).
2. according to claim 1 assisting back just reaches the deflector of ultimate damping formula, it is characterized in that: form a seal chamber (10) between interior ball cap and the helical spring seat (7), carry out the interior gas exchange of left and right sides cavity by the through hole on the tooth bar (9).
3. according to claim 1 and 2 assisting back just reaches the deflector of ultimate damping formula, it is characterized in that: described spring perch (7) has spring mounting groove (17) and rack stroke confined planes (18), the internal ball cap of rack stroke confined planes (18) carries out spacing, the movement travel of control tooth bar (11).
4. just reach the deflector of ultimate damping formula according to each described assisting back of claim 1-3, it is characterized in that: the rack stroke confined planes has tiny ripple on (18), to reduce the area of contact of rack stroke confined planes and interior ball cap.
5. just reach the deflector of ultimate damping formula according to each described assisting back of claim 1-4, it is characterized in that: described spring perch (7) is a plastic material.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910207442A CN101698416A (en) | 2009-11-03 | 2009-11-03 | Alignment assistance and ultimate damping type steering gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910207442A CN101698416A (en) | 2009-11-03 | 2009-11-03 | Alignment assistance and ultimate damping type steering gear |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101698416A true CN101698416A (en) | 2010-04-28 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910207442A Pending CN101698416A (en) | 2009-11-03 | 2009-11-03 | Alignment assistance and ultimate damping type steering gear |
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| CN (1) | CN101698416A (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103832465A (en) * | 2012-11-27 | 2014-06-04 | 重庆长安汽车股份有限公司 | Abnormal sound prevention structure of automobile mechanical steering gear |
| CN104512456A (en) * | 2013-09-27 | 2015-04-15 | 北汽福田汽车股份有限公司 | Automobile, power steering gear, and control method of power steering gear |
| CN105365880A (en) * | 2014-09-01 | 2016-03-02 | 广州汽车集团股份有限公司 | Rack and pinion steering gear |
| CN109305216A (en) * | 2018-09-10 | 2019-02-05 | 安徽德孚转向系统股份有限公司 | The dust guard of electric boosting steering system |
| CN109305217A (en) * | 2018-09-10 | 2019-02-05 | 安徽德孚转向系统股份有限公司 | Electric boosting steering system |
| CN111409693A (en) * | 2019-01-04 | 2020-07-14 | 森源汽车股份有限公司 | Vehicle and rack and pinion steering gear thereof |
| US10988171B2 (en) | 2019-04-04 | 2021-04-27 | Honda Motor Co., Ltd. | Steering rack stopper |
| CN112896309A (en) * | 2021-01-25 | 2021-06-04 | 江苏永捷工程物流有限公司 | Steering control system of multi-servo valve cooperative control heavy flat-bed transport vehicle |
| CN114132376A (en) * | 2021-11-29 | 2022-03-04 | 华人运通(江苏)技术有限公司 | Steering and correcting system |
-
2009
- 2009-11-03 CN CN200910207442A patent/CN101698416A/en active Pending
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103832465A (en) * | 2012-11-27 | 2014-06-04 | 重庆长安汽车股份有限公司 | Abnormal sound prevention structure of automobile mechanical steering gear |
| CN104512456A (en) * | 2013-09-27 | 2015-04-15 | 北汽福田汽车股份有限公司 | Automobile, power steering gear, and control method of power steering gear |
| CN105365880A (en) * | 2014-09-01 | 2016-03-02 | 广州汽车集团股份有限公司 | Rack and pinion steering gear |
| CN105365880B (en) * | 2014-09-01 | 2018-06-05 | 广州汽车集团股份有限公司 | A kind of rack and pinion steering gear |
| CN109305216A (en) * | 2018-09-10 | 2019-02-05 | 安徽德孚转向系统股份有限公司 | The dust guard of electric boosting steering system |
| CN109305217A (en) * | 2018-09-10 | 2019-02-05 | 安徽德孚转向系统股份有限公司 | Electric boosting steering system |
| CN111409693A (en) * | 2019-01-04 | 2020-07-14 | 森源汽车股份有限公司 | Vehicle and rack and pinion steering gear thereof |
| US10988171B2 (en) | 2019-04-04 | 2021-04-27 | Honda Motor Co., Ltd. | Steering rack stopper |
| CN112896309A (en) * | 2021-01-25 | 2021-06-04 | 江苏永捷工程物流有限公司 | Steering control system of multi-servo valve cooperative control heavy flat-bed transport vehicle |
| CN114132376A (en) * | 2021-11-29 | 2022-03-04 | 华人运通(江苏)技术有限公司 | Steering and correcting system |
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Open date: 20100428 |