CN103072439B - Suspension device - Google Patents
Suspension device Download PDFInfo
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- CN103072439B CN103072439B CN201210419444.XA CN201210419444A CN103072439B CN 103072439 B CN103072439 B CN 103072439B CN 201210419444 A CN201210419444 A CN 201210419444A CN 103072439 B CN103072439 B CN 103072439B
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- lower link
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Abstract
The present invention provides a suspension device which is used for improving position accuracy of each connecting rod in a multiple-connecting-rod suspension relative to a vehicle body. A back suspension crossbeam (21) is connected with a rear axle housing (11) through an back upper connecting rod (19), a front lower connecting rod (25), a back lower connecting rod (23) and a radius rod (27). In a condition that no load is applied for a rear suspension device (1), tension is generated on the front lower connecting rod (25) and the back lower connecting rod (23). Furthermore mounting bracket parts at ends of the connecting rods are fastened in the condition. When generation of tension is required, the front lower connecting rod (25) utilizes a cam mechanism (11) for adjusting an outer inclination angle, and the back lower connecting rod (23) utilizes a cam mechanism (29) for adjusting a front inclination angle.
Description
Technical field
The present invention relates to a kind of draft hitch with multi-link lever suspension fork.
Background technology
In the past, as the draft hitch with multi-link lever suspension fork, be known to the content described in following patent documentation 1.
Patent documentation 1: Japanese Unexamined Patent Publication No. 4195208 publication
But such draft hitch with multi-link lever suspension fork, by improving each connecting rod relative to the positional precision of vehicle body, makes the vehicle performances such as riding stability raise further.
Summary of the invention
Therefore, the object of the invention is to improve the positional precision of each connecting rod in multi-link lever suspension fork relative to vehicle body.
The invention is characterized in, under the state car load not being applied to draft hitch, the tension force that the tension force that the adjustment component adjusted for utilizing camber angle applies front lower link applies rear lower link with the adjustment component utilizing angle of toein to adjust, produce wherein at least one tension force, by fastening for the installation component of each end of each connecting rod and radius bar under this generation tension state.
Adopt the present invention, under the state car load not being applied to draft hitch, at least one connecting rod in front lower link and rear lower link produces tension force, under this generation tension state, because will to being set in each connecting rod, the installation component of end of radius bar carries out fastening, so installation component by be applied with load in advance state under fastening, thus each connecting rod, radius bar can be improved relative to the positional precision of suspension crossbeam.Now, due to can not on wheel mounting tyre, wheel rim state under carry out the link operation of each connecting rod, radius bar, therefore workability improves.
Accompanying drawing explanation
Fig. 1 is the back view seen from rear view of vehicle of the back suspension device of the left rear wheel side of the vehicle representing one embodiment of the present invention.
Fig. 2 is the block diagram of the left rear wheel periphery of the back suspension device representing Fig. 1.
Fig. 3 is the birds-eye view of the left rear wheel periphery of the back suspension device representing Fig. 1.
Fig. 4 is the lateral plan of the left rear wheel periphery of the back suspension device representing Fig. 1.
Fig. 5 is the A-A cutaway view in Fig. 1.
Fig. 6 represents the Action Specification figure producing the operation of tension force in front lower link in the back suspension device of Fig. 1 and rear lower link, (a) of Fig. 6 represents the state producing tension force in front lower link, (b) of Fig. 6 represents the state producing tension force in rear lower link, under (c) of Fig. 6 represents the state producing tension force in front lower link and rear lower link, in radius bar (radius rod), produce the state of compressive force.
Detailed description of the invention
Based on accompanying drawing, embodiments of the present invention are described below.
Fig. 1 ~ Fig. 4 represents the back suspension device 1 of one embodiment of the present invention.In addition, the back suspension device 1 of left side rear wheel 3 is illustrated in this Fig. 1 ~ Fig. 4, but the back suspension device of right side rear wheel is also identical with the basic structure of the back suspension device of left side rear wheel, therefore, only the back suspension device 1 corresponding with left side rear wheel 3 is described.Above-mentioned left and right trailing wheel forms wheel.
Trailing wheel 3 has wheel hub 5, and wheel hub 5 is provided with brake disc 7.Reference numeral 9 is the brake clamps for braking brake disc 7.Inside the vehicle-width direction of wheel hub 5, be configured with the rear-axle casing 11 as axle housing, the mode that after it, semiaxis 13 can rotate relatively supports rear semiaxis 13.Rear-axle casing 11 links the urceolus lower end of bumper 15, and the inner core upper end of bumper 15 is linked to vehicle body.Reference numeral 17 in Fig. 3 is coil springs.In addition, in Fig. 1, Fig. 4, eliminate brake disc 7 and brake clamp 9.
In the upper end of rear-axle casing 11, by erection support portion 19a be linked with as upper connecting rod rear upper connecting rod 19 by vehicle-width direction outboard end, two ends be positioned on vehicle fore-and-aft direction by inboard portion, vehicle-width direction of rear upper connecting rod 19 are linked to the top of the rear suspension crossbeam 21 as suspension crossbeam by erection support portion 19b, 19c.
And, as shown in Figure 1, in the rear view of vehicle side of the above-below direction substantial middle of rear-axle casing 11, be linked with the vehicle-width direction outboard end of rear lower link 23 by erection support portion 23a, the vehicle-width direction medial end of rear lower link 23 is linked to rear suspension crossbeam 21 by erection support portion 23b.This rear lower link 23 has angle of toein adjustment function.
And, with regard to regard to lower link 25 before above-mentioned rear lower link 23 more vehicle front and below, its vehicle-width direction outboard end is linked to the bottom of rear-axle casing 11 by erection support portion 25a, the vehicle-width direction medial end of front lower link 25 is linked to the bottom of rear suspension crossbeam 21 by erection support portion 25b.This front lower link 25 has camber angle adjustment function.In addition, rear suspension crossbeam 21 is eliminated in fig. 2.
As shown in Figure 3, rear suspension crossbeam 21 be included in vehicle front side direction vehicle-width direction extend front cross rail 21a, the after cross member 21b extended in the rear view of vehicle side direction vehicle-width direction of front cross rail 21a and by interconnected to these each crossbeam 21a, 21b and to vehicle fore-and-aft direction extension longeron 21c.Longeron 21c is longeron paired up and down, the longeron of its middle and upper part is by erection support portion 19b, 19c is linked with the end of above-mentioned rear upper connecting rod 19, and the position be positioned near after cross member 21b of the longeron of its middle and lower part is linked with the end of rear lower link 23 by erection support portion 23b.
And, as shown in Figure 3, this rear suspension crossbeam 21 comprise near extended portion, the front 21d that extends outside vehicle front and vehicle-width direction near the joint portion between front cross rail 21a and longeron 21c and the joint portion between the longeron 21c on after cross member 21b and top outside vehicle-width direction and extended portion, the rear 21e that extends of rear.
And, using the front end 21h of the front end 21f of above-mentioned front extended portion 21d, the rear end 21g of extended portion, rear 53e and the longeron 21c on top as the installation portion carrying out installing to vehicle body.
And, as shown in Figure 4, utilize radius bar 27 to be linked up the bottom near the front end 21h being positioned at longeron 21c in lower link 25 before the ratio of the bottom of the rear-axle casing 11 by the top position of position and rear suspension crossbeam 21.
As shown in Figure 3, the state that radius bar 27 tilts by the mode inside vehicle-width direction by rear view of vehicle side part than it by vehicle front side part with it extends to vehicle fore-and-aft direction.Its leading section is linked to suspension crossbeam 21 by erection support portion 27a by this radius bar 27, end is thereafter linked to the bottom of rear-axle casing 11 by erection support portion 27b.
There is the rear lower link 23 of angle of toein adjustment function, at it by carrying out the cam mechanism 29(Fig. 4 of the adjustment component fastening fastening part had as angle of toein adjustment by the erection support portion 23b of the end inside vehicle-width direction).And, there is the front lower link 25 of camber angle adjustment function, at it by carrying out cam mechanism 31(Fig. 1, Fig. 4 of the adjustment component fastening fastening part had as camber angle adjustment by the erection support portion 25b of the end inside vehicle-width direction).
These cam mechanisms 29,31 are identical structure substantially, therefore, utilize Fig. 5 to be only described cam mechanism 31.The erection support portion 25b carrying out installing relative to rear suspension crossbeam 21 of the vehicle-width direction medial end of front lower link 25 represents with the A-A cutaway view in Fig. 1 by Fig. 5.
This erection support portion 25b comprise front lower link 25 side urceolus 33, in the inner side of this urceolus 33 and with the resilient bushing 37 of the drum of the inner core 35 of urceolus 33 coaxial configuration and rubber between these urceolus 33 and inner cores 35.The axial two ends of inner core 35 are more protruding outside to axis than the axial two ends of urceolus 33, and each end that this is outstanding is separately fixed at the pair of flanges 21a of rear suspension crossbeam 21 side, the inside face of 21b.Resilient bushing 37 is individually fixed in the outer peripheral face of inner core 35 and the inner peripheral surface of urceolus 33, and the outer peripheral face of urceolus 33 is pressed in front lower link 25.
Inner core 35 has the through hole 35a running through its central part vertically, is provided with elongated hole 21a1,21b1 correspondingly on the pair of flanges 21a, 21b of rear suspension crossbeam 21.The direction (being the axis of front lower link 25 in FIG) that elongated hole 21a1,21b1 are orthogonal with paper is in Figure 5 formed longer, in these each elongated hole 21a1,21b1 and through hole 35a, is inserted with adjustment bolt 39.
Inner core 35 with lower link 25 before axial central portion and the roughly corresponding position of urceolus 33 outstanding to radial outside, between inner core 35 and urceolus 33, be formed with the space 40 of ring-type.Rotate relative to inner core 35 under the state that the bar portion 39b that adjustment bolt 39 can be positioned at the axial both sides in this space 40 at it and the inner peripheral surface of inner core 35 roughly contact.
Adjustment bolt 39 comprises head 39a, bar portion 39b, be positioned at the cam 39c of the end of the 39b side, rod portion of head 39a and be positioned at the cam 39d of tip side of bar portion 39b.As the cam 39c represented in Fig. 1, these two cams 39c, 39d make the circular plate shape of the eccentric axis relative to adjustment bolt 39, the outside that cam 39c is positioned at the outside of flange 21a, cam 39d is positioned at flange 21b, and they are integrated with adjustment bolt 39.
Shown in Fig. 1 an one cam 39c is relative to adjustment bolt 39 upward and slightly toward the state of left side bias, but another cam 39d that cannot see in figure be also to the state of an above-mentioned cam 39c to same direction bias.
And, as shown in Figure 1, the position of the axial both sides (being the left and right sides in FIG) of lower link 25 before being positioned at of radial outside of cam 39c, to cut from the lateral surface of flange 21a and the state of holding up is provided with a pair guide piece 41,43, and this pair guide piece 41,43 is in the state that be contacted with the periphery of this cam 39c in the mode that can rotate relative to cam 39c.Similarly, the position of the axial both sides (being the left and right sides in FIG) of lower link 25 before being positioned at of radial outside of cam 39d, be provided with a pair not shown guide piece with the state of the lateral surface being fixed on flange 21a, and this pair guide piece is in the state being contacted with the periphery of this cam 39d in the mode that can rotate relative to cam 39d.
Be formed with tabular surface 39b1 at the sidepiece (being bottom in Figure 5) on the 39b top, rod portion of adjustment bolt 39, be also formed with tabular surface 45a1 in the mode of mating with this tabular surface 39b1 at the inside face of the through hole 45a of guided rings 45.By being inserted in the through hole 45a of guided rings 45 while making these tabular surfaces 39b1,45a1 mutually mate, by the bar portion 39b of adjustment bolt 39, thus lead ring 45 cannot rotate relatively with adjustment bolt 39.
In addition, nut 47 is fastened with than cam 39d by the threaded portion of tip side at adjustment bolt 39.
Thus, rotate by making adjustment bolt 39 under the state having loosened nut 47, cam 39c, 39d also rotate integratedly with bolt 39, and this cam 39c, cam 39d guide by a pair guide piece 41,43 and a pair not shown guide piece and move to the left and right directions in Fig. 1 along each elongated hole 21a1,21b 1 respectively.As shown in Figure 1, in order to amount of movement now can be estimated, scale 49 is provided with on the surface of cam 39c.
At this, in the present embodiment, in order to improve the positional precision of each connecting rod in the multi-link lever suspension fork of back suspension device 1, carry out following operation.This operation is carried out under the state making left and right trailing wheel from ground hangs (back suspension device 1 not being applied to the state of car load), but owing to being same concerning both left and right trailing wheels, therefore, is only described left side rear wheel 3.
First, as mentioned above, under the state not applying car load to back suspension device 1, the nut 47 shown in Fig. 5 before loosening in lower link 25, makes adjustment bolt 39 rotate.By the rotation of adjustment with bolt 39, cam 39c and cam 39d is guide by a pair guide piece 41,43 and a pair not shown guide piece respectively and rotates integratedly with adjustment bolt 39.
When cam 39c, 39d rotate, move to the left and right directions in Fig. 1 along each elongated hole 21a1,21b1 of flange 21a, 21b relative to the adjustment bolt 39 of cam 39c, 39d bias.Now, in the present embodiment, in order to produce tension force on front lower link 25, and cam 39c, 39d are rotated to the anticlockwise direction in Fig. 1 from the state of Fig. 1.
Rotated by this cam 39c, 39d, the adjustment vehicle-width direction medial movement on bolt 39 right side in Fig. 1, accompany therewith, front lower link 25 is pulled by inside vehicle-width direction relative to the erection support portion 25a of vehicle-width direction outboard end.Thus, as shown in the schematic diagram of Fig. 6 (a), front lower link 25 produces tension force F 1.Now, carrying out operation by estimating scale 49, the adjustment amount of the rotation amount of adjustment bolt 39, i.e. the tension force F1 of front lower link 25 can be held, thus the high efficiency adjusting operation can be sought.
Before making, lower link 25 produces in the operation process of tension force F1, the erection support portion 25a of the vehicle-width direction outboard end of front lower link 25 is not fastening, it is only the state linked, under the state that front lower link 25 creates the Fig. 6 (a) after tension force F1, fastening erection support portion 25b also carries out the lashing operation of erection support portion 25a.Now, as shown in Figure 6 (a), the rear-axle casing 11 of trailing wheel 3 is pulled by front lower link 25 and tilts relative to vehicle above-below direction by the mode of (in figure 6 (a) for right side) inside vehicle-width direction than top with bottom.
Then, in the same manner as the operation carried out front lower link 25, under the state not applying car load to back suspension device 1, make as shown in Figure 6 (b) rear lower link 23 produces tension force F2.
After making, lower link 23 produces in the operation process of tension force F2, the erection support portion 23a of its vehicle-width direction outboard end is not fastening, it is only the state linked, under the state that rear lower link 23 creates the Fig. 6 (b) after tension force F2, fastening erection support portion 23b is fastening and carry out the lashing operation of erection support portion 23a.Now, as shown in Figure 6 (b), the rear-axle casing 11 of trailing wheel 3 is pulled by rear lower link 23 and tilts relative to vehicle fore-and-aft direction by the mode of outside (for right side in Fig. 6 (b)) in vehicle-width direction with more inboard than paper outside paper.
As described above make respectively before lower link 25 and rear lower link 23 produce in the operation process of tension force F1 and tension force F2, erection support portion 27a, the 27b at the two ends of radius bar 27 are not fastening, it is only the state linked, when producing tension force F1 and tension force F2, radius bar 27 becomes vertically by the state compressed.
By being carried out the fastening of erection support portion 27a, the 27b at the two ends of radius bar 27 at this radius bar 27 by under the state that have compressed, as shown in Figure 6 (c), become the state that compressive force F3 paid vertically by pair radius bar 27.
And, as described above make respectively before lower link 25 and rear lower link 23 produce in the operation process of tension force F1 and tension force F2, erection support portion 19a, 19b, the 19c at the two ends of rear upper connecting rod 19 are not fastening, it is only the state linked, when producing tension force F1 and tension force F2, rear upper connecting rod 19 becomes by the state pulled vertically.By in this condition by fastening to erection support portion 19a, 19b, the 19c at the two ends of rear upper connecting rod 19, become and the state pulling load is paid to rear upper connecting rod 19.
Like this, front lower link 25 and rear lower link 23 produce tension force F1 and tension force F2, connecting rod 19 also produces tension force on rear, and the state that pair radius bar 27 applies compressive force F3 becomes the state close to real vehicle state, and real vehicle state is the state of instigating tire interface in ground, back suspension device 1 to be applied with to vehicle weight.
And, in the present embodiment, in order to reach above-mentioned real vehicle state, fastening each erection support portion under the state that front lower link 25 and rear lower link 23 create tension force, and on radius bar 27, produce compressive force and fastening each erection support portion under state connecting rod 19 also producing tension force on rear.Thus, each erection support portion of each connecting rod (front lower link 25, rear lower link 23, radius bar 27, rear upper connecting rod 19) can be fastened with the state of having been paid load in advance, can eliminate rocking thus improving the positional precision of each connecting rod relative to vehicle body (rear suspension crossbeam 21) of each erection support portion.
As this for improving the operation of the positional precision of each connecting rod, in the present embodiment, can on wheel non-mounting tyre, wheel rim state under carry out the lashing operation of each connecting rod, therefore, this tire, wheel rim can not become interference, easily can carry out lashing operation.
In addition, the final adjustment of camber angle, angle of toein is carried out after the lashing operation of above-mentioned each connecting rod terminates.
And in the present embodiment, adjustment component comprises and can to rotate integratedly with adjustment bolt 39 and relative to cam 39c, 39d of this adjustment bolt 39 bias.Therefore, only make adjustment bolt 39 rotate, cam 39c, 39d will rotate, and based on these, easily can produce tension force F1 and tension force F2 on front lower link 25 and rear lower link 23.
In addition, in the above-described embodiment, both front lower link 25 and rear lower link 23 produce tension force, but also can produce tension force on any one connecting rod.In this case, also can under the state of paying load in advance each erection support portion of fastening each connecting rod, thus rocking and improving the positional precision of each connecting rod relative to vehicle body (rear suspension crossbeam 21) of each erection support portion can be eliminated.
description of reference numerals
1, back suspension device (draft hitch); 3, trailing wheel (wheel); 11, rear-axle casing (axle housing); 19, upper connecting rod (going up connecting rod afterwards); 21, rear suspension crossbeam (suspension crossbeam); 23, rear lower link; 25, front lower link; 27, radius bar; 29, cam mechanism (adjustment component of angle of toein adjustment); 31, cam mechanism (adjustment component of camber angle adjustment); 39c, 39d, cam.
Claims (2)
1. a draft hitch, is characterized in that,
This draft hitch comprises:
Upper connecting rod, it links with the top of the axle housing of the revolvable mode supporting wheel of wheel and vehicle body;
Front lower link, it links bottom and the vehicle body of above-mentioned axle housing;
Rear lower link, it links the part by rear view of vehicle side being positioned at above-below direction central portion and the vehicle body of above-mentioned axle housing;
Radius bar, it links bottom and the vehicle body of above-mentioned axle housing;
Above-mentioned front lower link is provided with the adjustment component of camber angle adjustment, and, above-mentioned rear lower link is provided with the adjustment component of angle of toein adjustment, under the state car load not being applied to draft hitch, for the tension force that the adjustment component utilizing above-mentioned camber angle to adjust applies rear lower link with the adjustment component utilizing above-mentioned angle of toein to adjust the tension force that front lower link applies, produce wherein at least one tension force, under this generation tension state, by fastening for the installation component of each end of above-mentioned each connecting rod and above-mentioned radius bar.
2. draft hitch according to claim 1, is characterized in that,
Under the state car load not being applied to draft hitch, the adjustment component utilizing camber angle to adjust produces tension force on front lower link, and, the adjustment component utilizing angle of toein to adjust produces tension force on rear lower link, by fastening for the installation component of each end of above-mentioned each connecting rod and above-mentioned radius bar under this generation tension state.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011-234684 | 2011-10-26 | ||
| JP2011234684A JP6203993B2 (en) | 2011-10-26 | 2011-10-26 | Suspension device assembly method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103072439A CN103072439A (en) | 2013-05-01 |
| CN103072439B true CN103072439B (en) | 2015-03-18 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210419444.XA Active CN103072439B (en) | 2011-10-26 | 2012-10-26 | Suspension device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6203993B2 (en) |
| CN (1) | CN103072439B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5812039B2 (en) * | 2013-05-08 | 2015-11-11 | トヨタ自動車株式会社 | Steering wheel suspension system |
| CN106005007B (en) * | 2016-05-24 | 2017-03-29 | 合肥工业大学 | The adjusting apparatus of vehicle camber angle and toe-in angle |
| DE102018214289A1 (en) * | 2018-08-23 | 2020-02-27 | Bayerische Motoren Werke Aktiengesellschaft | Rear axle of a vehicle |
| US11584160B2 (en) * | 2019-12-10 | 2023-02-21 | Fca Us Llc | Vehicle having adjustment mechanism |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0299413A (en) * | 1988-10-06 | 1990-04-11 | Mazda Motor Corp | Suspension device for vehicle |
| CN101011927A (en) * | 2006-01-31 | 2007-08-08 | 本田技研工业株式会社 | Suspension structure |
| CN101088787A (en) * | 2006-06-14 | 2007-12-19 | 丰田自动车株式会社 | Device for changing distance between wheel and vehicle body, and system including the device |
| CN201109361Y (en) * | 2007-11-07 | 2008-09-03 | 郑州日产汽车有限公司 | Automobile rear suspension |
| JP2009029254A (en) * | 2007-07-26 | 2009-02-12 | Nissan Motor Co Ltd | Front suspension device for vehicle |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006160006A (en) * | 2004-12-03 | 2006-06-22 | Nissan Motor Co Ltd | Vehicle movement control device |
| JP2010052583A (en) * | 2008-08-28 | 2010-03-11 | Honda Motor Co Ltd | Rear suspension device |
-
2011
- 2011-10-26 JP JP2011234684A patent/JP6203993B2/en active Active
-
2012
- 2012-10-26 CN CN201210419444.XA patent/CN103072439B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0299413A (en) * | 1988-10-06 | 1990-04-11 | Mazda Motor Corp | Suspension device for vehicle |
| CN101011927A (en) * | 2006-01-31 | 2007-08-08 | 本田技研工业株式会社 | Suspension structure |
| CN101088787A (en) * | 2006-06-14 | 2007-12-19 | 丰田自动车株式会社 | Device for changing distance between wheel and vehicle body, and system including the device |
| JP2009029254A (en) * | 2007-07-26 | 2009-02-12 | Nissan Motor Co Ltd | Front suspension device for vehicle |
| CN201109361Y (en) * | 2007-11-07 | 2008-09-03 | 郑州日产汽车有限公司 | Automobile rear suspension |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103072439A (en) | 2013-05-01 |
| JP6203993B2 (en) | 2017-09-27 |
| JP2013091416A (en) | 2013-05-16 |
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