CN103754262B - Method for designing linkage steering relation of semi-trailer type highway passenger vehicle - Google Patents
Method for designing linkage steering relation of semi-trailer type highway passenger vehicle Download PDFInfo
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- CN103754262B CN103754262B CN201410023715.9A CN201410023715A CN103754262B CN 103754262 B CN103754262 B CN 103754262B CN 201410023715 A CN201410023715 A CN 201410023715A CN 103754262 B CN103754262 B CN 103754262B
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Abstract
The invention discloses a method for designing a linkage steering relation of a semi-trailer type highway passenger vehicle. A gap between a rear wall of a driving cab and a front wall of a passenger compartment is small, so that running wind resistance is reduced, the inner space of the driving cab and the inner space of the passenger compartment are expanded, and passenger capacity is improved. Owing to the linkage steering relation, the width of a turning channel is reduced, road resources are saved, the tail of the body of the vehicle cannot swing outwards, and the running safety is improved.
Description
Technical field
The present invention relates to the turn-around design method of passenger vehicle and semi-mounted passenger vehicle, more specifically, design a kind of method of designing of linked steering relation of semi-trailer highway passenger vehicle.
Background technology
Since nearly half a century, the semi-trailer bus once runed abroad makes no public appearances.Traditional semi-trailer type passenger car exists that car load is overweight, occupant exchanges inconvenience with chaufeur, between tractor truck and compartment, the not high and car load of space availability ratio is turned and taken the problems such as larger path resource.But the advantages such as the passenger capacity that semi-trailer type passenger car itself has is large, safety is high, comfort type is good can not be ignored.
In recent years, emerge in multitude based on full-bearing type passenger vehicle, full carrying designing technique becomes better and approaching perfection day by day, communication in car, electron audio-visual technology etc. is all developed by leaps and bounds, Chinese Patent Application No. 201310177331.8 discloses a kind of semi-trailer all-loading coach body structure, solve traditional semi-trailer type passenger car car load overweight, chaufeur exchanges the problem of inconvenience with passenger, but owing to arranging that between driving compartment back wall and passenger accommodation front wall exposed passenger loading is stepped, institute takes up space larger, cause space availability ratio not high, travel air resistance also larger, and exposed marking time not only not easily keeps clean but also affects sleet sky passenger loading comfort feature, safety.
In addition, traditional semi-trailer type passenger car is turned, and to take the problems such as larger path resource still unresolved.Chinese Patent Application No. 201310164321.0 discloses the interaction relation between the secondary car linked steering bridge wheel shaft mid point angle of deflection of a kind of four axle simple chain articulated bus and the relative pivot angle β between main car and secondary car:
linear relationship α=k β is reduced to by adopting method of least square NUMERICAL MATCH METHOD FOR.The program reduces the turn clearance width of large-sized articulated coach to a great extent, but the linear linked steering relation α=k β after adopting NUMERICAL MATCH METHOD FOR to simplify can cause secondary car in turning process may occur putting phenomenon outward, be unfavorable for driver, affect traffic safety.
Therefore, if can solve existing various problems on the basis of traditional semi-trailer type passenger car advantage, semi-trailer type passenger car will grow a lot space.Now in conjunction with highway in China passenger vehicle current situation, a kind of novel semi-trailer highway passenger vehicle structure is proposed for above problem.
Summary of the invention
The present invention proposes a kind of method of designing of linked steering relation of semi-trailer highway passenger vehicle, when turning based on guarantee, tail of body is without the design philosophy of outer pendulum, establishes a kind of rear-axle linkage and turns to relation, reduce turn clearance width, improve driving safety, strengthen the practicality of organization plan.
A kind of method of designing of linked steering relation of semi-trailer highway passenger vehicle, tractor truck (1) and semi-trailer vehicle body (2) are double-bridge structure, tractor truck propons (10) is steeraxle, and back axle (11) is drive axle, and the doube bridge (12) of semi-trailer car is linked steering bridge; Step one, setting semi-trailer highway passenger vehicle are when turning, and the linked steering wheel of tractor truck wheel flutter foreign steamer, drive wheel and semi-trailer vehicle body is all turned around same center-point; Step 2, tractor truck and semi-trailer vehicle body hinge-point are minor increment m and the semi-trailer vehicle body rearmost end mid point of R circumference to radius is that the minor increment n of R circumference is equal to radius; The wherein excircle orbital radius that formed for car load outermost point projection on the ground in turning process of R; Step 3, according to m=n condition, establish the interaction relation of semi-trailer vehicle body first bridge wheel shaft mid point angle of deflection and tractor truck and semi-trailer vehicle body splice angle β: α=arccot{ [cos β (L
l+ L
s+ L
f)-2L
e]/[sin β (L
l-L
s-L
f)]; Wherein: L
ethe distance of towing pin axis to tractor truck rear axle, L
lthe distance of towing pin axis to semi-trailer vehicle body first axis, L
sthe distance of semi-trailer vehicle body first axis to second axle, L
fsemi-trailer body overhang length.
As further preferably, also comprise step 4, ask according to numerical value and be worth method most, be reduced to linear interaction relation α=k β by approximate for described interaction relation; Several splice angles β is chosen in [0 °, 45 °] scope
i(i=0,1 ..., n), obtain corresponding α by described interaction relation
i; Make k
i'=α
i/ β
i, find minimum ratio k ', i.e. k '=min{k
i', then be multiplied by safety factor
as final k value, namely
As further preferred, described safety factor
scope
As further preferably, in [0 °, 45 °] scope, choose a splice angle every 1 degree.Beneficial effect:
Based on when ensureing to turn, tail of body is without the design philosophy of outer pendulum, and a kind of rear-axle linkage of proposition turns to the determination method of relation, reduces turn clearance width, improves driving safety, strengthen the practicality of organization plan.Semi-trailer vehicle body two suspension both can adopt independent suspension structure, improved travelling comfort, dependent suspension also can be adopted to reduce costs, for manufacturing enterprise provides more wide selection space.
Accompanying drawing explanation
Fig. 1 is semi-trailer highway passenger vehicle car load schematic diagram of the present invention.
Fig. 2 is the overall skeleton schematic diagram of semi-trailer highway passenger vehicle structure semi-trailer vehicle body of the present invention.
Fig. 3 is semi-trailer highway passenger vehicle structure car load birds-eye view of the present invention.
Fig. 4 is semi-trailer highway passenger vehicle structure tractor truck schematic diagram of the present invention.
Fig. 5 is semi-trailer highway passenger vehicle structure semi-trailer vehicle body schematic diagram of the present invention.
Fig. 6 is that semi-trailer highway passenger vehicle structure driving compartment back wall of the present invention is got on the bus access door partial schematic diagram.
Fig. 7 is that semi-trailer highway passenger vehicle structure passenger accommodation front wall of the present invention is got on the bus access door partial schematic diagram.
Fig. 8 is semi-trailer highway passenger vehicle structure turning schematic diagram of the present invention.
Fig. 9 is the main dimension parameter schematic diagram of semi-trailer highway passenger vehicle of the present invention.
Figure 10 is the linkage steering apparatus schematic diagram of semi-trailer highway passenger vehicle of the present invention.
Wherein: 1, tractor truck 2, semi-trailer vehicle body 3, driving compartment back wall 4, passenger accommodation front wall 5, the outside entrance door 6 of passenger, driving compartment get on the bus access door 7, passenger accommodation get on the bus to mark time 9 in access door 8, driving compartment of getting on the bus, mark time 10 in passenger accommodation of getting on the bus, tractor truck propons 11, tractor truck back axle 12, semi-trailer vehicle body Double-linkage steeraxle 13, driving compartment back wall and passenger accommodation front wall structure interval.
Detailed description of the invention
By reference to the accompanying drawings the specific embodiment of the present invention is further illustrated.
The main dimension parameter used in this programme as shown in Figure 9, wherein: L
ctractor truck front overhang length, L
dtractor truck wheelbase, L
ethe distance (fifth wheel lead) of towing pin axis to tractor truck rear axle, L
lthe distance (long wheelbase) of towing pin axis to semi-trailer vehicle body first axis, L
sthe distance (little wheelbase) of semi-trailer vehicle body first axis to second axle, L
fbe semi-trailer body overhang length, W is car load width.
Semi-trailer vehicle body integral skeleton structure as shown in Figure 2, is the full-bearing type integral structure of employing small bore rod member welding.Semi-trailer highway passenger vehicle structure car load schematic diagram as shown in Figure 1, birds-eye view as shown in Figure 3, tractor truck 1 and semi-trailer vehicle body 2 are double-bridge structure, car load is four bridge constructions, tractor truck propons 10 is steeraxle, back axle 11 is drive axle, semi-trailer vehicle body doube bridge 12 is linked steering bridge, drive axle is wherein only had to be that every side twin tire is arranged, other vehicle bridge are every side single tire and arrange, when turning to, semi-trailer vehicle body first bridge wheel shaft mid point angle of deflection and tractor truck and semi-trailer vehicle body splice angle β link.
Driving compartment back wall is the arc surface structure 3 of indent, and passenger accommodation front wall is the arc surface structure 4 of lordosis, as shown in Figure 4,5.Two arc surfaces are coaxial, and axis is towing pin axis, and two arc surface gaps 13 are certain values chosen within the scope of 200 ~ 300mm, and this gap value will meet the relevant regulations being mechanically connected interchangeability between GB/T20070-2006 on-road vehicle tractor truck and superimposed trailer.Semi-trailer front body overhang (towing pin axis is to semi-trailer vehicle body distance foremost) is namely the radius of passenger accommodation front wall arc surface, in turning process, driving compartment back wall and passenger accommodation front wall such as to remain at the gap, without movement interference when ensureing to turn, this structure design not only takes full advantage of the space between driving compartment and passenger accommodation, increase passenger capacity, and also reduce the air resistance in driving process.
Passenger loading Men Yousan sect forms, and is respectively one outside entrance door and twice and gets on the bus access door.Offer outside entrance door 5 at driving compartment right side wall, as shown in Figure 1, be arranged on front axle rear portion, reduce passenger loading height, conveniently get on the bus; Passenger loading access door 6,7 is offered at driving compartment back wall and passenger accommodation front wall correspondence position; as shown in Figure 4,5; arc is adopted to break away synchronous hatch door; preferred as one; and safety guard is housed; when ensureing that vehicle travels, passenger loading access door can not be opened, and during unlatching, vehicle can not start, and saves interior space and improves occupant safety.
Get on the bus mark time by mark time in driving compartment 8 with passenger accommodation in mark time and 9 to form with two parts, as shown in Figure 6,7.Mark time in driving compartment and 8 to mark time for three grades of being fixed in tractor chassis, arc along driving compartment back wall arc surface moves towards to arrange, mark time 9 in passenger accommodation for two-stage stepping, be arranged in the middle of two anti-rolling chocks, what one-level marked time that the degree of depth ends at front wall and gusset welds plane.This mode actv. of getting on the bus make use of space in driving compartment and passenger accommodation, ensure that symmetry and the integraty of semi-trailer body structure, improves vehicle body load-carrying capacity.
The turning situation of semi-trailer highway passenger vehicle structure as shown in Figure 8, all turn around same center-point O by the Double-linkage wheel flutter of semi-trailer type passenger car the wheel flutter foreign steamer of tractor truck, drive wheel and semi-trailer vehicle body when turning.Turn clearance width A is the difference of R and r, i.e. A=R-r, wherein, and the excircle orbital radius that R is formed for the projection on the ground of car load outermost point, the inner periphery orbital radius that r is formed for the most inside line projection on the ground of car load.For ensureing that tractor truck overlaps with the turning center of semi-trailer vehicle body in turning process, link to realize by controlling semi-trailer vehicle body first bridge wheel shaft mid point angle of deflection and tractor truck and semi-trailer vehicle body splice angle β.
A kind of defining method of linked steering relation: in order to avoid occurring that tail of body puts phenomenon outward when turning, ensure that the front and back running orbit of vehicle body is consistent by control m=n, the wherein minor increment of m to be tractor truck and semi-trailer vehicle body hinge-point h to radius be R circumference, the minor increment of n to be semi-trailer vehicle body rearmost end mid point t to radius be R circumference.
According to the geometric relationship in Fig. 8, derive semi-trailer vehicle body first bridge wheel shaft mid point angle of deflection and the interaction relation between tractor truck and semi-trailer vehicle body splice angle β, process is as follows:
Cross turning center O and do semi-trailer vehicle body longitudinal centerline vertical line, ∠ iOp=β can be obtained, ∠ pOq=α;
By m=n, Δ Oph ≌ Δ Opt can be obtained, so hp=pt,
In Δ Opi, there is Op=ipcot β, in Δ Opq, have Op=pqcot α,
By ipcot β=pqcot α,
Substitute into
ip＝hp-hi，hi＝hj/cosβ，hp＝（L
L+L
S+L
F）/2，hj＝L
E，
pq＝pt-qt，pt＝（L
L+L
S+L
F）/2，qt＝L
S+L
F，
Can obtain
[（L
L+L
S+L
F）/2-L
E/cosβ]cotβ＝[（L
L+L
S+L
F）/2-L
S+L
F]cotα，
Arrangement can obtain
α＝arccot{[cosβ(L
L+L
S+L
F)-2L
E]/[sinβ(L
L-L
S-L
F)]}。
But this interaction relation is too complicated, engineering realizes difficulty large, preferred as one, need to simplify it.
Due to the more difficult situation observed vehicle and put outward of chaufeur in turning process, affect vehicle safety, and in GB1589-2004 " on-road vehicle contour dimension, axle load and quality limit value ", the outer pendulum value of vehicle is limited (must not be greater than 0.8 meter) to some extent, so the present invention is by controlling to improve driving safety without outer pendulum or slight interior pendulum in turn inside diameter process, this can be realized by rational interaction relation α=k β, needs the minimum ratio k found between α and β.
Value process is as follows to utilize derivative to ask:
Order
f(β)＝α/β＝arccot{[cosβ(L
L+L
S+L
F)-2L
E]/[sinβ(L
L-L
S-L
F)]}/β
Pass through
obtain fmin (β),
Make k=f
min(β).
But above-mentionedly solve k(f
min(β)) process is comparatively complicated, adopts simplification thought to be similar to herein and obtains k:
Specify according to being mechanically connected interchangeability between GB/T20070-2006 on-road vehicle tractor truck and superimposed trailer, under turn condition, splice angle β should be able to reach 90 degree, but because the present invention is the semi-trailer structure being applied to passenger traffic, be different from common freight semitrailer, herein with reference to the limit value of general articulated bus major-minor car level angle, choosing splice angle β higher limit is 45 degree.
The present invention utilizes and choose several splice angles β in [0 °, 45 °] interval
i(i=0,1 ..., n), by α=arccot{ [cos β (L
l+ L
s+ L
f)-2L
e]/[sin β (L
l-L
s-L
f)] interaction relation obtains corresponding α
i, make k
i'=α
i/ β
i, therefrom choose k '=min (k
i').The k ' that said method calculates necessarily is greater than or equal to f
min(β), in order to ensure in turning process, when β is the arbitrary value in [0 °, 45 °] interval, vehicle, all without outer pendulum, makes
wherein
for safety factor,
Linear interaction relation α=k β after simplification can have multiple implementation, the present invention only provides one comparatively simple mechanical system exemplarily property explanation, as shown in Figure 10, mechanical type linkage steering mechanism forms primarily of angle converting mechanism, transmission mechanism and double rocker mechanism.Angle converting mechanism comprises miniature gears 15 and big gear wheel 16: miniature gears 15 and big gear wheel 16 are arranged on semi-trailer vehicle body gooseneck portion, and wherein the line of centers of miniature gears 15 is towing pin axis, miniature gears 15 and big gear wheel 16 radius ratio r
1/ r
2=α/β=k, miniature gears 15 has keyway 14, in turning process, is coordinated with keyway by mechanism on tractor truck saddle, and drive miniature gears 15 to rotate, rotational angle is β, thus drives big gear wheel 16 to rotate, and rotational angle is α; Transmission mechanism comprises rocking arm 17, connecting rod 18 and rocking arm 19: the transmission being realized angle [alpha] by rocking arm 17, connecting rod 18 and the rocking arm 19 be welded on deflecting plate 20 be welded in big gear wheel 16, and rocking arm 17 is isometric with rocking arm 19; Rocking arm 19 drives deflecting plate 20 to rotate α around attachment point A, thus drives double rocker mechanism AA
1a
2a
3and AA
4a
5a
6, realize left and right wheels and rotate, left and right wheels rotational angle γ
1with γ
2can realize by designing rocker mechanism rod member length with the relation of α, when ignoring tyre slip angle and lateral sliding, desirable left and right wheels rotational angle can ensure that in turning process, wheel is pure rolling state.
The one exemplary embodiment provided below in conjunction with accompanying drawing is described in further detail the present invention.
This programme based on GB1589-2004 " on-road vehicle contour dimension, axle load and quality limit value ", using the exradius 12.50 meters of porte-cochere circle as the turn radius R of vehicle body outermost point.In this programme, main dimension parameter following (unit: rice): tractor truck front overhang length L
c=1.00, tractor truck wheelbase L
d=3.50, towing pin axis is to distance (fifth wheel lead) L of tractor truck rear axle
e=0.50, towing pin axis is to distance (long wheelbase) L of semi-trailer vehicle body first axle
l=8.00, semi-trailer vehicle body first axis is to distance (little wheelbase) L of second axle
s=1.30, semi-trailer body overhang length L
f=2.4, car load width W=2.50.Semi-trailer type passenger car tractor truck length 5.50 meters, semi-trailer bodywork length 13.20 meters, towing pin axis to the vertical distance 4.00 meters of headstock, towing pin axis to the vertical distance 11.70 meters of the tailstock, passenger vehicle total length 15.70 meters.
According to the geometric relationship in Fig. 8, calculate the inner periphery orbital radius r that the most inside line projection on the ground of vehicle body is formed, thus obtain turn clearance width A.
Adopt following formula to be similar to and obtain r value:
Due to L
ebeing worth less and turning center comparatively large to the distance of hinge-point, therefore when shifting above-mentioned formula onto, can be the distance of turning center to tractor truck rear axle mid point to the distance Approximate Equivalent of hinge-point by turning center.
Substitution data are obtained r value and are about 7.36m.
By A=R-r, obtain A value and be about 5.14m.
Because vehicle similar to this programme in bus market is little, so place chooses general 12 meters of highway passenger vehicles as a reference.General 12 meters of highway passenger vehicles (wide 2.5 meters, wheelbase 6 meters, front overhang 2.5 meters, rear overhang 3.5) turn clearance width A is about 5.80 meters.The turn clearance width needed for 15.7 meters of semi-trailer highway passenger vehicles of the present embodiment is compared common 12 meters of highway passenger vehicles and is also reduced about 0.70 meter, reaches the object reducing turn clearance width.
This programme asks value method to find semi-trailer vehicle body first bridge wheel shaft mid point angle of deflection and the minimum ratio k between tractor truck and semi-trailer vehicle body splice angle β, by interaction relation α=arccot{ [cos β (L of complexity by adopting numerical value
l+ L
s+ L
f)-2L
e]/[sin β (L
l-L
s-L
f)] being reduced to linear relationship α=k β, process is as follows:
Splice angle β, i.e. a β is chosen every 1 degree in [0 °, 45 °] is interval
i(i=0,1 ..., be n) 0,1,2 ... 44,45 degree, by analytic expression α=arccot{ [cos β (L
l+ L
s+ L
f)-2L
e]/[sin β (L
l-L
s-L
f)] obtain corresponding α
i(solve α
i=0,0.402,0.804,1.207,1.610,2.014,2.420,2.827,3.236,3.646,4.059,4.474,4.893,5.314,5.738,6.166,6.598,7.034,7.475,7.920,8.371,8.827,9.289,9.758,10.233,10.715,11.205,11.702,12.208,12.723,13.248,13.782,14.327,14.883,15.450,16.030,16.624,17.231,17.852,18.489,19.143,19.813,20.502,21.210,21.938 and 22.687 degree), make k
i'=α
i/ β
i(i ≠ 0) (solves k
i'=0.402,0.402,0.402,0.403,0.403,0.403,0.404,0.404,0.405,0.406,0.407,0.408,0.409,0.410,0.411,0.412,0.414,0.415,0.417,0.419,0.420,0.422,0.424,0.426,0.429,0.431,0.433,0.436,0.439,0.442,0.445,0.448,0.451,0.454,0.458,0.462,0.466,0.470,0.474,0.479,0.483,0.488,0.493,0.499,0.504) k '=min (k, is therefrom chosen
i')=0.402, order
choose safety factor
be 0.9, k=0.9k ' ≈ 0.362, namely semi-trailer vehicle body first bridge wheel shaft mid point angle of deflection and the interaction relation between tractor truck and semi-trailer vehicle body splice angle β are α=0.362 β.
Above-mentioned is can understand and apply the invention for ease of those skilled in the art to the description of embodiment.Person skilled in the art obviously easily can make various amendment to these embodiments, and General Principle described herein is applied in other embodiments and need not through performing creative labour.Therefore, the invention is not restricted to embodiment here, those skilled in the art, according to announcement of the present invention, do not depart from improvement that scope makes and amendment all should within protection scope of the present invention.
Claims (4)
1. the method for designing of the linked steering relation of a semi-trailer highway passenger vehicle, tractor truck (1) and semi-trailer vehicle body (2) are double-bridge structure, tractor truck propons (10) is steeraxle, back axle (11) is drive axle, and the doube bridge (12) of semi-trailer car is linked steering bridge; It is characterized in that:
Step one, setting semi-trailer highway passenger vehicle are when turning, and the linked steering wheel of tractor truck wheel flutter foreign steamer, drive wheel and semi-trailer vehicle body is all turned around same center-point;
Step 2, tractor truck and semi-trailer vehicle body hinge-point are minor increment m and the semi-trailer vehicle body rearmost end mid point of R circumference to radius is that the minor increment n of R circumference is equal to radius; The wherein excircle orbital radius that formed for car load outermost point projection on the ground in turning process of R;
Step 3, according to m=n condition, establish the interaction relation of semi-trailer vehicle body first bridge wheel shaft mid point angle of deflection and tractor truck and semi-trailer vehicle body splice angle β: α=arccot{ [cos β (L
l+ L
s+ L
f)-2L
e]/[sin β (L
l-L
s-L
f)];
Wherein: L
ethe distance of towing pin axis to tractor truck rear axle, L
lthe distance of towing pin axis to semi-trailer vehicle body first axis, L
sthe distance of semi-trailer vehicle body first axis to second axle, L
fsemi-trailer body overhang length.
2. method of designing according to claim 1, is characterized in that: also comprise step 4, ask be worth method most according to numerical value, is reduced to linear interaction relation α=k β by approximate for described interaction relation; Several splice angles β is chosen in [0 °, 45 °] scope
i(i=0,1 ..., n), obtain corresponding α by described interaction relation
i; Make k
i'=α
i/ β
i, find minimum ratio k ', i.e. k '=min{k
i', then be multiplied by safety factor
as final k value, namely
3. method of designing according to claim 2, is characterized in that: described safety factor
scope
4. method of designing according to claim 2, is characterized in that: in [0 °, 45 °] scope, choose a splice angle every 1 degree.
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|---|---|---|---|
| CN201410023715.9A CN103754262B (en) | 2014-01-20 | 2014-01-20 | Method for designing linkage steering relation of semi-trailer type highway passenger vehicle |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410023715.9A CN103754262B (en) | 2014-01-20 | 2014-01-20 | Method for designing linkage steering relation of semi-trailer type highway passenger vehicle |
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5700023A (en) * | 1993-04-19 | 1997-12-23 | Lohr Industrie | Vehicle formed from a series of modules interconnected by a composite articulated connection |
| CN102046447A (en) * | 2008-05-06 | 2011-05-04 | 罗尔工业公司 | Disconnectable articulated connection between two successive road-going modules of a road train |
| WO2013064848A2 (en) * | 2011-11-02 | 2013-05-10 | Szabo Istvan | Double pivot joint unit with running gear for road vehicles |
| CN103231744A (en) * | 2013-05-07 | 2013-08-07 | 吉林大学 | Four-axis single-hinge hinge type passenger car structure |
| CN103241299A (en) * | 2013-05-14 | 2013-08-14 | 吉林大学 | Semi-trailing full-load-bearing highway passenger vehicle body structure |
-
2014
- 2014-01-20 CN CN201410023715.9A patent/CN103754262B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5700023A (en) * | 1993-04-19 | 1997-12-23 | Lohr Industrie | Vehicle formed from a series of modules interconnected by a composite articulated connection |
| CN102046447A (en) * | 2008-05-06 | 2011-05-04 | 罗尔工业公司 | Disconnectable articulated connection between two successive road-going modules of a road train |
| WO2013064848A2 (en) * | 2011-11-02 | 2013-05-10 | Szabo Istvan | Double pivot joint unit with running gear for road vehicles |
| CN103231744A (en) * | 2013-05-07 | 2013-08-07 | 吉林大学 | Four-axis single-hinge hinge type passenger car structure |
| CN103241299A (en) * | 2013-05-14 | 2013-08-14 | 吉林大学 | Semi-trailing full-load-bearing highway passenger vehicle body structure |
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