CN203283307U - Four-shaft single-hinge articulated type passenger car structure - Google Patents
Four-shaft single-hinge articulated type passenger car structure Download PDFInfo
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- CN203283307U CN203283307U CN2013202414816U CN201320241481U CN203283307U CN 203283307 U CN203283307 U CN 203283307U CN 2013202414816 U CN2013202414816 U CN 2013202414816U CN 201320241481 U CN201320241481 U CN 201320241481U CN 203283307 U CN203283307 U CN 203283307U
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Abstract
The utility model discloses a four-shaft single-hinge articulated type passenger car structure, and relates to the field of passenger car structural design. The four-shaft single-hinge articulated type passenger car structure comprises a main car (1) and a secondary car (2), wherein the length of the secondary car is equal to or slightly smaller than that of the main car, the main car (1) and the secondary car (2) are both of a double-axle structure, a front axle (3) of the main car is a steering axle, a rear axle (4) of the main car is a driving axle, a front axle (5) of the secondary car is a servo axle, a rear axle (6) of the secondary car is a linkage steering axle, the main car and the secondary car are connected with each other through a traction capstan (8) and flexible casings (9), and the deflection angle alpha of the midpoint of the linkage steering axle of the secondary car is in linkage with the relative tilt angle beta between the main car and the secondary car. The four-shaft single-hinge articulated type passenger car structure can ensure that the moving track of the main car and the moving track of the secondary car are basically the same, a driver can easily drive a passenger car, the turning clearance width of the articulated type passenger car is also reduced, and the road resources are saved. In addition, due to the fact that the load in the perpendicular direction is not borne by the connecting capstan between the main car and the secondary car, the working load of the capstan is greatly reduced, and the four-shaft single-hinge articulated type passenger car structure is beneficial to reducing manufacturing cost.
Description
Technical field
The utility model relates to passenger vehicle structure design field, a kind of novel articulated bus version of utility model.
Background technology
At present, most of articulated bus of domestic operation is mostly to realize three axle articulated bus of front-wheel steering with engine at extreme rear, and when traditional articulated bus is applied to the BRT system, needed turn clearance width is larger, takies more path space., for rear-engined passenger vehicle structure, need to use expensive pushing-type hinged disk.Now according to China's current situation of traffic, a kind of novel four axle simple chain radial type buses are proposed.
Summary of the invention
The utility model will provide a kind of turn clearance width little, easily drives the four axle simple chain radial type buses that cost is low.
By reference to the accompanying drawings, be described as follows:
A kind of four axle simple chain articulated bus structures, be comprised of main car 1 and secondary car 2 two parts, and main car 1 and secondary car 2 are logical
Cross capstan hinged, secondary vehicle commander degree is equal to or slightly less than main vehicle commander's degree, and main car 1 and secondary car 2 are double-bridge structure, main car propons 3 is steeraxle, and back axle 4 is drive axle, and secondary car propons 5 is follow-up bridge, secondary car back axle 6 is the linked steering bridge, secondary car linked steering bridge wheel shaft mid point angle of inclination
With the relative pivot angle between main car and secondary car
Interlock.
Described secondary car linked steering bridge wheel shaft mid point angle of inclination
With the relative pivot angle between main car and secondary car
Interlock is to incite somebody to action by numerical fitting
Interaction relation simplify linear relationship
Or simple nonlinear relationship
, both can link mechanically, also can link by automatically controlled mode.
Describedly by numerical fitting, obtain secondary car linked steering bridge wheel shaft mid point angle of inclination
With the relative pivot angle between the major-minor car
The simplification interaction relation, the turning error of its generation, compensated by the interior or outer pendulum of secondary car follow-up bridge, and is smooth and easy to guarantee that car load travels.
Capstan hinged between described main car 1 and secondary car 2 is drawn capstan 8 for the low cost of not bearing vertical load,
Groundwork load only has drawbar load, lateral loading and part member load when bend is exercised.
Described traction capstan 8 centers equate with the distance of capstan center to secondary car front axle to the distance of main car rear axle, and the ratio of main car 1 length and secondary car 2 length is in 1.0 ~ 1.2 scopes, and secondary car 2 wheelbases are equal to or slightly less than main car 1 wheelbase.
Described steeraxle, follow-up bridge and linked steering bridge are two-wheel and arrange, i.e. each wheel of left and right, drive axle are 4 to take turns layout, i.e. each 2 wheels of left and right.
Described main car is respectively arranged a car door before propons front and rear bridge, secondary car is respectively being arranged a car door after propons He after back axle.
Beneficial effect
The utility model can guarantee main car and secondary car running orbit basic identical, the driver is more easily driven, increased the vehicle commander not affecting under the prerequisite of travelling, effectively improved carrying capacity (approximately 25% ~ 30%).The utility model has also reduced the turn clearance width (turn clearance width is less than existing 3 pivot hinge passenger vehicles) of articulated bus simultaneously, during as the BRT system, can effectively reduce the special lane floor area, has saved path resource.In addition, because major and minor car of the present utility model connects capstan, do not bear vertical loads, greatly alleviated the working load of capstan, more be conducive to reduce manufacturing cost.
Description of drawings
Fig. 1 is the side schematic view of traditional articulated bus;
Fig. 2,3 is four axle list articulated bus side schematic views described in the utility model;
Fig. 4 is four axle list articulated bus underframe schematic top plan view described in the utility model;
Fig. 5 is four axle list articulated bus turning schematic diagrams described in the utility model;
Fig. 6 is the main dimension parameter schematic diagram that the utility model relates to;
Wherein: 1, main car, 2, secondary car, 3, main car propons, 4, main car back axle, 5, secondary car propons, 6, secondary car back axle, 7, driving engine, 8, traction capstan, 9, soft fluffy.
Embodiment
The main dimension parameter of using in this programme as shown in Figure 6, wherein: C is front overhang length, and L is the wheelbase between main car front wheel spindle and hind axle, and D is the distance that main back wheels of vehicle axle and secondary car front wheel spindle arrive the capstan center, E is the wheelbase between secondary car front wheel spindle and hind axle, and K is the car load width.
Complete vehicle structure is comprised of main car 1, secondary car 2 two parts, and two parts interconnect by traction capstan 8 and soft fluffy 9.
Wherein steeraxle, follow-up bridge and linked steering bridge are two-wheel and arrange, i.e. each wheel of left and right, drive axle are 4 to take turns layout, i.e. each 2 wheels of left and right.And respectively arrange a car door before main car propons front and rear bridge, secondary car is respectively being arranged a car door after propons He after back axle.This passenger vehicle is full-bearing type low floor articulated bus, and main car 1 propons adopts low floor to arrange to back axle front end and secondary car 2.
The turning situation of four axle simple chain radial type BRT buses as shown in Figure 5, wherein: the 1st, main car, the 2nd, secondary car, the articulated bus wheel of the linked steering on wheel flutter foreign steamer, drive wheel and secondary car, flower wheel when turning all should be turned around same center-point O.R is the formed excircle orbital radius of vehicle body outermost point projection on the ground, and r is the formed inner periphery orbital radius of inside line projection on the ground of vehicle body, and the difference of R and r is required turn clearance width A, i.e. A=R-r.
Be that the turning center that guarantees main car and secondary car keeps overlapping when car load turns to, can be by controlling secondary car linked steering bridge wheel shaft mid point corner
With the relative pivot angle between main car and secondary car
Interlock realizes, and then reaches and make the identical purpose of major-minor car running orbit.
, according to the geometric relationship in Fig. 5, calculate secondary car linked steering bridge wheel shaft mid point angle of inclination
With the relative pivot angle between main car and secondary car
Between interaction relation, that is:
.
But above-mentioned relation can't accurately realize, the utility model utilize 0 degree, 5 degree, 10 degree, 15 degree, 20 degree 30 degree and 45 degree etc. several
The pivot angle value, by numerical fitting, with secondary car linked steering bridge wheel shaft mid point angle of inclination
With the relative pivot angle between main car and secondary car
Between interaction relation:
, be reduced to linear relationship
Or simple nonlinear relationship
, both can link mechanically, also can link by automatically controlled mode.And, for simplifying the issuable turning error of interaction relation, proposed to compensate solution by the interior or outer pendulum of secondary car follow-up bridge, smooth and easy to guarantee that car load travels.
Utilize the interaction relation NUMERICAL MATCH METHOD FOR of method of least square:
Be example with simple nonlinear dependence, order
, wherein
, more respectively S is asked K
1And K
2Partial derivative and be zero (
), thereby determine parameter k
1, k
2Value.
The embodiment that provides below in conjunction with accompanying drawing is described in further detail the utility model.
This programme is based on GB1589-2004 on-road vehicle contour dimension, axle load and quality limit value, 12.50 meters R of the turn radius as the vehicle body outermost point of exradius of the porte-cochere of using circle.Dimensional parameters with reference to existing articulated bus, in this programme, following (the unit: rice): front overhang length C=2.40 of vehicle body main dimension parameter, the wheelbase L=6.10 of main car front axle and rear axle, main back wheels of vehicle axle and secondary car front wheel spindle are to capstan centre distance D=3.25, secondary axletree is apart from E=6.00, rear overhang length F=2.50, car load width K=2.50.11.00 meters of articulated bus master vehicle commander degree, 11.00 meters of secondary vehicle commander degree, the hinged disk center is to 11.75 meters of the length of headstock, and the hinged disk center is to 11.75 meters of the length of the tailstock, 23.50 meters of passenger vehicle total lengths.
, according to the geometric relationship in Fig. 5, calculate the formed inner periphery orbital radius of the inside line projection on the ground r of vehicle body, thereby obtain turn clearance width A.
Adopt the approximate value of obtaining r of following formula:
The r value is about 6.67 meters.
, by A=R-r, obtain the A value and be about 5.8 meters.
Less than the vehicle with the present embodiment equal length, therefore selected the more common articulated bus of 18 meters to compare, 18 meters at present common passenger vehicle turn clearance width A values are generally between 6.5 meters to 6.7 meters due at present domestic.
23.5 meters required turn clearance widties of articulated bus of the present embodiment are compared common 18 meters articulated buss and have also been reduced about 0.7 meter to 0.9 meter, have reached the purpose that reduces turn clearance width.
Adopt the simple linear approximating method to determine secondary car linked steering bridge wheel shaft mid point corner in this programme
With the relative pivot angle between the major-minor car
Between interaction relation.
Order
(wherein),
β
iGet respectively 0,4.5,9,13.5,18,22.5,27,31.5,36,40.5 and 45 degree, by analytic expression
Obtain
(solve
=0,4.149,8.267,12.326,16.299,20.164,23.904,27.505,30.958,34.258 and 37.405 degree), then to S ask the k partial derivative and be zero (
), thereby the value (trying to achieve K=0.86) of definite parameter K.
Be simplified interaction relation by NUMERICAL MATCH METHOD FOR and produce the problem of secondary car interlock bridge turning error, can give adequate compensation by pendulum inside and outside secondary car follow-up bridge, to realize the major-minor car roughly the same purpose of track of travelling.
Claims (6)
1. an axle simple chain articulated bus structure, consist of main car main car (1) and secondary car (2) two parts
(1) and secondary car (2) by capstan hinged, secondary vehicle commander degree is equal to or slightly less than main vehicle commander's degree, it is characterized in that:
Main car (1) and secondary car (2) are double-bridge structure, and main car propons (3) is steeraxle, and back axle (4) is drive axle, and secondary car propons (5) is follow-up bridge, and secondary car back axle (6) is the linked steering bridge, secondary car linked steering bridge wheel shaft mid point angle of inclination
With the relative pivot angle between main car and secondary car
Interlock.
2. four axle simple chain articulated bus structures described according to claim 1 is characterized in that:
Described secondary car linked steering bridge wheel shaft mid point angle of inclination
With the relative pivot angle between main car and secondary car
Interlock is to incite somebody to action by numerical fitting
Interaction relation simplify linear relationship
Or simple nonlinear relationship
, both can link mechanically, also can link by automatically controlled mode.
3. four axle simple chain articulated bus structures described according to claim 2 is characterized in that:
Obtain secondary car linked steering bridge wheel shaft mid point angle of inclination by numerical fitting
With the relative pivot angle between the major-minor car
The simplification interaction relation, the turning error of its generation, compensated by the interior pendulum of secondary car follow-up bridge or outer pendulum, and is smooth and easy to guarantee that car load travels.
4. four axle simple chain articulated bus structures described according to claim 1 is characterized in that:
Capstan hinged between described main car (1) and secondary car (2) is drawn capstan (8) for the low cost of not bearing vertical load,
Groundwork load only has drawbar load, lateral loading and part member load when bend is exercised.
5. four axle simple chain articulated bus structures described according to claim 4 is characterized in that:
Described traction capstan (8) center equates with the distance of capstan center to secondary car front axle to the distance of main car rear axle, the ratio of main car (1) length and secondary car (2) length is in 1.0 ~ 1.2 scopes, and secondary car (2) wheelbase is equal to or slightly less than main car (1) wheelbase.
6. four axle simple chain articulated bus structures described according to above arbitrary claim is characterized in that:
Described steeraxle, follow-up bridge and linked steering bridge are two-wheel and arrange, i.e. each wheel of left and right, drive axle are 4 to take turns layout, i.e. each 2 wheels of left and right.
7.Four axle simple chain articulated bus structures according to claim 6 is characterized in that:
Described main car is respectively arranged a car door before propons front and rear bridge, secondary car is respectively being arranged a car door after propons He after back axle.
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103231744A (en) * | 2013-05-07 | 2013-08-07 | 吉林大学 | Four-axis single-hinge hinge type passenger car structure |
CN106599470A (en) * | 2016-12-15 | 2017-04-26 | 武汉理工大学 | All-wheel steering analytical algorithm for large three-axle semitrailer |
CN113696969A (en) * | 2021-09-02 | 2021-11-26 | 浙江吉利控股集团有限公司 | Vehicle steering control method and system and vehicle |
-
2013
- 2013-05-07 CN CN2013202414816U patent/CN203283307U/en not_active Withdrawn - After Issue
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103231744A (en) * | 2013-05-07 | 2013-08-07 | 吉林大学 | Four-axis single-hinge hinge type passenger car structure |
CN103231744B (en) * | 2013-05-07 | 2015-04-01 | 吉林大学 | Four-axis single-hinge hinge type passenger car structure |
CN106599470A (en) * | 2016-12-15 | 2017-04-26 | 武汉理工大学 | All-wheel steering analytical algorithm for large three-axle semitrailer |
CN113696969A (en) * | 2021-09-02 | 2021-11-26 | 浙江吉利控股集团有限公司 | Vehicle steering control method and system and vehicle |
CN113696969B (en) * | 2021-09-02 | 2022-07-26 | 浙江吉利控股集团有限公司 | Vehicle steering control method and system and vehicle |
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C14 | Grant of patent or utility model | ||
GR01 | Patent grant | ||
AV01 | Patent right actively abandoned |
Granted publication date: 20131113 Effective date of abandoning: 20150401 |
|
RGAV | Abandon patent right to avoid regrant |