The two torsion bar coupled bogies of independent wheel
Technical field
The present invention relates to for motor vehicle independent wheel bogie of a kind of novel railway, between existing single axle truck, increase a pair of torsion bar coupling mechanism specifically.
Background technology
Be accompanied by domestic socioeconomic steady-state growth, along with the Chinese society rapid economy development, greatly developing of comprehensive speed-raising of main line railway and urban track traffic is imperative.But design has brought acid test to vehicle stability in the speed-raising of train; And the light rail vehicle in the urban track traffic requires to adopt the structural requirement of low floor face usually.Independent wheel bogie can solve this type of problem just: on the one hand, the use of independent wheel can improve Stability of high-speed train; On the other hand, independent wheel also can effectively reduce the height of floor from rail top of municipal rail train, brings great convenience for passenger's trip.
But, because independent wheel lacks vertical creep power that guiding is played an important role, so its guidance capability is very poor, wheel-rail wear will aggravate like this, and then big, the maintenance cost of noise increases when causing train operation, also may cause the derailing safety misadventure when serious.
The application scheme of independent wheel mainly contains following several at present: right to directly being replaced with independent wheel as taking the front and back tight pulley of existing two-axle bogie, the front and back wheel of this type of independent wheel two-axle bogie is to connecting by a rigid frame, during by curve, front and back wheel is under a shared framework constraint and present the not enough form of launching, be front and back wheel to not being tending towards radial position, its steering capability is relatively poor; In addition, also the independent wheel two-axle bogie can be changed into the form of independent wheel single axle truck, two independent wheel single axle trucks below the car body adjacent end portion of front and back will be subjected to the constraint of car body separately respectively, during by curve, they are under the constraint of car body and present the form of launching transition, can not be tending towards radial position, so the steering capability of independent wheel single axle truck is also bad; Moreover present external adopt increases various guide piecees to independent wheel bogie more, but its structure is all complicated, manufacturing cost is higher, and do not fit into the home market application.
Summary of the invention
The two torsion bar coupled bogies of independent wheel of the present invention, its purpose is intended to address the above problem and is not enough and independently take turns in front and back and to be connected with the elastic element that is coupled between the right single axle truck, this coupling elastic element is the two torsion bar coupling mechanisms that are in series by two torsion bars, and wherein the symmetrical configuration of two elasticity torsion bars, technical parameter are identical.
Be different from two-axle bogie and single axle truck, institute's bonded assembly coupling elastic element between single axle truck, before and after can making independent wheel between joint stiffness K
ψBetween 0 to ∞, get a reasonable value, thereby make independent wheel bogie have steering capability, so just can meet the operating needs of high speed train and urban light rail train.But coupling element must satisfy following two conditions:
1, adopt coupling element to be connected between the single axle truck, the anti-angular rigidity degree of shaking the head should only be provided, the rigidity of other directions all should discharge as far as possible, and just only the right motion of shaking the head relatively has effect of contraction to coupling element to forward and backward independent wheel, and does not interfere other relative motions between them.
2, use the independent wheel coupled bogie of coupling element, the right single axle truck of its front and rear wheel is installed in respectively under the car body end, front and back, the coupling element that is adopted should possess certain displacement regulating power is arranged, and to remedy the manufacturing errors of train body and bogie truck, is convenient to the car assembling.。
The two torsion bar coupled bogies of independent wheel of the present invention are to adopt two torsion bar coupling mechanisms to solve the foregoing invention purpose.
The two torsion bar coupled bogies of described independent wheel are that the front and back independent wheel below the forward and backward car body adjacent end portion of train adopts single axle truck.Be connected with an anti-elastic element of shaking the head between single axle truck, this elastic element is the two torsion bar coupling mechanisms that are in series by two torsion bars.
Can think that straight line is a kind of special curve (being equivalent to the curve that radius R is ∞), existing is the steering capability that example is analyzed independent wheel flexible couplings bogie truck with the curve.
For independent wheel concerning, vertical creep power of its left and right wheels is 0 in theory, so the right motion of shaking the head of the front and rear wheel of independent wheel flexible couplings bogie truck mainly is subjected to coupling element to produce the moment M that shakes the head
CziThe moment M that shakes the head with the generation of secondary suspension system
SziCombined action, when the train stable state when the curve, these two the moment sums of shaking the head should be 0, that is:
M
czi+M
szi=0 (1)
According to the vehicle dynamics theory, coupling element produces the moment M that shakes the head
CziThe moment M that shakes the head with the generation of secondary suspension system
SziRespectively should for:
In the aforesaid equation, i=1~2,
K
SxSecondary suspension longitudinal rigidity for described independent wheel flexible couplings bogie truck one side;
K
ψThe angular rigidity of shaking the head that provides for the coupling element of independent wheel single axle truck before and after described connect;
B
sBe the horizontal stride values of described secondary suspension half;
L is a vehicle name spacing half;
B is the nominal wheelbase half of described independent wheel flexible couplings bogie truck;
R is the circular curve radius of train by curve circuit
ψ
BPanning angle for the bogie truck set;
ψ
cPanning angle for the car body set.
Consider that wheel right displacement and suspension deflection are more much smaller than the nominal spacing 2l of vehicle, can think that therefore the middle body of car body is approximate tangent with circular curve, i.e. ψ
c≈ 0.
When the train stable state when the circular curve, for the front and back wheel that makes coupled bogie to being in radial position fully, must have: ψ
Bi=ψ
B (i+1)=0, so can get according to formula (1)~formula (3):
That is:
Wherein: B
sBe the horizontal stride values of described secondary suspension half;
K
SxSecondary suspension longitudinal rigidity for described independent wheel flexible couplings bogie truck one side;
B is the nominal wheelbase half of described independent wheel flexible couplings bogie truck;
L is a vehicle name spacing half.
Aforesaid equation (5) promptly is the required coupling stiffness K of the coupling element of independent wheel flexible couplings bogie truck of the present invention
ψExpression formula.
From above-mentioned derivation as can be seen, determine the coupling element stiffness K
ψOnly with the secondary suspension device longitudinal rigidity K of bogie of car wheelbase (2b), length between truck centers (2l) and bogie truck one side
SxRelevant, thus set up a kind of relation one to one.
Because described pair of torsion bar coupling mechanism is in series the angular rigidity K so integral body is shaken the head by two torsion bars
ψ, should be that the every torsion bar angular rigidity of shaking the head (is set at K
ψ 1) half, and the torsional stiffness of setting every torsion bar is K
δ
When on the two torsion bar coupled bogies of independent wheel, when using described pair of torsion bar coupling mechanism,, need to determine torsion bar torsional stiffness K for ease of the technical parameter of two torsion bar coupling mechanisms is provided
δLongitudinal rigidity K with the secondary suspension device
SxBetween relation, must derive torsion bar torsional stiffness K earlier so again
δThe integral body that provides with it angular rigidity K that shakes the head
ψBetween relation.
At first determine the every angular rigidity K that shakes the head that torsion bar provides
ψ 1And the relation between the torsional stiffness of torsion bar self, they satisfy following equation:
Wherein, L
nBe the length of every torsion bar,
L
nBe the length of every torsion bar two swivel arms.
Thereby the angular rigidity K that shakes the head that provides of two torsion bar coupling mechanisms
ψShould be:
In conjunction with aforesaid equation (5), can derive the torsional stiffness K of every torsion bar again
δLongitudinal rigidity K with the secondary suspension device of bogie truck one side
SxBetween the pass be:
In fact according to material mechanics principle, the torsional stiffness K of every torsion bar
δShould satisfy:
Wherein, G is constant elasticity modulus, i.e. G=76000MPa.That is to say, as long as choose an appropriate diameter d and length L for every torsion bar
n, the angular rigidity K that shakes the head that provides of two torsion bar coupling mechanisms just can be provided
ψLongitudinal rigidity K with the secondary suspension device
SxReach rational Match.
In sum, the two torsion bar coupled bogies of independent wheel of the present invention have the following advantages and beneficial effect:
1, adopts described pair of torsion bar coupling mechanism, the anti-angular rigidity of shaking the head only is provided, rigidity in other directions all has been released basically, thereby only the right motion of shaking the head relatively has effect of contraction to the forward and backward independent wheel of coupled bogie, and do not interfere between them other the motion, so described pair of torsion bar mechanism satisfies the requirement of independent wheel coupled bogie to its coupling element fully.
2, adopting described pair of torsion bar coupling mechanism to possess has certain displacement regulating power, can remedy the manufacturing errors and the assembly error of train body and bogie truck, is convenient to the car assembling.
3, the two torsion bar coupled bogies of described independent wheel have solved the guiding difficult problem of existing independent wheel bogie and have worn away serious problem by two torsion bar coupling mechanisms.Torsional stiffness K with two torsion bar coupling mechanisms
δSecondary suspension longitudinal rigidity K with bogie truck one side
SxSet up corresponding relation accurately, workable, and two torsion bar mechanism structure is simple, technical risk is little, cost of development is low, and promotional value is higher.
Description of drawings
Fig. 1 is side-looking and the elevational schematic view of described flexible couplings bogie truck in the train installation site;
Fig. 2-the 1st, the scheme drawing when described existing independent wheel two-axle bogie passes through curved path;
Fig. 2-the 2nd, the scheme drawing when described existing independent wheel single axle truck passes through curved path;
Fig. 2-the 3rd, the scheme drawing when described flexible couplings bogie truck passes through curved path;
Fig. 3 is the moment M that shakes the head that the front and rear wheel of described coupled bogie produced when motion on curve
CziAnd M
SziScheme drawing.
Fig. 4 is a described pair of torsion bar coupling mechanism scheme drawing.
Wherein, M1 is that car body 1, M2 are that car body 2, M3 are car bodies 3.
The tradition wheel is taken turns single axle truck G2, independent wheel flexible couplings bogie truck G3 two-axle bogie G1, tradition;
The specific embodiment
Embodiment 1, as shown in Figure 1 and Figure 4, the two torsion bar coupled bogies of described independent wheel, it is the front and back independent wheel employing single axle truck below the forward and backward car body adjacent end portion of train, be connected with an anti-elastic element of shaking the head between the single axle truck of front and back independent wheel, this elastic element is the two torsion bar coupling mechanisms that are in series by two torsion bars.
Wherein, described couple of angular rigidity K that shakes the head that the torsion bar coupling mechanism provides
ψShould be that every torsion bar provides the angular rigidity K that shakes the head
ψ 1Half, the torsional stiffness of establishing every torsion bar is K
δ
Shown in Fig. 2-1, existing independent wheel two-axle bogie since its I, II position wheel to being subjected to the constraint of same rigid frame, front and back independently take turns between joint stiffness K
ψBe tending towards ∞, be far longer than secondary suspension longitudinal rigidity K
SxSo the front and back wheel of independent wheel two-axle bogie is very little and be subjected to the constraint of framework bigger to the constraint that is subjected to car body.During by curve, be subjected to the influence of radius of curve R and wheel-base bogie 2b, front and back wheel is right shake the head motion to superpose respectively one (±
b/
R) angle, wheel forms high incidence (+ψ with respect to omnibearing line usually to I like this
1), and wheel forms the negative angle of attack (ψ with respect to omnibearing line usually to II
2), so I, II position wheel be to can not being tending towards radial position on curve, and present the not enough form of launching.
Shown in Fig. 2-2, existing independent wheel single axle truck is because its I, constraint (the joint stiffness K they between of II position wheel to no longer being subjected to same framework
ψ=0), so I, II position take turns directly be subjected to the constraint of car body under the effect of secondary suspension system.During by curve, be subjected to the influence of radius of curve R and length between truck centers 2l because wheel is in the rear end of front car body to I, so the right motion of shaking the head of I position wheel to superpose one (
l/
R) angle; And wheel is in the front end of back car body to II, thus the right motion of shaking the head of II position wheel to superpose one (+
l/
R) angle, wheel forms the negative angle of attack (ψ with respect to omnibearing line usually to I like this
1), and wheel forms high incidence (+ψ with respect to omnibearing line usually to II
2), so I, II position wheel be to can not being tending towards radial position on curve, and present the form of launching transition.
The I of independent wheel two-axle bogie, II position wheel are to the excessive (K of their constraint because of rigid frame to launch deficiency on curve
ψ=∞); The I of independent wheel single axle truck, II position wheel to launch on the curve transition be because they only are subjected to the constraint of car body separately front and back wheel between lack necessary constraint (K
ψ=0).
Shown in Fig. 2-3, institute's bonded assembly coupling elastic element can solve the defective that has two-axle bogie and single axle truck now, the stiffness K of coupling element between the independent wheel single axle truck of front and back
ψAt (0<K
ψGet a rational value in<∞) the scope, then can make I, II position wheel under the combined action of coupling element and secondary suspension device, be tending towards radial position (ψ to by curve the time
1=ψ
2=0).
As Fig. 2-3 and shown in Figure 3, the I of described independent wheel flexible couplings bogie truck, the right motion of shaking the head of II position wheel mainly are subjected to coupling element to produce the moment M that shakes the head
CziThe moment M that shakes the head with the generation of secondary suspension system
SziCombined action, when the train stable state when the curve, these two the moment sums of shaking the head should be 0, that is:
M
czi+M
szi=0 (1)
According to the vehicle dynamics theory, coupling element produces the moment M that shakes the head
CziThe moment M that shakes the head with the generation of secondary suspension system
SziRespectively should for:
In the aforesaid equation, i=1~2,
K
SxSecondary suspension longitudinal rigidity for described independent wheel flexible couplings bogie truck one side;
K
ψThe angular rigidity of shaking the head that provides for the coupling element of independent wheel single axle truck before and after described connect;
B
sBe the horizontal stride values of described secondary suspension half;
L is a vehicle name spacing half;
B is the nominal wheelbase half of described independent wheel flexible couplings bogie truck;
R is the circular curve radius of train by curve circuit
ψ
BPanning angle for the bogie truck set;
ψ
cPanning angle for the car body set.
Consider that wheel right displacement and suspension deflection are more much smaller than the nominal spacing 21 of vehicle, can think that therefore the middle body of car body is approximate tangent with circular curve, i.e. ψ
c≈ 0.
When the train stable state when the circular curve, for the front and back wheel that makes coupling traveling portion to being in radial position fully, must have: ψ
Bi=ψ
B (i+1)=0, so can get according to formula (1)~formula (3):
That is:
Wherein: B
sBe the horizontal stride values of described secondary suspension half;
K
SxSecondary suspension longitudinal rigidity for described independent wheel flexible couplings bogie truck one side;
B is the nominal wheelbase half of described independent wheel flexible couplings bogie truck;
L is a vehicle name spacing half.
As shown in Figure 4, described pair of torsion bar coupling mechanism is to be in series by two torsion bars, i.e. AB and A ' B ', and its symmetrical configuration, technical parameter are identical.
Be that example illustrates now with torsion bar AB, torsion bar and base frame, and pivoted arm between annexation.On single shaft framework I, AD and BC are two pivoted arms of torsion bar AB by bearings in the rotating shaft at torsion bar AB two ends, and point of connection A point and the B point of they and torsion bar AB are similar to rigid joint.AB and A ' B ' couple together by two connecting rod DD ' and CC '.Point of connection D point between connecting rod and the pivoted arm, D ' point, C point and C ' point all are that ball pivot connects.By said structure, only there is effect of contraction in two torsion bar mechanism to shaking the head the relatively motion between I, II position single axle truck, and does not interfere other relative motions between them; In addition, two torsion bar coupling mechanisms all have certain displacement regulatory function on X, Y, three directions of Z, so it can remedy the train manufacturing errors and the car assembly error that falls.
When torsion bar AB cw in horizontal surface (xy plane) produces one when shaking the head angle ψ, pivoted arm BC in upright plane (xz plane) to anticlockwise motion, and pivoted arm AD rotates to clockwise direction in upright plane, thereby make torsion bar AB produce a twist angle δ, and the elasticity torsion bar can be revolted the torsional deflection of self, thereby opposing torsion bar AB produces the angular transposition of shaking the head in horizontal surface, so two torsion bar coupling mechanism is equivalent to an anti-head-shaking device.
The angular rigidity K that shakes the head that two torsion bar coupling mechanisms provide
ψ, with the torsional stiffness K of torsion bar self
δBetween corresponding relation, and torsion bar torsional stiffness K
δLongitudinal rigidity K with the secondary suspension device
SxBetween relation, by calculate derive definite.
According to aforesaid equation (5) as can be known, the angular rigidity K that shakes the head that two torsion bars need provide
ψLongitudinal rigidity K with the secondary suspension device
SxBetween concern and should satisfy:
Described pair of torsion bar coupling mechanism is to be in series by two torsion bars, the angular rigidity K that shakes the head that it provides
ψ, should be the angular rigidity K that shakes the head that every torsion bar provides
ψ 1Half.
The twist angle δ of described torsion bar and the relation between the ψ of angle of shaking the head can be determined by the longitudinal extension amount of torsion bar side a and b in horizontal surface.
The torsion bar AB length of setting among Fig. 4 is L
n, the length of pivoted arm BC and AD is L
zLongitudinal extension amount its longitudinal deformation amount X of torsion bar side a and b in horizontal surface
cFor:
Then the twist angle δ of torsion bar and the pass of shaking the head between the ψ of angle are:
The torsional stiffness K of every torsion bar
δ, the equivalence that provides with it angular rigidity K that shakes the head
ψ 1Between relation can pass through bonding force F
cProducing two moments in the space determines:
(a), bonding force F
cIn horizontal surface with respect to O
1Point is got the rectangle moment M that becomes to shake the head
ψ, its size is:
M
ψ=F
c·L
n=K
ψ1·ψ (8)
(b), bonding force F
cIn upright plane,, get rectangle and become twist moment M with respect to A point and B point
δ, its size is:
According to equation (8) and (9), can extrapolate the torsional stiffness K of every torsion bar
δWith its equivalence that is provided angular rigidity K that shakes the head
ψ 1Between the pass be:
Can get in conjunction with equation (7) again:
When δ hour,
Then have:
Because described pair of torsion bar coupling mechanism be to be in series by two torsion bars, thereby the integral body of the two torsion bar coupling mechanisms angular rigidity K that shakes the head
ψShould be the angular rigidity K that shakes the head that every torsion bar provides
ψ 1Half, that is:
Again in conjunction with aforesaid equation (5), the torsional stiffness K of every torsion bar
δLongitudinal rigidity K with the secondary suspension device of bogie truck one side
SxBetween the pass be:
In fact according to material mechanics principle, the torsional stiffness K of every torsion bar
δShould satisfy:
Wherein, G is constant elasticity modulus, i.e. G=76000MPa.That is to say, as long as choose an appropriate diameter d and length L for every torsion bar
n, just can make the integral body of the two torsion bar coupling mechanisms angular rigidity K that shakes the head
ψLongitudinal rigidity K with the secondary suspension device
SxReach rational Match.
It is as follows to set the train composition parameter of using described pair of torsion bar coupled bogie;
The longitudinal rigidity K of bogie truck secondary suspension device
Sx=0.2MN.m/rad, half l=4m of vehicle name spacing, half b=1m of coupled bogie name wheelbase, two is half B of horizontal span
s=1m, the torsion bar length L
n=2m, torsion bar pivoted arm length L
z=0.3m.
Can calculate out the torsional stiffness K of required every torsion bar according to equation (14)
δThe actual 0.072MN.m/rad that should be.
Can calculate out that it is 66mm that the torsion bar diameter d is answered value, can satisfy above-mentioned requirements again according to equation (15).