CN1754733A - Flexible coupling bogie for independent wheel - Google Patents

Abstract

This invention relates to independent wheel flexibility couple rotation rack, which is a simple structure and good directing independent rotation rack and adds one couple element between single rotation rack to connect the elastic elements of two independent wheels single axis near front and back car bodies to make it become new flexible couple rotation rack between independent wheel two axis and single axis rack. Through selecting one proper swing angle rigidity it makes it's front and back wheels to radium direction under action of couple elements and two suspension systems.

Description

Independent wheel flexible couplings bogie truck

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 by a coupling element specifically.

Background technology

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

Independent wheel flexible couplings bogie truck of the present invention, its purpose are to address the above problem and are not enough and propose a kind of simple in structure and novel independent wheel bogie that steering capability is good.The present invention increases by a coupling element between single axle truck, two independent wheel single axle trucks before and after being about to below the car body adjacent end portion link up with anti-elastic element of shaking the head, and make it to become the novel flexible coupled bogie between independent wheel two-axle bogie and single axle truck.Choose a suitable angular rigidity value of shaking the head by the coupling element of giving described flexible couplings bogie truck, make its front and rear wheel, under the combined action of coupling element and secondary suspension system, can be tending towards radial position the time by curve.

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:

$M_{\mathrm{szi}}=-2K_{\mathrm{sx}}{B_s}^2[{\mathrm{\ψ}}_{\mathrm{Bi}}-{\mathrm{\ψ}}_c+{(-1)}^i\frac{l}{R}]---\left(2\right)$

$M_{\mathrm{czi}}={(-1)}^i{K}_{\mathrm{\ψ}}[{(-1)}^{i+1}{\mathrm{\ψ}}_{\mathrm{Bi}}-{(-1)}^{i+1}{\mathrm{\ψ}}_{B(i\±1)}+\frac{2b}{R}]---\left(3\right)$

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 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):

$K_{\mathrm{\ψ}}\frac{2b}{R}=2K_{\mathrm{sx}}{B_s}^2\frac{l}{R}---\left(4\right)$

That is:

$K_{\mathrm{\ψ}}={B_s}^2\frac{l}{b}{K}_{\mathrm{sx}}---\left(5\right)$

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.

According to above-mentioned derivation and equation (5), as long as the secondary suspension stiffness K of length between truck centers 2l, bogie truck name wheelbase 2b and bogie truck one side _SxIn case determine, the required coupling stiffness K that provides of coupling element just can be provided exactly _ψ

It can also be seen that coupling stiffness K from equation (5) _ψChoose with radius of curve R irrelevantly, that is to say that as long as the radius of curve size of the route of pipe line is coupling stiffness K _ψPress equation (5) and secondary suspension stiffness K _SxReasonably mate, independent wheel flexible couplings bogie truck just can the automatically regulating front and back wheel be to being tending towards radial position under the combined action of secondary suspension system and elasticity coupling element, and this also is the gordian technique point of independent wheel flexible couplings bogie truck of the present invention.

As long as independent wheel is to occupying radial position, its horizontal creep power is just very little, just can rely on the gravity recuperability to reset on straight line; Form with pure rolling on curve is passed through, and its curving performance is inevitable fine.

In sum, independent wheel flexible couplings bogie truck of the present invention has the following advantages and beneficial effect:

1, described independent wheel flexible couplings bogie truck has been to solve the guiding difficult problem of existing independent wheel bogie.When this mainly showed by curve, the front and back wheel of independent wheel flexible couplings bogie truck was to being tending towards radial position automatically under the effect of coupling element; When moving on straight line, the independent wheel of coupled bogie is subjected to the track excitation and can automatically reverts to track centre behind the offset track line of centers.

2, the independent wheel coupled bogie has from leading function, thereby it not only makes the abrasion of independent wheel on curve minimum, but also having solved the eccentric wear problem of independent wheel on the straight line, this is very beneficial for independent wheel bogie and uses on the less urban light rail of high-spe-ed trunk line railway train and radius of curve.

3, above-mentioned independent wheel flexible couplings bogie truck is with the coupling stiffness K of coupling element _ψSecondary suspension longitudinal rigidity K with bogie truck one side _SxSet up corresponding relation accurately, workable.

4, independent wheel flexible couplings bogie truck is exactly to have increased a coupling element on the basis of single axle truck, and is simple in structure, technical risk is little, cost of development is low, and promotional value is higher.

Description of drawings

Fig. 1 is installation side-looking and the elevational schematic view of described independent wheel flexible couplings bogie truck in train;

Fig. 2 is the moment M that shakes the head that the front and rear wheel of described flexible couplings bogie truck produced when motion on curve _CziAnd M _SziScheme drawing.

Fig. 3-the 1st, the scheme drawing when described existing independent wheel two-axle bogie passes through curve;

Fig. 3-the 2nd, the scheme drawing when described existing independent wheel single axle truck passes through curve;

Fig. 3-the 3rd, the scheme drawing when described independent wheel flexible couplings bogie truck passes through curve;

Wherein, part is an independent wheel flexible couplings bogie structure sketch in the frame of broken lines among Fig. 1.

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, and as shown in Figure 1, traditional two-axle bogie is still installed at the train two ends, at car body and car body joint described independent wheel flexible couplings bogie truck is installed.

Described independent wheel flexible couplings bogie truck is to connect an anti-elasticity coupling element of shaking the head between forward and backward single axle truck (its coupling stiffness is K _ψ).

Shown in Fig. 3-1, 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. 3-2, 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 and Fig. 3-3, 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:

$M_{\mathrm{szi}}=-2K_{\mathrm{sx}}{B_s}^2[{\mathrm{\ψ}}_{\mathrm{Bi}}-{\mathrm{\ψ}}_c+{(-1)}^i\frac{l}{R}]---\left(2\right)$

$M_{\mathrm{czi}}={(-1)}^i{K}_{\mathrm{\ψ}}[{(-1)}^{i+1}{\mathrm{\ψ}}_{\mathrm{Bi}}-{(-1)}^{i+1}{\mathrm{\ψ}}_{B(i\±1)}+\frac{2b}{R}]---\left(3\right)$

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 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):

$K_{\mathrm{\ψ}}\frac{2b}{R}=2K_{\mathrm{sx}}{B_s}^2\frac{l}{R}---\left(4\right)$

That is:

$K_{\mathrm{\ψ}}={B_s}^2\frac{l}{b}{K}_{\mathrm{sx}}---\left(5\right)$

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.

It is as follows to set the train composition parameter of using described flexible couplings bogie truck;

The longitudinal elastic coefficient K of the secondary suspension device of bogie truck one side _Sx=0.2MN.m/rad;

Half l=4m of vehicle name spacing;

Half b=1m of the vehicle name wheelbase of coupled bogie;

Half B of the horizontal stride values of secondary suspension device _s=1m;

The elasticity modulus K of coupling element then _ψ=0.8MN.m/rad.

Claims (2)

1, a kind of independent wheel flexible couplings bogie truck is that the forward and backward independent wheel below the forward and backward car body adjacent end portion of train adopts single axle truck, it is characterized in that: be connected with an anti-coupling elastic element of shaking the head between forward and backward single axle truck.

2, independent wheel flexible couplings bogie truck according to claim 1 is characterized in that: the coupling stiffness K of described coupling element _ψSatisfy following expression formula,

$K_{\mathrm{\ψ}}={B_s}^2\frac{l}{b}{K}_{\mathrm{sx}}$

Wherein: B _sBe the horizontal stride values of described secondary suspension half,

K _SxBe the secondary suspension longitudinal rigidity of 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.

Images