CN102310867B

CN102310867B - Tilt bolster and include the secondary suspension of this bolster

Info

Publication number: CN102310867B
Application number: CN201110159781.5A
Authority: CN
Inventors: 本杰明·费斯
Original assignee: Hutchinson SA
Current assignee: Hutchinson SA
Priority date: 2010-06-08
Filing date: 2011-06-08
Publication date: 2016-06-08
Anticipated expiration: 2031-06-08
Also published as: EP2394881A1; EP2394881B1; FR2960844B1; FR2960844A1; CN102310867A

Abstract

The present invention relates to a kind of inclination bolster, tilt the suspension that bolster is vehicle to design, first of all for the absorption guaranteeing normal load produced by vehicle body, secondly in order to tilt along with relative horizontal movement, bolster includes: the first support member, is arranged on the element of vehicle, and second support member, it is spaced vertically apart from the first support member, to receive the end of pendulum spring, it is characterized in that, bolster also includes :-central vertical guides pivot (50), including cylinder or conical butt flexible member (53), this flexible member is arranged between inner part (51) and external part (52), inner part (51) is integral with in the first support member (70) and the second support member (71), another in external part and the first support member and the second support member is integral, the horizontal rigidity of pivot (50) is more than its vertical stiffness, and-at least one pair of Elastic Bolts (60), bolt is symmetrically disposed in centerpivot both sides, bolt is centrally located on the first trunnion axis, bolt is arranged between the first support member (70) and the second support member (71), and has high-caliber vertical stiffness relative to its horizontal rigidity.

Description

Tilt bolster and include the secondary suspension of this bolster

Technical field

The present invention relates to bolster and include the secondary suspension of this bolster.

Background technology

Bolster is known, it is that (secondary) hangs for the two of rolling stock (such as lorry, passenger vehicle or locomotive), to guarantee the vehicle body suspension relative to chassis, its axis-wheel assembly is that (primary) suspension is arranged on chassis by one.

For such as including two axles and the bogie of four wheels (or such as including three axles), known two or four secondary suspension sub-component is set, each secondary suspension sub-component has a bolster for obtaining horizontal flexible or a pair bolster, and and bolster be arranged in series or be arranged on the one or more metal springs between bolster, the function of this metal spring is in that to obtain the vertical flexibility needed for secondary suspension.

The bolster of the some types existing for such application and design, but their limited capacity.

Patent application EP155209 pays close attention to resilient supporting unit, and this device includes the elastomeric ring of lamination, and this elastomeric ring and helical spring are installed in series, to form the secondary suspension of railway bogie. When horizontal stress is applied in, the amplitude in the gap of elastomeric ring is limited by central frusto-conical shape stop member. This device only has common slope characteristic, and therefore the decoupling (decoupling) according to the horizontal rigidity in horizontal stress direction is poor.

Patent FR1540148 describes the sub-component including two helical springs, the upper end of helical spring is connected to vehicle body, the lower end of helical spring is connected to the support member (or blade assembly) freely pivoted around junction surface, and lateral cushioning device is set to serve as the elastic stop member of the inclination of the support member of pivot. Except the fact that do not weaken except tilting, this device also has integrated and maintenance aspect problem.

Patent BE700027 describes a kind of vehicle body supports element, and it makes spring and a hemispherical ball-and-socket joint be correlated with. The use of ball-and-socket joint can not improve (differentiate) characteristic according to the direction on horizontal plane.

Patent application FR2801268 makes a helical spring relevant with two elastomeric ball and-socket joint series connection of lamination or no lamination, and they are that tail is installed by head. In practice, this kind of device needs basic size in the height direction, to guarantee required performance level. Additionally, the use of ball-and-socket joint can not improve the characteristic according to horizontal direction.

Patent application FR2354299 suggestion saves metal spring by series connection conical butt spring and helical spring, conical butt spring has high-caliber axial flexibility to guarantee that the down suction hung and low-level horizontal flexible are to guarantee the function of vertical guide, and helical spring has high-caliber vertical stiffness with the weight of supportive body and high-caliber horizontal flexible to adapt to the relative horizontal movement of main body and bogie. This device can not improve the characteristic according to horizontal direction.

In addition; the conical butt spring of lamination is likely to be of and guarantees substantially vertical gap and ensure that the vertical stiffness independent of load level is (for this base part; the characteristic of axial displacement is intended to nonlinear by axial force) problem; in addition, there is also the problem of protuberance and therefore there is the problem of adjustment to guarantee the base plate height relative to platform within a period of time.

Present inventor considers, it is desired to be able to the lateral decoupling performance improved while restriction vertical dimension.

Summary of the invention

For this, the present invention proposes one can be integrated in the inclination bolster hung in sub-component (especially the secondary suspension of vehicle), it has the framework of parallel type, and wherein function is dispensed between centerpivot and at least one pair of Elastic Bolts being arranged on centerpivot both sides.

Present invention is accordingly directed to a kind of inclination bolster, this inclination bolster is vehicle (especially rolling stock, such as lorry, passenger vehicle or locomotive) suspension and design, first of all for the absorption guaranteeing normal load produced by vehicle body, secondly in order to move into line tilt along with relative level, bolster includes: the first support member, is arranged on the element of vehicle; And second support member, vertically spaced apart with the first support member, to receive the end of pendulum spring, it is characterised in that bolster also includes:

-central vertical guides pivot, including cylinder or conical butt flexible member, this flexible member is arranged between inner part and external part, one in inner part and the first support member and the second support member integral, another in external part and the first support member and the second support member is integral, and the horizontal rigidity of pivot is more than its vertical stiffness; And

-at least one pair of Elastic Bolts, bolt is symmetrically disposed in the both sides of centerpivot, bolt is centrally located on the first trunnion axis, and bolt is arranged between the first support member and the second support member, and bolt has high-caliber vertical or compression stiffness relative to its level or shearing rigidity.

First trunnion axis constitutes the preferred axle of the inclination of bolster, for the mainly tensioning angularly of this axle, pivot and Elastic Bolts.

The existence of one or more pairs of bolts of centrally disposed pivot both sides can increase rigidity during being perpendicular to the second transverse axis of the first axle, because the rigidity caused by the compression of Elastic Bolts is added in the inclined rigidity of previously existence.

Parallel configurations has the specific advantages of restriction vertical dimension, thus avoiding the major defect of existing apparatus, including the performance limiting this device due to vertical dimension constraint. It is true that vertical dimension constraint usually needs to reduce the size of parts, thus technical specification can not be complied fully with, especially affect the comfort level of passenger.

The geometry of centerpivot is preferably conical butt, reduces its rigidity with conical, thus reducing the rigidity (not improved) when it tilts by centerpivot.

Cylindrical or conical butt flexible member can be made up of elastomer at least in part, especially laminated elastic body.

Elastic Bolts can be metal gasket, or Elastic Bolts can be made up of elastomer at least in part, especially laminated elastic body.

Ratio between horizontal rigidity and the horizontal rigidity of bolt assembly of centerpivot is equal to 1 or more than 1, and can such as between 5 and 50, it is preferable that at least equal to 10.

The vertical stiffness K ' of bolt assembly_APVertical stiffness K with centerpivot_APBetween ratio equal to 1 or more than 1, and can such as between 5 and 50, it is preferable that at least equal to 10.

Ratio between horizontal rigidity and the vertical stiffness of centerpivot especially may be located between 1 and 5, and such as between 2 and 5, and/or the ratio between the vertical stiffness of bolt and horizontal rigidity can be equal to 10 or more than 10, and can such as between 50 and 500.

Bolster can have following feature, and cylinder or the conical butt element of centerpivot have at least one pair of hole, and hole is symmetrically disposed in the both sides of centerpivot, and aligns in the middle face in hole on the second trunnion axis be perpendicular to the first axle.

Bolster can have following feature, at least one centerpivot has and its inner part all-in-one-piece stop member, stop member has bulge loop, and bulge loop is separated by the external part of functional play j Yu centerpivot, to limit the displacement of the traction of the flexible member of centerpivot.

The invention still further relates to a kind of suspension sub-component, it is characterised in that hang sub-component and include the inclination bolster of at least one aforesaid definition, the second support member tilting bolster receives the end of one or more pendulum springs.

Hanging sub-component and can have following feature, hang sub-component and include two described inclination bolsters that tail is installed by head, pendulum spring is arranged between the second support member of two bolsters.

Hang sub-component and can have following feature, first bolster includes the first stop member, second bolster includes arresting stop, arresting stop includes band, band is fixed by with the first stop member all-in-one-piece band support member, and walking around semi-cylindrical support member, semi-cylindrical support member is formed at and stops in support member with the second bolster all-in-one-piece.

Accompanying drawing explanation

By reading as explained below and in conjunction with accompanying drawing, other features and advantages of the present invention will become apparent from, wherein:

Fig. 1 a and 1b is the diagram of side view and the top view representing car team respectively;

Fig. 2 a illustrates, in the way of perspective, the secondary suspension comprising four sub-components, each sub-component makes at least one metal spring and two inclination bolsters according to the decoupling that can provide improvement of the present invention be correlated with, with top view, Fig. 2 b illustrates that axle is to limit the orientation of bolster, Fig. 2 c and Fig. 2 d illustrates the combination (2d) of secondary suspension sub-component (2c) and correlation function;

Fig. 3 illustrates the skeleton diagram tilting bolster according to the present invention;

Fig. 4 a to 4d respectively in the way of front view (4a), vertical cross-section AA (4b), horizontal cross-section BB (4c) and isometric transparent view (4d) represent according to the present invention tilt bolster embodiment;

Fig. 5 and Fig. 6 is separately by making interface integral with the support member of main body and metal spring on the height of centerpivot, and passes through to make high stop member represent two kinds of component patterns in the way of section AA with centerpivot (frame of the enlarged drawing comprising the functional play j illustrating this stop member) is integral; And

Fig. 7 a to 7d being respectively provided with a pair cylindrical bolt (7b), have two pairs of (or more to) bolts (7c) and have a pair the bolt (7d) with segment form illustrate bolt variant embodiment.

Detailed description of the invention

Fig. 1 a and 1b represents vehicle, and vehicle has main body 1 and two bogies 2, and each bogie includes two axles 21 and four wheels 22, axle 21 and wheel 22 are suspended on the chassis 23 of bogie 2 by single stage suspension 24, and single stage suspension 24 includes four sub-components 25.

Each bogie 2 is provided with secondary suspension 3, and secondary suspension 3 includes four sub-components 31 according to tetragon distribution.

Fig. 2 a illustrates that four sub-components 31, each sub-component 31 include two and tilt bolster 32 and 33, tilts and is provided with one or more metallic suspension spring 4 between bolster 32 and 33. Surface thereof bolster 32 is with for integral with the parts 11 of main body 1 mutual (interface), and lower inclination bolster 33, with to be used for the parts 26 mutual with bogie 2 integral, bogie 2 is also equipped with single stage suspension sub-component 25. H_suspSpecifying the height of secondary suspension, this highly comprises the size of bolster 32 and 33.

Direction x is the longitudinal direction of vehicle, the direction that namely its straight line travels.

Direction y is the horizontal direction of vehicle, and the direction z rectangular with both of the aforesaid direction is vertically oriented.

Appointment that direction u (sees also Fig. 2 b) tilts the preferred axle of the inclination of bolster 32 and 33, and direction v specifies the horizontal direction being perpendicular to direction u and z. U is the longitudinal direction of bolster, and v is their horizontal direction.

According to the present invention, tilt bolster for providing the decoupling of improvement, provide the bolster preferred angled around u axle and bolster around the finite inclination of v axle especially, and metal spring guarantees the vertical stiffness obtained needed for secondary suspension that does as usual. Therefore the decoupling improved by tilting bolster to obtain, tilts bolster and has the characteristic of the different-stiffness according to horizontal direction.

O1 and O2 is the geometric center of deck beam assembly 32 and 33, and each bolster 32 has center A1, B1, C1, D1, and each bolster 33 has center A2, B2, C2, D2. O1 is the center of tetragon A1, B1, C1, D1, and O2 is the center of tetragon A2, B2, C2, D2.

K_x��K_yAnd K_��zRespectively specify that the longitudinal rigidity (x-axis) of suspension, its lateral stiffness (y-axis) and its rotation (inaloop) rigidity (main body/bogie is around the rotation of z-axis).

First trunnion axis u is the preferred axle of the inclination of sub-component 31.

Second trunnion axis v is the axle (upper rigidity) with finite inclination.

L, �� are distance and the angle of the embedding of the secondary suspension sub-component limited by client respectively.

�� is that local is with reference to (u, v, z) relative to the overall situation with reference to (x, y, azimuth z).

The orientation of system is selected according to the flexible preferred orientations needed for client.

When ��=0, obtain the greatest flexibility hung according to lateral shaft (y).

As ��=��, in rotation, (�� z) obtains the greatest flexibility hung.

When ��=90 ��, obtain the greatest flexibility hung according to longitudinal axis (x).

Fig. 2 c and 2d illustrates secondary suspension sub-component, it includes a pair surface thereof bolster 32 and lower inclination bolster 33 and one or more metallic suspension spring 4, and metallic suspension spring 4 is arranged between bolster 32 and 33 by upper element surface 42 and the lower component surface 43 of spring 4. High and low halt system (46,47,48) can be contained in the central authorities of spring 4.

In order to realize first function (the lateral decoupling of improvement) of sub-component, the framework tilting bolster is divided into difference in functionality (Fig. 3) based on this product:

-at middle part, there is the deformable system 50 (being referred to as pivot) of remarkable rigidity in the horizontal direction, its can:

. transmission longitudinal stress and lateral stress (guiding),

. guarantee the guiding of the satisfaction according to vertical axis,

. pivot can comprise different technologies, the technology of (be parallel to armature lamination or the no lamination) technology namely or do not have with the elastomer type in chamber or the type with metal gasket;

-at outer peripheral portion, there is the support body assembly 60 (being referred to as bolt) of remarkable rigidity in vertical direction, its can:

. absorb the normal load of train's body,

. contribute to the inclination on the u of direction by selected concrete layout (namely, for instance the pair of bolts 60 according to the alignment of u axle),

. increase the rigidity of the inclination in the direction vertical with aforementioned direction on the contrary, and

. restriction system vertical dimension, and between bolster space slot milling.

Bolt 60 can comprise different technologies, i.e. lamination (is parallel to armature) or the technology of the elastomer type of no lamination, or has the technology of the type of metal gasket as required.

Pivot 50 and bolt 60 be arranged in parallel, and they all work concurrently with in horizontal direction in vertical direction.

In the horizontal direction, rigidity is combined, and is therefore the radial rigidity K of pivot 50_RPShearing rigidity K with bolt assembly 60_CPSum. Radial rigidity K due to pivot 50_RPShearing rigidity K much larger than bolt assembly 60_CP, therefore pivot 50 absorbs the horizontal force of the overwhelming majority.

In vertical direction, rigidity is also combined, and rigidity in the direction is the axial rigidity K of pivot 50_APAxial rigidity K ' with bolt assembly 60_APThe sum of (that is, the sum of the rigidity of bolt), and due to the axial rigidity K of pivot 50_APAxial rigidity K ' much smaller than bolt 60_AP, therefore bolt 60 absorbs the vertical force of the overwhelming majority.

This parallel configurations can greatly limit vertical dimension, therefore meets the specification requirement in the space of the height with reduction.

Paired bolt 60 can absorb vertical force (according to z) with the used in parallel of centerpivot 50 and control the conical inclination �� v around v axle (axle of finite inclination), retain the flexibility of the inclination in other direction simultaneously, and the inclination in particular about u axle, for these directions, the flexibility of inclination limits mainly through the cylinder of centerpivot or conical resilient body layer (lamination or no lamination).

In figure 3, bolt 60 is depicted as column shaped rotating part but it also may use other form (polygon etc.).

Pivot 50 is depicted as having conical butt flexible member 53, and it has half angle ��. It can also be column shaped rotating part. The value of subtended angle �� may be located between 0 �� and 60 ��, particular between 8 �� and 30 ��. Pivot includes interior cylindrical or conical butt armature 51, external cylindrical or conical butt armature 52 and flexible member 53, and flexible member 53 is such as made up of the elastomer of lamination or no lamination.

Horizontal rigidity (the radial rigidity K of centerpivot 50_RP) with horizontal rigidity (the shearing rigidity K of bolt_CP) between ratio may be located between 5 and 50, and be preferably at least equal to 10. The representative value of about 20 can be recommended.

This than value (there is the cylinder form of the bolt of relative armature essentially by geometry; There is cylinder or the frusto-conical shape of the pivot of interior armature and external armature) limit.

Axial (vertically) rigidity of bolt assembly 60 (K '_AP) with axial (vertical) rigidity (K of centerpivot 50_AP) between ratio may be located between 5 and 50, and be preferably at least equal to 10. The representative value of about 20 can be recommended.

The vertical stiffness of bolt 60 is selected by their geometry, their characteristic (material) and production method (lamination or the elastomer of no lamination, metal gasket).

In practice:

The horizontal rigidity K of-centerpivot_RPWith vertical stiffness (K_ZPivot) between ratio more than 1, and can such as between 2 and 5; This than value by the fact that the major function of pivot is limit levels displacement explaining;

-and/or the vertical stiffness (K of bolt_ZBolt) and horizontal rigidity K_CPBetween ratio at least equal to 10, and can such as between 50 and 500; The high level of this final ratio passes through horizontal rigidity K_CPIt is the fact that major function is and absorbs normal load explaining of shearing rigidity and bolt. Specifically, the use of the elastomer bolt of metal gasket or lamination disclosure satisfy that this demand.

The value of two aforementioned ratios is that the independent each parts obtained are intrinsic, rather than the key of the decoupling performance of product.

Fig. 4 a to 4d represents the preferred implementation hanging sub-component, hangs sub-component and includes two inclination bolsters that tail is installed by the head according to the present invention.

Surface thereof bolster 32 includes centerpivot 50, the interior armature 51 of centerpivot 50 is integral with plate 71, plate 71 constitutes the parts 11 mutual with main body 1, and the external armature 52 of centerpivot 50 is integral with plate 70, and the lower surface of plate 70 is the stayed surface 42 of spring 4 (having two in this case). Opening up in the cone of flexible member 53, this contribute to bolt and the inclination of pivot Natural Central close to or overlap. Being left out the rigidity of the inclination caused by the compression member of bolt 60, i.e. in practice, by considering u axle, this specific arrangements of these Natural Centrals can make the drag reduction to the inclination according to u axle.

Each cylindrical bolt 60 all includes two plates 62 and 63 and pad 61, and pad 61 is preferably metal gasket, plate 62 and 63 and pad 61 be provided entirely between plate 70 and 71. Pad 61 is placed in the middle by pin 56. They are mounted to relative to ZZ axle at diametrically opposite, and align according to direction u. On interior armature 51, being provided with low elasticity stop member 46 and support member 46b thereof also by axle 57, assembly (50,60,61,62,63,70,71) is sandwiched. Plate 62 and 63 is selected from having the material being enough to bear the hardness of the contact pressure of pad 61.

The through beam 33 tail installed relative to bolster 32 has central bolt 50, the interior armature 51 of central bolt 50 is integral with plate 71, palette 71 constitutes the parts 26 mutual with bogie 2, and the external armature 52 of central bolt 50 is integral with plate 70, and the upper surface of plate 70 is the stayed surface 43 of spring 4. Through beam 33 is similar to the framework of described deck beam 32, except lower stopping support member 47 be arranged on interior armature 51 by fixing screw 58 and cone open mouth down except.

In extreme circumstances, stop member 46 can contact support member 47, with the suppressed range of restraining spring 4.

Owing to the space between bolster can be used, lower stopping support member 47 can be set to the passage 471 comprised with (not shown), therefore, it is possible to guarantee the function promoting stop member, promote the stop member restriction secondary suspension sub-component 31 stretch amplitude during vehicle promotes, and guarantee the preload of spring 4 alternatively.

Preferably, assembly 47 is positioned at below stop member 46, due under gravity, at the rear-mounted band of two securing member 46c being integrated in stop member 46 relative to passage 47₁Semi-cylindrical outline 47₂Enter correct position. If the securing member 46c of the band of band and lower section acts on satisfactorily, then stop member 46 can with stopping support member 47 and passage 47₁Exchange.

Except plate 71 and pin 56 thereof outside the angular alignment function with assembly (50,70,56), the fastening torque of screw 58 or nut 59 is transferred to plate 71 by pin 55. The latter has another function during the assembling of sub-component 31, because:

-in composing room, secondary suspension assembly 31 is not placed in below train, and is therefore not subject to the load of main body 1. Owing to the down suction scope between high stop member and low stop member needs when meeting with and using rolling stock to optimize, therefore spring 4 preload will not caused big down suction, or cause the reinforcement of vertical stiffness, thus damaging the comfort level of passenger. It is true that relative to the big normal load applied by main body 1 (considering that it does not have the situation of passenger), the vertical stiffness of spring 4 is relatively low. Being complete once assemble, therefore this preload of spring 4 causes the tensioning of band;

-therefore, before clamping, spring 4 comprise parts 46,46b, 46c, 47, and band;

-therefore the securing member 46c of elevator belt must be installed before spring 4 is arranged on plate 70;

-due to also can not touch from outside stopping support member 46b, therefore pin 55 guarantee in this untouchable region angle location, and make terminate sub-component 31 be mounted for possibility;

-on the other hand, it is possible to prepare stopping support component 47 in advance.

During tilting the industrialization of bolster, it is possible to optimize the number of the number of assembling steps tilting bolster by parts 51 and 71 being combined as single parts (shown in the variant in Fig. 5). In the figure, parts 51 ' include the flange 51 that serves as plate 71 ". In both cases, if the material of plate 71 (or flange 51 ") can bear the hammering pressure applied by bolt, i.e. if material is enough hard, then may be omitted with plate 62 and 63.

The axial flexibility of pivot 50 may be used for the assembling of auxiliary bolt 60. The pin 56 for making bolt 60 placed in the middle can be increased from outside.

In Figure 5, the Interface integration between the support member 70 of main body 1 or bogie 2 and metal spring is at the At The Height of centerpivot.

In figure 6, it is preferred that emphasis is do not use the embodiment of the high stop member (or promoting stop member) of internal band. Each bolster includes high stop member 46b '/46 of themselves "/47 ", and outside lifting system (such as cable rope or belt) can be integrated between two plates 70, with the stretching, extension of restraining spring 4.

Stop support member 46b '/47 ' formed bulge loop 46 "/47 ", bulge loop 46 "/47 " periphery and external armature 52 between there is vertical play j. Common duty keeps functional play j, thus not suppressing the inclination of bolster. Bulge loop 46 "/47 " value of functional play j is limited to pivot flexible member 53 traction in displacement, this displacement limits the traction stresses of pivot during main body promoting, and thereby, it is ensured that tilts the function of high stop member intrinsic in bolster 32 and 33.

Fig. 7 a to 7d is illustrated as to bolt three embodiments. In the various figures, bolt relative to the center A2 being positioned on ZZ ' axle at diametrically opposite. Fig. 7 a (vertical cross-section) is that Fig. 7 b to 7d is common.

In fig .7b, there is a pair cylindrical bolt 60, each bolt extends in u axle both sides and on angle �� 1, has at least one pair of alternatively at diametrically opposite through hole 65, and through hole 65 extends in v axle both sides and on angle section �� 2.

In figure 7 c, there are two pairs of bolts, respectively 60₁��60₂With 60₃��60₄, these two pair bolt extends in u axle both sides and on angle section �� 1. Their center P₁��P₂��P₃��P₄Lay respectively at straight line A2P₁��A2P₂��A2P₃��A4P₄On, straight line forms angle �� P with u axle respectively₁��P₂��P₃��P₄. The even number bolt more than 4 can also be used. Preferably, angle �� P₁��P₂��P₃��P₄Value be chosen as identical so that system in balance.

The compression stiffness K ' of bolt_APAxial rigidity K equal to or more than pivot_AP, i.e. K '_AP��K_AP, the ratio of the two is advantageously at least equal to 5, it is preferable that at least equal to 10, and can such as between 5 and 50.

Similarly, K_RP��K_CP, the ratio of the two is at least equal to 5, it is preferable that at least equal to 10, and can such as between 5 and 50.

In order to make performance optimization, i.e. making to maximize than K �� v/K �� u, wherein K �� v indicates the rigidity that bolster tilts around v axle, and K �� u indicates the rigidity that bolster tilts around u axle:

-�� 1 is chosen as low as far as possible (being formed under the extreme case of support member of local) at bolt to reduce the circular cone stiffness K �� u (rotating around u axle) of bolt;

-�� 2 may be selected and is not equal to 0 �� (producing hole 65), to reduce the circular cone stiffness K �� u of pivot. But, the value of angle �� 2 is subject to following true restriction: the existence in hole 65 is likely to not affect the absorption of the horizontal force according to v axle;

The diameter D (distance between the center C of single pair of bolt) of the embedding of-bolt is preferably equally big with the space distributed for Product License. It is true that due to rigidity (the K �� of bolt opposing connection v axle inclination_VP) depend on diameter D square, for the identical characteristics K ' of bolt_AP, when D becomes twice as, K ��_VPBecome 4 times. It should be noted that the self-stiffness in the inclination of bolt is second order term, it is not dependent on D, and can be not considered.

Preferably, system is symmetrical relative to center A2, so that the absorption of power keeps balance.

Bolt can have any cross section: they are illustrated as the form with cylinder or sector in an embodiment, represents to simplify. Can consider that their cross section is optimized by aforementioned parameters (�� 1, D).

In practice, �� 1 is chosen as less than 45 ��, and is preferably located between 0 �� and 25 ��, and/or �� 2 may be selected up to 60 ��, and is preferably located between 5 �� and 25 ��.

Claims

1. one kind tilts bolster, the suspension that described inclination bolster is vehicle designs, first of all for guaranteeing the absorption of normal load produced by the main body of described vehicle, secondly in order to move into line tilt along with relative level, described bolster includes: the first support member, for being arranged on the element of described vehicle; And second support member, vertically spaced apart with described first support member, to receive the end of pendulum spring, it is characterised in that described bolster also includes:

-central vertical guides pivot (50), including cylinder or conical butt flexible member (53), described flexible member (53) is arranged between inner part (51) and external part (52), described inner part (51) is integral with in described first support member (70) and described second support member (71), another in described external part (52) and described first support member and described second support member is integral, and described central vertical guides the horizontal rigidity of pivot (50) more than its vertical stiffness; And

-at least one pair of Elastic Bolts (60), it is symmetrically disposed in described central vertical and guides the both sides of pivot, described at least one pair of Elastic Bolts (60) is centrally located on the first trunnion axis, described at least one pair of Elastic Bolts (60) is arranged between described first support member (70) and described second support member (71), and has high-caliber vertical stiffness relative to their horizontal rigidity.

2. bolster according to claim 1, it is characterised in that described cylinder or conical butt flexible member (53) are made up of elastomer at least in part.

3. bolster according to claim 2, it is characterised in that described cylinder or conical butt flexible member (53) are laminations.

4. bolster according to any one of claim 1 to 3, it is characterised in that described Elastic Bolts (60) is metal gasket.

5. bolster according to any one of claim 1 to 3, it is characterised in that described Elastic Bolts (60) is made up of elastomer at least in part.

6. bolster according to claim 5, it is characterised in that described Elastic Bolts (60) is lamination.

7. bolster according to claim 1 and 2, it is characterised in that the vertical stiffness of described Elastic Bolts (60) and described central vertical guide the ratio between the vertical stiffness of pivot (50) equal to 1 or more than 1.

8. bolster according to claim 1 and 2, it is characterised in that the vertical stiffness of described Elastic Bolts (60) and described central vertical guide the ratio between the vertical stiffness of pivot (50) between 5 and 50.

9. bolster according to claim 1 and 2, it is characterised in that described central vertical guides the ratio between horizontal rigidity and the horizontal rigidity of described Elastic Bolts (60) of pivot (50) equal to 1 or more than 1.

10. bolster according to claim 1 and 2, it is characterised in that described central vertical guides the ratio between horizontal rigidity and the horizontal rigidity of described Elastic Bolts (60) of pivot (50) between 5 and 50.

11. bolster according to claim 1 and 2, it is characterised in that described central vertical guides the ratio between horizontal rigidity and the vertical stiffness of pivot (50) between 2 and 5.

12. bolster according to claim 1 and 2, it is characterised in that the ratio between vertical stiffness and the horizontal rigidity of described Elastic Bolts (60) is between 50 and 500.

13. bolster according to claim 1 and 2, it is characterized in that, described central vertical guides the cylinder of pivot (50) or conical butt flexible member (53) to have at least one pair of hole (65), at least one pair of hole described is symmetrically disposed in described central vertical and guides the both sides of pivot (50), and aligns in the middle face at least one pair of hole described on the second trunnion axis being perpendicular to described first trunnion axis.

14. bolster according to claim 1 and 2, it is characterized in that, at least one central vertical guides pivot (50) to have and its inner part (51) all-in-one-piece stop member (46,46b ', 47 '), described stop member (46,46b ', 47 ') have bulge loop (46 "; 47 "), described bulge loop (46 ", 47 ") guide external part (52) the spacer functionality play of pivot (50) with described central vertical, to limit the displacement of the traction of the flexible member (53) of described central vertical guiding pivot (50).

15. the suspension sub-component for vehicle, it is characterised in that described suspension sub-component includes at least one inclination bolster according to aforementioned any claim, and the second support member of described inclination bolster receives the end of at least one pendulum spring.

16. suspension sub-component according to claim 15, it is characterized in that, described suspension sub-component includes the first inclination bolster and the second inclination bolster that tail is installed by head, and at least one described pendulum spring (4) is arranged between the second support member of two bolsters.

17. suspension sub-component according to claim 16, it is characterized in that, described first tilts bolster includes the first stop member (46), described second tilts bolster includes arresting stop (47), described arresting stop (47) includes band, described band is fixed by with described first stop member (46) all-in-one-piece band support member (46c), and walks around semi-cylindrical support member (47₂), described semi-cylindrical support member (47₂) be formed to tilt in bolster all-in-one-piece arresting stop (47) with described second.