CN201646753U - Steering frame of railway carriage with large diamond resistant rigidity - Google Patents
Steering frame of railway carriage with large diamond resistant rigidity Download PDFInfo
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- CN201646753U CN201646753U CN2010201780065U CN201020178006U CN201646753U CN 201646753 U CN201646753 U CN 201646753U CN 2010201780065 U CN2010201780065 U CN 2010201780065U CN 201020178006 U CN201020178006 U CN 201020178006U CN 201646753 U CN201646753 U CN 201646753U
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- spring
- bolster
- drift angle
- wedge
- side frame
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Abstract
The utility model provides a steering frame of a railway carriage with large diamond resistant rigidity, which comprises a front-back wheel pair assembly, two side frame assemblies, a swing bolster assembly and two sets of central spring suspending devices, wherein each set of central spring suspending device comprises a bearing spring assembly, two vibration-reducing springs arranged at the two sides of the bearing spring assembly and two small vertex angle tapered wedges at the top of each vibration-reducing spring. A master friction surface of each small vertex angle tapered wedge is glued with a friction plate of a side bracket stand column of each side frame assembly, an assistant friction surface of each small vertex angle tapered wedge is glued with the splay surface of the swing bolster of the swing bolster assembly, and the structural parameters of the small vertex angle tapered wedges meet the following mathematic relationship: L=200-260mm, Alpha=16-30 degrees, and t*g*Alpha is more than mu and is less than mu+mu1, wherein L is the width of each small vertex angle tapered wedge, Alpha is an included angle between the assistant friction surface of each small vertex angle tapered wedge and a vertical plane, mu is the frictional factor is the master friction surface of each small vertex angle tapered wedge, and mu1 is the frictional factor of the assistant friction surface of each small vertex angle tapered wedge. The steering frame is simple and reliable in structure, low in manufacture cost and maintenance cost, has enough diamond resistant rigidity and good dynamics performance and curve passing performance, and can meet the requirement of greatly improving the speed of the railway carriage.
Description
Technical field
The utility model relates to railway freight car bogie, refers to a kind of large-diamond resistant rigidity railway truck steering frame particularly.
Background technology
Railway freight car bogie is the critical piece of rail freight.Traditional railway freight car bogie great majority comprise two bogie side frames compositions and the three-major-items formula structure that bolster is formed.The two ends drawing strickle guide that bogie side frame is formed becomes to be installed in front and back wheel on forming by adapter and bearing set, and the two ends that bolster is formed then are installed in the central square frame of bogie side frame composition by two groups of central authorities' spring suspensions.Central authorities' spring suspension mainly is made of the bearing spring assembly in the middle of being positioned at, the wedge that is positioned at the damper spring of both sides and is positioned at the damper spring top, the bolster Eight characters face wipe contact that side frame column face that the secondary friction face of vertical main friction face and bevelled is formed with bogie side frame respectively on the wedge and bolster are formed, bearing spring assembly, damper spring and on wedge bear the load that bolster is formed together.The both sides, top that bolster is formed are provided with bottom side bearing to be formed, the common bearing body weight of cartridge that itself and bolster are formed.Also be provided with foundation brake rigging in the bogie truck, be used for lorry is implemented brake.
Simple structure, wheel weight average carrying property are good though above-mentioned three-major-items formula structure bogie truck has, manufacturing and the cheap advantage of the cost of overhaul, but the defective that also has the rigidity difference of loose, the anti-water chestnut distortion of connection structure between bolster composition and the bogie side frame composition, be not enough to resist the violent motion of shaking the head between bolster composition and the bogie side frame composition thus, it takes turns forming bigger than normally to the angle of attack of rail when causing bogie truck by curve track, and wheel-rail wear increases.Particularly the wedge of central spring suspension has bigger design drift angle (angle between its secondary friction face and the vertical guide), big in 35～70 ° scope, its diamond resistant rigidity is very limited, when the bolster composition travels longitudinally with respect to the bogie side frame composition, the bolster Eight characters will be greater than the wedge master in the face of the vertical component of the application force of wedge, the vertical component sum of the friction force of secondary friction face, this moment, wedge can move downward, fore-and-aft distance between bolster composition and the bogie side frame composition is diminished, bolster composition and bogie side frame can produce relative rotation between forming, and diamonding takes place.Like this, the critical speed of vehicle can only be lower, and running velocity is limited, and riding quality is not high, can not satisfy the needs that rail freight significantly raises speed.
In order to address the above problem, the lorry that raises speed has at present adopted the mode that installs cross-braced device additional or install spring plank additional between two bogie side frames are formed, to strengthen the diamond resistant rigidity of traditional railway freight car bogie.But the structure that installs cross-braced device or spring plank additional is comparatively complicated, unsprung weight is laid particular stress on, manufacturing and the cost of overhaul are also higher.Therefore, traditional railway goods train bogie is improved, design a kind of bogie truck, the riding quality that improves railway vehicle is had important practical significance with enough diamond resistant rigidities and good dynamic performance.
Summary of the invention
The purpose of this utility model is exactly to overcome the existing existing deficiency of bogie truck that installs cross-braced device or spring plank additional, provide a kind of simple and reliable for structure, manufacturing and maintenance cost cheap, have good dynamic performance and curve negotiation ability, satisfy significantly the raise speed large-diamond resistant rigidity railway truck steering frame of needs of rail freight.
For achieving the above object, the large-diamond resistant rigidity railway truck steering frame that the utility model is designed, comprise that front and back wheel is to composition, two bogie side frame compositions, a bolster composition and two groups of central authorities' spring suspensions, the described wheel is equipped with the bearing composition to the two ends of forming, the two ends drawing strickle guide that described bogie side frame is formed is carried on described bearing by adapter and forms, the two ends that described bolster is formed are installed on the described central spring suspension, and described central spring suspension is carried in the central square frame of described bogie side frame composition.The little drift angle wedge that described central spring suspension comprises the bearing spring assembly, is installed in the damper spring of bearing spring assembly both sides and is installed in the damper spring top, the side frame column friction plate that the main friction face of described little drift angle wedge and bogie side frame are formed is fitted, and the bolster Eight characters face that the secondary friction face of described little drift angle wedge and bolster are formed is fitted.Its special character is: the parameter of structure design of described little drift angle wedge satisfies following mathematical relation: α=16～30 ° and μ＜tg α＜μ+μ
1Wherein, α is the angle between described secondary friction face and the vertical guide, and μ is the friction coefficient of described main friction face, μ
1Friction coefficient for described secondary friction face.
The utility model is defined as 30 ° with the maxim of α in the described little drift angle wedge, 35～70 ° big drift angle design in traditional wedge, and limit tg α＜μ+μ
1Like this when the bolster composition travels longitudinally with respect to the bogie side frame composition, the bolster Eight characters in the face of the vertical component of the application force of wedge all the time less than the vertical upwards component sum of the main friction face and the secondary friction face friction force of wedge, thereby guarantee that wedge can not move downward (locked), bolster is formed and bogie side frame is formed and can not be produced relative rotation, and bolster composition and bogie side frame have enough big diamond resistant rigidity between forming.Certainly,, can make wedge self-locking when the bolster composition moves downward with respect to the bogie side frame composition, worsen the dynamic performance of bogie truck if the α value is too small to the friction angle near wedge master friction face.So the utility model is defined as 16 ° with the minimum value of α in the described little drift angle wedge simultaneously, and limit μ＜tg α, can guarantee like this that wedge is formed in the process move up and down also at bolster can free motion (not locked), thereby makes whole bogie truck have good dynamic performance and curve negotiation ability.
Preferably, the design width L=200～260mm of described little drift angle wedge.This width approximately is that tradition becomes the friction wedge (becoming the friction wedge is meant that wedge is installed in and places bogie side frame to form on the damper spring in the central square frame, the change that the vibration damping friction force of wedge is formed the vertical load bear with the bolster change that is directly proportional) more than 1.3 times of width, this had both increased the arm of force length of diamonding moment between little drift angle wedge opposing bolster and the bogie side frame, increase the area of contact of major and minor friction face of little drift angle wedge and side frame column friction plate and bolster Eight characters face again, thereby further improved the diamond resistant rigidity between bolster composition and the bogie side frame composition.
More preferably, the mechanical property of described damper spring satisfies following mathematical relation: K
1* ctg α=K * C/2 μ; Wherein, K
1Rigidity for described damper spring, K is the global stiffness (can be determined by designing requirement) of described central spring suspension, C is the relative friction coefficient of railway freight car bogie, and the span of C is 0.05～0.15, and μ promptly is the friction coefficient of described main friction face.Stiffness K because of damper spring
1Be inversely proportional to the ctg α of little drift angle wedge, can be according to the corresponding adjusting of the variation of α value K
1Value, thus guarantee to obtain suitable friction damping power, do not cause the friction force of decay vertical vibration of vehicle and lateral vibration excessive.
Advantage of the present utility model is: the little drift angle wedge of designed bogie truck both can guarantee energy free motion when the bolster composition moves up and down, can guarantee when the bolster composition vertically moves locked again, bogie truck still has enough big diamond resistant rigidity and good dynamic performance under the condition that does not have bogie side frame cross-braced device or spring plank like this, and little drift angle wedge width becomes the design more than 1.3 times also the reinforcement from another point of view of friction wedge its diamond resistant rigidity and dynamic performance greater than tradition, thereby can significantly improve the critical design speed and the curve negotiation ability of vehicle operating, improve the riding quality of railway vehicle.Simultaneously, this bogie structure is simple, unsprung weight is light, manufacturing and the cost of overhaul are cheap, meets the designing requirement that speed per hour 120km/h rail freight is made, and can satisfy the needs that rail freight significantly raises speed.
Description of drawings
Fig. 1 is a kind of perspective view of large-diamond resistant rigidity railway truck steering frame;
Fig. 2 is the sectional structure scheme drawing of the central spring suspension of bogie truck shown in Figure 1;
Fig. 3 is the construction parameter sign picture of the little drift angle wedge of central spring suspension shown in Figure 2;
Fig. 4 is the stress balance scheme drawing of little drift angle wedge when bolster is formed longitudinal movement of central spring suspension shown in Figure 2;
Fig. 5 is the stress balance scheme drawing of little drift angle wedge when the bolster composition moves downward of central spring suspension shown in Figure 2.
The specific embodiment
Below in conjunction with the drawings and specific embodiments the utility model is described in further detail:
As shown in Figure 1, large-diamond resistant rigidity railway truck steering frame of the present utility model, mainly by front and back wheel to form 4, two bogie side frames form 1, bolster form 2, two groups of central authorities' spring suspensions 8, two bottom side bearings form 3 and foundation brake rigging 5 constitute.Wheel is equipped with bearing and forms 7 forming 4 two ends, and bogie side frame is formed 1 two ends drawing strickle guide and is carried on bearing by adapter 6 and forms on 7.The two ends of bolster composition 2 are installed on the central spring suspension 8, and central spring suspension 8 is carried in the central square frame of bogie side frame composition 1.
As shown in Figure 2, central spring suspension 8 mainly is made of bearing spring assembly 8c, the little drift angle wedge 8a that is installed in the damper spring 8b of bearing spring assembly 8c both sides and is installed in damper spring 8b top.The lower end of bearing spring assembly 8c and damper spring 8b is installed on the central square frame spring cushion cap of bogie side frame composition 1.Make the vertical main friction face 8a of little drift angle wedge 8a
1Contact the secondary friction face 8a of little drift angle wedge 8a bevelled with the side frame column friction plate 1a applying of bogie side frame composition 1
2Contact with the bolster Eight characters face 2a applying of bolster composition 2, realize that thus the vibration damping friction force of little drift angle wedge 8a is directly proportional with bolster composition 2 vertical loads of bearing.Little drift angle wedge 8a belongs to and becomes friction wedge classification, can both play the friction damping effect preferably when vehicle sky, heavy different load-carryings operation.
Fig. 3 has indicated keystone configuration design parameters L and the α of little drift angle wedge 8a.Wherein: L is the width of little drift angle wedge 8a, and α is the secondary friction face 8a of little drift angle wedge 8a
2And the angle between the vertical guide, they satisfy following mathematical relation: L=200～260mm, α=16～30 °, and μ＜tg α＜μ+μ
1Here, μ is the main friction face 8a of little drift angle wedge 8a
1Friction coefficient, μ
1 Secondary friction face 8a for little drift angle wedge 8a
2Friction coefficient.According to the designing requirement of α value, can select suitable material or structure to make μ value and μ
1Value also reaches designing requirement.
Fig. 4 has indicated bolster and has formed with respect to bogie side frame and form when travelling longitudinally, and bolster Eight characters face 2a gives application force N, the bolster Eight characters face 2a of little drift angle wedge 8a and the secondary friction face 8a of little drift angle wedge 8a
2Between friction force F
f, and the main friction face 8a of side frame column friction plate 1a and little drift angle wedge 8a
1Between friction force F
zAs shown in Figure 4, the vertical component N of the suffered application force N of little drift angle wedge 8a
y=N * sin α, vertical component N of the suffered application force N of little drift angle wedge 8a
z=N * cos α.And little drift angle wedge 8a is subjected to its main friction face 8a simultaneously
1With secondary friction face 8a
2Friction force upwards stops, main friction face 8a
1The friction force F of last generation
z=N
z* μ=N * cos α * μ, secondary friction face 8a
2Last generation friction force F
f=N * μ
1According to designing requirement N
y＜F
z+ F
f* cos α, i.e. N * sin α＜N * cos α * μ+N * μ
1* cos α promptly gets tg α＜μ+μ after the simplification
1Like this, little drift angle wedge 8a is by its main friction face 8a
1With secondary friction face 8a
2Friction force locked and can not move downward, bolster is formed and bogie side frame has enough big diamond resistant rigidity between forming.
Fig. 5 has indicated bolster and has formed with respect to bogie side frame and form when moving downward, and bolster Eight characters face 2a is to application force N, the bolster Eight characters face 2a of little drift angle wedge 8a and the secondary friction face 8a of little drift angle wedge 8a
2Between friction force F
f, and the main friction face 8a of side frame column friction plate 1a and little drift angle wedge 8a
1Between friction force F
zAs shown in Figure 5, the vertical component N of the suffered application force N of little drift angle wedge 8a
y=N * sin α, vertical component N of the suffered application force N of little drift angle wedge 8a
z=N * cos α.But little drift angle wedge 8a only is subjected to its main friction face 8a
1Friction force F makes progress
zPrevention, and its secondary friction face 8a
2On friction force F
fBe downward, main friction face 8a
1The friction force F of last generation
z=N
z* μ=N * cos α * μ.According to designing requirement F
z＜N
y, promptly N * cos α * μ＜N * sin α promptly gets μ＜tg α after the simplification.Like this, little drift angle wedge 8a can be by its main friction face 8a
1Friction force locked, forming when moving up and down at bolster can free motion, can guarantee the function of bogie truck normal attenuation vibration in vehicle operating.
By Fig. 5 also as can be known, the damping force of little drift angle wedge 8a mainly is its main friction face 8a
1The friction force F that produces
z, and friction force F
zAlso the bearing capacity P with damper spring 8b is relevant, F
z=P * ctg α * μ, P=K
1* y, wherein: K
1Be the rigidity of damper spring 8b, y is the amount of deflection of damper spring 8b.Can get F thus
z=K
1* y * ctg α * μ.For keeping the damping force of little drift angle wedge 8a appropriateness, the mechanical property of designed damper spring 8b should satisfy following mathematical relation: K
1* ctg α=K * C/2 μ; Wherein, K is the global stiffness of central spring suspension 8, and C is the relative friction coefficient of railway freight car bogie, and the span of C is 0.05～0.15.Because K value and μ value are definite by designing requirement, work as the α value like this and become hour, ctg α is corresponding to become greatly the stiffness K of damper spring 8b
1Can correspondingly select little, thereby the relative friction coefficient C all-the-time stable of guaranteeing railway freight car bogie does not cause the friction force of vertical and lateral vibration of decay vehicle excessive in 0.05～0.15 scope.
After the utility model adopts said structure, under the situation that does not install bogie side frame cross-braced device or spring plank additional, have enough diamond resistant rigidities, higher critical speed and fabulous curving performance equally, be applicable to the novel railway lorry of speed per hour 120km/h, satisfy the needs that rail freight significantly raises speed.
Claims (3)
1. large-diamond resistant rigidity railway truck steering frame, comprise that front and back wheel is to forming (4), two bogie side frames are formed (1), a bolster is formed (2) and two groups of central authorities' spring suspensions (8), the described wheel is equipped with bearing composition (7) to the two ends of forming (4), the two ends drawing strickle guide that described bogie side frame is formed (1) is carried on the described bearing composition (7) by adapter (6), the two ends that described bolster is formed (2) are installed on the described central spring suspension (8), described central spring suspension (8) is carried on described bogie side frame and forms in the central square frame of (1), described central spring suspension (8) comprises bearing spring assembly (8c), be installed in the damper spring (8b) of bearing spring assembly (8c) both sides, and the little drift angle wedge (8a) that is installed in damper spring (8b) top, the main friction face (8a of described little drift angle wedge (8a)
1) fit the secondary friction face (8a of described little drift angle wedge (8a) with the side frame column friction plate (1a) of bogie side frame composition (1)
2) the bolster Eight characters face (2a) of forming (2) with bolster fits, it is characterized in that: the parameter of structure design of described little drift angle wedge (8a) satisfies following mathematical relation: α=16～30 ° and μ＜tg α＜μ+μ
1Wherein, α is described secondary friction face (8a
2) and vertical guide between angle, μ is described main friction face (8a
1) friction coefficient, μ
1Be described secondary friction face (8a
2) friction coefficient.
2. large-diamond resistant rigidity railway truck steering frame according to claim 1 is characterized in that: the width L=200～260mm of described little drift angle wedge (8a).
3. large-diamond resistant rigidity railway truck steering frame according to claim 1 and 2 is characterized in that: the mechanical property of described damper spring (8b) satisfies following mathematical relation: K
1* ctg α=K * C/2 μ; Wherein, K
1Be the rigidity of described damper spring (8b), K is the global stiffness of described central spring suspension (8), and C is the relative friction coefficient of railway freight car bogie, and the span of C is 0.05～0.15.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010201780065U CN201646753U (en) | 2010-04-27 | 2010-04-27 | Steering frame of railway carriage with large diamond resistant rigidity |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010201780065U CN201646753U (en) | 2010-04-27 | 2010-04-27 | Steering frame of railway carriage with large diamond resistant rigidity |
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| Publication Number | Publication Date |
|---|---|
| CN201646753U true CN201646753U (en) | 2010-11-24 |
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ID=43111976
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|---|---|---|---|
| CN2010201780065U Expired - Lifetime CN201646753U (en) | 2010-04-27 | 2010-04-27 | Steering frame of railway carriage with large diamond resistant rigidity |
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|---|---|
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101844567A (en) * | 2010-04-27 | 2010-09-29 | 南车长江车辆有限公司 | Large-diamond resistant rigidity railway truck steering frame |
-
2010
- 2010-04-27 CN CN2010201780065U patent/CN201646753U/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101844567A (en) * | 2010-04-27 | 2010-09-29 | 南车长江车辆有限公司 | Large-diamond resistant rigidity railway truck steering frame |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20101124 Effective date of abandoning: 20111109 |