CN101830234B - Oblique wedge vibration damper for railway freight car bogie - Google Patents
Oblique wedge vibration damper for railway freight car bogie Download PDFInfo
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- CN101830234B CN101830234B CN2010101622371A CN201010162237A CN101830234B CN 101830234 B CN101830234 B CN 101830234B CN 2010101622371 A CN2010101622371 A CN 2010101622371A CN 201010162237 A CN201010162237 A CN 201010162237A CN 101830234 B CN101830234 B CN 101830234B
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- wedge
- vibration damper
- freight car
- railway freight
- oblique wedge
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- 239000000203 mixture Substances 0.000 claims description 51
- 238000013016 damping Methods 0.000 claims description 20
- 239000000463 material Substances 0.000 claims description 17
- 239000004677 Nylon Substances 0.000 claims description 6
- 229920001778 nylon Polymers 0.000 claims description 6
- 239000000725 suspension Substances 0.000 claims description 6
- CWYNVVGOOAEACU-UHFFFAOYSA-N Fe2+ Chemical compound [Fe+2] CWYNVVGOOAEACU-UHFFFAOYSA-N 0.000 claims description 5
- 229910000831 Steel Inorganic materials 0.000 claims description 5
- 239000010959 steel Substances 0.000 claims description 5
- 229910003460 diamond Inorganic materials 0.000 abstract description 9
- 239000010432 diamond Substances 0.000 abstract description 9
- 230000008901 benefit Effects 0.000 abstract description 4
- 238000012423 maintenance Methods 0.000 abstract description 3
- 230000008439 repair process Effects 0.000 abstract description 2
- QNRATNLHPGXHMA-XZHTYLCXSA-N (r)-(6-ethoxyquinolin-4-yl)-[(2s,4s,5r)-5-ethyl-1-azabicyclo[2.2.2]octan-2-yl]methanol;hydrochloride Chemical compound Cl.C([C@H]([C@H](C1)CC)C2)CN1[C@@H]2[C@H](O)C1=CC=NC2=CC=C(OCC)C=C21 QNRATNLHPGXHMA-XZHTYLCXSA-N 0.000 abstract 1
- 230000008859 change Effects 0.000 description 4
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
- B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
- B61F5/02—Arrangements permitting limited transverse relative movements between vehicle underframe or bolster and bogie; Connections between underframes and bogies
- B61F5/04—Bolster supports or mountings
- B61F5/12—Bolster supports or mountings incorporating dampers
- B61F5/122—Bolster supports or mountings incorporating dampers with friction surfaces
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
- Springs (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
The invention discloses an oblique wedge vibration damper for a railway freight car bogie. The vibration damper comprises an oblique wedge part and an anti-vibrating spring component arranged below the oblique wedge part; the oblique wedge part consists of an oblique wedge body, a main friction plate and an auxiliary friction block; the main friction plate is arranged on the side vertical surface of the oblique wedge body; the auxiliary friction block is arranged on the inclined plane of the oblique wedge body; the structural design parameter of the oblique wedge part meets the following mathematic relation: alpha is equal to 16 to 30 degrees, and tg alpha is more than mu and less than mu+mu1; alpha is an included angle between the rubbing surface of the auxiliary friction block and a vertical plane; mu is the friction coefficient of the main friction plate; mu1 is the friction coefficient of the auxiliary friction block. The vibration damper has the advantages of simple and reliable structure, convenient maintenance and repair, low using cost and capability of resisting rhombic deformation between a swing bolster part and a side frame part. Therefore, the bogie has enough diamond resistant rigidity, excellent dynamic performance and curve passage capacity, is suitable for a novel railway truck with a speed of 120 kilometers per hour and meets the requirement on large scale speed increase of the railway truck.
Description
Technical field
The present invention relates to railway freight car bogie, refer to a kind of oblique wedge vibration damper of railway freight car bogie 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 a bolster is formed this three-major-items formula structure, 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 is used to bear the load that bolster is formed, and it mainly is made of bearing spring assembly in the middle of being positioned at and the friction-type oblique wedge vibration damper that is positioned at both sides.Existing friction-type oblique wedge vibration damper comprises that wedge forms and be installed in the damping spring component that wedge is formed the below, and wedge is formed and gone up the bolster Eight characters face wipe contact that side frame column face that vertical main friction face and the secondary friction face of bevelled form with bogie side frame respectively and bolster are formed.
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 composition of the wedge in its friction-type oblique wedge vibration damper has bigger design drift angle (angle between its secondary friction face and the vertical guide), normally in 35 °～70 ° scope, diamonding ability between opposing bolster composition and bogie side frame are formed is relatively poor, and promptly the diamond resistant rigidity of bogie truck is very limited.When the bolster composition travels longitudinally with respect to the bogie side frame composition, the bolster Eight characters will be formed the vertical component sum of the friction force of major and minor friction face greater than wedge in the face of the vertical component of the application force that wedge is formed, this moment, the wedge composition 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 curve negotiation ability of vehicle is relatively poor, and critical speed 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 roller bearing adapter stabilizer bar 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, how effectively to improve the anti-diamonding ability of traditional railway freight car bogie, the riding quality that improves railway vehicle is had important practical significance.
Summary of the invention
Purpose of the present invention be exactly to provide that a kind of simple and reliable for structure, maintenance and repair is convenient, use cost is cheap, be highly resistant to bolster form form with bogie side frame between the oblique wedge vibration damper of railway freight car bogie of generation diamonding, to satisfy the needs that rail freight significantly raises speed.
For achieving the above object, the oblique wedge vibration damper of the designed railway freight car bogie of the present invention comprises the wedge composition and is installed in the damping spring component that described wedge is formed the below.Described wedge is made up of wedge body, the secondary friction shoe that is installed in the main friction plate of described wedge side facade and is installed in described wedge body dip plane and is constituted.The parameter of structure design that described wedge is formed satisfies following mathematical relation: α=16～30 ° and μ＜tg α＜μ+μ
1Wherein, α is the friction face of described secondary friction shoe and the angle between the vertical guide, and μ is the friction coefficient of described main friction plate, μ
1Friction coefficient for described secondary friction shoe.
The maxim of α was defined as 30 ° during the present invention formed described wedge, 35～70 ° big drift angle design in forming much smaller than 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 main friction plate that the vertical component of the application force that the bolster Eight characters is formed in the face of wedge is formed less than wedge all the time and the vertical upwards component sum of secondary friction shoe friction force, thereby guarantee that the wedge composition 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 anti-diamonding ability between forming.Certainly,, can make wedge form 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 of forming main friction plate near wedge.So the minimum value of α was defined as 16 ° during the present invention formed described wedge simultaneously, and limit μ＜tg α, can guarantee that like this wedge forms that form in the process that moves up and down also at bolster can free motion (not locked), thereby make whole bogie truck have good dynamic performance and curve negotiation ability.
Preferably, the design width L=200～260mm of described wedge composition.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 both can increase the arm of force length that wedge is formed diamonding moment between opposing bolster and the bogie side frame, can increase main friction plate and side frame column friction plate that wedge is formed again, the area of contact of secondary friction shoe and bolster Eight characters face, thus can improve further that bolster is formed and the bogie side frame composition between diamond resistant rigidity.
More preferably, the mechanical property of described damping spring component satisfies following mathematical relation: K
1* ctg α=K * C/2 μ; Wherein, K
1Rigidity for described damping spring component, K is the global stiffness (can be determined by designing requirement) of the central spring suspension of railway freight car bogie, 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 plate.Stiffness K because of described damping spring component
1The ctg α that forms with wedge is inversely proportional to, 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.
Best, be the convex-concave sphere structure that is connected between the dip plane of described secondary friction shoe and described wedge body.So both can guarantee that described secondary friction shoe contacted well with bolster Eight characters face, can guarantee that again described main friction plate contacts well with the side frame column face, thereby significantly increase the reliability of anti-diamonding between bolster composition and the bogie side frame composition, significantly reduce simultaneously the abrasion of bolster Eight characters face, reduce the cost of overhaul.
The invention has the advantages that: the wedge of designed oblique wedge vibration damper is formed both can guarantee energy free motion when the bolster composition moves up and down, can guarantee when the bolster composition vertically moves locked again, can effectively resist like this between bolster composition and the bogie side frame composition diamonding takes place, make bogie truck under the condition that does not have bogie side frame cross-braced device or spring plank, still have enough big diamond resistant rigidity and good dynamic performance.And wedge composition width is formed more than 1.3 times and the supplementary features such as convex-concave sphere fit structure of secondary friction shoe and wedge body greater than tradition change friction wedge, both increase wedge and formed the arm of force length of resisting bolster composition and bogie side frame composition water chestnut variable force square, the good contact of its major and minor friction face and stablizing of friction coefficient have been guaranteed again, the diamond resistant rigidity of bogie truck and good dynamic performance have been guaranteed from another point of view, 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 oblique wedge vibration damper is simple in structure, with low cost, reliable operation, easy to maintenance, 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 oblique wedge vibration damper of railway freight car bogie;
Fig. 2 is the main sectional structure scheme drawing of oblique wedge vibration damper shown in Figure 1;
Fig. 3 is the bolster composition of oblique wedge vibration damper shown in Figure 1 and bogie truck and the matching relationship scheme drawing between the bogie side frame composition;
Fig. 4 is the stress balance scheme drawing of oblique wedge vibration damper shown in Figure 3 when bolster is formed longitudinal movement;
Fig. 5 is the stress balance scheme drawing of oblique wedge vibration damper shown in Figure 3 when the bolster composition moves downward.
The specific embodiment
Be described in further detail below in conjunction with the oblique wedge vibration damper of the drawings and specific embodiments railway freight car bogie of the present invention:
As depicted in figs. 1 and 2, the oblique wedge vibration damper of this railway freight car bogie mainly forms 1 and be installed in wedge and form the damping spring component 2 of 1 below and constitute by wedge.Wedge is formed 1 and is made of wedge body 1b, the secondary friction shoe 1c that is arranged on the main friction plate 1a of wedge body 1b side elevation and is arranged on wedge body 1b dip plane again.Above-mentioned wedge is formed 1 parameter of structure design and is satisfied following mathematical relation: L=200～260mm, α=16～30 ° and μ＜tg α＜μ+μ
1Wherein, L is that wedge is formed 1 width, and α is the friction face of secondary friction shoe 1c and the angle between the vertical guide, and μ is the friction coefficient of main friction plate 1a, μ
1Friction coefficient for secondary friction shoe 1c.According to the designing requirement of α value, can select the main friction plate 1a and the secondary friction shoe 1c of suitable material or structure, make μ value and μ
1Value also reaches designing requirement.
As shown in Figure 3, oblique wedge vibration damper of the present invention is installed between the bogie side frame composition 3 and bolster composition 4 of bogie truck as the part of the central spring suspension of railway freight car bogie.Wherein: the lower end of damping spring component 2 is installed on the central square frame spring cushion cap of bogie side frame composition 3, wedge form 1 main friction plate 1a and bogie side frame form 3 side frame column friction plate 3a applying and contact, two secondary friction shoe 1c of wedge composition 1 fit with the bolster Eight characters face 4a of bolster composition 4 and contact, and play the friction damping effect when vehicle operating.
Fig. 4 has indicated bolster and has formed 4 and form 3 when travelling longitudinally with respect to bogie side frame, and bolster Eight characters face 4a forms the friction force F between the secondary friction shoe 1c of 1 application force N, bolster Eight characters face 4a and wedge composition 1 to wedge
f, and side frame column friction plate 3a and wedge form friction force F between 1 the main friction plate 1a
zAs shown in Figure 4, wedge is formed the vertical component N of 1 suffered application force N
y=N * sin α, wedge form vertical component N of 1 suffered application force N
z=N * cos α.And wedge is formed 1 friction force that made progress by its main friction plate 1a and secondary friction shoe 1c and is stoped, and main friction plate 1a goes up the friction force F that produces
z=N
z* μ=N * cos α * μ, secondary friction shoe 1c goes up the friction force F that produces
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, it is 1 locked and can not move downward by the friction force of its main friction plate 1a and secondary friction shoe 1c that wedge is formed, bolster form 4 and bogie side frame have enough big diamond resistant rigidity between forming 3.
Fig. 5 has indicated bolster and has formed 4 and form 3 when moving downward with respect to bogie side frame, and bolster Eight characters face 4a forms the friction force F between the secondary friction shoe 1c of 1 application force N, bolster Eight characters face 4a and wedge composition 1 to wedge
f, and side frame column friction plate 3a and wedge form friction force F between 1 the main friction plate 1a
zAs shown in Figure 5, wedge is formed the vertical component N of 1 suffered application force N
y=N * sin α, wedge form vertical component N of 1 suffered application force N
z=N * cos α.But wedge is formed 1 and is subjected to its main friction plate 1a friction force F that makes progress
zPrevention, and the friction force F on its secondary friction shoe 1c
fBe downward, main friction plate 1a goes up the friction force F that produces
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, wedge forms 1 can be not locked by the friction force of its main friction plate 1a, and energy free motion when bolster composition 4 moves up and down can guarantee the bogie truck function that normal attenuation vibrates in vehicle operating.
By Fig. 5 also as can be known, wedge is formed the friction force F that 1 damping force mainly is its main friction plate 1a generation
z, and friction force F
zAlso the bearing capacity P with damping spring component 2 is relevant, F
z=P * ctg α * μ, P=K
1* y, wherein: K
1Be the rigidity of damping spring component 2, y is the amount of deflection of damping spring component 2.Can get F thus
z=K
1* y * ctg α * μ.For keeping wedge to form the damping force of 1 appropriateness, the mechanical property of designed damping spring component 2 should satisfy following mathematical relation: K
1* ctg α=K * C/2 μ; Wherein, K is the global stiffness of the central spring suspension of railway freight car bogie, 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 damping spring component 2
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 adopting oblique wedge vibration damper of the present invention on the railway freight car bogie, under the situation that does not install bogie side frame cross-braced device or spring plank additional, bogie truck has 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 (9)
1. the oblique wedge vibration damper of a railway freight car bogie, comprise wedge composition (1) and be installed in the damping spring component (2) that described wedge is formed (1) below, described wedge is formed (1) and is made of wedge body (1b), the secondary friction shoe (1c) that is installed in the main friction plate (1a) of described wedge body (1b) side elevation and is installed in described wedge body (1b) dip plane, it is characterized in that: the parameter of structure design that described wedge is formed (1) satisfies following mathematical relation: α=16～30 ° and μ＜tg α＜μ+μ
1Wherein, α is the friction face of described secondary friction shoe (1c) and the angle between the vertical guide, and μ is the friction coefficient of described main friction plate (1a), μ
1Friction coefficient for described secondary friction shoe (1c); The mechanical property of described damping spring component (2) satisfies following mathematical relation: K
1* ctg α=K * C/2 μ; Wherein, K
1Be the rigidity of described damping spring component (2), K is the global stiffness of the central spring suspension of railway freight car bogie, and C is the relative friction coefficient of railway freight car bogie, and the span of C is 0.05～0.15.
2. according to the oblique wedge vibration damper of the described railway freight car bogie of claim 1, it is characterized in that: described wedge is formed the width L=200～260mm of (1).
3. according to the oblique wedge vibration damper of claim 1 or 2 described railway freight car bogies, it is characterized in that: be the convex-concave sphere structure that is connected between the dip plane of described secondary friction shoe (1c) and described wedge body (1b).
4. according to the oblique wedge vibration damper of claim 1 or 2 described railway freight car bogies, it is characterized in that: the quantity of described secondary friction shoe (1c) is two, is arranged symmetrically on the dip plane of described wedge body (1b).
5. according to the oblique wedge vibration damper of the described railway freight car bogie of claim 3, it is characterized in that: the quantity of described secondary friction shoe (1c) is two, is arranged symmetrically on the dip plane of described wedge body (1b).
6. according to the oblique wedge vibration damper of claim 1 or 2 described railway freight car bogies, it is characterized in that: described wedge body (1b) adopts steel or ferrous material to make, described main friction plate (1a) adopts High molecular material to make, and described secondary friction shoe (1c) adopts modified nylon materials to make.
7. according to the oblique wedge vibration damper of the described railway freight car bogie of claim 3, it is characterized in that: described wedge body (1b) adopts steel or ferrous material to make, described main friction plate (1a) adopts High molecular material to make, and described secondary friction shoe (1c) adopts modified nylon materials to make.
8. according to the oblique wedge vibration damper of the described railway freight car bogie of claim 4, it is characterized in that: described wedge body (1b) adopts steel or ferrous material to make, described main friction plate (1a) adopts High molecular material to make, and described secondary friction shoe (1c) adopts modified nylon materials to make.
9. according to the oblique wedge vibration damper of the described railway freight car bogie of claim 5, it is characterized in that: described wedge body (1b) adopts steel or ferrous material to make, described main friction plate (1a) adopts High molecular material to make, and described secondary friction shoe (1c) adopts modified nylon materials to make.
Priority Applications (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010101622371A CN101830234B (en) | 2010-04-27 | 2010-04-27 | Oblique wedge vibration damper for railway freight car bogie |
| AU2010352461A AU2010352461B2 (en) | 2010-04-27 | 2010-12-09 | Inclined wedge vibration reduction device for railway freight car bogie |
| PCT/CN2010/079610 WO2011134264A1 (en) | 2010-04-27 | 2010-12-09 | Inclined wedge vibration reduction device for railway freight car bogie |
| BR112012027540-2A BR112012027540B1 (en) | 2010-04-27 | 2010-12-09 | DEVICE OF INCLINED DAMPING PLAN FOR RAILWAY LOAD WAGON |
| US13/661,030 US20130056919A1 (en) | 2010-04-27 | 2012-10-25 | Damping device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010101622371A CN101830234B (en) | 2010-04-27 | 2010-04-27 | Oblique wedge vibration damper for railway freight car bogie |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101830234A CN101830234A (en) | 2010-09-15 |
| CN101830234B true CN101830234B (en) | 2011-11-16 |
Family
ID=42714492
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010101622371A Active CN101830234B (en) | 2010-04-27 | 2010-04-27 | Oblique wedge vibration damper for railway freight car bogie |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20130056919A1 (en) |
| CN (1) | CN101830234B (en) |
| AU (1) | AU2010352461B2 (en) |
| BR (1) | BR112012027540B1 (en) |
| WO (1) | WO2011134264A1 (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101830234B (en) * | 2010-04-27 | 2011-11-16 | 南车长江车辆有限公司 | Oblique wedge vibration damper for railway freight car bogie |
| CN102556098B (en) * | 2012-01-13 | 2014-12-03 | 南车长江车辆有限公司 | Variable friction control type oscillating damper of rail wagon |
| BR112015021066A2 (en) * | 2013-03-01 | 2017-07-18 | Nat Steel Car Ltd | side frame for a rail car trick, combination, apparatus comprising side frame, molded part of side frame for a rail car trick, and, rail car trick |
| US9446774B2 (en) * | 2014-09-02 | 2016-09-20 | Amsted Rail Company, Inc. | Railway car truck with friction damping |
| US20180257677A1 (en) * | 2017-03-08 | 2018-09-13 | Amsted Rail Company, Inc. | Railway car truck friction shoe spring group |
| CN112208567A (en) * | 2019-07-12 | 2021-01-12 | 包头北方创业有限责任公司 | Wedge type combined shock absorber and railway wagon bogie |
| WO2021077198A1 (en) * | 2019-10-22 | 2021-04-29 | National Steel Car Limited | Railroad car truck damper wedge fittings |
| CN113581238B (en) * | 2021-07-29 | 2022-12-20 | 中车齐齐哈尔车辆有限公司 | Vibration damping structure of vehicle, bogie and vehicle |
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2010
- 2010-04-27 CN CN2010101622371A patent/CN101830234B/en active Active
- 2010-12-09 BR BR112012027540-2A patent/BR112012027540B1/en active IP Right Grant
- 2010-12-09 WO PCT/CN2010/079610 patent/WO2011134264A1/en active Application Filing
- 2010-12-09 AU AU2010352461A patent/AU2010352461B2/en active Active
-
2012
- 2012-10-25 US US13/661,030 patent/US20130056919A1/en not_active Abandoned
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU1530513A1 (en) * | 1988-03-01 | 1989-12-23 | Ташкентский институт инженеров железнодорожного транспорта | Friction damper of vibrations of rail vehicle bogie |
| EP1090826A1 (en) * | 1999-10-07 | 2001-04-11 | Naco Incorporated | Friction wedge for a railroad car truck having a replaceable wear member |
| CN1845843A (en) * | 2003-07-08 | 2006-10-11 | 全国钢车有限公司 | Rail road car truck and fittings therefor |
| CN1911718A (en) * | 2005-08-12 | 2007-02-14 | Asf-基斯通公司 | Non-metallic insert for rail car bolster wedge |
| CN101397017A (en) * | 2008-09-08 | 2009-04-01 | 齐齐哈尔轨道交通装备有限责任公司 | Combination type slant wedge |
| CN201646752U (en) * | 2010-04-27 | 2010-11-24 | 南车长江车辆有限公司 | Tapered-wedge vibration damper for railway freight car bogie |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2011134264A1 (en) | 2011-11-03 |
| BR112012027540A2 (en) | 2016-08-02 |
| US20130056919A1 (en) | 2013-03-07 |
| AU2010352461B2 (en) | 2014-03-06 |
| BR112012027540B1 (en) | 2020-03-24 |
| CN101830234A (en) | 2010-09-15 |
| AU2010352461A1 (en) | 2012-11-29 |
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