CN107253483B - Railway wagon bogie - Google Patents
Railway wagon bogie Download PDFInfo
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- CN107253483B CN107253483B CN201710606885.3A CN201710606885A CN107253483B CN 107253483 B CN107253483 B CN 107253483B CN 201710606885 A CN201710606885 A CN 201710606885A CN 107253483 B CN107253483 B CN 107253483B
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- damping spring
- wedge
- friction
- friction damping
- swing bolster
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- 238000013016 damping Methods 0.000 claims abstract description 119
- 229910000831 Steel Inorganic materials 0.000 claims description 3
- 239000010959 steel Substances 0.000 claims description 3
- 238000010276 construction Methods 0.000 claims 1
- 229910003460 diamond Inorganic materials 0.000 abstract description 4
- 239000010432 diamond Substances 0.000 abstract description 4
- 230000007547 defect Effects 0.000 abstract description 3
- 239000000463 material Substances 0.000 description 7
- 239000006096 absorbing agent Substances 0.000 description 5
- 230000035939 shock Effects 0.000 description 5
- 230000009471 action Effects 0.000 description 4
- 229910001208 Crucible steel Inorganic materials 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 229910001141 Ductile iron Inorganic materials 0.000 description 1
- 241001669679 Eleotris Species 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 229910052755 nonmetal Inorganic materials 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
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
- B61F5/06—Bolster supports or mountings incorporating metal springs
-
- 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
- B61F5/50—Other details
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention discloses a railway wagon bogie, which comprises a side frame, a swing bolster and a friction damper, wherein the friction damper comprises a wedge, a normal friction damping spring, a variable friction damping spring and a push rod, a through hole is formed in a bottom plate at the lower part of a wedge groove of the swing bolster, the upper part of the push rod is positioned in the normal friction damping spring in the wedge, the lower part of the push rod is in contact with the variable friction damping spring, the wedge, the normal friction damping spring, the push rod and the through hole are deviated by a distance relative to the variable friction damping spring in a direction away from the center of the swing bolster, and the axes of the normal friction damping spring, the push rod and the through hole are not coincident with the axis of the variable friction damping spring. The bogie has ideal relative friction coefficient under the empty and heavy states, and has larger diamond-resistant rigidity and better vertical and transverse dynamics performance; meanwhile, the defect of the existing bogie is overcome, and the structural strength of the swing bolster can be obviously improved, so that the usability of the bogie is ensured.
Description
Technical Field
The invention relates to the technical field of railway vehicles, in particular to a bogie of a core member of a railway wagon.
Background
Railway freight cars generally consist of car bodies, bogies, brake devices, car coupler buffer devices and the like. Among them, the bogie functions to support the vehicle body, guide the vehicle to travel along the track, and receive various loads from the vehicle body and the course. The most common bogie on a railway wagon is a two-axle cast steel three-piece bogie, which consists of a swing bolster, two side frames, two wheel pairs, a spring vibration damper, a brake device and the like.
The most commonly used vibration damper on the truck bogie is a friction type vibration damper, which consists of parts such as a wedge, a damping spring and the like, and the vibration damper is arranged in a space surrounded by a side frame and a swing bolster. The friction type vibration damper converts the vertical supporting force of a spring into the horizontal lateral pressure of the wedge to a side frame column through the angle action of the wedge, a wearing plate is arranged at the opposite position of the side frame column, friction exists between the wedge and the wearing plate, and a swing bolster vibrates up and down along with the up and down vibration of a vehicle body, so that the wedge is driven to move up and down and the wedge and the wearing plate are rubbed with each other to generate friction force, and the friction force is the vibration damping force.
The friction damper can be divided into a constant friction damper and a variable friction damper, wherein the damping force of the constant friction damper is constant and cannot change along with the change of the bearing capacity, so that the relative friction coefficients of the constant friction damper cannot be in an ideal value range under the empty and heavy vehicle states, and the two states of the empty and heavy vehicle cannot be considered, and the vertical dynamics performance of the vehicle is poor.
The variable friction damper comprises a wedge, a constant friction damping spring, a variable friction damping spring, a top rod and the like, wherein a hole is formed in a bottom plate at the lower part of a wedge groove of the swing bolster, the upper part of the top rod is positioned in the constant friction damping spring in the wedge, the lower part of the top rod passes through the hole of the wedge groove of the swing bolster to be contacted with the variable friction damping spring, the constant friction damping spring only provides damping force in an empty state, the inner top part of the wedge is contacted with the upper end of the top rod in a heavy state, the variable friction damping spring can be compressed downwards, the damping force is provided by the constant friction damping spring and the variable friction damping spring together, the relative friction coefficients in an ideal value range can be achieved in both empty and heavy states of a vehicle, and the vertical dynamics performance of the vehicle is better.
However, the variable friction damper still has the disadvantage that, in particular, the constant friction damping spring and the ejector rod of the variable friction damper must be aligned with the axis of the variable friction damping inner spring, so that the positions of the constant friction damping spring and the wedge are required to be close to the center line of the swing bolster, and further, the size of the structural part between the two wedge grooves of the swing bolster is reduced, so that the strength of the swing bolster is reduced, and the service performance of the bogie is affected.
Therefore, how to further improve the strength of the wedge groove part of the swing bolster, thereby improving the service performance of the bogie, is a technical problem which needs to be solved by the person skilled in the art.
Disclosure of Invention
The invention aims to provide a railway wagon bogie. The bogie has ideal relative friction coefficient under the empty and heavy states, and has larger diamond-resistant rigidity and better vertical and transverse dynamics performance; meanwhile, the defect of the existing double-acting shock absorber bogie is overcome, and the structural strength of the swing bolster can be obviously improved, so that the usability of the bogie is ensured.
In order to achieve the above purpose, the railway wagon bogie comprises a side frame, a swing bolster and a friction damper arranged between the side frame and the swing bolster, wherein the friction damper comprises a wedge, a normal friction damping spring, a variable friction damping spring and a push rod, a through hole is formed in a bottom plate at the lower part of a wedge groove of the swing bolster, the push rod penetrates through the upper part of the through hole and is positioned in the normal friction damping spring in the wedge, the lower part of the push rod is in contact with the variable friction damping spring, the wedge, the normal friction damping spring, the push rod and the through hole are deviated by a distance relative to the variable friction damping spring in a direction away from the center of the swing bolster, and the axes of the normal friction damping spring, the push rod and the through hole are not coincident with the axis of the variable friction damping spring.
Preferably, a support is arranged between the lower end of the ejector rod and the upper end of the variable friction damping spring, the central line of the support coincides with the axis of the variable friction damping spring, and the lower end of the ejector rod is supported at the eccentric position of the support from above.
Preferably, the bottom surface of the ejector rod for supporting on the support and the top surface of the support for supporting the ejector rod are both plane surfaces.
Preferably, the side frame is provided with a circular sinking nest on a bearing platform thereof, and the lower end of the friction-changing vibration damping spring is installed in the sinking nest.
Preferably, the distance between the bottom of the sinking nest and the bottom surface of the bearing platform is 20% -50% of the height of the bearing platform, and the distance between one side of the sinking nest and the side wall of the bearing platform is 20% -40% of the height of the bearing platform.
Preferably, the inner top surface of the wedge is provided with a downward inverted conical convex navel, and the root diameter of the convex navel is smaller than the inner diameter of the constant friction damping spring.
Preferably, the wedge is of a combined structure and comprises a wedge body and a main friction plate arranged on the vertical face of the wedge body.
Preferably, the upper end of the ejector rod is provided with an extension section with the diameter smaller than the outer diameter of the ejector rod, the extension section upwards passes through the top surface of the wedge from the hole on the top surface of the wedge, and an annular groove or a transverse hole is arranged at the exposed part.
Preferably, the ejector rod is a steel pipe with a hollow structure.
Preferably, the top surface of the ejector rod is a spherical surface.
In order to prevent the middle section width of the swing bolster, namely the dimension B between wedge grooves, from being too small to influence the strength of the swing bolster, the axial lines of the normal friction damping springs and the ejector rods are designed to be misaligned with the variable friction damping springs below the normal friction damping springs, namely the axial lines of the normal friction damping springs, the ejector rods and the through holes are misaligned with the axial lines of the variable friction damping springs below the normal friction damping springs and the through holes by a distance A, namely the wedge, the normal friction damping springs, the ejector rods and the through holes are deviated together relative to the variable friction damping springs by a distance in a direction away from the center of the swing bolster. Therefore, the dimension B of the structure part in the middle of the two wedge grooves of the swing bolster can be widened to a distance A to two sides respectively, and the widened dimension is changed into B+2A, so that the bogie has ideal relative friction coefficients in the empty and heavy states, and has larger diamond resistance and better vertical and transverse dynamics performance; meanwhile, the structural strength of the swing bolster can be obviously improved, so that the usability of the bogie is ensured.
Drawings
FIG. 1 is a schematic view of an assembled side frame, bolster and friction damper of a railway truck steer carriage according to the present invention;
FIG. 2 is a schematic diagram of the motion of the jack shown in FIG. 1 as it moves downward to compress the friction-changing damping spring;
FIG. 3 is a schematic view of the structure of the wedge with an inverted cone-shaped convex navel on the inner top surface;
FIG. 4 is a schematic view of the structure of one side of the sinking nest and the side wall of the side frame platform.
In the figure:
1. side frame 2, swing bolster 3, inclined wedge 4, normal friction damping spring 5, variable friction damping spring 6, ejector rod 7, support 8, sinking nest 9, convex navel 10 and wearing plate
Detailed Description
In order to better understand the aspects of the present invention, the present invention will be described in further detail with reference to the accompanying drawings and detailed description.
In the present invention, the terms "upper, lower, inner, outer" and the like are established based on the positional relationship shown in the drawings, and the corresponding positional relationship may be changed depending on the drawings, and therefore, the terms are not to be construed as an absolute limitation of the scope of protection.
Referring to fig. 1, fig. 1 is an assembled schematic view of a side frame, a bolster and a friction damper of a railway truck according to the present invention.
As shown in the figure, the railway wagon bogie provided by the embodiment mainly comprises a side frame 1, a swing bolster 2, a friction damper and the like arranged between the side frame 1 and the swing bolster 2, wherein the friction damper comprises a wedge 3, a normal friction damping spring 4, a variable friction damping spring 5 (comprising an inner spring and an outer spring) and a push rod 6, the swing bolster 2 is provided with a through hole on a bottom plate at the lower part of a wedge groove, the push rod 6 penetrates through the upper part of the through hole and is positioned in the normal friction damping spring 5 in the wedge 3, the lower part of the push rod 6 is in contact with the variable friction damping spring 5, and the swing bolster springs (comprising the variable friction damping spring 5) arranged on a bearing platform at the bottom of the side frame 1 are symmetrically or obliquely symmetrically arranged relative to the center of the bearing platform of the side frame so as to ensure the stress balance of the side frame 1.
As can be seen from the figure, if the positions of the constant friction damping spring 5 and the wedge 3 are too close to the central line of the swing bolster 2, the size B of the structural part between the two wedge grooves of the swing bolster 2 is smaller, so that the strength of the swing bolster 2 is reduced, and the usability of the bogie is affected.
In order to prevent the middle section width of the swing bolster 2, namely the dimension B, from being too small to affect the strength of the swing bolster, the axes of the normal friction damping springs 4 and the ejector rods 6 are designed to be misaligned with the variable friction damping springs 5 below the swing bolster, namely the axes of the normal friction damping springs 4 and the ejector rods 6 are misaligned with the axes of the variable friction damping springs 5 below the swing bolster by a distance A, namely the inclined wedge 3, the normal friction damping springs 4, the ejector rods 6 and the through holes are deviated from the center of the swing bolster by the distance A. Therefore, the size B of the structural part in the middle of the two wedge grooves of the swing bolster 2 can be widened to a distance A to the two sides respectively, the widened size is changed into B+2A, the structural strength of the swing bolster 2 can be obviously improved, and the usability of the bogie is ensured.
A support 7 is arranged between the lower end of the ejector rod 6 and the upper end of the variable friction damping spring 5, the central line of the support 7 coincides with the axis of the variable friction damping spring 5, the lower end of the ejector rod 6 is supported at the eccentric position of the support 7 from above, and the bottom surface of the ejector rod 6 and the top surface of the support 7 are designed to be plane surfaces. Thus, when the variable friction damping spring 5 is deflected by a force of misalignment, a gap (see angle D in fig. 2) appears between the side of the bottom surface of the ejector pin 6 away from the center of the bolster and the top surface of the support 7, so that the point of action of the ejector pin 6 on the force (see force F in fig. 2) of the support 7 moves toward the center side of the bolster, thereby reducing the amount of eccentricity of the force and improving the spring-loaded state.
In order to increase the deflection of the variable friction vibration damping inner and outer springs and ensure that the variable friction vibration damping inner and outer springs have larger free height, a circular sinking nest 8 is designed on a side frame bearing platform to accommodate the variable friction vibration damping springs, the diameter of the sinking nest 8 is larger than the outer diameter of the variable friction vibration damping outer springs, the lower ends of the variable friction vibration damping inner springs and the variable friction vibration damping outer springs below the inclined wedges 3 are simultaneously arranged in the sinking nest 8 during assembly, and the forces of the inner springs and the outer springs at the positions are introduced together to serve as the variable friction vibration damping springs 5, so that the outer diameter of a support 7 is slightly smaller than the outer diameter of the variable friction vibration damping outer springs, and the variable friction vibration damping inner springs and the variable friction vibration damping outer springs are pressed simultaneously.
Alternatively, the diameter of the sinking nest 8 may be larger than the outer diameter of the variable friction vibration damping inner spring and smaller than the inner diameter of the vibration damping outer spring, and only the lower end of the variable friction vibration damping inner spring is installed into the sinking nest during assembly, and since only the force of the inner spring at the position is introduced as the variable friction vibration damping spring 5, the outer diameter of the support 7 should be slightly smaller than the outer diameter of the variable friction vibration damping inner spring, and only the variable friction vibration damping inner spring is pressed.
That is, the variable friction damping spring 5 may be selected to have only a variable friction damping inner spring, and its outer spring is supported between the bolster 2 and the table of the side frame 1, and is used as a bolster damping spring, and is not used as a variable friction damping spring, and the variable friction damping inner spring and the outer spring are simultaneously provided, and the inner spring and the outer spring are simultaneously used as variable friction damping springs.
Specifically, the distance C between the bottom of the sinking nest 8 and the bottom surface of the bearing platform can be 20% -50% of the height of the side frame bearing platform, and the distance E between one side of the sinking nest 8 and the side wall of the side frame bearing platform can be 20% -40% of the height of the side frame bearing platform (see FIG. 4). Therefore, the casting is convenient, the height of the variable friction damping spring is guaranteed to be consistent with or close to that of other pillow springs, the types of the springs are reduced, and the structural complexity of the product is simplified.
Referring to fig. 3, fig. 3 is a schematic structural view of an inverted cone-shaped navel disposed on an inner top surface of the wedge.
As shown in the figure, the material of the wedge 3 may be bainitic ductile iron, namely ADI, if the material is adopted, in order to improve the strength of the wedge 3, a downward inverted conical convex navel 9 may be arranged on the inner top surface of the wedge 3, the convex navel 9 and the wedge 3 are of an integral structure, the root diameter of the convex navel 9 is smaller than the inner diameter of the normal friction damping spring 4, and the convex navel can extend into the normal friction damping spring 4. If the top of the wedge 3 is provided with a process hole for lifting and positioning the ejector rod during assembly, the process hole simultaneously penetrates through the convex navel 9.
Under the heavy vehicle state, the inclined wedge 3 mainly pushes the ejector rod 6 to move downwards through the inner top surface so as to compress the friction-variable vibration damping spring 5, so that the strength of the contact part of the inclined wedge 3 and the ejector rod 6 can be obviously improved by increasing the convex navel 9, and meanwhile, the positioning and guiding effects on the friction-variable vibration damping spring 5 can be realized, and the friction-variable vibration damping spring 5 is ensured to be always in an accurate position without deflection, so that a better vibration damping effect is realized.
The wedge 3 can be of a combined structure and comprises a wedge body and a main friction plate arranged at the vertical face of the wedge body, wherein the wedge body can be made of cast steel materials, and the main friction plate can be made of nonmetal wear-resistant materials or metal wear-resistant materials.
As an improvement, the upper end of the ejector pin 6 may be provided with an extension having a diameter smaller than the outer diameter of the ejector pin, which extends upward through the top surface of the wedge 3 from the hole in the top surface of the wedge, and is provided with an annular groove at the exposed portion so as to be caught by a spring at the time of assembly to prevent the ejector pin from falling down, or a lateral hole is provided at the exposed portion so as to be penetrated through the lateral hole by a positioning pin at the time of assembly to perform the same function.
In addition, the ejector rod 6 can also be a steel pipe with a hollow structure, so that on the premise of ensuring the structural strength of the ejector rod, the material can be saved, the weight of the ejector rod can be reduced, and the assembly is convenient; moreover, the top surface of the ejector rod 6 can also be designed to be spherical, so as to better transmit the vertical acting force downwards.
The working principle of the railway wagon bogie is further described below:
the friction type shock absorber comprises a wedge 3, a constant friction damping spring 4, a variable friction damping spring 5, a push rod 6, a support 7 and the like, and the shock absorber and other parts inherent to the bogie, including a swing bolster 2, a side frame 1 and the like, jointly realize the functions of the shock absorber; the bottom plate of the lower part of the inclined wedge groove of the swing bolster 2 is provided with a through hole, the ejector rod 6 is positioned in the normal friction damping spring 4 in the inclined wedge 3, and the lower part of the ejector rod passes through the through hole on the bottom plate of the inclined wedge groove of the swing bolster and is contacted with the support 7 arranged on the variable friction damping spring 5.
In the empty state, the positional relationship among the wedge 3, the normal friction damper spring 4, the variable friction damper spring 5, the side frame 1, and the bolster 2 is as follows. The constant friction damping spring 4 and the ejector rod 6 are positioned in the inclined wedge 3, wherein the ejector rod 6 passes through a through hole on a bottom plate at the lower part of the inclined wedge groove of the swing bolster, and the constant friction damping spring, the ejector rod 6 and the support seat are arranged in a space formed by the side frame 1 and the inclined wedge groove of the swing bolster together, and the support seat 7 is arranged on the variable friction damping spring 5, and the top of the support seat is contacted with the ejector rod 6 to transmit vertical force. Because of the constant friction vibration reduction, 4 is in a compressed state, the spring can exert an upward force on the wedge 3, and because of the blocking of the inclined surface in the swing bolster inclined wedge groove, the wedge 3 is pressed towards the side frame upright post, and a positive pressure is generated between the wedge 3 and the side frame upright post. When the vertical movement of the car body and the bolster 2 occurs due to the running of the car, a friction force, i.e., a damping force, is generated between the wedge 3 and the wear plate 10 on the side frame column, which is proportional to the positive pressure and the friction coefficient between the wedge 3 and the wear plate 10.
Because the swing bolster 2 is higher in the empty state, the ejector rod 6 and the top surface of the inner cavity of the inclined wedge 3 can not be contacted, and can also be contacted; when the device is not in contact, the ejector rod 6 and the variable friction damping spring 5 are not under pressure, the force of the wedge 3 pressing against the side frame upright column is only generated by the action of the constant friction damping spring 4, and the force is small and is suitable for an empty state; in contact, the ejector rod 6 and the variable friction damping spring 5 are subjected to pressure, and the force of the wedge 3 pressing against the side frame column is generated by the combined action of the constant friction damping spring 4 and the variable friction damping spring 5, and the force is larger than the former but can be set to be suitable for an empty state.
When the vehicle is in a heavy state after being loaded, all sleeper springs are subjected to increased vertical force from the vehicle body and the swing bolster 2, so that the swing bolster 2 moves downwards, the top surface of the inner cavity of the inclined wedge 3 moves downwards and is pressed on the upper end of the ejector rod 6, the force is transmitted to the friction-variable damping spring 5 through the support 7, the generated elastic counter force acts on the support 7 and is transmitted through the ejector rod 6, the elastic counter force and the normal friction damping spring 4 act on the top surface of the inner cavity of the inclined wedge 3 together, the force is increased compared with that in a empty state, the positive pressure of the inclined wedge 3 on the side frame upright post is correspondingly increased, and the damping force is correspondingly increased because the damping force is proportional to the positive pressure, so that the requirements in the heavy state are met.
The above embodiments are merely preferred embodiments of the present invention, and are not limited thereto, and on the basis of these, specific adjustments may be made according to actual needs, thereby obtaining different embodiments. For example, the carrier rod 6 and the support 7 may be made of different kinds of materials for the purpose of light weight, small abrasion, etc. This is not illustrated here, as there are many possible implementations.
The bogie has ideal relative friction coefficients in the empty and heavy states, has larger diamond-resistant rigidity and better vertical and transverse dynamics performance, for example, when the structure is not adopted, the damping of the damping device is usually 20-40% of that of an empty car, 2-5% of that of a heavy car, and the damping of the heavy state is too small compared with an ideal value (the ideal value is usually 7-15%), but after the structure is adopted, the damping of the heavy state can reach 7-15% to realize ideal parameter requirements; moreover, the defect of the existing double-acting shock absorber bogie is overcome, and the structural strength of the swing bolster can be obviously improved, so that the usability of the bogie is ensured.
The railway wagon bogie provided by the invention is described in detail above. The principles and embodiments of the present invention have been described herein with reference to specific examples, the description of which is intended only to facilitate an understanding of the core concepts of the invention. It should be noted that it will be apparent to those skilled in the art that various modifications and adaptations of the invention can be made without departing from the principles of the invention and these modifications and adaptations are intended to be within the scope of the invention as defined in the following claims.
Claims (8)
1. The railway wagon bogie comprises a side frame, a swing bolster and a friction damper arranged between the side frame and the swing bolster, wherein the friction damper comprises a wedge, a normal friction damping spring, a variable friction damping spring and a push rod, a through hole is formed in a bottom plate at the lower part of a wedge groove of the swing bolster, the push rod passes through the upper part of the through hole and is positioned in the normal friction damping spring in the wedge, and the lower part of the push rod is supported above the variable friction damping spring; a support is arranged between the lower end of the ejector rod and the upper end of the variable friction damping spring, the central line of the support coincides with the axis of the variable friction damping spring, and the lower end of the ejector rod is supported at the eccentric position of the support from above; the side frame is provided with a round sinking nest on a bearing platform, and the lower end of the friction-changing vibration damping spring is installed in the sinking nest.
2. A railway wagon bogie according to claim 1, wherein the bottom surface of the carrier bar for supporting on the support and the top surface of the support for supporting the carrier bar are planar.
3. The railway wagon bogie according to claim 1, wherein the distance between the bottom of the sinking nest and the bottom surface of the platform is 20% -50% of the height of the platform, and the distance between one side of the sinking nest and the side wall of the platform is 20% -40% of the height of the platform.
4. The railway wagon bogie according to claim 1, wherein the inner top surface of the cam is provided with a downward inverted conical lug, and the root diameter of the lug is smaller than the inner diameter of the constant friction damping spring.
5. The railway wagon bogie according to claim 1, wherein the cam is of a combined structure comprising a cam body and a main friction plate mounted at a vertical face of the cam body.
6. A railway wagon bogie according to claim 1, wherein the upper end of the ejector pin is provided with an extension of diameter less than the outer diameter of the ejector pin, the extension passing upwardly through the top surface of the wedge from the aperture in the top surface of the wedge and being provided with an annular groove or transverse aperture in the exposed portion.
7. A railway wagon bogie as claimed in any one of claims 1 to 6, wherein the ejector pins are steel pipes of hollow construction.
8. A railway wagon bogie according to any of claims 1 to 6, wherein the top surface of the ejector pins is spherical.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710606885.3A CN107253483B (en) | 2017-07-24 | 2017-07-24 | Railway wagon bogie |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710606885.3A CN107253483B (en) | 2017-07-24 | 2017-07-24 | Railway wagon bogie |
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| Publication Number | Publication Date |
|---|---|
| CN107253483A CN107253483A (en) | 2017-10-17 |
| CN107253483B true CN107253483B (en) | 2023-11-21 |
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| CN201710606885.3A Active CN107253483B (en) | 2017-07-24 | 2017-07-24 | Railway wagon bogie |
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| CN112124348B (en) * | 2020-09-27 | 2022-02-01 | 成都工业学院 | Assembly method of railway wagon control type bogie damping device |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US6701850B2 (en) * | 2002-08-07 | 2004-03-09 | Westinghouse Air Brake Technologies Corporation | Friction wedge liner with backing plate |
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|---|---|---|---|---|
| UA69470C2 (en) * | 2002-02-05 | 2004-09-15 | Фірма "Юнікон Лтд" | Freight bogie with friction shock absorber of permanent friction |
| CN201099257Y (en) * | 2007-11-16 | 2008-08-13 | 中国北车集团沈阳机车车辆有限责任公司 | Meter gauge bogie |
| CN101797926A (en) * | 2010-04-22 | 2010-08-11 | 齐齐哈尔轨道交通装备有限责任公司 | Bogie |
| CN202413823U (en) * | 2012-01-13 | 2012-09-05 | 南车长江车辆有限公司 | Variable friction control type damper for railroad wagon |
| CN203477152U (en) * | 2013-09-27 | 2014-03-12 | 齐齐哈尔轨道交通装备有限责任公司 | Friction shock absorber for bogie of railway freight car and bogie of railway freight car |
| CN105151071A (en) * | 2015-09-10 | 2015-12-16 | 南车二七车辆有限公司 | Dual-mode damping device for wagon |
| CN206984001U (en) * | 2017-07-24 | 2018-02-09 | 中车齐齐哈尔车辆有限公司 | Railway goods train bogie |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107253483A (en) | 2017-10-17 |
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