US20130056919A1 - Damping device - Google Patents
Damping device Download PDFInfo
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- US20130056919A1 US20130056919A1 US13/661,030 US201213661030A US2013056919A1 US 20130056919 A1 US20130056919 A1 US 20130056919A1 US 201213661030 A US201213661030 A US 201213661030A US 2013056919 A1 US2013056919 A1 US 2013056919A1
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- wedge
- assembly
- damping device
- friction board
- friction
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- 238000013016 damping Methods 0.000 title claims abstract description 61
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 claims description 14
- 239000000463 material Substances 0.000 claims description 10
- 239000004677 Nylon Substances 0.000 claims description 8
- 229920001778 nylon Polymers 0.000 claims description 8
- 239000000725 suspension Substances 0.000 claims description 8
- 229910000831 Steel Inorganic materials 0.000 claims description 7
- 229910052742 iron Inorganic materials 0.000 claims description 7
- 239000002861 polymer material Substances 0.000 claims description 7
- 239000010959 steel Substances 0.000 claims description 7
- 229910003460 diamond Inorganic materials 0.000 description 17
- 239000010432 diamond Substances 0.000 description 17
- 238000012423 maintenance Methods 0.000 description 5
- 238000004519 manufacturing process Methods 0.000 description 5
- 238000010586 diagram Methods 0.000 description 3
- 238000000429 assembly Methods 0.000 description 2
- 230000000712 assembly Effects 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 238000009827 uniform distribution Methods 0.000 description 1
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Classifications
-
- 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
Definitions
- the invention relates to a damping device, and more particularly to a damping device for a wedge of a wheel truck of a railroad freight car.
- a typical wheel truck of a railroad freight car includes two side frame assemblies and a bolster assembly. Journal-box guides disposed on two ends of the side frame assembly are fixed on a front wheel pair and a rear wheel pair via roller bearing adapters and bearing assemblies, respectively.
- the bolster assembly has two ends, each of which is mounted in a central square hole of the side frame assembly via a spring suspension device.
- the spring suspension device is used to support the load of the bolster assembly and includes a bearing spring unit in the center and two frictional damping devices for a wedge on both sides.
- the existing frictional damping device includes a wedge assembly and a damping spring assembly underneath the wedge assembly.
- a vertical primary friction surface and an inclined secondary friction surface of the wedge assembly are attached to a column surface of the side frame assembly and an inclined surface of the bolster assembly, respectively.
- the wheel truck of a railroad freight car is advantageous in its simple structure, uniform distribution of the load, low cost in production and maintenance.
- the connection between the bolster assembly and the side frame assembly is loose and the diamond resistant rigidity is low, which cannot resist the violent shaking between the bolster assembly and the side frame assembly.
- the attack angle between the wheel pairs and the rail enlarges, thereby resulting in damages on the wheel and the rail.
- the wedge of the spring suspension device has a relative larger apex angle, that is, the angel between the secondary friction surface and a vertical plane is about 35-70°.
- the diamond resistant rigidity is highly limited.
- a vertical force component of a force from the inclined surface to the wedge is larger than a sum of vertical force components of the friction produced on the primary friction surface of the wedge and the friction produce on the secondary friction surface of the wedge, so that the wedge moves downwards, and the vertical distance between the bolster assembly and the side frame assembly becomes smaller, thereby resulting in relative rotation between the bolster assembly and the side frame assembly, as well as diamond deformation.
- the critical speed of the wheel truck is low, which limits the running speed and running performance of the freight car, and cannot meet the requirement of the speed-raising freight car.
- the current speed-raising trains employs a cross supporting device between two side frame assembly or a spring plank for improving the diamond resistant rigidity of the conventional wheel truck.
- the problem is that, such a cross supporting device or spring plank has a complicated structure, heavy weight, and high production and maintenance costs. Thus, it is very significant to improve the diamond resistant rigidity of the conventional wheel truck and the dynamic performance of the trains.
- a damping device comprising a wedge assembly and a damping spring assembly disposed underneath the wedge assembly.
- the wedge assembly comprises a wedge, a primary friction board disposed on a vertical surface of the wedge, and a secondary friction board disposed on an inclined surface of the wedge.
- the included angle ⁇ of the wedge assembly is no more than 30°, which is much smaller than the conventional vertex angle of 35-70°, and meets the requirement that tg ⁇ + ⁇ 1 .
- the wedge assembly will be self-limited once the bolster assembly moves downwards relative to the side frame assembly, thereby lowering the dynamic performance of the wheel truck. Therefore, the lower bound of the angle ⁇ of the wedge assembly is designed as 16°, and ⁇ tg ⁇ , to make sure that the wedge assembly moves freely during the vertical movement of the bolster assembly, and the wheel truck has a good dynamic performance for crossing curved tracks.
- the wedge having a variable friction herein means that a wedge is disposed on a damping spring which is arranged in a square hole in a center of a side frame, the damping friction exerted on the wedge changes in proportional to the variable vertical load exerted on the bolster assembly.
- width design of the wedge assembly increase the length of the torque arm to resist the diamond deformation between the bolster assembly and the side frame assembly; but also it increases attached area between the primary friction board and the column surface of the side frame assembly, and between the secondary friction board and the inclined surface of the bolster assembly, so that the diamond resistant rigidity between the bolster assembly and the side frame assembly is further improved.
- K 1 represents a rigidity of the damping spring assembly
- K represents a total rigidity of a spring suspension device
- C represents a relative friction coefficient of the wheel truck and ranges from 0.05 to 0.15
- ⁇ represents a friction coefficient of the primary friction board.
- the secondary friction board is in connection with the inclined surface of the wedge via a spherical structure comprising a convex surface and a corresponding concave surface, which ensures good contact between the secondary friction board and the inclined surface of the bolster, as well as good contact between the primary friction board and the column surface.
- a spherical structure comprising a convex surface and a corresponding concave surface
- the wedge assembly of the damping device not only assures a free movement of the wedge assembly when the bolster moves in a vertical direction, but also prevents the wedge assembly from moving when the bolster moves in a horizontal direction.
- the wheel truck has an enough high diamond resistant rigidity and good dynamic performance even without a crossed supporting device or a spring plank.
- the design of the width of the wedge assembly which is 1.3 times longer than that of the conventional also improves the diamond resistant rigidity and the dynamic performance, thereby highly improving the critical speed of the freight car, the capacity of crossing curved tracks, and the running performance.
- the wheel truck has a simple structure, light weight, and low production and maintenance costs, which is applicable to the new railroad freight car having a running speed of 120 km/h, and meets the requirements of the diamond resistant rigidity for the speed-raising trains.
- FIG. 1 is a stereogram of a damping device in accordance with one embodiment of the invention
- FIG. 2 is a cross-sectional view of a damping device of FIG. 1 ;
- FIG. 3 is a diagram of a damping device fitted with a bolster assembly and a side frame assembly in accordance with one embodiment of the invention
- FIG. 4 is a force balance diagram of a damping device as shown in FIG. 3 during a movement of a bolster in horizontal direction;
- FIG. 5 is a force balance diagram of a damping device as shown in FIG. 3 during a movement of a bolster downwards in vertical direction.
- a damping device for a wedge of a wheel truck of a railroad freight car comprises a wedge assembly 1 and a damping spring assembly 2 disposed underneath the wedge assembly 1 .
- the wedge assembly 1 comprises a wedge 1 b comprising a vertical surface and an inclined surface, a primary friction board 1 a is disposed on the vertical surface, and a secondary friction board 1 c is disposed on the inclined surface.
- L represents a width of the wedge assembly 1 ;
- ⁇ represents an included angle between a friction surface of the secondary friction board 1 c and a vertical plane;
- ⁇ represents a friction coefficient of the primary friction board 1 a;
- ⁇ 1 represents a friction coefficient of the secondary friction board 1 c.
- suitable materials of the primary friction board 1 a and the secondary friction board 1 b can be selected and structures thereof can be properly adjusted to make the values of ⁇ and ⁇ 1 meet their requirements.
- the wedge 1 b is made of steel or iron to meet the required intensity and rigidity.
- Two secondary friction boards 1 c are symmetrically disposed on the inclined surface of the wedge 1 b.
- the connection between the secondary friction board 1 c and the inclined surface of the wedge 1 b is achieved by a spherical structure comprising a convex surface and a corresponding concave surface.
- a convex spherical surface of the secondary friction board 1 c is received by a corresponding concave spherical surface of the inclined surface of the wedge 1 b.
- the structural design of the secondary friction board 1 c is advantageous in that: on one hand, the convex spherical surface of the secondary friction board 1 c matches well with the concave spherical surface of the inclined surface of the wedge 1 b, which assures the well contact between the secondary friction board 1 c and the inclined surface of the bolster, even when deviations occur in the apex angle ⁇ of the wedge assembly 1 , the angel and the flatness of the inclined surface of the bolster.
- the wedge assembly 1 and the secondary friction board 1 c can maintain stable, and a large friction is produced to prevent the wedge assembly 1 from moving downwards when diamond deformations occurs between the bolster unit and the side frame assembly, thereby effectively improve the diamond resistant rigidity of the wheel truck;
- the secondary friction board 1 c made of modified nylon materials has a good abrasive resistance and high friction coefficient, not only is the secondary friction board 1 c hard-wearing, but also it alleviates the abrasion on the inclined surface of the bolster, thereby being convenient to fix and replace, and lowering the production cost.
- the primary fiction board 1 a is an integrated friction board made of polymer materials that can be fixed in a slot on the vertical surface of the wedge 1 b via fasteners.
- the convex spherical surface of the secondary friction board 1 c and the matched concave spherical surface of the inclined surface of the wedge 1 b assure the well contact between the primary friction board 1 a and column surface of the side frame when deviation occurs in the apex angle ⁇ of the wedge assembly 1 , the flatness of the inclined surface of the bolster, and the column surface of the side frame. Thus, a stable damping property of the wedge assembly 1 is achieved.
- the damping device is disposed between the side frame assembly 3 and the bolster assembly 4 .
- a lower part of the damping spring assembly 2 is disposed on a spring plank in the square hole of the side frame assembly 3 .
- the primary friction board 1 a of the wedge assembly 1 is attached to the column surface 3 a of the side frame; and the two secondary friction boards 1 c of the wedge assembly 1 are attached to the inclined surface 4 a of the bolster.
- the function of frictional damping is achieved in the running of the freight car.
- the damping force exerted on the wedge assembly 1 is mainly from the friction F z produced on the primary friction board 1 a, and F z is relevant to a bearing capacity P of the damping spring assembly 2 .
- K 1 represents a rigidity of the damping spring assembly 2 ; and
- y represents a flexibility of the damping spring assembly 2 .
- K represents a total rigidity of the spring suspension device
- C represents a relative friction coefficient of the wheel truck and ranges from 0.05 to 0.15.
- K and ⁇ are determined by the designing requirements, when angle ⁇ is decreased, ctg ⁇ decreases correspondingly, and the damping spring assembly 2 should be selected from materials having a lower rigidity K 1 , to make the relative friction coefficient of the wheel truck remains in the range of 0.05-0.15, and to prevent frictions from being too large during movements in vertical and horizontal direction.
- the above damping device of the wheel truck of the freight car has a high diamond resistant rigidity, high critical speed, and superb dynamic performance for crossing curved tracks, even without adopting a crossed supporting device or a spring plank. Thus, it is applicable to the new railroad freight car having a running speed of 120 km/h, and meets the requirement for speed-raising.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
- Springs (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
A damping device, including: a wedge assembly having a wedge including a vertical surface and an inclined surface; a primary friction board disposed on the vertical surface; and a secondary friction board disposed on the inclined surface; and a damping spring assembly disposed underneath the wedge assembly. The wedge assembly has the following structure parameters: α=16-30°, and μ<tgα<μ+μ1, where α represents an included angle between a friction surface of the secondary friction board and a vertical plane, μ represents a friction coefficient of the primary friction board, and μ1 represents a friction coefficient of the secondary friction board.
Description
- This application is a continuation-in-part of International Patent Application No. PCT/CN2010/079610 with an international filing date of Dec. 9, 2010, designating the United States, now pending, and further claims priority benefits to Chinese Patent Application No. 201010162237.1 filed Apr. 27, 2010. The contents of all of the aforementioned applications, including any intervening amendments thereto, are incorporated herein by reference. Inquiries from the public to applicants or assignees concerning this document or the related applications should be directed to: Matthias Scholl P. C., Attn.: Dr. Matthias Scholl Esq., 14781 Memorial Drive, Suite 1319, Houston, Tex. 77079.
- 1. Field of the Invention
- The invention relates to a damping device, and more particularly to a damping device for a wedge of a wheel truck of a railroad freight car.
- 2. Description of the Related Art
- As a critical part of a freight car, a typical wheel truck of a railroad freight car includes two side frame assemblies and a bolster assembly. Journal-box guides disposed on two ends of the side frame assembly are fixed on a front wheel pair and a rear wheel pair via roller bearing adapters and bearing assemblies, respectively. The bolster assembly has two ends, each of which is mounted in a central square hole of the side frame assembly via a spring suspension device. The spring suspension device is used to support the load of the bolster assembly and includes a bearing spring unit in the center and two frictional damping devices for a wedge on both sides.
- The existing frictional damping device includes a wedge assembly and a damping spring assembly underneath the wedge assembly. A vertical primary friction surface and an inclined secondary friction surface of the wedge assembly are attached to a column surface of the side frame assembly and an inclined surface of the bolster assembly, respectively.
- The wheel truck of a railroad freight car, as described above, is advantageous in its simple structure, uniform distribution of the load, low cost in production and maintenance. However, the connection between the bolster assembly and the side frame assembly is loose and the diamond resistant rigidity is low, which cannot resist the violent shaking between the bolster assembly and the side frame assembly. And when the wheel truck runs on a curved rail track, the attack angle between the wheel pairs and the rail enlarges, thereby resulting in damages on the wheel and the rail. Particularly, the wedge of the spring suspension device has a relative larger apex angle, that is, the angel between the secondary friction surface and a vertical plane is about 35-70°. Thus, the diamond resistant rigidity is highly limited. When the bolster assembly moves downwards relative to the side frame assembly, a vertical force component of a force from the inclined surface to the wedge is larger than a sum of vertical force components of the friction produced on the primary friction surface of the wedge and the friction produce on the secondary friction surface of the wedge, so that the wedge moves downwards, and the vertical distance between the bolster assembly and the side frame assembly becomes smaller, thereby resulting in relative rotation between the bolster assembly and the side frame assembly, as well as diamond deformation. In such a condition, the critical speed of the wheel truck is low, which limits the running speed and running performance of the freight car, and cannot meet the requirement of the speed-raising freight car.
- To solve the above problems, the current speed-raising trains employs a cross supporting device between two side frame assembly or a spring plank for improving the diamond resistant rigidity of the conventional wheel truck. The problem is that, such a cross supporting device or spring plank has a complicated structure, heavy weight, and high production and maintenance costs. Thus, it is very significant to improve the diamond resistant rigidity of the conventional wheel truck and the dynamic performance of the trains.
- In view of the above-described problems, it is one objective of the invention to provide a damping device that has a simple structure, low production and maintenance costs, superb dynamic performance for crossing curved tracks, and can meet high requirements of the diamond resistant rigidity for speed-raising trains.
- To achieve the above objective, in accordance with one embodiment of the invention, there is provided a damping device comprising a wedge assembly and a damping spring assembly disposed underneath the wedge assembly. The wedge assembly comprises a wedge, a primary friction board disposed on a vertical surface of the wedge, and a secondary friction board disposed on an inclined surface of the wedge. The wedge assembly is provided with the following structure parameters: α=16-30°, and μ<tgα<μ+μ1. Of them, α represents an included angle between a friction surface of the secondary friction board and a vertical plane; μ represents a friction coefficient of the primary friction board; and μ1 represents a friction coefficient of the secondary friction board.
- The included angle α of the wedge assembly is no more than 30°, which is much smaller than the conventional vertex angle of 35-70°, and meets the requirement that tgα<μ+μ1. Thus, when the bolster assembly moves in a horizontal direction relative to the side frame assembly, a downward vertical force component of a force exerted on the wedge assembly from the inclined surface of the bolster remains smaller than a sum of upward vertical force components of the friction produced on the primary friction board and the friction produced on the secondary friction board, so that the wedge assembly is prevented from moving downwards, relative rotation between the bolster assembly and the side frame assembly cannot occur, and a high diamond resistant rigidity is maintained between the bolster assembly and the side frame assembly. Supposing that, the angle α is too small and approximates to the friction angle of the primary friction board of the wedge assembly, the wedge assembly will be self-limited once the bolster assembly moves downwards relative to the side frame assembly, thereby lowering the dynamic performance of the wheel truck. Therefore, the lower bound of the angle α of the wedge assembly is designed as 16°, and μ<tgα, to make sure that the wedge assembly moves freely during the vertical movement of the bolster assembly, and the wheel truck has a good dynamic performance for crossing curved tracks.
- In a class of this embodiment, a width of the wedge assembly is L=200-600 mm, which is at least 1.3 times longer than the width of the conventional wedge having a variable friction. The wedge having a variable friction herein means that a wedge is disposed on a damping spring which is arranged in a square hole in a center of a side frame, the damping friction exerted on the wedge changes in proportional to the variable vertical load exerted on the bolster assembly. Not only does the width design of the wedge assembly increase the length of the torque arm to resist the diamond deformation between the bolster assembly and the side frame assembly; but also it increases attached area between the primary friction board and the column surface of the side frame assembly, and between the secondary friction board and the inclined surface of the bolster assembly, so that the diamond resistant rigidity between the bolster assembly and the side frame assembly is further improved.
- In a class of this embodiment, a mechanical property of the damping spring meets the following relation formula: K1×ctgα=K×C/2μ, in which, K1 represents a rigidity of the damping spring assembly; K represents a total rigidity of a spring suspension device; C represents a relative friction coefficient of the wheel truck and ranges from 0.05 to 0.15; and μ represents a friction coefficient of the primary friction board. As the rigidity K1 of the damping spring assembly is inversely proportional to ctgα of the wedge assembly, K1 can be adjusted according to the value of angle α, thereby maintaining a suitable friction damping force, and preventing frictions from being too large during movements in vertical and horizontal directions.
- In a class of this embodiment, the secondary friction board is in connection with the inclined surface of the wedge via a spherical structure comprising a convex surface and a corresponding concave surface, which ensures good contact between the secondary friction board and the inclined surface of the bolster, as well as good contact between the primary friction board and the column surface. Thus, the reliability of the diamond resistance of the bolster assembly and the side frame assembly is highly improved, and at the same time, damages on the inclined surface of the bolster and the maintenance cost are largely decreased.
- Advantages of the invention are summarized hereinbelow:
- First of all, the wedge assembly of the damping device not only assures a free movement of the wedge assembly when the bolster moves in a vertical direction, but also prevents the wedge assembly from moving when the bolster moves in a horizontal direction. Thus, the wheel truck has an enough high diamond resistant rigidity and good dynamic performance even without a crossed supporting device or a spring plank. Furthermore, the design of the width of the wedge assembly which is 1.3 times longer than that of the conventional also improves the diamond resistant rigidity and the dynamic performance, thereby highly improving the critical speed of the freight car, the capacity of crossing curved tracks, and the running performance. Finally, the wheel truck has a simple structure, light weight, and low production and maintenance costs, which is applicable to the new railroad freight car having a running speed of 120 km/h, and meets the requirements of the diamond resistant rigidity for the speed-raising trains.
- The invention is described hereinbelow with reference to the accompanying drawings, in which:
-
FIG. 1 is a stereogram of a damping device in accordance with one embodiment of the invention; -
FIG. 2 is a cross-sectional view of a damping device ofFIG. 1 ; -
FIG. 3 is a diagram of a damping device fitted with a bolster assembly and a side frame assembly in accordance with one embodiment of the invention; -
FIG. 4 is a force balance diagram of a damping device as shown inFIG. 3 during a movement of a bolster in horizontal direction; and -
FIG. 5 is a force balance diagram of a damping device as shown inFIG. 3 during a movement of a bolster downwards in vertical direction. - To further illustrate the invention, experiments detailing a damping device are described below. It should be noted that the following examples are intended to describe and not to limit the invention.
- As shown in
FIGS. 1 and 2 , a damping device for a wedge of a wheel truck of a railroad freight car comprises awedge assembly 1 and adamping spring assembly 2 disposed underneath thewedge assembly 1. Thewedge assembly 1 comprises awedge 1 b comprising a vertical surface and an inclined surface, aprimary friction board 1 a is disposed on the vertical surface, and asecondary friction board 1 c is disposed on the inclined surface. Structure parameters of thewedge assembly 1 are as follows: L=200-260 mm, α=16-30°, and μ<tgα<μ+μ1. Of them, L represents a width of thewedge assembly 1; α represents an included angle between a friction surface of thesecondary friction board 1 c and a vertical plane; μ represents a friction coefficient of theprimary friction board 1 a; and μ1 represents a friction coefficient of thesecondary friction board 1 c. According to the designing requirement of the value of the angle α, suitable materials of theprimary friction board 1 a and thesecondary friction board 1 b can be selected and structures thereof can be properly adjusted to make the values of μ and μ1 meet their requirements. - As a supporting base, the
wedge 1 b is made of steel or iron to meet the required intensity and rigidity. Twosecondary friction boards 1 c, being made of modified nylon materials, are symmetrically disposed on the inclined surface of thewedge 1 b. The connection between thesecondary friction board 1 c and the inclined surface of thewedge 1 b is achieved by a spherical structure comprising a convex surface and a corresponding concave surface. As shown inFIG. 2 , a convex spherical surface of thesecondary friction board 1 c is received by a corresponding concave spherical surface of the inclined surface of thewedge 1 b. The structural design of thesecondary friction board 1 c is advantageous in that: on one hand, the convex spherical surface of thesecondary friction board 1 c matches well with the concave spherical surface of the inclined surface of thewedge 1 b, which assures the well contact between thesecondary friction board 1 c and the inclined surface of the bolster, even when deviations occur in the apex angle α of thewedge assembly 1, the angel and the flatness of the inclined surface of the bolster. Thus, thewedge assembly 1 and thesecondary friction board 1 c can maintain stable, and a large friction is produced to prevent thewedge assembly 1 from moving downwards when diamond deformations occurs between the bolster unit and the side frame assembly, thereby effectively improve the diamond resistant rigidity of the wheel truck; on the other hand, thesecondary friction board 1 c made of modified nylon materials has a good abrasive resistance and high friction coefficient, not only is thesecondary friction board 1 c hard-wearing, but also it alleviates the abrasion on the inclined surface of the bolster, thereby being convenient to fix and replace, and lowering the production cost. Theprimary fiction board 1 a is an integrated friction board made of polymer materials that can be fixed in a slot on the vertical surface of thewedge 1 b via fasteners. Also, the convex spherical surface of thesecondary friction board 1 c and the matched concave spherical surface of the inclined surface of thewedge 1 b assure the well contact between theprimary friction board 1 a and column surface of the side frame when deviation occurs in the apex angle α of thewedge assembly 1, the flatness of the inclined surface of the bolster, and the column surface of the side frame. Thus, a stable damping property of thewedge assembly 1 is achieved. - As shown in
FIG. 3 , as a part of a spring suspension device, the damping device is disposed between theside frame assembly 3 and the bolsterassembly 4. A lower part of the dampingspring assembly 2 is disposed on a spring plank in the square hole of theside frame assembly 3. Theprimary friction board 1 a of thewedge assembly 1 is attached to thecolumn surface 3 a of the side frame; and the twosecondary friction boards 1 c of thewedge assembly 1 are attached to theinclined surface 4 a of the bolster. Thus, the function of frictional damping is achieved in the running of the freight car. - As shown in
FIG. 4 , when the bolsterassembly 4 moves in a horizontal direction relative to theside frame assembly 3, theinclined surface 4 a of the bolster assembly exerts a force N on thewedge assembly 1, then, a fiction Ff is produced between theinclined surface 4 a of the bolster assembly and thesecondary friction board 1 c of thewedge assembly 1, and a fiction Fz is produced between thecolumn surface 3 a of the side frame assembly and theprimary friction board 1 a of thewedge assembly 1. It is known fromFIG. 4 that a vertical force component of N is Ny=N×sin α, and a horizontal force component of N is Nz=N×cos α. In addition, two upward frictions are exerted on thewedge assembly 1 on theprimary friction board 1 a and thesecondary friction board 1 c, respectively, in which, the friction produced on theprimary friction board 1 a is Fz=Nz×μ=N×cos α×μ, and the friction produced on thesecondary friction board 1 c is Ff=N×μ1. According to the requirement that Ny<Fz+Ff×cos α, that is, N×sin α<N×cos α×μ+N×μ1×cos α, a relation formula tgα<μ+μ1 is acquired after simplification. Thus, thewedge assembly 1 is limited by the frictions produced on the primary friction board la and thesecondary friction board 1 c from moving downwards, and an enough high diamond resistant rigidity between the bolsterassembly 4 and theside frame assembly 3 is achieved. - As shown in
FIG. 5 , when the bolsterassembly 4 moves downwards in a vertical direction relative to theside frame assembly 3, theinclined surface 4 a of the bolster assembly exerts a force N on thewedge assembly 1, then, a fiction Ff is produced between theinclined surface 4 a of the bolster assembly and thesecondary friction board 1 c of thewedge assembly 1, and a fiction Fz is produced between thecolumn surface 3 a and theprimary friction board 1 a of thewedge assembly 1. It is known fromFIG. 5 that a vertical force component of N is Ny=N×sin α, and a horizontal force component of N is Nz=N×cos α. At this moment, two frictions are exerted on thewedge assembly 1, of them, the friction produced on theprimary friction board 1 a Fz is upward, and the friction produced on thesecondary friction board 1 c Ff is downward, and Fz=Nz×μ=N×cos α×μ. According to the requirement that Fz<Ny, that is, N×cos α×μ<N×sin α, a relation formula μ<tgα is acquired after simplification. In such a way, thewedge assembly 1 isn't limited by the friction produced on theprimary friction board 1 a, and can move freely when the bolsterassembly 4 moves in vertical direction, thereby achieving a normal attenuation vibration of the wheel truck during the running of the freight car. - It is also known from
FIG. 5 that the damping force exerted on thewedge assembly 1 is mainly from the friction Fz produced on theprimary friction board 1 a, and Fz is relevant to a bearing capacity P of the dampingspring assembly 2. The relation formula between Fz and P is Fz=P×ctgα×μ, in which, P=K1×y. K1 represents a rigidity of the dampingspring assembly 2; and y represents a flexibility of the dampingspring assembly 2. Thus, the formula above is converted as Fz=K1×y×ctgα×μ. In order to remain a suitable damping force for thewedge assembly 1, a mechanical property of the dampingspring assembly 2 should meet the following requirement: K1×ctgα=K×C/2μ, in which, K represents a total rigidity of the spring suspension device, and C represents a relative friction coefficient of the wheel truck and ranges from 0.05 to 0.15. As values of K and μ are determined by the designing requirements, when angle α is decreased, ctgα decreases correspondingly, and the dampingspring assembly 2 should be selected from materials having a lower rigidity K1, to make the relative friction coefficient of the wheel truck remains in the range of 0.05-0.15, and to prevent frictions from being too large during movements in vertical and horizontal direction. - The above damping device of the wheel truck of the freight car, has a high diamond resistant rigidity, high critical speed, and superb dynamic performance for crossing curved tracks, even without adopting a crossed supporting device or a spring plank. Thus, it is applicable to the new railroad freight car having a running speed of 120 km/h, and meets the requirement for speed-raising.
- While particular embodiments of the invention have been shown and described, it will be obvious to those skilled in the art that changes and modifications may be made without departing from the invention in its broader aspects, and therefore, the aim in the appended claims is to cover all such changes and modifications as fall within the true spirit and scope of the invention.
Claims (18)
1. A damping device, comprising:
a) a wedge assembly (1) comprising a wedge (1 b) comprising a vertical surface and an inclined surface; a primary friction board (1 a) disposed on the vertical surface; and a secondary friction board (1 c) disposed on the inclined surface; and
b) a damping spring assembly (2) disposed underneath the wedge assembly (1);
wherein
in the wedge assembly (1), α=16-30°, and μ<tgα<μ+μ1, where α represents an included angle between a friction surface of the secondary friction board (1 c) and a vertical plane, μ represents a friction coefficient of the primary friction board (1 a), and μ1 represents a friction coefficient of the secondary friction board (1 c).
2. The damping device of claim 1 , wherein a width of the wedge assembly (1) is L=200-260 mm
3. The damping device of claim 1 , wherein a mechanical property of the damping spring assembly (2) meets the following formula: K1×ctgα=K×C/2μ, in which K1 represents a rigidity of the damping spring assembly (2), K represents a total rigidity of a spring suspension device, and C represents a relative friction coefficient of the wheel truck of a railroad freight car and ranges from 0.05 to 0.15.
4. The damping device of claim 2 , wherein a mechanical property of the damping spring assembly (2) meets the following formula: K1×ctgα=K×C/2μ, in which K1 represents a rigidity of the damping spring assembly (2), K represents a total rigidity of a spring suspension device, and C represents a relative friction coefficient of the wheel truck of a railroad freight car and ranges from 0.05 to 0.15.
5. The damping device of claim 1 , wherein the secondary friction board (1 c) is in connection with the inclined surface of the wedge (1 b) via a spherical structure comprising a convex surface and a corresponding concave surface.
6. The damping device of claim 2 , wherein the secondary friction board (1 c) is in connection with the inclined surface of the wedge (1 b) via a spherical structure comprising a convex surface and a corresponding concave surface.
7. The damping device of claim 3 , wherein the secondary friction board (1 c) is in connection with the inclined surface of the wedge (1 b) via a spherical structure comprising a convex surface and a corresponding concave surface.
8. The damping device of claim 4 , wherein the secondary friction board (1 c) is in connection with the inclined surface of the wedge (1 b) via a spherical structure comprising a convex surface and a corresponding concave surface.
9. The damping device of claim 5 , wherein two secondary friction boards (1 c) are symmetrically disposed on the inclined surface of the wedge (1 b).
10. The damping device of claim 6 , wherein two secondary friction boards (1 c) are symmetrically disposed on the inclined surface of the wedge (1 b).
11. The damping device of claim 7 , wherein two secondary friction boards (1 c) are symmetrically disposed on the inclined surface of the wedge (1 b).
12. The damping device of claim 8 , wherein two secondary friction boards (1 c) are symmetrically disposed on the inclined surface of the wedge (1 b).
13. The damping device of claim 1 , wherein
the wedge (1 b) is made of steel or iron;
the primary friction board (1 a) is made of polymer materials; and
the secondary friction board (1 c) is made of modified nylon materials.
14. The damping device of claim 2 , wherein
the wedge (1 b) is made of steel or iron;
the primary friction board (1 a) is made of polymer materials; and
the secondary friction board (1 c) is made of modified nylon materials.
15. The damping device of claim 3 , wherein
the wedge (1 b) is made of steel or iron;
the primary friction board (1 a) is made of polymer materials; and
the secondary friction board (1 c) is made of modified nylon materials.
16. The damping device of claim 4 , wherein
the wedge (1 b) is made of steel or iron;
the primary friction board (1 a) is made of polymer materials; and
the secondary friction board (1 c) is made of modified nylon materials.
17. The damping device of claim 5 , wherein
the wedge (1 b) is made of steel or iron;
the primary friction board (1 a) is made of polymer materials; and
the secondary friction board (1 c) is made of modified nylon materials.
18. The damping device of claim 6 , wherein
the wedge (1 b) is made of steel or iron;
the primary friction board (1 a) is made of polymer materials; and
the secondary friction board (1 c) is made of modified nylon materials.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201010162237.1 | 2010-04-27 | ||
CN2010101622371A CN101830234B (en) | 2010-04-27 | 2010-04-27 | Oblique wedge vibration damper 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 |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/CN2010/079610 Continuation-In-Part WO2011134264A1 (en) | 2010-04-27 | 2010-12-09 | Inclined wedge vibration reduction device for railway freight car bogie |
Publications (1)
Publication Number | Publication Date |
---|---|
US20130056919A1 true US20130056919A1 (en) | 2013-03-07 |
Family
ID=42714492
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/661,030 Abandoned US20130056919A1 (en) | 2010-04-27 | 2012-10-25 | Damping device |
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) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2993104A1 (en) * | 2014-09-02 | 2016-03-09 | Amsted Rail Company, Inc. | Railway car truck with friction damping |
Families Citing this family (7)
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 |
WO2014131117A1 (en) * | 2013-03-01 | 2014-09-04 | National Steel Car Limited | Truck and sideframe therefor |
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 |
CA3154988A1 (en) * | 2019-10-22 | 2021-04-29 | Jamal Hematian | 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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- 2010-12-09 WO PCT/CN2010/079610 patent/WO2011134264A1/en active Application Filing
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Also Published As
Publication number | Publication date |
---|---|
AU2010352461B2 (en) | 2014-03-06 |
BR112012027540A2 (en) | 2016-08-02 |
BR112012027540B1 (en) | 2020-03-24 |
CN101830234A (en) | 2010-09-15 |
WO2011134264A1 (en) | 2011-11-03 |
CN101830234B (en) | 2011-11-16 |
AU2010352461A1 (en) | 2012-11-29 |
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